JP2023082450A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP2023082450A
JP2023082450A JP2021196234A JP2021196234A JP2023082450A JP 2023082450 A JP2023082450 A JP 2023082450A JP 2021196234 A JP2021196234 A JP 2021196234A JP 2021196234 A JP2021196234 A JP 2021196234A JP 2023082450 A JP2023082450 A JP 2023082450A
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Japan
Prior art keywords
heat exchanger
flat tube
windward
ribs
fin
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JP2021196234A
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Japanese (ja)
Inventor
祥太 飯塚
Shota Iizuka
諭 太田
Satoshi Ota
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Priority to JP2021196234A priority Critical patent/JP2023082450A/en
Priority to PCT/JP2022/043955 priority patent/WO2023100859A1/en
Publication of JP2023082450A publication Critical patent/JP2023082450A/en
Pending legal-status Critical Current

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • 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

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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)

Abstract

To provide a heat exchanger capable of enhancing draining of drain water generating from the heat exchanger in a defrosting operation.SOLUTION: A heat exchanger includes a plate-like fin having: a cutout portion to which a flat tube is inserted; a communication protrusion at a windward side; and a projecting portion at a leeward side with respect to the communication protrusion. The projecting portion is positioned so that its upper end of the projecting portion is close to the communication portion at a leeward side with respect to a windward-side end portion of the flat tube and above a top face of the flat tube, and its lower end is close to the communication portion at a windward side with respect to the windward-side end portion of the flat tube and at a lower portion with respect to a lower face of the flat tube. Further the lower end of the projecting portion is positioned at a lower portion with respect to an upper end of the other projecting portion positioned below in a gravity direction.SELECTED DRAWING: Figure 3

Description

本発明の実施形態は、扁平管を利用したフィンチューブ式の熱交換器に関する。 An embodiment of the present invention relates to a finned-tube heat exchanger using flat tubes.

従来、フィンに複数の切欠きが設けられ、その切欠きに、フィンの配置方向に延びる扁平管を挿入した、フィンチューブ型熱交換器が知られている。 Conventionally, a finned-tube heat exchanger is known in which a plurality of notches are provided in fins, and flat tubes extending in the direction in which the fins are arranged are inserted into the notches.

この熱交換器を使用した空気調和機が暖房運転を行う際、外気に含まれる水蒸気がドレンとなって熱交換器に付着し、そのドレンが外気によって冷却されることで霜となり、熱交換器に着霜することがある。
そのため、暖房運転が一定時間経過した後に、除霜運転が行われる。 When an air conditioner using this heat exchanger performs heating operation, the water vapor contained in the outside air becomes drain and adheres to the heat exchanger. may frost.
Therefore, the defrosting operation is performed after the heating operation has passed for a certain period of time.

ＷＯ－Ａ１－２０１９／１７５９７３WO-A1-2019/175973

除霜運転が行われる際、熱交換器に着霜した霜が溶けドレンとなり排出されるが、扁平管の上部にドレンが停滞することで除霜運転時にドレンの排水がうまく行われないことがあった。
また、ドレンが排水されないまま暖房運転が再開されると、扁平管の上部に停滞したドレンが再凍結する虞があった。 When the defrosting operation is performed, the frost that forms on the heat exchanger melts and is discharged as a drain. there were.
Further, if the heating operation is restarted without draining the drain, there is a possibility that the drain stagnating in the upper portion of the flat tube may refreeze.

本発明が解決しようとする課題は、除霜運転によって発生するドレンが扁平管の上部に停滞することを防ぎ、熱交換率を向上させる熱交換器を提供することを目的とする。 SUMMARY OF THE INVENTION An object of the present invention is to provide a heat exchanger that prevents drain generated by a defrosting operation from stagnating above flat tubes and improves heat exchange efficiency.

上記の課題を解決するために、本発明による熱交換器は、風下側で重力方向となる長手方向に一定の間隔を置いて複数の切欠き部が形成された板状フィンと、複数の切欠き部に装着される複数の扁平管と、板状フィンの風上側の長手方向に突出して設けられる連通凸部と、連通凸部よりも風下側で板状フィンの平面部から突出した複数の突出部と、を備える。
この突出部は、扁平管の風上側端部よりも風下側かつ扁平管の上面の高さよりも上部に位置する突出部の上端部と、扁平管の風上側端部よりも風上側かつ扁平管の下面の高さよりも下部に位置し連通部に近接する突出部の下端部と、が設けられる。
さらに、突出部の下端部は、重力方向でこの突出部よりも下に設けられる他の突出部の突出部の上端部よりも下方に位置する。 In order to solve the above problems, a heat exchanger according to the present invention includes a plate-like fin having a plurality of cutouts formed at regular intervals in the longitudinal direction, which is the direction of gravity on the leeward side, and a plurality of cutouts. A plurality of flat tubes attached to the notch, a communicating protrusion provided protruding in the longitudinal direction on the windward side of the plate-like fin, and a plurality of protruding from the planar portion of the plate-like fin on the leeward side of the communicating protrusion. and a protrusion.
This projecting portion includes an upper end portion of the projecting portion located on the leeward side of the windward end of the flat tube and above the height of the upper surface of the flat tube, and and a lower end portion of the protruding portion located below the height of the lower surface of the and close to the communicating portion.
Furthermore, the lower end of the projection is positioned below the upper end of the projection of another projection provided below this projection in the direction of gravity.

第１の実施形態の空気調和機の冷凍サイクルの概略図。Schematic of the refrigerating cycle of the air conditioner of 1st Embodiment. 第１の実施形態の空気調和機に係る室外熱交換器の平面図。The top view of the outdoor heat exchanger concerning the air conditioner of 1st Embodiment. 第１の実施形態の室外熱交換器に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the outdoor heat exchanger of 1st Embodiment. 第１の実施形態に係るＡ－Ａ’線における板状フィンの断面図。FIG. 2 is a cross-sectional view of the plate-like fin taken along line A-A' according to the first embodiment; 第１の実施形態の第１変形例に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the 1st modification of 1st Embodiment. 第１の実施形態の第２変形例に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the 2nd modification of 1st Embodiment. 第２の実施形態の室外熱交換器に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the outdoor heat exchanger of 2nd Embodiment. 第２の実施形態に係るｔ－ｔ’線における板状フィンの断面図１。FIG. 1 is a cross-sectional view 1 of a plate-like fin taken along line t-t' according to the second embodiment; 第２の実施形態に係るｘ－ｘ’線における板状フィンの断面図１。FIG. 1 is a cross-sectional view 1 of a plate-like fin taken along line x-x' according to a second embodiment; 第２の実施形態に係るｔ－ｔ’線における板状フィンの断面図２。FIG. 2 is a cross-sectional view 2 of the plate-like fin taken along line t-t' according to the second embodiment; 第２の実施形態に係るｘ－ｘ’線における板状フィンの断面図２。FIG. 2 is a cross-sectional view 2 of the plate-like fin taken along line x-x' according to the second embodiment; 第２の実施形態の第１変形例に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the 1st modification of 2nd Embodiment. 第２の実施形態の第２変形例に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the 2nd modification of 2nd Embodiment. 第２の実施形態の第３変形例に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on the 3rd modification of 2nd Embodiment. 第３の実施形態に係る板状フィンの平面図。The top view of the plate-shaped fin which concerns on 3rd Embodiment.

以下、発明を実施するための実施形態について説明する。 Embodiments for carrying out the invention will be described below.

（第１の実施形態）
第１の実施形態の熱交換器を、図１を参照して説明する。図１は、第１の実施形態の空気調和機１の冷凍サイクルの概略図である。 (First embodiment)
A heat exchanger of the first embodiment will be described with reference to FIG. FIG. 1 is a schematic diagram of the refrigeration cycle of the air conditioner 1 of the first embodiment.

（空気調和機）
本実施形態の空気調和機１は、圧縮機２、四方弁３、室外熱交換器４、室外ファン４’、膨張弁５、室内熱交換器６、室内ファン６’と、これら要素を接続する冷媒配管７から構成され、冷凍サイクル１０を形成する。
圧縮機２は、圧縮機本体２ａとアキュームレータ２ｂとを備える。アキュームレータ２ｂは、冷媒の気液の分離を行い、ガス冷媒を圧縮機本体２ａに送る。圧縮機本体２ａは、アキュームレータ２ｂから供給されるガス冷媒を圧縮して高温高圧のガス冷媒を生成する。
また、四方弁３の流路の切り替えを行うことで、冷凍サイクル１０の冷房運転と暖房運転等の切り替えを行う。 (air conditioner)
The air conditioner 1 of this embodiment connects the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the outdoor fan 4', the expansion valve 5, the indoor heat exchanger 6, the indoor fan 6', and these elements. A refrigeration cycle 10 is formed by a refrigerant pipe 7 .
The compressor 2 includes a compressor main body 2a and an accumulator 2b. The accumulator 2b separates the gas-liquid refrigerant and sends the gas refrigerant to the compressor main body 2a. The compressor body 2a compresses the gas refrigerant supplied from the accumulator 2b to generate high-temperature and high-pressure gas refrigerant.
Also, by switching the flow path of the four-way valve 3, switching between the cooling operation and the heating operation of the refrigeration cycle 10 is performed.

（冷房運転）
以下、図１の実線矢印に示される、冷房運転時の冷媒の流れについて説明する。
圧縮機２によって排出されたガス冷媒は、冷媒配管７を通じて四方弁３の実線で描かれる流路を通過する。そして、室外熱交換器４に流入し、室外ファン４‘の送風によって室外熱交換器４で外気に熱を放出して、冷媒は凝縮される。凝縮された液体冷媒は、冷媒配管７を通じて、膨張弁５を通過する。この際に、冷媒の圧力が下げられる。低圧の液冷媒は、室内熱交換器６および室内ファン６’によって、室内の空気の熱を奪うことで蒸発し、熱交換を行う。この蒸発されたガス冷媒は、再び圧縮機２に流入する。 (cooling operation)
Hereinafter, the flow of the refrigerant during the cooling operation indicated by the solid line arrows in FIG. 1 will be described.
The gaseous refrigerant discharged by the compressor 2 passes through the four-way valve 3 through the refrigerant pipe 7 and the passage drawn by the solid line. Then, the refrigerant flows into the outdoor heat exchanger 4, and is condensed by the outdoor heat exchanger 4 releasing heat to the outside air by blowing air from the outdoor fan 4'. The condensed liquid refrigerant passes through the expansion valve 5 through the refrigerant pipe 7 . At this time, the pressure of the refrigerant is lowered. The low-pressure liquid refrigerant takes heat from the air in the room by the indoor heat exchanger 6 and the indoor fan 6', evaporates, and performs heat exchange. This evaporated gaseous refrigerant flows into the compressor 2 again.

（暖房運転）
一方暖房運転では、図１の破線矢印に示すように、圧縮機２によって排出されたガス冷媒は、四方弁３を破線方向に通過し、室内熱交換器６に流入する。室内熱交換器６および室内ファン６’によって、ガス冷媒は室内の空気と熱交換を行い、室内の空気に熱を放出することで凝縮され、液体冷媒に変化する。この凝縮された冷媒は、冷媒配管７を通じて膨張弁５を通過する。この際、冷媒の圧力が下げられることで、低圧の液体冷媒になる。この低圧の液体冷媒は、室外熱交換器４に流入し、室外ファン４’の送風によって外気の熱を奪い、ガス冷媒に変化する。この蒸発したガス冷媒は、再び圧縮機２に流入する。
このように、冷凍サイクル１０が形成され、冷房および暖房運転が行われる。 (heating operation)
On the other hand, in heating operation, gas refrigerant discharged by the compressor 2 passes through the four-way valve 3 in the direction of the dashed line and flows into the indoor heat exchanger 6, as indicated by the dashed arrow in FIG. The gas refrigerant exchanges heat with the indoor air by the indoor heat exchanger 6 and the indoor fan 6', releases heat to the indoor air, is condensed, and changes to liquid refrigerant. This condensed refrigerant passes through the expansion valve 5 through the refrigerant pipe 7 . At this time, the pressure of the refrigerant is lowered, so that it becomes a low-pressure liquid refrigerant. This low-pressure liquid refrigerant flows into the outdoor heat exchanger 4, absorbs heat from the outside air by the ventilation of the outdoor fan 4', and changes into gas refrigerant. This evaporated gaseous refrigerant flows into the compressor 2 again.
Thus, the refrigerating cycle 10 is formed, and cooling and heating operations are performed.

（除霜運転）
空気調和機１が暖房運転を行う際、冷媒は室外熱交換器４で蒸発する。
その際に、冷媒は外気から熱を奪い、外気を凝縮させるため、外気に含まれる水蒸気が水となって室外熱交換器４に付着する。さらに、外気の気温が低いことによって、室外熱交換器４に付着した水分が凍結し、霜となることがあり、熱の交換効率を下げてしまう。
この付着した霜を除去するため、除霜運転が行われる。 (defrosting operation)
When the air conditioner 1 performs heating operation, the refrigerant evaporates in the outdoor heat exchanger 4 .
At that time, the refrigerant takes heat from the outside air and condenses the outside air, so that water vapor contained in the outside air turns into water and adheres to the outdoor heat exchanger 4 . Furthermore, when the temperature of the outside air is low, the moisture adhering to the outdoor heat exchanger 4 may freeze and become frost, which lowers the efficiency of heat exchange.
A defrosting operation is performed to remove the adhering frost.

例えば、暖房運転から除霜運転に切り替える方法として、室外熱交換器４の温度に基づいて、室外熱交換器４の着霜量を測定し、その着霜量が規定値以上になった場合に、暖房運転から除霜運転に切り替える。
また、除霜運転は、着霜量が規定値未満に減少するまで、あるいは規定時間に達するまで行われる。
除霜運転は、暖房運転の動作から、四方弁３を冷房運転時の状態に切り替え、室内ファン６’および室外ファン４’を停止させる。これにより、圧縮機２から吐出される高温ガスが室外熱交換器４に流入し、室外熱交換器４に着霜した霜を溶かし、ドレンとなって排出される。 For example, as a method of switching from heating operation to defrosting operation, the amount of frost on the outdoor heat exchanger 4 is measured based on the temperature of the outdoor heat exchanger 4, and when the amount of frost exceeds a specified value, , to switch from heating operation to defrosting operation.
Also, the defrosting operation is performed until the amount of frost formation decreases below a specified value or until a specified time is reached.
In the defrosting operation, the four-way valve 3 is switched from the operation of the heating operation to the state of the cooling operation, and the indoor fan 6' and the outdoor fan 4' are stopped. As a result, the high-temperature gas discharged from the compressor 2 flows into the outdoor heat exchanger 4, melts the frost formed on the outdoor heat exchanger 4, and is discharged as drain.

（室外熱交換器）
図２は、第１の実施の形態の空気調和機１に係る室外熱交換器４の平面図である。
この室外熱交換器４は、フィンチューブ型の熱交換器であり、主にアルミ製の熱交換器である。
図２における、室外熱交換器４への風の流れ方向は、紙面に対して垂直な方向であり、白抜き矢印で示す。ここでは、矢印の下側を紙面手前側、矢印の上側を紙面奥側とし、紙面手前側から紙面奥側へ風が流れることを表している。また、風の流れ方向に直行する冷媒の流れ方向を、実線矢印で示す。
室外熱交換器４は、冷媒の流れ方向に積層された複数の板状フィン４１と、板状フィン４１に重力方向に複数装着される扁平管４２と、扁平管４２の両端部に備えられる、二本のヘッダ４３、４４と、を有する。 (outdoor heat exchanger)
FIG. 2 is a plan view of the outdoor heat exchanger 4 according to the air conditioner 1 of the first embodiment.
The outdoor heat exchanger 4 is a finned-tube heat exchanger, and is mainly made of aluminum.
In FIG. 2, the direction of air flow to the outdoor heat exchanger 4 is the direction perpendicular to the plane of the paper and is indicated by white arrows. Here, the lower side of the arrow is the front side of the paper surface, and the upper side of the arrow is the back side of the paper surface. Solid arrows indicate the flow direction of the coolant that is perpendicular to the flow direction of the wind.
The outdoor heat exchanger 4 includes a plurality of plate-like fins 41 stacked in the refrigerant flow direction, a plurality of flat tubes 42 attached to the plate-like fins 41 in the direction of gravity, and both ends of the flat tubes 42. It has two headers 43 and 44 .

（扁平管）
図３は、第１の実施形態の室外熱交換器４に係る板状フィン４１の平面図である。
扁平管４２は略長円形状ないし、略楕円形状の断面を有しており、図３に示すように、例えば、長円形状の横断面を有している。そして、複数の流体通路４５が互いに並行に延びるように設けられた伝熱管である。
また、扁平管４２は、撥水性加工がされており、例えば撥水コーティング材が塗布されている。 (flat tube)
FIG. 3 is a plan view of plate-like fins 41 according to the outdoor heat exchanger 4 of the first embodiment.
The flattened tube 42 has a substantially oval or substantially elliptical cross-section, and as shown in FIG. 3, has, for example, an oval cross-section. It is a heat transfer tube in which a plurality of fluid passages 45 are provided so as to extend parallel to each other.
Further, the flat tube 42 is processed to be water-repellent, for example, a water-repellent coating material is applied.

（ヘッダ）
ヘッダ４３、４４は、図２に示すように、それぞれ一端に扁平管４２が挿入される細長い中空円筒状で、上端および下端はエンドキャップ４３ａ、４３ｂ、および、４４ａ、４４ｂによって閉塞されている。また、ヘッダ４３、４４の内部には複数の仕切り版（図示しない）が設けられ、冷媒の流れが制御される。
ヘッダ４３には、液側継手管４３ｃの一端が接続される。この液側継手管４３ｃの他端は、冷媒配管７と接続され、膨張弁５に接続される。
同じくヘッダ４４には、ガス側継手管４４ｃの一端が接続される。このガス側継手管４４ｃの他端は、四方弁３に繋がる冷媒配管７と接続される。
このように、冷房運転を行う際の室外熱交換器４での冷媒流路は、四方弁３から冷媒配管７、ガス側継手管４４ｃを介してヘッダ４４、扁平管４２に流入する。そして、板状フィン４１により熱交換を行い、ヘッダ４３を通過し、液側継手管４３ｃ、冷媒配管７を介して膨張弁５に流入する。 (header)
As shown in FIG. 2, the headers 43, 44 are elongated hollow cylinders into which the flat tube 42 is inserted at one end, and whose upper and lower ends are closed by end caps 43a, 43b and 44a, 44b. A plurality of partition plates (not shown) are provided inside the headers 43 and 44 to control the flow of the coolant.
One end of a liquid side joint pipe 43c is connected to the header 43 . The other end of the liquid side joint pipe 43 c is connected to the refrigerant pipe 7 and the expansion valve 5 .
Similarly, the header 44 is connected to one end of a gas side joint pipe 44c. The other end of the gas side joint pipe 44 c is connected to the refrigerant pipe 7 connected to the four-way valve 3 .
In this manner, the refrigerant flow path in the outdoor heat exchanger 4 during cooling operation flows from the four-way valve 3 into the header 44 and the flat tube 42 via the refrigerant pipe 7 and the gas side joint pipe 44c. Then, heat is exchanged by the plate-like fins 41 , passes through the header 43 , and flows into the expansion valve 5 via the liquid side joint pipe 43 c and the refrigerant pipe 7 .

（フィン）
板状フィン４１は、図３に示すように、略矩形に形成され、風下側で重力方向となる長手方向の辺を長辺４１ａ、長辺４１ａに対向する風上側の辺を長辺４１ｃ、重力方向に対して上側の短手方向の辺を短辺４１ｂ、短辺４１ｂに対向する下側の辺を短辺４１ｄとする。
この板状フィン４１には、親水性加工、例えば親水処理コーティング材が塗布される。 (fin)
As shown in FIG. 3, the plate-like fin 41 is formed in a substantially rectangular shape, with a long side 41a extending in the direction of gravity on the leeward side, a long side 41c extending on the windward side opposite to the long side 41a, and The short side 41b is the side in the short direction above the direction of gravity, and the short side 41d is the side opposite to the short side 41b.
The plate-like fins 41 are subjected to hydrophilic treatment, for example, a hydrophilic treatment coating material is applied.

また、風の流れる方向を実線矢印で示す。
この板状フィン４１の風下側の長辺４１ａには、一定の間隔を置いて複数の切欠き部４１ｅが形成され、切欠き部４１ｅは、短手方向に向かって延びている。この切欠き部４１ｅは、風上側端部４１ｅ’が、扁平管４２の端部形状に合わせて、略半円形状または略楕円形状となっており、扁平管４２が挿入されている。 The direction of air flow is indicated by solid arrows.
A plurality of notches 41e are formed at regular intervals on the long side 41a on the leeward side of the plate-like fin 41, and the notches 41e extend in the lateral direction. A windward end 41e' of the notch 41e has a substantially semicircular or substantially elliptical shape in accordance with the end shape of the flat tube 42, into which the flat tube 42 is inserted.

（連通部）
図４は、実線矢印方向から見た、板状フィン４１のＡ－Ａ’線における断面図である。
図４に示すように、板状フィン４１には、風上側の長辺４１ｃ側に、この長辺４１ｃと平行に設けられる連通凸部４６が形成される。連通凸部４６は、長辺４１ｃから一定の間隔を空けて、板状フィン４１の面に凸となるように、板状フィン４１の上端部から下端部まで連続して設けられている。 (Communication part)
FIG. 4 is a cross-sectional view of the plate-like fin 41 taken along the line AA', viewed in the direction of the solid arrow.
As shown in FIG. 4, the plate-like fin 41 is formed with a communication convex portion 46 provided parallel to the long side 41c on the windward side. The communicating convex portion 46 is provided continuously from the upper end portion to the lower end portion of the plate-like fin 41 so as to be convex on the surface of the plate-like fin 41 at a certain interval from the long side 41c.

（突出部）
板状フィン４１には突出部４００（４００Ａ、～・・・～、４００Ｎ）が設けられる。
この突出部４００の断面は、図４に示すように、半円形状となるように形成される。この突出部４００の断面は、半円形状のみでなく、突出が鋭利になるような形状や、略矩形などの形にに形成されてもよい。 (protrusion)
The plate-like fin 41 is provided with protrusions 400 (400A, . . . , 400N).
The cross section of the projecting portion 400 is formed to have a semicircular shape, as shown in FIG. The cross section of the protruding portion 400 may be formed in a shape such as a shape with a sharp protrusion or a shape such as a substantially rectangular shape, instead of being limited to a semicircular shape.

突出部４００（４００Ａ、～・・・～、４００Ｎ）は扁平管４２（４２Ａ、～・・・～、４２Ｎ）に対応して設けられる。
詳しくは、図３に示すように、扁平管４２は、扁平管４２Ａから扁平管４２Ｎの順に所定間隔を空けて配置されている。
それに対応して、突出部４００も、突出部４００Ａから突出部４００Ｎまで形成される。 The protrusions 400 (400A, . . . , 400N) are provided corresponding to the flat tubes 42 (42A, . . . , 42N).
Specifically, as shown in FIG. 3, the flat tubes 42 are arranged at predetermined intervals in order from the flat tube 42A to the flat tube 42N.
Correspondingly, protrusions 400 are also formed from protrusions 400A to 400N.

突出部４００Ａの上端部４００Ａａは、扁平管４２Ａの下面４２Ａｂの高さよりも低く位置し、かつ扁平管４２Ｂの風上側端部４２Ｂｕよりも風下側で扁平管４２Ｂの上面４２Ｂｔの高さよりも高く位置する。
一方、下端部４００Ａｂは、扁平管４２Ｃの上面４２Ｃｔの高さよりも高く位置する。また、この下端部４００Ａｂは、扁平管４２Ｂの風上側端部４２Ｂｕよりも風上側で、かつ扁平管４２Ｂの下面４２Ｂｂの高さよりも下部に下端部４００Ａｂが位置する。
すなわち、突出部４００Ａは、扁平管４２Ｂの上面４２Ｂｔおよび下面４２Ｂｂの高さ分を必ず有するように形成される。 The upper end portion 400Aa of the protruding portion 400A is positioned lower than the lower surface 42Ab of the flat tube 42A, and is positioned higher than the upper surface 42Bt of the flat tube 42B on the leeward side of the windward end 42Bu of the flat tube 42B. do.
On the other hand, the lower end portion 400Ab is positioned higher than the height of the upper surface 42Ct of the flat tube 42C. The lower end portion 400Ab is located on the windward side of the windward end portion 42Bu of the flat tube 42B and below the height of the lower surface 42Bb of the flat tube 42B.
That is, the projecting portion 400A is formed so as to necessarily have the height of the upper surface 42Bt and the lower surface 42Bb of the flat tube 42B.

同じく突出部４００Ｂは、上端部４００Ｂａが扁平管４２Ｂの下面４２Ｂｂの高さよりも低く位置し、かつ扁平管４２Ｂの風上側端部４２Ｂｕよりも風下側で扁平管４２Ｃの上面４２Ｃｔの高さよりも高く位置する。また、この下端部４００Ｂｂは、扁平管４２Ｃの風上側端部４２Ｃｕよりも風上側で、かつ扁平管４２Ｃの下面４２Ｃｂの高さよりも低く位置する。 Similarly, the projecting portion 400B has an upper end portion 400Ba positioned lower than the lower surface 42Bb of the flat tube 42B, and higher than the upper surface 42Ct of the flat tube 42C on the leeward side of the windward end 42Bu of the flat tube 42B. To position. The lower end portion 400Bb is located on the windward side of the windward end portion 42Cu of the flat tube 42C and lower than the lower surface 42Cb of the flat tube 42C.

突出部４００Ａと突出部４００Ｂとの位置関係は、突出部４００Ｂの上端部４００Ｂａと突出部４００Ａの下端部４００Ａｂとが、扁平管４２Ｂの下面４２Ｂｂよりも低い位置で、ａ’の高さ分、重なりを持つように風向き方向に並ぶ。
さらに、下端部４００Ａｂは、連通凸部４６に近接する位置に設けられる。
このように、突出部４００は、他の突出部４００と所定の高さ分を有して、突出部４００Ａから突出部４００Ｎまで複数並んでいる。 The positional relationship between the protruding portion 400A and the protruding portion 400B is such that the upper end portion 400Ba of the protruding portion 400B and the lower end portion 400Ab of the protruding portion 400A are positioned lower than the lower surface 42Bb of the flat tube 42B by the height of a', Lined up in the direction of the wind so as to have an overlap.
Furthermore, the lower end portion 400Ab is provided at a position close to the communicating convex portion 46 .
In this way, the protrusion 400 has a predetermined height from the other protrusions 400, and the plurality of protrusions 400A to 400N are arranged side by side.

この構造によって、扁平管４２から落下するドレンが、他の扁平管４２の上面４２ｔに停滞することなく、突出部４００によって形成される排水流路に排水される。
また、突出部４００の下端部４００ｂが、連通凸部４６に近づいていくように設けられていることで、突出部４００による排水流路を流れたのち、毛細管現象により、連通凸部４６に排水されやすくなる。
さらに、複数の突出部４００の下端部４００ｂが、連通凸部４６に集まるように形成されていることで、１枚の板状フィン４１のドレンが連通凸部４６に集中し、ドレンの排水速度を向上させることができる。 With this structure, the drain that falls from the flat tubes 42 is discharged to the drainage channel formed by the projecting portion 400 without stagnation on the upper surfaces 42 t of the other flat tubes 42 .
Further, since the lower end portion 400b of the projecting portion 400 is provided so as to approach the communicating projecting portion 46, after flowing through the drainage channel formed by the projecting portion 400, the water is discharged to the communicating projecting portion 46 by capillary action. easier to be
Furthermore, since the lower end portions 400b of the plurality of projecting portions 400 are formed so as to gather at the communicating convex portion 46, the drain of one plate-like fin 41 concentrates on the communicating convex portion 46, and the drainage speed of the drain increases. can be improved.

（第１変形例）
図５は、第１の実施形態の第１変形例に係る板状フィン４１の平面図である。
実施形態１では、図５に示すように、直線状の突出部４００が傾斜するように設けられ、かつ、他の突出部４００と平行になり、複数の突出部４００の長さが同じになるように配置されているが、本変形例では、図５に示すように、複数の突出部４００～４００”の長さと傾きがそれぞれ異なっている。
突出部４００～４００”が偏平管４２から連通凸部４６に向けて傾斜すれば、他の突出部４００との長さが等しくならなくても、他の突出部４００と平行にならなくてもよい。 (First modification)
FIG. 5 is a plan view of plate-like fins 41 according to a first modification of the first embodiment.
In Embodiment 1, as shown in FIG. 5, the linear protrusions 400 are provided so as to be inclined and parallel to other protrusions 400, and the lengths of the plurality of protrusions 400 are the same. However, in this modified example, as shown in FIG. 5, the lengths and inclinations of the plurality of protrusions 400 to 400″ are different.
If the projecting portions 400 to 400″ are inclined from the flat tube 42 toward the communicating projecting portion 46, even if the lengths of the projecting portions 400 to 400 are not equal to or parallel to the other projecting portions 400. good.

（第２変形例）
図６は、第１の実施形態の第２変形例に係る板状フィン４１の平面図である。
図６の突出部４２０に示すように、突出部４２０の下端部４２０ｂを、連通凸部４６と平行になるような平行部４２０ｐを設けてもよい。
さらに、突出部４３０に示すように、突出部４３０の上端部４３０ａと、下端部４３０ｂとの両端に平行部４３０ｐを設けてもよい。 (Second modification)
FIG. 6 is a plan view of plate-like fins 41 according to a second modification of the first embodiment.
As shown in the projecting portion 420 in FIG. 6 , a parallel portion 420 p may be provided such that the lower end portion 420 b of the projecting portion 420 is parallel to the communicating projecting portion 46 .
Furthermore, as shown in the protrusion 430, parallel portions 430p may be provided at both ends of the upper end 430a and the lower end 430b of the protrusion 430. FIG.

このように、平行部が直線形状となるため、排水速度を向上させることができる。
また、平行部は、他の平行部と長さが同じにならなくてもよい。
さらに、図６に示すように、突出部４００は突出部４２０や突出部４３０、突出部４００Ｃなど、同じ形状でない突出部を組み合わせて形成してもよい。 In this way, since the parallel portion has a linear shape, it is possible to improve the drainage speed.
Also, the parallel portion may not have the same length as the other parallel portions.
Furthermore, as shown in FIG. 6, the protrusion 400 may be formed by combining protrusions having different shapes, such as a protrusion 420, a protrusion 430, and a protrusion 400C.

（第２の実施形態）
図７、図８（ａ）、図８（ｂ）、図９（ａ）、図９（ｂ）は、本発明の実施形態２に係る板状フィン４１を示す平面図および断面図である。
図７は、第２の実施形態の室外熱交換器４に係る板状フィン４１の平面図である。
図８（ａ）は、実線矢印方向から見た、図７の板状フィン４１のｔ－ｔ’線における断面図１、図８（ｂ）は、実線矢印方向から見た、図７の板状フィン４１のｘ－ｘ‘線における断面図１、である。
同じく図９（ａ）は、実線矢印方向から見た、図７の板状フィン４１のｔ－ｔ’線における断面図２、図９（ｂ）は、実線矢印方向から見た、図７の板状フィン４１のｘ－ｘ‘線における断面図２、である。 (Second embodiment)
7, 8(a), 8(b), 9(a), and 9(b) are a plan view and a sectional view showing a plate-like fin 41 according to Embodiment 2 of the present invention.
FIG. 7 is a plan view of the plate-like fins 41 of the outdoor heat exchanger 4 of the second embodiment.
8(a) is a cross-sectional view of the plate-like fin 41 of FIG. 7 taken along the line tt', viewed from the direction of the solid arrow, and FIG. 8(b) is the plate of FIG. FIG. 1 is a cross-sectional view of the shaped fin 41 taken along line xx'.
Similarly, FIG. 9(a) is a cross-sectional view taken along the line tt' of the plate-like fin 41 in FIG. 7 seen from the direction of the solid arrow, and FIG. FIG. 2 is a cross-sectional view 2 of the plate-like fin 41 taken along line xx'.

図７で示すように、本実施形態では、突出部４００Ａは、風の流れ方向に２本のリブ４０１Ａおよび４０２Ａが連続して並ぶ形状である。
そのため、第１の実施形態の突出部４００Ａと比べて、図８（ａ）に示すように、リブ４０１Ａおよびリブ４０２Ａのリブ間に形成される隙間に、毛細管現象によってドレンが流れ込みやすくなる。
また、排水流路がこのリブ間の隙間によって形成されるため、実施形態１よりもドレンが導かれやすくなり、排水速度が更に向上する。
そして、図８（ａ）および図８（ｂ）に示すように、突出部４００は、連通凸部４６に近づいていくように構成されるため、リブ間を流れたのち、連通凸部４６に沿って排水される。板状フィン４１に付着するドレンを連通凸部４６に集める構造にすることで、ドレンの排水効率が更に向上する。 As shown in FIG. 7, in this embodiment, the protruding portion 400A has a shape in which two ribs 401A and 402A are continuously arranged in the air flow direction.
Therefore, compared to the projecting portion 400A of the first embodiment, as shown in FIG. 8A, it is easier for drain to flow into the gap formed between the ribs 401A and 402A due to capillary action.
In addition, since the drainage channel is formed by the gaps between the ribs, the drainage is more easily guided than in the first embodiment, and the drainage speed is further improved.
As shown in FIGS. 8A and 8B, since the protruding portion 400 is configured to approach the communicating convex portion 46, the liquid flows between the ribs and then reaches the communicating convex portion 46. drained along. By adopting a structure in which the drain adhering to the plate-like fins 41 is collected in the communication convex portion 46, the drainage efficiency of the drain is further improved.

この２本のリブ４０１および４０２の断面形状は、図８（ａ）および図８（ｂ）に示すように半円状のリブを２本並べる形状でも、図９（ａ）および図９（ｂ）に示すように突出が鋭利になるようなリブを２本並べる形状でもよい。
また、突出部４００は、２本のリブに限らず、複数本のリブを連続して配置したものでもよい。
さらに、第１の実施例の第１変形例および第２変形例を、第２の実施形態に組み合わせてもよい。 The cross-sectional shapes of these two ribs 401 and 402 are the same as those shown in FIGS. ), two ribs having sharp projections may be arranged side by side.
Moreover, the projecting portion 400 is not limited to two ribs, and may be formed by continuously arranging a plurality of ribs.
Furthermore, the first and second modifications of the first embodiment may be combined with the second embodiment.

（第１変形例）
図１０は、第２の実施形態の第１変形例に係る板状フィン４１を示す平面図である。
図１０に示すように、本実施例では、突出部４００Ａは、２本のリブ４０１Ａ、４０２Ａから形成され、風下側のリブ４０１Ａの上端部４０１Ａａが、風上側のリブ４０２Ａの上端部４０２Ａａと比べて高く位置するように形成される。
この形状にすることで、毛細管現象により２本のリブ４０１Ａ、４０２Ａによって形成されるリブ間の隙間に、さらににドレンが流れ込みやすくなる。 (First modification)
FIG. 10 is a plan view showing plate-like fins 41 according to the first modification of the second embodiment.
As shown in FIG. 10, in this embodiment, the projecting portion 400A is formed from two ribs 401A and 402A, and the upper end portion 401Aa of the rib 401A on the leeward side is larger than the upper end portion 402Aa of the rib 402A on the windward side. It is formed to be positioned high on the
This shape makes it easier for drain to flow into the gap between the ribs formed by the two ribs 401A and 402A due to capillary action.

（第２変形例）
図１１は、第２の実施形態の第２変形例に係る板状フィン４１を示す平面図である。
図１１に示すように、風上側のリブ４０２Ａの下端部４０２Ａｂが、風下側のリブ４０１Ａの下端部４０１Ａｂよりも低く位置するように形成されてもよい。
この形状にすることにより、リブ間の隙間に流れ込んだドレンが、リブ間の隙間を通り、リブ４０２Ａの下端部４０２Ａｂ側に導かれるため、連通凸部４６に更に導かれやすくなることや、突出部４００Ａの下端部４００Ａｂからの水切りが行われやすくなる。 (Second modification)
FIG. 11 is a plan view showing plate-like fins 41 according to a second modification of the second embodiment.
As shown in FIG. 11, the lower end 402Ab of the rib 402A on the windward side may be positioned lower than the lower end 401Ab of the rib 401A on the leeward side.
With this shape, the drain that has flowed into the gaps between the ribs passes through the gaps between the ribs and is guided toward the lower ends 402Ab of the ribs 402A. Water can be easily drained from the lower end portion 400Ab of the portion 400A.

（第３変形例）
さらに、図１２は、第２の実施形態の第３変形例に係る板状フィン４１を示す平面図である。
図１２で示すように、突出部４１０（４１０Ａ、～・・・～、４１０Ｎ）は複数のリブ（４０３～４０５）により構成される。この突出部４１０の隣り合うリブは、風上側のリブの上端部よりも風下側のリブの上端部の方が高く位置するように形成される。。すなわち、リブ４０５の上端部４０５Ａａよりもリブ４０４の上端部４０４Ａａの方が高く位置し、また、リブ４０４の上端部４０４Ａａよりもリブ４０３の上端部４０３Ａａの方が高く位置する。
また、複数のリブの下端部も同様に、隣り合うリブの、風上側のリブの下端部よりも風下側のリブの下端部の方が高く位置するように形成されてもよい。すなわち、リブ４０５の下端部４０５Ａｂよりもリブ４０４の下端部４０４Ａｂの方が高く位置し、また、リブ４０４の下端部４０４Ａｂよりもリブ４０３の下端部４０３Ａｂの方が高く位置する。 (Third modification)
Furthermore, FIG. 12 is a plan view showing a plate-like fin 41 according to a third modified example of the second embodiment.
As shown in FIG. 12, the projecting portion 410 (410A, . . . , 410N) is composed of a plurality of ribs (403-405). Adjacent ribs of the projecting portion 410 are formed such that the upper end of the rib on the leeward side is positioned higher than the upper end of the rib on the windward side. . That is, the upper end 404Aa of the rib 404 is positioned higher than the upper end 405Aa of the rib 405, and the upper end 403Aa of the rib 403 is positioned higher than the upper end 404Aa of the rib 404.
Likewise, the lower end portions of the plurality of ribs may be formed such that the lower end portion of the adjacent rib on the leeward side is positioned higher than the lower end portion of the rib on the windward side. That is, the lower end 404Ab of the rib 404 is positioned higher than the lower end 405Ab of the rib 405, and the lower end 403Ab of the rib 403 is positioned higher than the lower end 404Ab of the rib 404.

この形状にすることにより、リブが複数になった場合でも、隣り合う端部の高さに差がついていることで、毛細管現象が更に起こりやすくなり、突出部４１０にドレンが流れ込みやすくなる。
また、複数のリブが設けられることで、リブ間の隙間も複数構成され、扁平管４２に付着したドレンの排水を複数に分散することができる。
さらに、リブの高さに差がついていることによって、連通凸部４６に導かれやすくなる。 By adopting this shape, even when there are a plurality of ribs, the difference in height between adjacent ends makes capillary action more likely to occur, and drainage can easily flow into the projecting portion 410 .
In addition, by providing a plurality of ribs, a plurality of gaps are formed between the ribs, and the drain water adhering to the flat tube 42 can be dispersed in a plurality of areas.
Furthermore, the difference in the height of the ribs makes it easier to be guided to the communicating protrusions 46 .

（第３実施形態）
図１３は、本発明の実施形態３に係る板状フィン４１を示す平面図である。
図１３で示すように、実施形態３では、扁平管４２が重力方向に対して風上側端部４２ｕが風下側端部４２ｌよりも下に傾斜する構造、すなわち、扁平管４２が板状フィン４１の重力方向に対して右下がりに傾斜するように形成される。
この形状にすることで、扁平管４２の上面または下面にドレンが停滞することを防ぎ、扁平管４２から、突出部４００または連通凸部４６へのドレンの排水が更に促進される。
また、第１の実施形態および第２の実施形態に記載の構造を、第３の実施形態に組み合わせてもよい。 (Third Embodiment)
FIG. 13 is a plan view showing plate-like fins 41 according to Embodiment 3 of the present invention.
As shown in FIG. 13, in the third embodiment, the flat tube 42 has a structure in which the windward end 42u is inclined downward from the leeward end 42l with respect to the direction of gravity. It is formed so as to incline downward to the right with respect to the direction of gravity.
This shape prevents drain from stagnation on the upper or lower surface of the flat tube 42 , and further promotes drainage from the flat tube 42 to the projecting portion 400 or the communicating protrusion 46 .
Also, the structures described in the first and second embodiments may be combined with the third embodiment.

以上、本発明の実施形態を説明したが、本実施形態は、例として提示したものであり、発明の範囲を限定することは意図していない。
本実施形態では、室外熱交換器として利用した例を示したが、室内熱交換器等、様々な熱交換器に使用することができる。
この新規な実施形態は、その他の様々な形態で実施されることが可能であり、発明の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行うことができる。
本実施形態やその変形は、発明の範囲や要旨に含まれるとともに、特許請求の範囲に記載された発明とその均等の範囲に含まれる。 Although the embodiment of the present invention has been described above, the present embodiment is presented as an example and is not intended to limit the scope of the invention.
In this embodiment, an example of use as an outdoor heat exchanger is shown, but it can be used for various heat exchangers such as an indoor heat exchanger.
This novel embodiment can be embodied in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention.
This embodiment and its modifications are included in the scope and gist of the invention, and are included in the scope of the invention described in the claims and equivalents thereof.

板状フィン４１、切欠き部４１ｅ、扁平管４２、風上側端部４２ｕ、上面４２ｔ、下面４２ｂ、連通凸部４６、突出部４００、上端部４００ａ、下端部４００ｂ Plate-like fin 41, notch 41e, flat tube 42, windward end 42u, upper surface 42t, lower surface 42b, communicating protrusion 46, protrusion 400, upper end 400a, lower end 400b

Claims (6)

風下側で、重力方向となる長手方向に一定の間隔を置いて複数の切欠部が形成された板状のフィンと、
前記複数の切欠部に装着される複数の扁平管と、
前記板状フィンの風上側の長手方向に設けられる連通凸部と、
前記連通凸部よりも風下側で、前記フィンの平面部から突出した複数の突出部と、を備え、
前記突出部は、
前記扁平管の風上側端部よりも風下側かつ、前記扁平管の上面の高さよりも上部に位置する突出部の上端部と、
前記扁平管の風上側端部よりも風上側かつ、前記扁平管の下面の高さよりも下部に位置し、前記連通凸部に近接する突出部の下端部と、が設けられ、
前記突出部の下端部は、重力方向で前記突出部よりも下に設けられる他の突出部の上端部よりも下方に位置する、熱交換器。 A plate-like fin having a plurality of notches formed at regular intervals in the longitudinal direction, which is the direction of gravity, on the leeward side;
a plurality of flat tubes attached to the plurality of notches;
a communicating convex portion provided in the longitudinal direction on the windward side of the plate-like fin;
a plurality of protrusions protruding from the planar portion of the fin on the leeward side of the communication protrusion,
The protrusion is
an upper end of a projecting portion located on the leeward side of the windward end of the flat tube and above the height of the upper surface of the flat tube;
a lower end portion of a projecting portion positioned on the windward side of the windward side end of the flat tube and below the height of the lower surface of the flat tube and adjacent to the communicating convex portion;
The heat exchanger, wherein the lower end of the protrusion is positioned below the upper end of another protrusion provided below the protrusion in the gravitational direction. 前記突出部は、前記連通凸部と平行になる平行部を前記突出部の端部の少なくとも一か所に設けた、請求項１に記載の熱交換器。 2. The heat exchanger according to claim 1, wherein said projecting portion has a parallel portion parallel to said communicating convex portion provided at least at one end of said projecting portion. 前記突出部は、風の流れ方向に連続して並ぶ複数のリブによって構成される、請求項１または２に記載の熱交換器。 3. The heat exchanger according to claim 1, wherein said protruding portion is composed of a plurality of ribs arranged continuously in the air flow direction. 前記複数のリブの風上側端部に設けられるリブは、風下側端部に設けられるリブよりも上端が高く位置するように形成される、請求項３に記載の熱交換器。 4. The heat exchanger according to claim 3, wherein the ribs provided on the windward end of the plurality of ribs are formed such that the upper end is positioned higher than the rib provided on the leeward end. 前記複数のリブの風上側端部に設けられるリブは、風下側端部に設けられるリブよりも下端が低く位置するように形成される、請求項３または４に記載の熱交換器。 5. The heat exchanger according to claim 3, wherein the ribs provided on the windward end of the plurality of ribs are formed such that the lower ends are positioned lower than the ribs provided on the leeward end. 前記扁平管は、重力方向に対して風上側端部が風下側端部よりも下方に位置する、請求項１ないし５のいずれか１項に記載の熱交換器。 6. The heat exchanger according to any one of claims 1 to 5, wherein the flat tube has an upwind side end located lower than a lee side end with respect to the direction of gravity.
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