WO2015182782A1 - 熱交換器コア - Google Patents
熱交換器コア Download PDFInfo
- Publication number
- WO2015182782A1 WO2015182782A1 PCT/JP2015/065704 JP2015065704W WO2015182782A1 WO 2015182782 A1 WO2015182782 A1 WO 2015182782A1 JP 2015065704 W JP2015065704 W JP 2015065704W WO 2015182782 A1 WO2015182782 A1 WO 2015182782A1
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- WO
- WIPO (PCT)
- Prior art keywords
- core
- louver
- heat exchanger
- qup
- fins
- Prior art date
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Classifications
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
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- 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
- F25B39/00—Evaporators; Condensers
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/08—Fins with openings, e.g. louvers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
Definitions
- the present invention relates to a corrugated fin type heat exchanger in which the direction of a louver formed on the fin is cut and formed only in one direction.
- the corrugated fin type heat exchanger a plurality of flat tubes and corrugated fins are alternately arranged in parallel, and the first fluid flows in the tubes, and the second fluid flows in the outer surface side of the tubes and the corrugated fins.
- the second fluid is mainly a gas such as air.
- the fins currently put to practical use are those in which a diverting louver is disposed in the middle, and louvers in which the directions of inclination are opposite to each other are cut and raised.
- Patent Document 1 a corrugated fin type heat exchanger in which the direction of the louver is limited to only one direction is proposed as Patent Document 1 below.
- This heat exchanger is formed by cutting and raising a one-way louver at an acute angle to the inflow direction of the air flow over the entire length of the core width.
- the present invention according to claim 1 is a large number of corrugated fins (hereinafter, unidirectional fins) in which all the louvers are cut and raised in the same direction in parallel in the width direction of the fins through which the fluid flows.
- the core height H (mm), the louver cutting and raising width W (mm) in the main flow direction of the fluid, and the louver cutting and raising angle ⁇ are set to satisfy the following inequality (1).
- the height H (mm) of the core, the louver cutting width W (mm) in the main flow direction of the fluid, and the louver cutting angle ⁇ satisfy the inequality (1) in claim 1 , Since the height H of the core is H> Qup / (Qup-1) ⁇ ⁇ H, the heat exchange performance is higher than that of the conventional fin. Specifically, the W-H curve of FIG. 6 has the height of the core H in the range exceeding the curve connecting the plotted points at the cut-and-raised angle ⁇ of each louver.
- the louver cut and raised width W refers to the range in which the one-way louver is cut and raised in FIG. The reasons why the effect can be obtained are described below.
- Unidirectional fins have disadvantages and benefits over conventional diverted louver fins,
- the disadvantage is the increase ⁇ H in the ventilation reduction area (heat transfer reduction area), and the merit is the improvement (ratio) Qup of heat transfer in the ventilation part.
- the conditions for the merit to outweigh the disadvantages are: Qup ⁇ (H ⁇ H) / H> 1 and Transforming this inequality, H> Qup / (Qup-1) ⁇ ⁇ H.
- FIG. 1 is an explanatory view comparing air flow by the fins of the present invention with air flow by the fins of the conventional heat exchanger.
- FIG. 2A is an explanatory view showing a flow state of the air flow of the present invention
- FIG. 2B is an explanatory view showing the flow state of the air flow of the conventional heat exchanger.
- FIG. 3 (A) is an explanatory view of a louver of a heat exchanger core according to the present invention
- FIG. 3 (B) is an explanatory view of a louver of a conventional heat exchanger core.
- FIG. 4 is experimental data in which the horizontal axis represents the louver cutting width W, and the vertical axis represents the ratio of the heat transfer coefficient of the main heat transfer area (ventilation portion) in the core of the present invention and the conventional core.
- FIG. 5 is a graph in which the horizontal axis represents the louver cutting width W, and the vertical axis represents the increment ⁇ H of the heat transfer reduction area (draft reduction area) of the core of the present invention with respect to the conventional core.
- FIG. 6 is a graph in which the louver cutting width W is taken on the horizontal axis, and the lower limit of the effective core height of the core of the present invention is shown on the vertical axis with respect to the conventional core.
- FIG. 7 is a graph in which the abscissa represents the louver cutting width W and the ordinate represents the ratio of the amount of heat exchange between the heat exchanger core of the present invention and the conventional heat exchanger core.
- FIG. 1 is a longitudinal sectional view of the heat exchanger core.
- FIG. 2 shows (A) an air flow passage by the louver of the present invention, and (B) shows an air flow passage of the conventional core.
- FIG. 3 (A) (B) is explanatory drawing which shows the cutting-and-raising state of each each louver.
- the heat exchanger core of the present invention forms a core by alternately arranging flat tubes and corrugated fins. And in this example, a pair of tanks 3 are arranged up and down, and the both ends of a flat tube penetrate the tank 3.
- the core height H is the separation distance between the upper and lower pairs of tanks 3 (the height of the space between the pair of tanks 3).
- the louver cut and raised width W of the core is shorter than the core width of FIG. 3 by the flat portion length of the fin.
- only one direction fin is inclined to the corrugated fin and is cut and raised at equal intervals in the range of the louver cutting and raising width W.
- flat portions 6 d are present on both sides of the louver cut and raised width W, and half louvers 6 c are formed on the flat portions 6 d.
- the width of this half louver 6 c is half of the width of the other louvers 6.
- the conventional fin 8 has a diverting louver 6b at the center in the width direction of the fin, and louvers 6a in which the direction of the louver is changed on both sides. Are parallel ones. Half louvers are cut and raised on both sides of the diverting louvers 6b.
- the unidirectional fins 7 and the conventional fins 8 which are the subject of the present invention are completely different in their channels, such as the directional fins 4 and the conventional fins 5, respectively. It is based on the structural difference between the unidirectional fin 7 of the invention and the conventional fin 8. And the following differences arise.
- the unidirectional fin 7 more louvers 6 can be cut and raised compared to the conventional fin 8. This is because the unidirectional louvers can be cut and raised instead of the diverting louvers 6 b of the conventional fin 8. In that respect, the core of the present invention improves the heat transfer coefficient.
- FIG. 4 shows the experimental data, in which the horizontal axis represents the louver cutting width W, and the vertical axis represents the ratio of the heat transfer coefficient. And experiment was tried at louver angle, 20 degrees, 30 degrees and 40 degrees respectively. As apparent from FIG. 4, the ratio of the heat transfer coefficient higher than that of the conventional louver in the range of the effective core height H 1 at any angle is shown. Further, FIG.
- the value of the lower limit for the louver cut and raised width W is on the curve a3. If the core height is equal to or more than the lower limit value, heat exchange performance higher than that of a conventional core can be obtained. The same applies to the cases of louver angles of 30 degrees and 40 degrees. Therefore, the heat exchanger core of the one-way louver should be set such that H, W and ⁇ satisfy the formula (1) H> Qup / (Qup-1) ⁇ ⁇ H.
- the louver cutting and raising width W is 6 to 46 mm
- the louver cutting and raising angle ⁇ is 20 to 35 degrees
- the louver pitch is 0.5 to 1.5 mm
- the fin pitch is 2 to 5 mm.
- the air flow was obtained from the study in which the core front surface flow velocity was 2 to 8 m / s.
- More preferable application conditions are a louver cut and raised width W of 6 to 26 mm, a louver cut and raised angle ⁇ of 20 to 30 degrees, a louver pitch of 0.5 to 1.0 mm, and a fin pitch of 2 to 3 mm
- the fluid is an air flow
- the core front surface flow velocity is 4 to 8 m / s.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Blinds (AREA)
Abstract
Description
第2流体は、主として空気等の気体である。
このようなコルゲートフィン型熱交換器において、現在実用されているフィンは、中間に転向ルーバを配置し、その両側に傾斜の向きを、互いに逆向きにしたルーバを切り起こしたものである。
次に、ルーバの向きを一方向のみに限定したコルゲートフィン型熱交換器が下記特許文献1として提案されている。
この熱交換器は、空気流の流入方向に対して、鋭角の角度の一方向ルーバがそのコア幅の全長に渡って切り起こし形成されたものである。この発明によれば、コア幅全長に渡って一方向に切り起こしたフィンでは、そのコアの上端部及び下端部の空気流が淀むことが指摘されている。
そこで、この発明は、コアの上下に配置されたタンクと、フィンの端部との間に空隙部を形成するスペーサ部材を配置する。すると、その空隙部の存在によってフィン内の空気流の淀みがなくなり、通気抵抗を大幅に低減させることができると記載している。
本発明は係る知見に基づいて開発されたものである。
コアの高さH(mm)と、流体の主たる流れ方向のルーバ切り起こし幅W(mm)と、ルーバ切り起こし角度θとが、下記不等式(1)を満たすように設定されたことを特徴とする熱交換器コアである。
H>Qup/(Qup−1)×ΔH (1)
Qup=Qup(W,θ)=α(W)+β(W,θ)+1 (2)
α(W)=η/(W−η) (3)
β(W,θ)=ξ/(W・tan22θ−ξ) (4)
ΔH=ΔH(W,θ)=j・W(sinθ+k・sin2θ) (5)
η=0.3553(mm)
ξ=0.5447(mm)
j=0.1419
k=4.2789
コアの高さHが、H>Qup/(Qup−1)×ΔHであるため、従来型フィンに比べて熱交換性能が高いものとなる。
具体的には、図6のW−H曲線で、各ルーバの切り起こし角度θにおいて、プロットされた各点を結ぶ曲線を超える範囲のコアHの高さを有する。なお、ここにルーバ切り起こし幅Wは、図3において、一方向ルーバが切り起こされた範囲をいう。
効果が得られる理由を以下に記す。
一方向フィンは、従来の転向ルーバフィンに対してデメリットおよびメリットがあり、
デメリットは、通風低下領域(伝熱低下領域)の増加ΔHであり、メリットは通風部における伝熱の向上(比)Qupである。
ここで、メリットがデメリットを上回るための条件は、
Qup×(H−ΔH)/H>1 であり、
この不等式を変形すると、
H>Qup/(Qup−1)×ΔH となる。
図2(A)は本発明の空気流の流通状態を示す説明図、(B)は従来型熱交換器の空気流の流通状態を示す説明図である。
図3(A)は本発明の熱交換器コアのルーバの切り起こし説明図、(B)は従来型熱交換器コアのルーバの切り起こし説明図である。
図4は横軸にルーバ切り起こし幅Wをとり、本発明のコアと従来型コアにおける主たる伝熱領域(通風部)の熱伝達率の比を縦軸にとった実験データである。
図5は横軸にルーバ切り起こし幅Wをとり、従来型コアに対する本発明のコアの伝熱低下領域(通風低下領域)の増分ΔHを縦軸に表したグラフである。
図6は横軸にルーバ切り起こし幅Wをとり、従来型コアに対して、本発明のコアの効果のあるコア高さの下限を縦軸に表したグラフである。
図7は横軸にルーバ切り起こし幅Wをとり、本発明の熱交換器コアと従来型熱交換器コアとの熱交換量の比率を縦軸にとったグラフである。
図1~図3は、本発明の熱交換器コアと、現在実用化されている従来型熱交換器コアとの比較を夫々表す。
図1はその熱交換器コアの縦断面説明図である。また、図2は(A)に本発明のルーバによる空気の流通路を示し、(B)に従来型コアの空気の流通路を示す。そして図3(A)(B)は、夫々の各ルーバの切り起こし状態を示す説明図である。
本発明の熱交換器コアは、偏平チューブとコルゲートフィンとを交互に並列してコアを形成する。そして、この例では上下に一対のタンク3を配置し、そのタンク3に偏平チューブの両端が貫通する。図1において、コア高さHは、上下一対のタンク3間の離間距離(一対のタンク3間の空間部高さ)である。そのコアのルーバ切り起こし幅Wは、図3のコア幅よりもフィンの平坦部長さ分、短い。
この例においては、図2(A),図3(A)に示す如く、コルゲートフィンに一方向フィンのみが傾斜してルーバ切り起こし幅Wの範囲に等間隔に切り起こされている。またルーバ切り起こし幅Wの両側には、平坦部6dが存在し、その平坦部6dには半ルーバ6cが形成されている。この半ルーバ6cの幅は、それ以外のルーバ6の幅の半分である。
そして図2(A)の如く、一方向フィン7に空気流1が流入すると、その一方向フィンの各ルーバ6に案内されて、その一方向の流路4が上流側から下流側に斜めの帯状に形成される。
これに対して、従来型フィン8は、図2(B),図3(B)に示す如く、フィンの幅方向中央に転向ルーバ6bを有し、その両側にルーバの向きを変えたルーバ6aが並列されたものである。その転向ルーバ6bの両側には半ルーバが切り起こされている。
そして、従来型フィン8に空気流1が流入すると、図2(B)の如く、従来型フィンの流路5が山形に形成される。
このように本発明の対象である一方向フィン7と、従来型フィン8はその流路が、それぞれ一方向フィンの流路4及び従来型フィンの流路5の如く全く異なる。
それは、本発明の一方向フィン7と従来型フィン8との、構造状の違いに基づく。そして、次の差異が生じる。
先ず、一方向フィン7では従来型フィン8に比べてより多くのルーバ6の切り起こしが可能となる。これは、従来型フィン8の転向ルーバ6bに代えて、一方向ルーバを切り起こすことができるからである。その点で本発明のコアは、熱伝達率が向上する。
次に、転向ルーバ6bによって空気流1を完全に転向させることは困難であり、従来型フィン8では転向部下流直後に滞留域が生じていたが、本発明においてはそれが無くなる。この点でも熱伝達率が向上する。
図1において、左側から流入する空気流1は、一方向フィン7では、その実効コア高さH1の範囲で熱交換器コア2内を斜めに流通する。
これに対し、従来型フィン8の場合は、従来型の実効コア高さH2の範囲で熱交換器コア2内で山形の点線の如く流通する。図1から明らかなように、本発明の一方向フィンの実効コア高さH1よりも、従来型の実効コア高さH2の方が高い。そのため同図において、本発明では、一方向フィンとすることで、通風低下領域の増加ΔHが生じる。そして、このΔHの領域において熱伝達率は低下する。
そこで、先ず、本発明者は図1における一方向フィンの実効コア高さH1における熱伝達率を、従来型フィン8に対する比として実験的に求めた。図4がその実験データであり、横軸にルーバ切り起こし幅Wをとり、縦軸に熱伝達率の比率をとる。そして、ルーバ角度、20度,30度,40度において夫々実験を試みた。
図4から明らかなように、何れの角度でも実効コア高さH1の範囲においては、従来型ルーバの熱伝達率よりも高い熱伝達率の比率を示す。
また、図7はルーバ切り起こし幅Wとコア全体の熱交換量の比率を示したものである。
これらのデータを回帰分析すると、
Qup=Qup(W,θ)=α(W)+β(W,θ)+1を得る。
ここに、α(W)=η/(W−η)であり、η=0.3553(mm)である。そして、β(W,θ)=ξ/(W・tan22θ−ξ)であり、ξ=0.5447(mm)である。
α(W)はルーバ枚数増加の効果を、β(W,θ)は転向部下流滞留域消滅の効果を表している。
また、Qup=(通風部における一方向フィン1山あたりの熱交換量)/(通風部における従来型フィン1山あたりの熱交換量)である。
次に、本発明者は図1に示す如く、一方向フィンとすることにより、従来型の実効高さH2に対してロスする領域ΔHを実験的に確認した。それが、図5である。図5において、横軸はコアのルーバ切り起こし幅Wであり、縦軸は一方向ルーバとしたことによる伝熱低下領域の増分ΔHであり、夫々単位はmmである。
そして、数値計算による流線を元に、各ルーバ角度θにおいて回帰分析をし、回帰式(5)
ΔH=ΔH(W,θ)=j・W・(sinθ+k・sin2θ)
(j=0.1419, k=4.2789)
を得た。
ここで、一方向ルーバのメリットとデメリットとを従来型フィンと比較考慮すると、その効果の表れる範囲は、Qup×(H−ΔH)/H>1である。
そして、この式を変形すると、H>Qup/(Qup−1)×ΔHとなる。
図6に、この不等式から求めた、一方向ルーバの効果があるコア高さの下限(曲線a3~c3)を示した。
一例として、ルーバ角度20度の場合は、ルーバ切り起こし幅Wに対するその下限の値はa3の曲線上にある。
この下限値以上のコア高さであれば、従来型のコアよりも高い熱交換性能を得ることができる。
ルーバ角度30度および40度の場合についても同様である。
従って、一方向ルーバの熱交換器コアは、そのHとWとθとを式(1)H>Qup/(Qup−1)×ΔH を満たすように設定すればよい。
なお、本発明は、ルーバ切り起こし幅Wが6~46mm,ルーバ切り起こし角度θが20度~35度,ルーバピッチが0.5~1.5mm,フィンピッチが2~5mmであって、流体を空気流とし、そのコア前面流速を2~8m/sとした検討から得られたものである。
そして、より好ましい適用条件は、ルーバ切り起こし幅Wが6~26mm,ルーバ切り起こし角度θが20度~30度,ルーバピッチが0.5~1.0mm,フィンピッチが2~3mmであって、流体は空気流であり、そのコア前面流速は4~8m/sである。
1a 空気流
2 熱交換器コア
3 タンク
4 一方向フィンの流路
5 従来型フィンの流路
6 ルーバ
6a ルーバ
6b 転向ルーバ
6c 半ルーバ
6d 平坦部
7 一方向フィン
8 従来型フィン
H コア高さ
W ルーバ切り起こし幅
θ ルーバ切り起こし角度
Claims (1)
- 流体が流通するフィンの幅方向に並列して、全てのルーバが同一方向に傾斜して切り起こし加工された多数のコルゲートフィンと、多数の偏平チューブとが交互に並列した熱交換器コアにおいて、
コアの高さH(mm)と、流体の主たる流れ方向のルーバ切り起こし幅W(mm)と、ルーバ切り起こし角度θとが、下記不等式(1)を満たすように設定されたことを特徴とする熱交換器コア。
H>Qup/(Qup−1)×ΔH (1)
Qup=Qup(W,θ)=α(W)+β(W,θ)+1 (2)
α(W)=η/(W−η) (3)
β(W,θ)=ξ/(W・tan22θ−ξ) (4)
ΔH=ΔH(W,θ)=j・W(sinθ+k・sin2θ)(5)
η=0.3553(mm)
ξ=0.5447(mm)
j=0.1419
k=4.2789
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JP2016523601A JP6574763B2 (ja) | 2014-05-27 | 2015-05-25 | 熱交換器コア |
RU2016142518A RU2679092C2 (ru) | 2014-05-27 | 2015-05-25 | Сердцевина теплообменника |
US15/309,927 US10309729B2 (en) | 2014-05-27 | 2015-05-25 | Heat exchanger core |
EP15799507.7A EP3150951B1 (en) | 2014-05-27 | 2015-05-25 | Heat exchanger core |
KR1020167030750A KR102360670B1 (ko) | 2014-05-27 | 2015-05-25 | 열교환기 코어 |
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