JP5396580B2

JP5396580B2 - Air heat exchanger with built-in cold / hot water coil

Info

Publication number: JP5396580B2
Application number: JP2011240237A
Authority: JP
Inventors: 高光櫻庭; 奉昭井浦
Original assignee: 株式会社サクラプロリンク
Priority date: 2011-11-01
Filing date: 2011-11-01
Publication date: 2014-01-22
Anticipated expiration: 2031-11-01
Also published as: JP2013096647A

Description

本発明は、筒体内に冷温水コイルを内蔵して筒体内を貫流する空気を冷却又は加温する空気熱交換器に関するものであり、エアーコンディショニングの技術分野に属するものである。 The present invention relates to an air heat exchanger that incorporates a cold / hot water coil in a cylinder and cools or heats air flowing through the cylinder, and belongs to the technical field of air conditioning.

冷温水コイルにフィン群を配置して冷温水コイルで加熱又は冷却したフィン群によって、フィン群に吹付けた空気を加熱又は冷却することは、エアーコンディショニング分野の慣用技術であり、現在、冷温水コイルを使用した暖冷房手段は実用に供されている。 Heating or cooling the air blown to the fin group by the fin group arranged in the cold / hot water coil and heated or cooled by the cold / hot water coil is a common technique in the air conditioning field. A heating / cooling means using a coil has been put to practical use.

図８（Ａ）は、非特許文献１で挙げた従来例１の、コイルにフィン群を配置したタイプの冷温水コイルであり、冷温水を流水するパイプ群（コイル）を平行に配置して各パイプをヘアピンチューブで連通し、コイルの一端から冷温水を流入し、他端から流出させ、コイルに直交形態で平行に突出配置したフィン群に熱交換用空気を、各フィン間隔に平行形態に吹付けて、空気流に各フィンの側面から熱を伝達するものである。 FIG. 8A is a cold / hot water coil of the type of the conventional example 1 described in Non-Patent Document 1 in which a fin group is arranged on a coil, and a pipe group (coil) for flowing cold / hot water is arranged in parallel. Each pipe is connected with a hairpin tube, cold / hot water flows in from one end of the coil, flows out from the other end, and heat exchange air is formed in a group of fins that are arranged in parallel and projecting perpendicular to the coil. The heat is transferred to the air flow from the side surface of each fin.

そして、コイルの大きさは、コイルを通過する空気の風速を２〜３ｍ／ｓになるように決め、この風速の値でコイルを通過する風量を除して決め、冷温水コイルが空気流の大きな抵抗とならないように、且つ、コイル表面に発生する結露水を風下に飛散させないようにしている。
そして、冷却又は加温する空気流は、図８（Ａ）に示す如く、フィンに平行して冷温水コイルを貫流し、各フィンに均斉な伝達効果を発揮させている。 The size of the coil is determined by determining the wind speed of the air passing through the coil to be 2 to 3 m / s, and dividing the amount of air passing through the coil by the value of this wind speed. Condensation water generated on the coil surface is prevented from scattering to the lee so as not to cause a large resistance.
As shown in FIG. 8 (A), the air flow to be cooled or heated flows through the cold / hot water coil in parallel with the fins so that each fin exhibits a uniform transmission effect.

図８（Ｂ）は非特許文献１で挙げた従来例１の中の、ヘッダー式の冷温水コイルであって、往き側及び戻り側の２列のヘッダーから分岐してコイル群を配管するものであり、往き側ヘッダーからコイル内に冷温水を流入し、コイル内を通水して戻り側ヘッダーに還水するものであり、コイルの外側にプレート状のフィン群を直交形態で平列突出被覆し、冷却又は加熱用の空気流をフィン群と平行に貫流させ、各フィンに均斉な伝達作用を発揮させるものである。 FIG. 8B is a header-type hot / cold water coil in Conventional Example 1 listed in Non-Patent Document 1, which branches from two headers on the forward side and the return side, and pipes the coil group. Cold and warm water flows into the coil from the forward header, passes through the coil and returns to the return header, and plate-like fin groups are projected in parallel in an orthogonal form on the outside of the coil. The air flow for covering or cooling or heating is made to flow in parallel with the fin group so that each fin exhibits a uniform transmission action.

また、図８（Ｃ），（Ｄ）は、非特許文献２として挙げた従来例２のファンコイルユニットであって、図８（Ｃ）は一部破断斜視図、図８（Ｄ）は横断面図である。
即ち、従来例２のファンコイルユニットは、ファン（送風機）と、冷温水コイルと、ユニットフィルターとを１つのケーシングに収納したもので、冷暖房器として現在多用されているもので、モーターを中央として、左右に短尺（２５０〜４００mm）のシロッコファンを配置し、ファンボックスを介して、ファンの全長と略同寸の冷温水コイルを配置し、冷温水コイルに直交形態で平行配置したフィン群を還気流（空気流）が平行に貫流するものである。 8C and 8D show the fan coil unit of Conventional Example 2 cited as Non-Patent Document 2, in which FIG. 8C is a partially broken perspective view, and FIG. FIG.
In other words, the fan coil unit of Conventional Example 2 is a fan (blower), a cold / hot water coil, and a unit filter housed in a single casing, and is currently widely used as an air conditioner, with a motor at the center. A sirocco fan with a short length (250 to 400 mm) is arranged on the left and right sides, a chilled / hot water coil having approximately the same length as the entire length of the fan is arranged through a fan box, and a fin group arranged in parallel with the chilled / hot water coil in an orthogonal form The return airflow (airflow) flows through in parallel.

（株）オーム社、平成２２年３月２０日発行、第１版第４２刷、小原淳平編、「１００万人の空気調和」「第２章、空気線図の話」、「２．３項、空気の実際の状態変化を追う、５６頁、表２．１及び表２．２」OHM Co., Ltd., published on March 20, 2010, 1st edition, 42nd edition, Kohei Kohara, “1 million people's air conditioning”, “Chapter 2, story of air diagram”, “2.3 Section, Tracking the actual change in the state of air, page 56, Table 2.1 and Table 2.2 " （株）オーム社、平成２２年３月２０日発行、第１版第４２刷、小原淳平編、「第６章、空調方法さまざま」「６．３項、荷物を運ぶ経路」「１５６頁図６．１４、空調機とファンコイルユニットは親子関係、及び図６．１５、全水方式とルームクーラーとの比較」OHM Co., Ltd., issued March 20, 2010, 1st edition, 42nd edition, Kohei Kohara, “Chapter 6, Various air conditioning methods”, “6.3, Routes for luggage”, “Page 156 6.14, parent-child relationship between air conditioner and fan coil unit, and Fig. 6.15, comparison between whole water system and room cooler "

従来例１（図８（Ａ），（Ｂ））の冷温水コイルは、空気流をフィン群間に平行に貫流させるため、空気流は、スムーズに貫流するが、冷温水コイルの長さ方向に対する直交流となり、空気流の冷温水コイルへの供給貫流は、冷温水コイルの全長に対応した幅での貫流となるため、空気流のフィン群と接触時間が短くて熱交換効率が低く、しかも、空気流のフィン群に対する供給口及び放出口は、大寸、即ちフィン群の平行配置した寸法となる。
そのため、従来例１のタイプの該冷温水コイルシステムは、空気流に対する熱交換効率が低いにもかかわらず、冷温水コイルの全長、即ちフィン群の配置寸法、に対応する空気供給口幅及び空気吹出口幅が設定出来る広い環境でしか適用出来なく、広い配置スペースが必要である。 Since the cold / hot water coil of the prior art example 1 (FIGS. 8A and 8B) allows the air flow to flow in parallel between the fin groups, the air flow smoothly flows, but the length direction of the cold / hot water coil Since the flow through the air flow to the cold / hot water coil is a flow through the width corresponding to the entire length of the cold / hot water coil, the contact time with the fins of the air flow is short and the heat exchange efficiency is low. In addition, the supply port and the discharge port for the fin group of the air flow are large, that is, the dimension in which the fin group is arranged in parallel.
Therefore, the cold / hot water coil system of the type of Conventional Example 1 has an air supply port width and air corresponding to the entire length of the cold / hot water coil, that is, the arrangement size of the fin group, although the heat exchange efficiency with respect to the air flow is low. It can be applied only in a wide environment where the outlet width can be set, and a wide arrangement space is required.

また、従来例２（図８（Ｃ），（Ｄ））の冷温水コイルシステムにあっても、従来例１（図８（Ａ），（Ｂ））同様に、貫流空気は、空気供給側から空気吹出側に、フィン群内をフィンと平行にスムーズに貫流通過するため、空気流の供給口及び放出口の幅は、冷温水コイル全長、即ちフィン群の配置寸法に対応する幅寸法となり、貫流空気流の供給幅及び放出幅が十分採れる部位でしか適用出来ない。 Further, even in the cold / hot water coil system of Conventional Example 2 (FIGS. 8C and 8D), the through air is supplied to the air supply side as in Conventional Example 1 (FIGS. 8A and 8B). Therefore, the width of the air flow supply port and the discharge port is the width corresponding to the total length of the cold / hot water coil, that is, the arrangement size of the fin group. In addition, the present invention can be applied only to a portion where the supply width and discharge width of the once-through air flow can be taken sufficiently.

本発明は、従来の欠陥、即ち冷温水コイルの熱伝達機能を高めるために、長尺化すれば空気流の供給口の幅も冷温水コイルの長尺幅と対応して広げる必要があった問題点を解決するものであり、冷温水コイルの長手方向、即ちフィン群と直交方向に空気流を貫流させて、冷温水コイルから貫流空気流に高効率の熱伝達を可能とした新規な発明を提供するものである。 In order to increase the heat transfer function of the conventional defect, that is, the cold / hot water coil, the present invention has to increase the width of the air flow supply port correspondingly to the long width of the cold / hot water coil. A novel invention that solves the problem and allows high-efficiency heat transfer from the cold / hot water coil to the through-air flow by passing the air flow in the longitudinal direction of the cold / hot water coil, that is, in the direction orthogonal to the fin group. Is to provide.

本発明の空気熱交換器は、例えば図１に示す如く、循環パイプ２Ａに、フィン２Ｆ群を空気貫流間隔を保って並列密集形態で直交配置した長尺の冷温水コイル２を、筒本体１Ａ内にフィン２Ｆが筒本体１Ａの長手方向に直交した形態で、長手方向に配置し、吸気側１Ｓから筒本体１Ａ内に流入する吸引空気流ａ３は冷温水コイル２の上面空間Ｓｕに案内し、筒本体１Ａ内に吸気側１Ｓから供給側１Ｒに亘って順次通過風量が減少するように配置した風偏向板ｂｔ群によって、冷温水コイル２の上面空間Ｓｕから冷温水コイル２の下面空間Ｓｄへ、空気流を順次偏向案内して冷温水コイル２のフィン２Ｆ群の隙間を貫流案内し、供給側１Ｒからは、冷温水コイル２の下面空間Ｓｄからの空気流ａ４として流出させるものである。
For example, as shown in FIG. 1, the air heat exchanger according to the present invention includes a long chilled water coil 2 in which a fin 2F group is arranged orthogonally in a parallel dense form while maintaining an air flow-through interval on a circulation pipe 2A. in the form of fins 2F are orthogonal to the longitudinal direction of the tube body 1A within, and placed in the longitudinal direction, the suction air stream a3 flowing into the cylinder body 1A from the intake side 1S is guided to the upper surface space Su of cold and hot water coil 2 Then, the wind deflector bt group disposed in the cylinder body 1A so that the passing air volume decreases sequentially from the intake side 1S to the supply side 1R, thereby the upper surface space Su of the cold / hot water coil 2 to the lower surface space of the cold / hot water coil 2 The air flow is sequentially deflected and guided to Sd and guided through the gaps of the fins 2F group of the chilled / hot water coil 2, and flows out from the supply side 1R as the airflow a4 from the lower surface space Sd of the chilled / hot water coil 2. is there.

この場合、冷温水コイル２は、従来の冷温水コイル同様に、並列連通の循環パイプ２Ａの外周に平板の放熱用のフィン２Ｆ群を密集平行形態に配置し、循環パイプ２Ａに冷水又は温水を循環させるものであるが、熱交換用の空気の流し方向は、冷温水コイルの長手方向、即ち放熱フィン２Ｆ群に直交方向に熱交換用空気を流し、放熱フィン２Ｆ群によって空気を冷却又は加熱するものである。 In this case, the cold / hot water coil 2 is arranged in the form of a dense parallel arrangement of flat heat dissipating fins 2F on the outer periphery of the parallel communication circulation pipe 2A, and the cold / hot water is supplied to the circulation pipe 2A. Although the heat exchange air is circulated, the heat exchange air flows in the longitudinal direction of the cold / hot water coil, that is, the heat exchange air flows in a direction orthogonal to the heat radiation fins 2F group, and the air is cooled or heated by the heat radiation fins 2F group. To do.

従って、典型的には、図５に示す如く、高熱伝導性の鋼管の循環パイプ２Ａを千鳥状に上下おのおの８本配置して、端部をヘアピンチューブ２Ｂ及びＵベント２Ｃで一体化連通し、全循環パイプ２Ａ群が貫通形態で、放熱フィン２Ｆ群を循環パイプ２Ａ群の外周に平行密集配置（標準間隔：０．５mm）したもので、長さＬ２が６５０mm、幅Ｗ２が２０３mm、厚さ（高さ）ｈ２が４４mm、各フィン２Ｆ間の間隔０．５mmのものである。 Therefore, typically, as shown in FIG. 5, eight high-thermal conductivity steel pipe circulation pipes 2A are arranged in a staggered manner on the upper and lower sides, and the ends thereof are integrally communicated with the hairpin tube 2B and the U vent 2C. The entire circulation pipe 2A group is a through configuration, and the radiating fins 2F group are arranged in parallel and densely on the outer periphery of the circulation pipe 2A group (standard interval: 0.5 mm). The length L2 is 650 mm, the width W2 is 203 mm, and the thickness (Height) h2 is 44 mm, and the interval between the fins 2F is 0.5 mm.

また、筒本体１Ａは、長尺の冷温水コイル２を長手方向に収納配置出来て、長尺の冷温水コイル２の、上面には、冷温水コイル２の上面を長手方向に空気流を流す上面空間Ｓｕが、下面には、上面空間Ｓｕから分流して冷温水コイル２を横断貫流した空気流を冷温水コイル２の下面に沿って送風するための下面空間Ｓｄが形成出来れば良く、筒本体１Ａの断面形状は、円形でも、楕円形でも、方形でも良く、収納する冷温水コイル２の断面形状を勘案して決定すれば良く、上下分割型でも、一体型でも良いが、上側函体１Ｕと下側函体１Ｄとの分割型であれば、冷温水コイル２の収納装着作業、及び風偏向板ｂｔ群の配置作業性が容易となり、断面方形の分割型は特に好都合である。 Further, the cylinder main body 1A can accommodate and arrange the long chilled / hot water coil 2 in the longitudinal direction, and the upper surface of the long chilled / hot water coil 2 causes the upper surface of the cold / hot water coil 2 to flow in the longitudinal direction. The upper surface space Su may be formed on the lower surface so that a lower surface space Sd can be formed on the lower surface to blow an air flow that is diverted from the upper surface space Su and flows through the cold / hot water coil 2 along the lower surface of the cold / hot water coil 2. The cross-sectional shape of the main body 1A may be circular, elliptical, or rectangular, and may be determined in consideration of the cross-sectional shape of the chilled / hot water coil 2 to be accommodated. If the split type of 1U and lower box 1D is used, the storage / mounting operation of the cold / hot water coil 2 and the arrangement workability of the wind deflector bt group are facilitated, and the split type having a square cross section is particularly advantageous.

また、風偏向板ｂｔ群は、冷温水コイル２のフィン２Ｆ群の上面と筒本体１Ａの内面との間に、通過風量が、吸気側１Ｓ、即ち前部から、供給側１Ｒ、即ち後部に順次減少するように、且つ、冷温水コイル２の、上面空間Ｓｕから各フィン２Ｆ間の隙間を介して、下面空間Ｓｄに空気流が偏向出来るように、複数板の板材を配置すれば良く、風偏向板ｂｔ群は、例えば、冷温水コイル２の密集平行配置（標準：０．５mm間隔配置）形態のフィン２Ｆ群間に差し込み形態で傾斜立設しても良く、筒本体１Ａの内面に、幅方向に差し渡し状に配置しても良い。 Further, the wind deflector bt group has a passing air volume between the upper surface of the fins 2F group of the cold / hot water coil 2 and the inner surface of the cylinder body 1A from the intake side 1S, that is, the front part, to the supply side 1R, that is, the rear part. A plurality of plates may be arranged so that the airflow can be deflected to the lower surface space Sd from the upper surface space Su of the cold / hot water coil 2 through the gaps between the fins 2F so as to decrease sequentially. For example, the wind deflector bt group may be inclined and inserted in an interleaved manner between the fins 2F group of the cold and hot water coils 2 in a closely parallel arrangement (standard: 0.5 mm interval arrangement). Alternatively, they may be arranged in the form of a span in the width direction.

また、筒本体１Ａに吸引した空気流ａ３を上面空間Ｓｕに流入し、下面空間Ｓｄから吹出し空気流ａ４として流出供給させるためには、筒本体１Ａの吸気側１Ｓにあっては、冷温水コイル２の下面の前端と筒本体１Ａの下半内面とを、筒本体１Ａの供給側１Ｒにあっては、冷温水コイル２の上面２Ｕ後端と筒本体１Ａの上半内面とを、空気流遮断すれば良い。
この場合、冷温水コイル２の両側面と筒本体１Ａの内側面との隙間も、空気流遮断するのが好ましい。 Further, in order to allow the air flow a3 sucked into the cylinder main body 1A to flow into the upper surface space Su and to flow out as the blown air flow a4 from the lower surface space Sd, a cold / hot water coil is provided on the intake side 1S of the cylinder main body 1A. 2 and the lower half inner surface of the cylinder body 1A on the supply side 1R of the cylinder body 1A, the air flow between the upper surface 2U rear end of the cold / hot water coil 2 and the upper half inner surface of the cylinder body 1A Block it.
In this case, it is preferable that the air flow is also cut off between the both side surfaces of the cold / hot water coil 2 and the inner side surface of the cylinder main body 1A.

従って、本発明の空気熱交換器にあっては、長尺の筒本体１Ａ内に長手方向に流入する前方からの吸引空気流ａ３は、冷温水コイル２の上面空間Ｓｕに流入して上面空間Ｓｕを高圧域とし、各風偏向板ｂｔ群によって、幅方向（径方向）に密集並列した各フィン２Ｆ群の隙間を、高圧域の上面空間Ｓｕから低圧域の下面空間Ｓｄに貫流して冷温水コイル２の下面空間Ｓｄに流入するため、吸引空気流ａ３は、風偏向板ｂｔ群の整流偏向作用により、冷温水コイル２の前端から後端までの全長に亘ってフィン２Ｆ群による均斉な熱伝達を受けて、冷却空気流又は加熱空気流として供給側１Ｒから流出する。 Therefore, in the air heat exchanger of the present invention, the suction air flow a3 flowing from the front flowing into the long cylindrical body 1A in the longitudinal direction flows into the upper surface space Su of the cold / hot water coil 2 and flows into the upper surface space. Su is a high pressure region, and the wind deflector plates bt group causes the gaps between the fins 2F group densely arranged in parallel in the width direction (radial direction) to flow from the upper surface space Su of the high pressure region to the lower surface space Sd of the low pressure region. Since the air flows into the lower surface space Sd of the water coil 2, the suction air flow a <b> 3 is uniform by the fins 2 </ b> F group over the entire length from the front end to the rear end of the cold / hot water coil 2 due to the rectifying and deflecting action of the wind deflector bt group. Upon receiving heat transfer, it flows out from the supply side 1R as a cooling air flow or a heating air flow.

そして、吸引空気流ａ３は、後端の閉止された上面空間Ｓｕでの加圧状態から、前端の閉止された低圧域の下面空間Ｓｄへの流入と成るため、各フィン２Ｆ間の隙間を加圧状態の空気が貫流可能な狭い間隔（標準：０．５mm）を、スムーズに貫通し、各フィン２Ｆによって好適に熱伝達を受けた下面空気流ａ４として、供給側１Ｒから流出し、空気熱交換器１内を貫流する吸引空気流ａ３及び供給空気流ａ４は、フィン２Ｆ群と直交方向、即ち冷温水コイル２の循環パイプ２Ａと同方向、に貫流させても、高効率の熱交換が可能となる。 Since the suction air flow a3 flows from the pressurized state in the upper surface space Su closed at the rear end to the lower surface space Sd in the low pressure region closed at the front end, a gap between the fins 2F is added. The air flows out from the supply side 1R as a lower surface air flow a4 that smoothly passes through a narrow space (standard: 0.5 mm) through which air in a pressurized state can flow and receives heat transfer suitably by the fins 2F. Even if the suction air flow a3 and the supply air flow a4 flowing through the heat exchanger 1 flow in a direction orthogonal to the fins 2F group, that is , in the same direction as the circulation pipe 2A of the cold / hot water coil 2 , high-efficiency heat exchange is achieved. Is possible.

そのため、冷温水コイル２による貫流空気への熱交換原理は、従来例同様に、各フィン２Ｆ間の隙間を貫流させて熱交換するが、貫流空気流は、冷温水コイルの幅、即ちフィン２Ｆ群の幅に対する直交方向、即ち冷温水コイル２の循環パイプ２Ａの長さ方向での流入流出となり、熱交換能力は、貫流空気の、吸引口及び供給口の寸法、即ち筒本体１Ａの断面寸法とは無関係で、冷温水コイル２の長手方向寸法でのフィン２Ｆの枚数の増域で決定出来ることとなり、本発明の空気熱交換器１は、フィン２Ｆ間隔が極小（０．５mm）と出来ることと相俟って、幅寸法、即ちフィン２Ｆの幅寸法が小でも、フィン２Ｆの枚数に依存する高効率の熱交換機能が付与出来、本発明の空気熱交換器１は、天井裏等の小スペースの部位にも配置可能な、適用範囲の自由度の高い、小型で高性能な空気熱交換器となる。 Therefore, the heat exchange principle of the cold / hot water coil 2 to the once-through air is the same as in the prior art, in which heat is exchanged through the gaps between the fins 2F, but the once-through air flow is the width of the cold / hot water coil, that is, the fin 2F. It becomes inflow / outflow in the direction orthogonal to the width of the group, that is, in the length direction of the circulation pipe 2A of the cold / hot water coil 2, and the heat exchange capacity is the dimension of the suction port and the supply port of the through-flow air, that is, the cross-sectional dimension of the cylinder body 1A. The air heat exchanger 1 according to the present invention can minimize the interval between the fins 2F (0.5 mm), regardless of the number of fins 2F in the longitudinal dimension of the cold / hot water coil 2. Combined with this, even if the width dimension, that is, the width dimension of the fin 2F is small, a high-efficiency heat exchange function depending on the number of fins 2F can be imparted. Can be placed in small space areas High degree of freedom of the circumference, a high performance air heat exchanger compact.

また、本発明の空気熱交換器にあっては、図１（Ａ）に示す如く、筒本体１Ａの上面からは洗浄ノズル９Ａ群を間隔配置し、且つ筒本体１Ａの前部上面からは加湿用の噴霧ノズル１０Ａを配置し、筒本体１Ａの、後端内底面には止水板８Ｒを配置し、止水板８Ｒの前部からはドレンパイプ８Ａを垂下するのが好ましい。 In the air heat exchanger of the present invention, as shown in FIG. 1 (A), the group of cleaning nozzles 9A is spaced from the upper surface of the cylinder body 1A, and the humidification is performed from the front upper surface of the cylinder body 1A. It is preferable that a spray nozzle 10A is disposed, a water stop plate 8R is disposed on the inner bottom surface of the rear end of the cylinder body 1A, and the drain pipe 8A is suspended from the front portion of the water stop plate 8R.

この場合、洗浄ノズル９Ａ群としては、円錐形状に放水する慣用の噴霧ノズルを、洗浄回路に連通形態で採用すれば良い。
また、加湿ノズルは、慣用の加圧機能内蔵の噴霧ノズルを採用し、慣用の湿度検知器で制御すれば良い。 In this case, as the cleaning nozzle 9A group, a conventional spray nozzle that discharges water in a conical shape may be employed in a communication form with the cleaning circuit.
The humidifying nozzle may be a conventional spray nozzle with a built-in pressurizing function and may be controlled by a conventional humidity detector.

また、止水板８Ｒは、筒本体１Ａの底面に溜まる水が送風と共に飛散するのを阻止出来れば良く、筒本体１Ａの底面から堰板を起立させれば良い。
また、ドレンパイプ８Ａは筒本体１Ａ内に溜まる水を排水出来れば良く、図１（Ａ）に示す如く、筒本体１Ａの底面で、後端の止水板８Ｒの前部近傍に配置すれば良く、筒本体１Ａの底面の所望位置（標準:後端から９０mm位置）にドレンパイプ用の孔を開け、ドレンパイプ８Ａ（標準：外径２０mm、肉厚１mm、長さ４０mmのステンレス製パイプ）を垂下固定すれば良い。 The water stop plate 8R only needs to prevent the water accumulated on the bottom surface of the cylinder main body 1A from being scattered along with the air blow, and the dam plate may be raised from the bottom surface of the cylinder main body 1A.
The drain pipe 8A only needs to be able to drain the water accumulated in the cylinder main body 1A. As shown in FIG. 1A, the drain pipe 8A is disposed near the front portion of the water stop plate 8R at the rear end on the bottom surface of the cylinder main body 1A. Well, drill a hole for the drain pipe at the desired position (standard: 90 mm from the rear end) of the bottom surface of the cylinder body 1A, and drain pipe 8A (standard: stainless steel pipe with outer diameter 20mm, wall thickness 1mm, length 40mm) Can be fixed by drooping.

従って、本発明の空気熱交換器１は、図２（Ａ）に示す如く、前端に吸気側ダクト管３Ｄを、後端に供給側ダクト管４Ｄが接続出来る場所であれば設置可能であり、冷温水コイル２によって、筒本体１Ａ内を吸気側ダクト管３Ｄから供給側ダクト管４Ｄへと流れる貫流空気に、夏季には冷却作用と除湿とが出来、冬季には暖房加熱と噴霧ノズル１０Ａでの必要湿度の付与が出来、居室内への供給空気流ａ５に、所望の除湿冷房及び加湿暖房が出来る。 Therefore, as shown in FIG. 2A, the air heat exchanger 1 of the present invention can be installed in a place where the intake side duct pipe 3D can be connected to the front end and the supply side duct pipe 4D can be connected to the rear end. The cold / hot water coil 2 can cool and dehumidify the through-flow air flowing from the intake side duct pipe 3D to the supply side duct pipe 4D in the cylinder body 1A in the summer, and heating and spray nozzles 10A in the winter. The required humidity can be given, and desired dehumidification cooling and humidification heating can be performed on the supply air flow a5 into the living room.

また、空気熱交換器１内の冷温水コイル２の周面、即ちフィン２Ｆ周面に付着した埃やゴミも、冷温水コイル２の上方に間隔配置した洗浄ノズル９Ａ群での定期的な洗浄作用によって洗い流し、冷温水コイル２は、設計値どおりの熱交換機能を持続出来る。
そして、冷温水コイル２の、冷却による空気除湿作用で生じる結露水も、洗浄作用で生じる流下水も、止水板８Ｒによって空気熱交換器１からの飛散を生ずること無く、ドレンパイプ８Ａを介して排水処理出来る。 Also, dust and debris adhering to the peripheral surface of the cold / hot water coil 2 in the air heat exchanger 1, that is, the peripheral surface of the fin 2 </ b> F, are periodically cleaned by the cleaning nozzle 9 </ b> A group disposed above the cold / hot water coil 2. The cold / hot water coil 2 can be maintained by the heat exchange function as designed.
And the dew condensation water generated by the air dehumidifying action by the cooling and the flowing water generated by the cleaning action of the cold / hot water coil 2 are not scattered from the air heat exchanger 1 by the water stop plate 8R, and are passed through the drain pipe 8A. Can be treated.

そのため、本発明の空気熱交換器１は、居室内に必要な除湿作用、加湿作用を付与した冷房空気又は暖房空気の供給、及び空気熱交換器１内の必要洗浄作用が、水漏れの心配無く実施出来、輻射用パネルヒーター等の一義的な冷暖房システムに、空気調和作用を伴った二義的冷暖房手段として併用出来、空気熱交換器１の配置位置の自由度と相俟って、エアーコンディショニングシステムの構築の自由度が向上する。 For this reason, the air heat exchanger 1 of the present invention is concerned with water leakage due to the necessary dehumidifying action in the living room, the supply of cooling air or heating air with a humidifying action, and the necessary cleaning action in the air heat exchanger 1. It can be implemented without any problem, and it can be used in combination with a unique air conditioning system such as a panel heater for radiation, as a secondary air conditioning unit with air conditioning, and in combination with the degree of freedom of the location of the air heat exchanger 1, The degree of freedom in building a conditioning system is improved.

また、本発明の空気熱交換器にあっては、例えば図２に示す如く、筒本体１Ａは、上側函体１Ｕと下側函体１Ｄとを上下に連接一体化した断面方形であり、風偏向板ｂｔ群を上側函体１Ｕの両側板１Ｆ間に差し渡し形態に配置し、冷温水コイル２は、フィン２Ｆ群の上面を下側函体１Ｄの上端縁Ｆｕと整合配置するのが好ましい。 In the air heat exchanger of the present invention, for example, as shown in FIG. 2, the cylinder main body 1A has a rectangular cross section in which the upper box 1U and the lower box 1D are connected and integrated vertically. It is preferable that the deflection plate bt group is disposed between both side plates 1F of the upper box 1U, and the cold / hot water coil 2 is arranged so that the upper surface of the fin 2F group is aligned with the upper end edge Fu of the lower box 1D.

この場合、筒本体１Ａは、断面コ字形の上側函体１Ｕと下側函体１Ｄとを上下接合一体化して組み立てることとなるため、上下函体１Ｕ，１Ｄは、共に板金加工で準備出来、上下函体１Ｕ，１Ｄを一体化する以前に、風偏向板ｂｔの配置は、上側函体１Ｕの両側板１Ｆ間の所定位置に、所定の風偏向板ｂｔを、差し渡し状に溶接固定すれば良く、下側函体１Ｄでは、止水板８Ｒ及びドレンパイプ８Ａを加工形成した後に、冷温水コイル２の上面を下側函体１Ｄの両側板１Ｆの上端縁Ｆｕに整合してボルトナット手段で固定出来、上側函体１Ｕと下側函体１Ｄとの一体化は、上下両側板１Ｆをオーバーラップ形態でボルト締着すれば良い。 In this case, since the cylinder body 1A is assembled by vertically joining and integrating the upper box 1U and the lower box 1D having a U-shaped cross section, the upper and lower boxes 1U and 1D can be prepared by sheet metal processing. Before the upper and lower cases 1U and 1D are integrated, the wind deflector bt is arranged by fixing the predetermined wind deflector bt at a predetermined position between both side plates 1F of the upper case 1U by welding. In the lower case 1D, after the water stop plate 8R and the drain pipe 8A are processed and formed, the upper surface of the cold / hot water coil 2 is aligned with the upper end edges Fu of the both side plates 1F of the lower case 1D, and the bolt nut means The upper box 1U and the lower box 1D can be integrated by bolting the upper and lower side plates 1F in an overlapping manner.

尚、冷温水コイル２の前端と下面空間Ｓｄとの閉止、及び冷温水コイル２の後端と上面空間Ｓｕとの閉止も、上下函体１Ｕ，１Ｄの一体化前に、必要に応じて堰板手段やゴム板等のシール手段で容易に実施出来る。
従って、本発明の空気熱交換器１の製作は、筒本体１Ａ内に配置する風偏向板ｂｔ群、冷温水コイル２、止水板８Ｒ、ドレンパイプ８Ａ等の内装部材が、上側函体１Ｕ及び下側函体１Ｄの開放形態での装着作業となるため、適正位置に内装部材を備えた、品質にばらつきの無い高性能製品として、量産にも適した合理的作業で、容易に実施出来る。 It should be noted that the front end of the cold / hot water coil 2 and the lower surface space Sd and the rear end of the cold / hot water coil 2 and the upper surface space Su are also closed as needed before the upper and lower cases 1U and 1D are integrated. It can be easily implemented by a sealing means such as a plate means or a rubber plate.
Therefore, the air heat exchanger 1 according to the present invention is manufactured in such a manner that the interior members such as the wind deflector bt group, the cold / hot water coil 2, the water stop plate 8R, and the drain pipe 8A arranged in the cylinder body 1A are arranged in the upper box 1U. Since the lower box 1D is mounted in an open form, it can be easily implemented with reasonable work suitable for mass production as a high-performance product with interior components at the appropriate position and without variations in quality. .

また、本発明の空気熱交換器１は、図２（Ｂ），（Ｄ）に示す如く、上側函体１Ｕの両側板１Ｆは、吸気側１Ｓから供給側１Ｒへと側板１Ｆが上下幅を減じる傾斜形態であり、下側函体１Ｄの両側板１Ｆは、吸気側１Ｓから供給側１Ｒへと上下幅を増大させる傾斜形態であり、冷温水コイル２は、下側函体１Ｄ内に上面を両側板１Ｆの上端縁Ｆｕと整合して配置し、上側函体１Ｕの両側板１Ｆ間には、吸気側１Ｓへ傾斜上昇する風偏向板ｂｔ群を差し渡し状に配置するのが好ましい。 Further, in the air heat exchanger 1 of the present invention, as shown in FIGS. 2B and 2D, the side plates 1F of the upper box 1U have a side plate 1F having a vertical width from the intake side 1S to the supply side 1R. The lower side box 1D has an inclined form in which both side plates 1F are inclined to increase the vertical width from the intake side 1S to the supply side 1R, and the cold / hot water coil 2 has an upper surface in the lower case 1D. Are arranged in alignment with the upper end edge Fu of the side plates 1F, and a group of wind deflector plates bt inclined and rising to the intake side 1S is arranged between the side plates 1F of the upper box 1U.

この場合、上側函体１Ｕの両側板１Ｆと下側函体１Ｄの両側板１Ｆとは、合体一体化するものであるから、傾斜角度は同一とすれば良く、典型的には７．５°の傾斜角である。
また、上側函体１Ｕと下側函体１Ｄとは、両側板１Ｆ相互で接続一体化するものであり、上下側板１Ｆ相互は、重ね幅Ｊｕ（標準：１０mm）で、重層形態としてねじ締着すれば良い。 In this case, since both side plates 1F of the upper box 1U and both side plates 1F of the lower box 1D are united and integrated, the inclination angles may be the same, typically 7.5 °. The inclination angle.
The upper case 1U and the lower case 1D are connected and integrated with each other on both side plates 1F. The upper and lower side plates 1F are overlapped with each other with a stacking width Ju (standard: 10 mm) and screwed together as a multilayered form. Just do it.

従って、冷温水コイル２の、前端は下側函体１Ｄの底板１Ｂに当接形態に、後端は上側函体１Ｕの天板１Ｔに当接形態に配置出来るため、冷温水コイル２の前端と後端との筒本体１Ａに対する空気流閉止構造は、図４に示す如く、当接部位にゴム板１Ｇを介在するだけで容易に実施出来、吸気側１Ｓから筒本体１Ａ内に流入する空気流ａ３の上面空間Ｓｕへの流入、及び筒本体１Ａ内から居室内への供給空気流ａ４の下面空間Ｓｄからの流出機能付与が簡便に実施出来る。 Therefore, since the front end of the cold / hot water coil 2 can be arranged in contact with the bottom plate 1B of the lower box 1D and the rear end can be arranged in contact with the top board 1T of the upper box 1U, the front end of the cold / hot water coil 2 can be arranged. As shown in FIG. 4, the air flow closing structure for the cylinder main body 1A at the rear end and the rear end can be easily implemented only by interposing the rubber plate 1G at the contact portion, and the air flowing into the cylinder main body 1A from the intake side 1S. Inflow of the flow a3 into the upper surface space Su and provision of an outflow function from the lower surface space Sd of the supply air flow a4 from the cylinder main body 1A to the living room can be easily performed.

そして、冷温水コイル２の、上面空間Ｓｕは前部から後部へ漸減し、下面空間Ｓｄは前部から後部へ漸増するため、吸気側１Ｓから筒本体１Ａ内へ流入する空気流は、上面空間Ｓｕでは、入口から奥へと圧力が漸増する高圧状態となり、下面空間Ｓｄで低圧状態となり、流入空気流ａ３は、冷温水コイル２の前後全長に亘って、各フィン２Ｆ間の、均斉な隙間貫流及び均斉な熱交換作用が期待出来る。 And since the upper surface space Su of the cold / hot water coil 2 gradually decreases from the front part to the rear part and the lower surface space Sd increases gradually from the front part to the rear part, the air flow flowing into the cylinder body 1A from the intake side 1S In Su, a high pressure state in which the pressure gradually increases from the inlet to the back, a low pressure state in the lower surface space Sd, and the inflow air flow a3 is a uniform gap between the fins 2F across the entire length of the cold / hot water coil 2. Throughflow and uniform heat exchange can be expected.

従って、冷温水コイルの傾斜配置は、前端下面と筒本体１Ａの底面、及び後端上面の筒本体１Ａの上面との空気流閉止が簡便に実施出来ると共に、上面空間Ｓｕでは前端から後端へと圧力が増加した高圧域となって、風偏向板ｂｔ群の助力の下に、冷温水コイル２の前後全長に亘って、均斉なフィン２Ｆ間の間隙（標準：０．５mm）の貫流作用が得られ、各フィン２Ｆ群による均斉、且つ高効率の熱伝達を奏し、空気熱交換器１の高効率化を達成する。 Therefore, the inclined arrangement of the cold / hot water coils can easily close the air flow between the lower surface of the front end, the bottom surface of the cylinder main body 1A, and the upper surface of the cylinder main body 1A of the rear end upper surface, and from the front end to the rear end in the upper surface space Su. With the help of the wind deflector bt group, the flow through the gap between the uniform fins 2F (standard: 0.5 mm) is provided over the entire length of the cold / hot water coil 2 with the help of the wind deflector bt group. Is achieved, and uniform and high-efficiency heat transfer is achieved by each fin 2F group, and high efficiency of the air heat exchanger 1 is achieved.

また、本発明の空気熱交換器１にあっては、図１に示す如く、冷温水コイル２の前端の下面と両側面、及び冷温水コイル２後端の上面と両側面とは、ゴム板１Ｇを配置して、下面空間Ｓｄ前端、及び上面空間Ｓｕ後端を空密処理し、止水板８Ｒは、下側函体１Ｄの底板１Ｂから筒本体１Ａの高さの３５±５％の高さまで、後方に傾斜上昇配置するのが好ましい。 Moreover, in the air heat exchanger 1 of this invention, as shown in FIG. 1, the lower surface and both side surfaces of the front end of the cold / hot water coil 2, and the upper surface and both side surfaces of the rear end of the cold / hot water coil 2 are rubber plates. 1G is disposed and the front end of the lower surface space Sd and the rear end of the upper surface space Su are airtightly treated, and the water stop plate 8R is 35 ± 5% of the height of the cylinder body 1A from the bottom plate 1B of the lower box 1D. It is preferable to arrange it to be inclined and raised to the height.

この場合、止水板８Ｒの傾斜は、下面空間Ｓｄから流出する空気流ａ４が斜め上昇流として偏向出来、且つ底板１Ｂ上の滞溜水の後方への流出が阻止出来れば良く、典型的には、図４（Ａ）に示す如く、空気熱交換器１の筒本体１Ａの高さｈ１（標準：１４４mm）に対し止水板８Ｒは３８％高さ（標準：４０mm）で、傾斜は底板１Ｂから仰角６０°で起立させれば良い。 In this case, the water stop plate 8R is inclined as long as the air flow a4 flowing out from the lower surface space Sd can be deflected as an oblique upward flow, and the outflow of stagnant water on the bottom plate 1B to the rear can be prevented. As shown in FIG. 4A, the water stop plate 8R is 38% height (standard: 40 mm) with respect to the height h1 (standard: 144 mm) of the cylinder body 1A of the air heat exchanger 1, and the inclination is the bottom plate. What is necessary is just to stand at an elevation angle of 60 ° from 1B.

また、下面空間Ｓｄの前端及び上面空間Ｓｕの後端に対するゴム板１Ｇによる空密処理は、図４（Ｂ），（Ｃ），（Ｄ）に示す如く、冷温水コイル２の、前端にあっては、底板１Ｂに対してゴム板１Ｇを介在させ、後端にあっては、ゴム板１Ｇを介在させ、側面にあっては、フィン２Ｆ群の側面と両側板１Ｆ間にゴム板１Ｇを介在させれば良い。 Further, the airtight treatment by the rubber plate 1G on the front end of the lower surface space Sd and the rear end of the upper surface space Su is applied to the front end of the cold / hot water coil 2 as shown in FIGS. 4 (B), (C), (D). The rubber plate 1G is interposed between the bottom plate 1B, the rubber plate 1G is interposed at the rear end, and the rubber plate 1G is interposed between the side surface of the fin 2F group and the side plates 1F at the side surface. What is necessary is just to interpose.

従って、筒本体１Ａ内の空気流挙動は、吸気側１Ｓから圧送状態で流入する空気流ａ３が冷温水コイル２のフィン２Ｆ群の上面空間Ｓｕにのみ流入して高圧状態となり、流入空気流ａ３は、全てが風偏向板ｂｔ群によってフィン２Ｆ群面に指向して各フィン２Ｆ間の隙間（標準：０．５mm）から低圧の下面空間Ｓｄ内に流入し、下面空間Ｓｄの空気流ａ４は、並列密集フィン２Ｆの隙間通過によって高効率の熱交換を受けて供給空気流ａ５として居室内に放出される。
そして、下面空間Ｓｄの空気流ａ４は、筒本体１Ａ後端の傾斜した止水板８Ｒによる上昇偏向作用により、フィン２Ｆ群の下面に沿った流出となって、熱交換効率の向上が期待出来る。 Accordingly, the air flow behavior in the cylinder main body 1A is such that the air flow a3 flowing in from the intake side 1S in a pumped state flows into only the upper surface space Su of the fins 2F group of the cold / hot water coil 2 to be in a high pressure state. Is directed toward the fin 2F group surface by the wind deflector bt group and flows into the low pressure lower surface space Sd from the gaps (standard: 0.5 mm) between the fins 2F, and the air flow a4 in the lower surface space Sd is The high-efficiency heat exchange is performed by passing through the gaps between the parallel dense fins 2F, and is discharged into the living room as a supply air flow a5.
The air flow a4 in the lower surface space Sd becomes an outflow along the lower surface of the fin 2F group due to the upward deflection action by the inclined water stop plate 8R at the rear end of the cylinder body 1A, and improvement in heat exchange efficiency can be expected. .

本発明の空気熱交換器は、筒本体１Ａに冷温水コイル２を長手方向に、即ち循環パイプ２Ａを筒本体１Ａと同一長手方向に配置し、空気熱交換器１内に圧送する処理用の空気流ａ３を冷温水コイル２の長手方向、即ちフィン２Ｆ群に直交方向に流入させて、筒本体１Ａ内では、風偏向板ｂｔ群によって各フィン２Ｆ間の隙間を貫流させて熱交換するため、空気熱交換器１の機能増大は、筒本体１Ａの断面積を変更することなく、冷温水コイル２の長さ寸法、即ちフィン２Ｆ群の配置枚数の増加で対応出来、縦横スペースの狭い場所への適用が可能な、断面小型の高性能な空気熱交換器となる。 The air heat exchanger according to the present invention is for processing in which the cold / hot water coil 2 is arranged in the longitudinal direction in the cylinder body 1A, that is, the circulation pipe 2A is arranged in the same longitudinal direction as the cylinder body 1A, and pumped into the air heat exchanger 1. In order to exchange heat by letting the air flow a3 flow in the longitudinal direction of the cold / hot water coil 2, that is, in the orthogonal direction to the fins 2F group, and through the gaps between the fins 2F by the wind deflection plates bt group in the cylinder body 1A. The increase in the function of the air heat exchanger 1 can be accommodated by increasing the length of the cold / hot water coil 2, that is, the number of arranged fins 2F, without changing the cross-sectional area of the cylinder main body 1A. It becomes a high-performance air heat exchanger with a small cross section that can be applied to the above.

また、筒本体１Ａ内は、冷温水コイル２で上面空間Ｓｕと下面空間Ｓｄとに区画して、筒本体１Ａ内に圧送する熱交換用の空気流ａ３は上面空間Ｓｕに流入し、下面空間Ｓｄからのみの供給空気流ａ４として放出するため、筒本体１Ａの空気流の挙動は、圧送された高圧域としての上面空間Ｓｕから低圧域としての下面空間Ｓｄへの、冷温水コイル２の上下貫流、即ち各並列密集フィン２Ｆ間の隙間の貫流となり、フィン２Ｆ群の密集（標準：０．５mm間隔）配置した冷温水コイル２の全長に亘る均斉な熱交換作用が達成出来る。 Further, the inside of the cylinder main body 1A is partitioned into the upper surface space Su and the lower surface space Sd by the cold / hot water coil 2, and the air flow a3 for heat exchange pumped into the cylinder main body 1A flows into the upper surface space Su, and the lower surface space In order to discharge as the supply air flow a4 only from Sd, the behavior of the air flow of the cylinder main body 1A is as follows: the upper and lower sides of the cold / hot water coil 2 from the upper surface space Su as the high pressure region to the lower surface space Sd as the low pressure region Throughflow, that is, through the gaps between the parallel dense fins 2F, can achieve a uniform heat exchange action over the entire length of the cold / hot water coil 2 in which the fins 2F are densely arranged (standard: 0.5 mm intervals).

従って、熱交換用空気流ａ３を冷温水コイル２に対する長手方向、即ち各フィン２Ｆに対する直交方向に流すことにより、本発明の空気熱交換器は、従来の各フィン２Ｆ群と同方向に流す熱交換と、フィン２Ｆ間隔では同等、若しくはそれ以上の熱交換作用の期待出来る性能でありながら、断面積が小さくて、配置の自由度の高い、小型の、高性能な空気熱交換器となる。 Accordingly, the air heat exchanger according to the present invention causes the heat to flow in the same direction as the conventional fins 2F group by flowing the heat exchange air flow a3 in the longitudinal direction with respect to the cold / hot water coil 2, that is, in the orthogonal direction to each fin 2F. It is a small, high-performance air heat exchanger having a small cross-sectional area and a high degree of freedom in arrangement, while the performance can be expected to be equal to or higher than the exchange and the fin 2F interval.

本発明の空気熱交換器の説明図であって、（Ａ）は縦断側面図、（Ｂ）は（Ａ）の矢印Ｂ視図、（Ｃ）は（Ａ）の矢印Ｃ視図である。It is explanatory drawing of the air heat exchanger of this invention, Comprising: (A) is a vertical side view, (B) is the arrow B view of (A), (C) is the arrow C view of (A). 空気熱交換器の説明図であって、（Ａ）は使用状態の側面図、（Ｂ）は上側函体の側面図、（Ｃ）は上側函体の前面図、（Ｄ）は下側函体の側面図、（Ｅ）は下側函体の前面図、（Ｆ）は上下函体の接続状態説明図である。It is explanatory drawing of an air heat exchanger, (A) is a side view of a use condition, (B) is a side view of an upper side box, (C) is a front view of an upper side box, (D) is a lower side box. A side view of a body, (E) is a front view of a lower box, and (F) is an explanatory view of a connection state of upper and lower boxes. 空気熱交換器に装着する継手部材の説明図であって、（Ａ）は斜視図、（Ｂ）は縦断面図、（Ｃ）は横断面図である。It is explanatory drawing of the coupling member with which an air heat exchanger is mounted | worn, Comprising: (A) is a perspective view, (B) is a longitudinal cross-sectional view, (C) is a cross-sectional view. 空気熱交換器の冷温水コイルの配置説明図であって、（Ａ）は空気流説明図、（Ｂ）は後端部の配置側面説明図、（Ｃ）は前端部の配置側面説明図、（Ｄ）は前端部の配置正面部分拡大図である。It is arrangement explanatory drawing of the cold / hot water coil of an air heat exchanger, (A) is air flow explanatory drawing, (B) is the arrangement side explanatory drawing of the rear end part, (C) is the arrangement side explanatory drawing of the front end part, (D) is the arrangement | positioning front surface partial enlarged view of a front-end part. 冷温水コイルの説明図であって、（Ａ）は平面図、（Ｂ）は側面図、（Ｃ）は（Ａ）の矢印Ｃ視図、（Ｄ）は（Ａ）の矢印Ｄ視図、（Ｅ）はフィンに対する循環パイプの貫入説明図、（Ｆ）は両端のエンドプレートの分解斜視図である。It is explanatory drawing of a cold / hot water coil, Comprising: (A) is a top view, (B) is a side view, (C) is the arrow C view of (A), (D) is the arrow D view of (A), (E) is explanatory drawing of penetration of the circulation pipe with respect to a fin, (F) is an exploded perspective view of the end plate of both ends. 空気熱交換器の製作説明図であって、（Ａ）は下側函体１Ｄの斜視図、（Ｂ）は下側函体内に冷温水コイルを装着した状態の斜視図、（Ｃ）は上下函体を一体化した状態の斜視図、（Ｄ）は前後端に継手部材を装着した状態の斜視図、（Ｅ）は外装仕上状態の斜視図である。It is manufacture explanatory drawing of an air heat exchanger, (A) is a perspective view of lower box 1D, (B) is a perspective view in the state where a cold / hot water coil was installed in the lower box, (C) is up and down. The perspective view of the state which integrated the box, (D) is a perspective view of the state which attached the joint member to the front-back end, (E) is a perspective view of an exterior finishing state. 本発明空気熱交換器の第２実施例の説明図であって、（Ａ）は縦断側面図、（Ｂ）は（Ａ）の矢印Ｂ視図、（Ｃ）は（Ａ）の矢印Ｃ視図である。It is explanatory drawing of 2nd Example of this invention air heat exchanger, Comprising: (A) is a vertical side view, (B) is the arrow B view of (A), (C) is the arrow C view of (A). FIG. 従来例の説明図であって、（Ａ）は従来例１のフィン説明斜視図、（Ｂ）は従来例１のヘッダ使用タイプの斜視図、（Ｃ）は従来例２の斜視図、（Ｄ）は従来例２の縦断側面図である。It is explanatory drawing of a prior art example, (A) is a fin explanatory perspective view of the prior art example 1, (B) is a perspective view of the header use type of the prior art example 1, (C) is a perspective view of the prior art example 2, (D ) Is a longitudinal side view of Conventional Example 2. FIG.

〔空気熱交換器１の全体構成（図１）〕
図１（Ａ）は空気熱交換器の縦断側面図であり、図１（Ｂ）は（Ａ）の矢印Ｂ視図、図１（Ｃ）は（Ａ）の矢印Ｃ視図である。
本発明の空気熱交換器１は、図１（Ｂ），（Ｃ）に示す如く、断面方形の筒本体１Ａ内に、断面方形の冷温水コイル２を、前端を筒本体１Ａの底板１Ｂに当接し、後端を筒本体１Ａの上面天板１Ｔに当接配置し、冷温水コイル２の、前端下面及び後端上面を閉止し、筒本体１Ａの後端下面から止水板８Ｒを起立すると共に、止水板８Ｒの前部にドレンパイプ８Ａを配置しておき、筒本体１Ａの前端及び後端には継手部材１１を装着したものである。 [Overall configuration of air heat exchanger 1 (FIG. 1)]
FIG. 1A is a longitudinal side view of an air heat exchanger, FIG. 1B is a view as viewed from an arrow B in FIG. 1A, and FIG. 1C is a view as viewed from an arrow C in FIG.
As shown in FIGS. 1B and 1C, the air heat exchanger 1 of the present invention has a square hot water coil 2 having a square cross section in a cylindrical main body 1A having a square cross section, and a front end serving as a bottom plate 1B of the cylindrical main body 1A. The rear end is placed in contact with the upper surface top plate 1T of the cylinder main body 1A, the front end lower surface and the rear end upper surface of the cold / hot water coil 2 are closed, and the water stop plate 8R is erected from the rear end lower surface of the cylinder main body 1A. In addition, a drain pipe 8A is disposed in front of the water stop plate 8R, and a joint member 11 is attached to the front end and the rear end of the cylinder body 1A.

そして、空気熱交換器１の全体形状は、筒本体１Ａの、長さＬ１が８３０mm、幅Ｗ１が２０９mm、高さｈ１が１４４mmであって、継手部材１１を前後に装着した状態の全長Ｌ１´は１２７０mmである。
また、筒本体１Ａの上面には、図１（Ａ）に示す如く、冷温水コイル２の前端対応位置での１本の噴霧ノズル１０Ａと、後方に順次洗浄ノズル９Ａ群を間隔配置した。
また、図１（Ａ）に示す如く、冷温水コイル２の上面空間Ｓｕには、筒本体１Ａの両側板１Ｆに差し渡し状に風偏向板ｂｔ群を間隔配置したものである。 The overall shape of the air heat exchanger 1 is such that the length L1 of the cylinder body 1A is 830 mm, the width W1 is 209 mm, the height h1 is 144 mm, and the joint member 11 is attached to the front and rear. Is 1270 mm.
Further, as shown in FIG. 1A, one spray nozzle 10A at a position corresponding to the front end of the cold / hot water coil 2 and a group of cleaning nozzles 9A are sequentially arranged on the upper surface of the cylinder main body 1A.
Further, as shown in FIG. 1 (A), in the upper surface space Su of the cold / hot water coil 2, a group of wind deflector plates bt are arranged so as to be spaced from both side plates 1F of the cylinder body 1A.

従って、図４（Ａ）に示す如く、前端の継手部材から圧送される熱交換用の空気流ａ３は、冷温水コイル２の上面空間Ｓｕのみに流入して上面空間Ｓｕを高圧域とし、流入空気流ａ３は、風偏向板ｂｔ群の助力によって冷温水コイル２の上面全面から低圧域の下面空間Ｓｄへと、冷温水コイル２の各密集平行配置のフィン２Ｆ間を貫流して、熱交換作用を受け、下面空間Ｓｄから継手部材１１を介して、所定の居室内に供給出来る。
そして、冷温水コイル２の各フィン２Ｆ群に発生した結露水、及び洗浄ノズル９Ａ群で定期洗浄した水は、止水板８Ｒによって居室内に飛散されることなく、ドレンパイプ８Ａを介して排除処理出来るものである。 Accordingly, as shown in FIG. 4A, the heat exchange air flow a3 fed from the joint member at the front end flows only into the upper surface space Su of the cold / hot water coil 2, and the upper surface space Su is set as a high pressure region. The air flow a3 flows between the fins 2F of the cold / hot water coil 2 between the closely parallel fins 2F from the entire upper surface of the cold / hot water coil 2 to the lower surface space Sd in the low pressure region with the help of the wind deflector bt group. Under the action, it can be supplied from the lower surface space Sd to the predetermined living room via the joint member 11.
And the dew condensation water which generate | occur | produced in each fin 2F group of the cold / hot water coil 2, and the water regularly wash | cleaned by the washing nozzle 9A group are excluded through the drain pipe 8A, without being scattered by the water stop board 8R. It can be processed.

〔冷温水コイル（図５）〕
図５は、冷温水コイルの説明図であって、（Ａ）は平面図、（Ｂ）は（Ａ）の矢印Ｂ視図、（Ｃ）は（Ａ）の矢印Ｃ視後面図、（Ｄ）は（Ａ）の矢印Ｄ視前面図、（Ｅ）はフィンと循環パイプとの関係説明図、（Ｆ）はフィン２Ｆ群の両端に止着配置する前後エンドプレートの斜視図である。 [Cold / hot water coil (Fig. 5)]
5A and 5B are explanatory diagrams of the cold / hot water coil, in which FIG. 5A is a plan view, FIG. 5B is a view as viewed from an arrow B in FIG. (A) is a front view as viewed from arrow D in (A), (E) is an explanatory view of the relationship between the fins and the circulation pipe, and (F) is a perspective view of the front and rear end plates that are fixedly disposed at both ends of the fins 2F group.

冷温水コイル２は、空気熱交換器１内に配置して、空気熱交換器内を貫流する空気に熱交換作用を付与するものであって、全体形状は、図５（Ａ）〜（Ｄ）に示す如く、両端のエンドプレート間の長さＬ２が６５０mm、幅Ｗ２´が２０５mm、高さ（厚さ）ｈ２が４４mmの断面矩形立方体であって、前端及び後端からは、図４（Ａ）に示す如く、エンドプレート２Ｅ，２Ｅ´の取付片２Ｐ及び循環パイプ２Ａ連通用の、ヘアピンチューブ２Ｂ及びＵベント２Ｃが、前端ではＬ２´（標準：３５mm）後端ではＬｄ（標準：４５mm）突出したものである。 The cold / hot water coil 2 is disposed in the air heat exchanger 1 and imparts a heat exchanging action to the air flowing through the air heat exchanger. The overall shape is shown in FIGS. ), The length L2 between the end plates at both ends is 650 mm, the width W2 ′ is 205 mm, and the height (thickness) h2 is 44 mm. As shown in A), the hair pin tube 2B and the U vent 2C for connecting the end plate 2E, 2E 'mounting piece 2P and the circulation pipe 2A are L2' (standard: 35 mm) at the front end and Ld (standard: 45 mm) at the rear end. ) Protruding.

フィン２Ｆは、図５（Ｅ）に示す如く、高さｈ２が４４mm、幅Ｗ２が２０３．２mm、厚さが０．２mmのアルミ矩形平板であって、上縁からｈｂ（１１mm）の線上と、下縁からｈｂ（１１mm）の線上に、上下各８個の貫入用孔Ｈ２を、左右間隔Ｗａが２５．４mmで、上下孔Ｈ２列をずらして千鳥状に配置したもので、各貫入用孔Ｈ２には、上側８本、下側８本の循環パイプ２Ａを貫通して、各フィン２Ｆを、最小の空気貫流間隔（標準：０．５mm）を保って並列密集配置したものである。
そして、フィン２Ｆ群の前端及び後端には、エンドプレート２Ｅ，２Ｅ´を配置して、各フィン２Ｆ群の配置形態を確保する。 As shown in FIG. 5 (E), the fin 2F is an aluminum rectangular flat plate having a height h2 of 44 mm, a width W2 of 203.2 mm, and a thickness of 0.2 mm, on the line hb (11 mm) from the upper edge. The upper and lower penetrating holes H2 are arranged in a staggered pattern on the line hb (11mm) from the lower edge, with the horizontal interval Wa of 25.4mm and the upper and lower holes H2 arranged in a staggered manner. In the hole H2, the upper eight and lower eight circulation pipes 2A are penetrated, and the fins 2F are densely arranged in parallel with a minimum air flow interval (standard: 0.5 mm).
Then, end plates 2E and 2E ′ are arranged at the front end and the rear end of the fin 2F group to secure the arrangement form of each fin 2F group.

エンドプレート２Ｅ，２Ｅ´は、図５（Ｆ）に示す如く、高さｈ２がフィン２Ｆと同高で、前側エンドプレート２Ｅは前方に、後側エンドプレート２Ｅ´は後方に、それぞれボルト挿入用孔Ｈ１´を備えた取付片２Ｐを突出したもので、取付片２Ｐは、突出長３５mm（Ｌ２´）で、上下を欠込み２Ｇによって高さ２５mm（ｈ２´）とし、冷温水コイル２の傾斜配置でのエンドプレート２Ｅ，２Ｅ´の筒本体１Ａへの当接配置を欠込み２Ｇで可能とする。 As shown in FIG. 5 (F), the end plates 2E and 2E ′ have the same height h2 as the fins 2F, the front end plate 2E is forward, the rear end plate 2E ′ is rearward, and a bolt is inserted. A mounting piece 2P provided with a hole H1 ′ is projected. The mounting piece 2P has a protruding length of 35 mm (L2 ′), has a top and bottom and a height of 25 mm (h2 ′) by 2G. The arrangement of the end plates 2E and 2E ′ in contact with the cylinder main body 1A is enabled by the notch 2G.

そして、循環パイプ２Ａの配置は、図５（Ｅ）に示す如く、フィン２Ｆ群を上側８本、下側８本串刺し貫通して、前端では、ヘアピンチューブ２Ｂで、図５（Ｄ）に示す如く、各左右２本を連通し、後端では、図５（Ｃ）に示す如く、各上下２本をＵベント２Ｃで連通し、後端の、上側左端のパイプには往き側接続管２Ｓを、下側右端には戻り側接続管２Ｒを、後端エンドプレート２Ｅ´から４５mm（Ｌｄ）後方へ突出して、両接続管２Ｓ，２Ｒ間をＷｄ（標準：８５mm）で、フィン２Ｆ上面から４５mm（Ｌｂ）上方へ突出させたものである。 As shown in FIG. 5 (E), the circulation pipe 2A is arranged through the fin 2F group by piercing the upper eight and the lower eight, with the hairpin tube 2B at the front end, as shown in FIG. 5 (D). As shown in FIG. 5 (C), the upper and lower two pipes are communicated with each other by a U vent 2C, and the rear left upper pipe is the forward connection pipe 2S. From the upper surface of the fin 2F, the return side connecting pipe 2R protrudes 45mm (Ld) rearward from the rear end plate 2E 'at the lower right end, and Wd (standard: 85mm) between both the connecting pipes 2S and 2R. It is projected upward by 45 mm (Lb).

従って、図５（Ｅ）に示す如く、往き側接続管２Ｓから冷水又は温水を流入すれば、流入水ｆ１は、図の上列左端の循環パイプ２Ａ内をｆ２として流れて右側隣接循環パイプ２Ａ内へｆ３として入り、順次上下千鳥状配置の循環パイプ２Ａ内をｆ３→ｆ４・・・ｆ１７と貫流して戻り側接続管２Ｒからｆ１８として流出し、循環パイプ２Ａ群を貫通確保した並列密集フィン２Ｆ群は、循環パイプ２Ａ群内を循環する冷温水から全面均斉な熱伝達を受ける。 Therefore, as shown in FIG. 5E, if cold water or hot water flows from the forward connection pipe 2S, the inflowing water f1 flows as f2 in the circulation pipe 2A at the left end of the upper row in the figure, and the right adjacent circulation pipe 2A. Parallel dense fins that enter into the inside as f3, sequentially flow through f3 → f4... F17 through the circulation pipe 2A arranged in a staggered manner and flow out as f18 from the return side connection pipe 2R, and pass through the circulation pipe 2A group. The 2F group receives uniform heat transfer from the cold / hot water circulating in the circulation pipe 2A group.

〔筒本体１Ａ（図２）〕
筒本体１Ａは、上側函体１Ｕと下側函体１Ｄとを衝合接続して断面矩形筒としたものであり、図２（Ａ）は、筒本体１Ａに前後の継手部材１１を装着して天井内に配置した使用状態側面図であり、図２（Ｂ）は上側函体１Ｕの側面図、（Ｃ）は上側函体１Ｕの前面図であり、図２（Ｄ）は下側函体１Ｄの側面図、図２（Ｅ）は下側函体の前面図であり、図２（Ｆ）は、上側函体１Ｕと下側函体１Ｄとの接続状態説明図である。 [Cylinder body 1A (Fig. 2)]
The cylinder body 1A has a rectangular cross section formed by abutting connection between the upper box 1U and the lower box 1D. FIG. 2 (A) shows that the front and rear joint members 11 are attached to the cylinder body 1A. FIG. 2B is a side view of the upper box 1U, FIG. 2C is a front view of the upper box 1U, and FIG. 2D is a lower box. A side view of the body 1D, FIG. 2E is a front view of the lower box, and FIG. 2F is an explanatory diagram of a connection state between the upper box 1U and the lower box 1D.

図２（Ｂ），（Ｃ）に示す如く、上側函体１Ｕは、０．５mm厚のステンレス鋼板の折曲加工品であって、天板１Ｔと両側板１Ｆとを断面コ字状に形成した長さＬ１が８３０mm、幅Ｗ１´が２１３mmで、側板１Ｆは前端の高さｈ１´が１１４mm、後端の高さが１８mmで、後端には小寸の水平部ｆｐを保って、前端へ７．５°の傾斜で延びるものである。
そして、下側函体１Ｄとの重ね幅Ｊｕを１０mm設けるため、両側板１Ｆに差し渡し状に、側板下端縁Ｆｄの１５mm上方から、厚さ０．５mmのステンレス鋼板を仰角θｂが５５°に溶接固着して風偏向板ｂｔ群を配置する。 As shown in FIGS. 2B and 2C, the upper box 1U is a bent product of a stainless steel plate having a thickness of 0.5 mm, and the top plate 1T and both side plates 1F are formed in a U-shaped cross section. The length L1 is 830 mm, the width W1 ′ is 213 mm, the side plate 1F has a front end height h1 ′ of 114 mm, a rear end height of 18 mm, and a rear end with a small horizontal portion fp. It extends with an inclination of 7.5 °.
Then, in order to provide 10 mm of overlap width Ju with the lower box 1D, a stainless steel plate having a thickness of 0.5 mm is welded to the side plates 1F from 15 mm above the side plate lower edge Fd at an elevation angle θb of 55 °. The wind deflector bt group is arranged by being fixed.

風偏向板ｂｔ群は、図２（Ｂ）に示す如く、上端が順次後側から前側へ低位置となるように、そして、各風偏向板ｂｔ間を、図４（Ａ）に示す如く、間隔Ｌａが１４４mmで、前端の風偏向板ｂｔは筒本体１Ａの前端から１８０mm（Ｌｂ）となるように配置する。
この場合、風偏向板ｂｔの上下幅は、ｂｔ１が１６mm、ｂｔ２が１９mm、ｂｔ３が２２mm、ｂｔ４が２５mmとすれば良い。
また、天板１Ｔの後端上面には冷温水コイル２の往き側接続管２Ｓと戻り側接続管２Ｂを突出させるための貫通孔Ｈ２´を穿孔しておく。 As shown in FIG. 2 (B), the wind deflector bt group has its upper end sequentially lowered from the rear side to the front side, and the space between the wind deflector plates bt is as shown in FIG. 4 (A). The interval La is 144 mm, and the wind deflection plate bt at the front end is arranged to be 180 mm (Lb) from the front end of the cylinder body 1A.
In this case, the vertical width of the wind deflection plate bt may be 16 mm for bt1, 19 mm for bt2, 22 mm for bt3, and 25 mm for bt4.
Further, a through hole H2 ′ for projecting the forward connection pipe 2S and the return connection pipe 2B of the cold / hot water coil 2 is drilled in the upper surface of the rear end of the top plate 1T.

下側函体１Ｄは、上側函体１Ｕと嵌合一体化するものであって、０．５mm厚のステンレス鋼板加工で用意するもので、図２（Ｄ）に示す如く、長さＬ１が８３０mm、幅Ｗ１が２０９mm、の両側板１Ｆと底板１Ｂとで形成し、両側板１Ｆは、後端の高さｈ１”が１４２mm、前端高さが４１．５mmで、後端の小寸の水平部ｆｐを保って前端へ７．５°で傾斜しており、底板１Ｂの後端近傍から高さ４０mm、仰角θＲが６０°の止水板８Ｒを両側板１Ｆ間に差し渡し溶接で立設し、止水板８Ｒの前部の底板１Ｂ後端から９０mm位置には、外径２０mm、長さ４０mmのステンレス製ドレンパイプ８Ａを垂下配置する。
また、下側函体１Ｄも上側函体１Ｕも、両側板１Ｆの前後に、一体化接合用のボルト挿入用孔Ｈ１を配置しておく。 The lower box 1D is fitted and integrated with the upper box 1U and is prepared by processing a 0.5 mm thick stainless steel plate. As shown in FIG. 2D, the length L1 is 830 mm. , The width W1 is 209 mm, and is formed by both side plates 1F and the bottom plate 1B. The side plates 1F have a rear end height h1 "of 142 mm, a front end height of 41.5 mm, and a small horizontal portion at the rear end. Inclined by 7.5 ° to the front end while maintaining fp, standing from the vicinity of the rear end of the bottom plate 1B with a height of 40 mm and an elevation angle θR of 60 ° between both side plates 1F by welding. A stainless drain pipe 8A having an outer diameter of 20 mm and a length of 40 mm is suspended from the rear end of the bottom plate 1B at the front of the water stop plate 8R.
Further, in both the lower case 1D and the upper case 1U, bolt insertion holes H1 for integral joining are arranged before and after the side plates 1F.

〔継手部材１１（図３）〕
継手部材１１は、図１（Ａ）に示す如く、冷温水コイル２を筒本体１Ａ内に組付けた空気熱交換器１の前後に嵌着して、図２（Ａ）に示す如く、空気熱交換器１を吸気側ダクト管３Ｄ及び供給側ダクト管４Ｄと接続する筒体であって、図３（Ａ）は全体斜視図、図３（Ｂ）は長さ方向縦断側面図、図３（Ｃ）は長さ方向横断面図である。 [Fitting member 11 (FIG. 3)]
As shown in FIG. 1 (A), the joint member 11 is fitted to the front and rear of the air heat exchanger 1 in which the cold / hot water coil 2 is assembled in the cylinder body 1A. FIG. 3A is an overall perspective view, FIG. 3B is a longitudinal longitudinal side view, and FIG. 3 is a cylinder that connects the heat exchanger 1 to the intake side duct pipe 3D and the supply side duct pipe 4D. (C) is a longitudinal cross-sectional view.

図３に示す如く、継手部材１１は、空気熱交換器１の筒本体１Ａの前端及び後端に嵌合するための嵌合部１１Ｔと円錐部１１Ｓと接続パイプ部１１Ｊとを備えたものであり、標準品は、横（Ｗ１１）が２１７mm、縦（ｈ１１）が１４８mmの垂直辺１１Ｆから、重ね代（Ｄ１１）が３０mmの幅の周縁フランジで嵌合部１１Ｔを突設し、円錐部１１Ｓは、垂直辺１１Ｆから長さ（Ｌ１１´）が１２０mmで突出し、接続パイプ部１１Ｊは外径ｈ１１´が９８mm、長さ（Ｌ１１”）が１００mmで円錐筒部から延出したもので、厚さ０．５mmの板金で製作すれば良いが、空気熱交換器１の使用形態に応じて、円錐部１１Ｓ及び接続パイプ部１１Ｊは適寸で準備すれば良い。 As shown in FIG. 3, the joint member 11 includes a fitting portion 11T, a conical portion 11S, and a connection pipe portion 11J for fitting to the front end and the rear end of the cylinder body 1A of the air heat exchanger 1. The standard product has a conical portion 11S projecting from a vertical side 11F having a width (W11) of 217 mm and a length (h11) of 148 mm, with a peripheral flange having a width of overlap (D11) of 30 mm, and a conical portion 11S. Is protruding from the vertical side 11F with a length (L11 ′) of 120 mm, and the connecting pipe part 11J has an outer diameter h11 ′ of 98 mm and a length (L11 ″) of 100 mm and extends from the conical cylinder part. What is necessary is just to manufacture with a 0.5 mm sheet metal, but according to the usage form of the air heat exchanger 1, the cone part 11S and the connection pipe part 11J should just prepare with an appropriate dimension.

〔空気熱交換器１の製作（図６）〕
図６は空気熱交換器１の製作説明図であり、（Ａ）は上側函体１Ｕの斜視図、（Ｂ）は上側函体１Ｕに冷温水コイル２を配置した斜視図、（Ｃ）は下側函体１Ｄと上側函体１Ｕとを一体化した状態を、（Ｄ）は前後に継手部材を嵌合した状態を、（Ｅ）は仕上製品を示す図であり、塗装被覆した状態図である。 [Production of air heat exchanger 1 (FIG. 6)]
6A and 6B are diagrams for explaining the manufacture of the air heat exchanger 1. FIG. 6A is a perspective view of the upper case 1U, FIG. 6B is a perspective view in which the cold / hot water coil 2 is arranged on the upper case 1U, and FIG. The state where the lower case 1D and the upper case 1U are integrated, (D) is the state where the joint members are fitted back and forth, (E) is the view showing the finished product, and the state of the paint coating It is.

図６（Ａ）、及び図４（Ｄ）に示す如く、ステンレススチール鋼板の折曲加工で準備した下側函体１Ｄには、両側板１Ｆの上部内側面に、厚さ１．５mmで、幅がフィン２Ｆの上下寸法（標準：４５mm）のゴム板１Ｇを貼着し、底板１Ｂの前端にも図４（Ｃ）に示す如く、厚さ１．５mm、幅１０mmのゴム板１Ｇを両側板１Ｆ間に差し渡し状に貼着しておく（図（Ａ））。
次いで、準備した冷温水コイル２を下側函体１Ｄ内に、フィン２Ｆ群の両側面がゴム板１Ｇに当接し、且つ冷温水コイル２の前端下縁が底板１Ｂ上のゴム板１Ｇに当接する形態で嵌入して、前端及び後端のエンドプレート２Ｅ，２Ｅ´の取付片２Ｐを両側板１Ｆにボルトｂ１で固着する（図（Ｂ））。 As shown in FIG. 6 (A) and FIG. 4 (D), the lower box 1D prepared by bending a stainless steel plate has a thickness of 1.5 mm on the upper inner surface of both side plates 1F. A rubber plate 1G having a width of fin 2F in the vertical dimension (standard: 45 mm) is attached, and a rubber plate 1G having a thickness of 1.5 mm and a width of 10 mm is also attached to the front end of the bottom plate 1B as shown in FIG. Affixed between the plates 1F in a stretched manner (FIG. (A)).
Next, the prepared cold / hot water coil 2 is placed in the lower box 1D, both side surfaces of the fin 2F group are in contact with the rubber plate 1G, and the lower edge of the front end of the cold / hot water coil 2 contacts the rubber plate 1G on the bottom plate 1B. The attachment pieces 2P of the front and rear end plates 2E and 2E ′ are fixed to the both side plates 1F with bolts b1 (FIG. (B)).

次いで、上側函体１Ｕにも、図４（Ｂ）に示す如く、天板１Ｔの内面前部のエンドプレート２Ｅ´の当接部位には、厚さ１．５mm、幅１０mmのゴム板１Ｇを両側板１Ｆ間に亘って貼着して、下側函体１Ｄに上方から、上側函体１Ｕの両側板１Ｆが下側函体１Ｄの両側板１Ｆの外側に重ね幅Ｊｕ部１０mmの形態に被せ、冷温水コイルの、往き側接続管２Ｓ及び戻り側接続管２Ｒを天板１Ｔの貫通孔Ｈ２から突出させて、上下両側板を、図２（Ｆ）の如く、重ね幅Ｊｕ（１０mm）を介してねじｎ１で締着し、上下函体１Ｕ，１Ｄを、冷温水コイル２を装着した状態で一体化する（図（Ｃ））。 Next, as shown in FIG. 4 (B), a rubber plate 1G having a thickness of 1.5 mm and a width of 10 mm is also applied to the upper box 1U at the contact portion of the front end plate 2E 'on the inner surface of the top plate 1T. Adhering between both side plates 1F, the upper side box 1U has both side plates 1F stacked on the outer side of both side plates 1F of the lower side box 1D from the upper side to the lower side box 1D. Cover the front and rear connecting pipes 2S and 2R of the cold / hot water coil so that they protrude from the through hole H2 of the top plate 1T, and the upper and lower side plates are overlapped as shown in FIG. The upper and lower cases 1U and 1D are integrated with the cold / hot water coil 2 attached (FIG. (C)).

次いで、筒本体１Ａの前端及び後端に、それぞれ、継手部材１１を、嵌合部１１Ｔを筒本体１Ａの端部から被覆嵌合して、嵌合部１１Ｔと筒本体１Ａの端部をねじｎ２で締着一体化し、上下函体１Ｕ，１Ｄの重ね幅Ｊｕ部及び継手部材１１の接続部に慣用の気密テープ４Ｔを被覆貼着して、空気熱交換器１内の貫流空気の漏洩を阻止する（図（Ｄ））。 Next, the coupling member 11 is covered and fitted to the front end and the rear end of the cylinder main body 1A from the end of the cylinder main body 1A, and the fitting part 11T and the end of the cylinder main body 1A are screwed. N2 is fastened and integrated, and a conventional airtight tape 4T is coated and pasted on the overlapping width Ju portion of the upper and lower boxes 1U and 1D and the connection portion of the joint member 11, and leakage of the through air in the air heat exchanger 1 is prevented. Block (Figure (D)).

そして、慣用の、−３０℃でも柔軟性を保持し、耐火性、低発煙性、耐湿耐候性に優れた、独立気泡エラストマー断熱材のエアロフレックス（イースタンポリマー社登録商標名）の厚さ１３mmの粘性断熱材４Ａを、空気熱交換器の全周に貼着して結露防止を図る（図（Ｅ））。 And, it is 13 mm thick of Aeroflex (registered trademark name of Eastern Polymer Co., Ltd.), a closed-cell elastomer heat insulating material that retains flexibility even at a conventional temperature of −30 ° C. and is excellent in fire resistance, low smoke generation and moisture resistance. The viscous heat insulating material 4A is adhered to the entire circumference of the air heat exchanger to prevent condensation (FIG. (E)).

〔空気熱交換器の使用（図２（Ａ））〕
図２（Ａ）は、天井内への配置形態側面図であり、空気熱交換器１の吸気側１Ｓの継手部材１１には、慣用のダクト管３Ｄ、ダクトファン３Ｆを介在して天井面に配置したフィルター付吸気グリル３Ｇと接続し、空気熱交換器１の供給側１Ｒの継手部材１１には居室内へ送風する慣用の供給側ダクト管４Ｄを接続した。
また、洗浄ノズル９Ａ群は、タイマースイッチ介在の洗浄回路に、噴霧ノズル１０Ａは検湿器介在の加湿回路に接続した。
また、ドレンパイプ８Ａも、慣用の手段で、排水パイプ８Ｂを接続して排水回路を形成した。 [Use of air heat exchanger (Fig. 2 (A))]
FIG. 2 (A) is a side view of the arrangement form in the ceiling. The joint member 11 on the intake side 1S of the air heat exchanger 1 has a conventional duct pipe 3D and a duct fan 3F interposed on the ceiling surface. Connected to the intake grille with filter 3G arranged, a conventional supply side duct pipe 4D for blowing air into the living room was connected to the joint member 11 on the supply side 1R of the air heat exchanger 1.
The cleaning nozzle 9A group was connected to a cleaning circuit with a timer switch, and the spray nozzle 10A was connected to a humidification circuit with a humidity detector.
Further, the drain pipe 8A is also connected to the drain pipe 8B by a conventional means to form a drain circuit.

本実施例の空気熱交換器１は、冷房運転時には、冷温水コイル２内に冷却水を循環させることにより、空気熱交換器１内に流入する空気流ａ３はフィン２Ｆ群からの熱交換作用を受けて、除湿冷風ａ４として居室内に供給出来、同時に冷却作用で生じたフィン２Ｆ群の結露水は、止水板８Ｒの介在によってドレンパイプ８Ａから支障無く排除出来た。 In the air heat exchanger 1 of the present embodiment, the cooling water is circulated in the cold / hot water coil 2 during the cooling operation, whereby the air flow a3 flowing into the air heat exchanger 1 is exchanged with heat from the fins 2F group. In response, the dehumidified cool air a4 can be supplied into the room, and at the same time, the condensed water of the fins 2F generated by the cooling action can be removed from the drain pipe 8A without any trouble by the interposition of the water stop plate 8R.

また、暖房運転時には、冷温水コイル２に加温水を循環させて、空気熱交換器１内への吸気空気流ａ３をフィン２Ｆ群での熱交換作用で加温空気流として居室内に供給出来、必要に応じて、噴霧ノズル１０Ａの室内検湿器との連動で、適正に加湿温風として居室内に供給出来た。 Further, during the heating operation, the warm water is circulated through the cold / hot water coil 2, and the intake air flow a3 into the air heat exchanger 1 can be supplied to the living room as a warm air flow by the heat exchange action in the fins 2F group. If necessary, it was able to be appropriately supplied into the room as humidified hot air in conjunction with the indoor humidity detector of the spray nozzle 10A.

また、フィン２Ｆ群に付着した埃等も、必要に応じて洗浄ノズル９Ａ群で洗浄出来、洗浄水もドレンパイプ８Ａからの排水回路で支障無く排水出来た。
そして、空気熱交換器１は、長尺であるが、上下左右寸法、即ち幅方向の断面寸法は小寸であるため、天井内等の、上下左右のスペースの限られた場所にも、簡便に配置出来る。 Also, dust or the like adhering to the fins 2F group could be washed by the washing nozzle 9A group as needed, and the washing water could be drained without any trouble by the drain circuit from the drain pipe 8A.
And although the air heat exchanger 1 is long, since the vertical and horizontal dimensions, that is, the cross-sectional dimension in the width direction is small, it can be easily applied to places where the vertical and horizontal spaces are limited, such as in the ceiling. Can be placed.

また、熱交換作用は、上下左右寸法（標準：縦４４mm、横２０３．２mm）の小なフィン２Ｆを多数長手方向に配置し、空気流を各フィン２Ｆの上下面に、フィン２Ｆ配向面直交形態で貫流させたが、高圧域となる上面空間Ｓｕでは、入口から奥へ、スペースが側面視三角形状で狭くなって、吸引空気流ａ３は、最奥では最大圧力となり、対応して、下面空間Ｓｄは低圧域となるため、吸引空気流ａ３は、間隔配置した風偏向板ｂｔ群での整流偏向作用の助力の下に、冷温水コイル２の長さ方向全長に亘って、各フィン２Ｆ間の隙間を貫通して均斉な熱交換作用を発揮した。
尚、各風偏向板ｂｔの下端はフィン２Ｆ群の上面と小間隔Ｓｍ（標準：５mm）を有するが、小間隔５mmに流入する空気流も低圧域の下面空間Ｓｄに支障無く吸引出来た。 In addition, the heat exchanging action is made by arranging a number of small fins 2F having vertical and horizontal dimensions (standard: vertical 44 mm, horizontal 203.2 mm) in the longitudinal direction, and the air flow is perpendicular to the fin 2F orientation plane on each fin 2F. In the upper surface space Su that is a high pressure region, the space is narrowed in a triangular shape in a side view, and the suction air flow a3 has the maximum pressure at the innermost portion, Since the space Sd is in a low pressure region, the suction air flow a3 is applied to each fin 2F over the entire length in the length direction of the cold / hot water coil 2 with the aid of the rectifying and deflecting action of the wind deflector plates bt arranged at intervals. A uniform heat exchange effect was demonstrated through the gaps between them.
The lower end of each wind deflector plate bt has a small interval Sm (standard: 5 mm) from the upper surface of the fin 2F group, but the air flow flowing into the small interval 5 mm could be sucked into the lower surface space Sd in the low pressure region without any trouble.

〔変形実施例（図７）〕
図７は変形実施例（第２実施例）の説明図であって、（Ａ）は縦断側面図、（Ｂ）は（Ａ）の矢印Ｂ視図、（Ｃ）は（Ａ）の矢印Ｃ視図である。
本実施例は、第１実施（図１）と同一寸法の空気熱交換器であるが、冷温水コイル２の配置形態のみを変更し、該形態変更に相応して、冷温水コイル２の前端と後端の空密処理も相応に変形した。
そのため、図７（Ｂ）,（Ｃ）に示す如く、上側函体１３Ｕの両側板１３Ｆは６０mm高さ（ｈ１３´）とし、下側函体１３Ｄの両側板１３Ｆは、高さ（ｈ１３”）９４mmとし、冷温水コイル２は下側函体１３Ｄの両側板１３Ｆの上端縁と整合配置して、重ね幅Ｊｕが１０mmで、高さｈ１３が１４４mmとした。 [Modified Example (FIG. 7)]
FIGS. 7A and 7B are explanatory views of a modified embodiment (second embodiment), in which FIG. 7A is a longitudinal side view, FIG. 7B is a view from arrow B of FIG. FIG.
This embodiment is an air heat exchanger having the same dimensions as the first embodiment (FIG. 1), but only the arrangement of the chilled / hot water coil 2 is changed, and the front end of the chilled / hot water coil 2 is changed in accordance with the change of the configuration. And the airtight treatment at the rear end was also changed accordingly.
Therefore, as shown in FIGS. 7B and 7C, both side plates 13F of the upper box 13U have a height (h13 ′), and both sides 13F of the lower box 13D have a height (h13 ″). The cold / hot water coil 2 was aligned with the upper edge of the both side plates 13F of the lower box 13D, the overlap width Ju was 10 mm, and the height h13 was 144 mm.

そして、筒本体１３Ａ内では、冷温水コイル２の前端下面と筒本体底板１３Ｂとの間隔は、風偏向板ｂｔ１で閉止し、冷温水コイル２の後端上面と筒本体天板１３Ｔとの間隔は、後部から前部へと順次突出長を漸減した間隔配置の風偏向板ｂｔ群の最後部の風偏向板ｂｔ２で閉止し、吸気側１Ｓからの流入空気流は、上面空間Ｓｕに流入して、各風偏向板ｂｔ群の整流偏向によって、冷温水コイル２の全長に亘って各フィン２Ｆ間を貫流して低圧の下面空間Ｓｄに流れ、居室内への供給空気流ａ４は下面空間Ｓｄから流出させた。 In the cylinder main body 13A, the space between the front lower surface of the cold / hot water coil 2 and the cylinder main body bottom plate 13B is closed by the wind deflection plate bt1, and the distance between the rear upper surface of the cold / hot water coil 2 and the tube main body top plate 13T. Is closed by the rearmost wind deflector bt2 of the wind deflector bt group with the spacing gradually reduced from the rear to the front, and the inflow air flow from the intake side 1S flows into the upper surface space Su. By the rectifying deflection of each wind deflector plate bt group, the air flows through the fins 2F through the entire length of the cold / hot water coil 2 and flows into the low pressure lower surface space Sd, and the supply air flow a4 into the living room is the lower surface space Sd. Spilled from.

本実施例にあっては、上下函体１３Ｕ，１３Ｄの製作、接続作業は簡単となったが、風偏向板ｂｔ群の配置が、強度面、寸法面から、煩雑且つ精緻な作業となり、製作コスト面からは実施例１よりも若干不利であった。
しかし、空気熱交換作用は、実施例１（図１）のそれと略同一の効果が得られ、発明の所期の目的は達成出来た。 In this embodiment, the manufacture and connection of the upper and lower boxes 13U and 13D are simplified, but the arrangement of the wind deflector bt group is complicated and precise work in terms of strength and dimensions. In terms of cost, it was slightly disadvantageous compared to Example 1.
However, the effect of air heat exchange was almost the same as that of Example 1 (FIG. 1), and the intended purpose of the invention could be achieved.

１，１３空気熱交換器
１Ａ，１３Ａ筒本体
１Ｂ，１３Ｂ底板
１Ｄ，１３Ｄ下側函体
１Ｆ，１３Ｆ側板
１Ｇゴム板
１Ｒ供給側
１Ｓ吸気側
１Ｔ，１３Ｔ天板
１Ｕ，１３Ｕ上側函体
２冷温水コイル
２Ａ循環パイプ
２Ｂヘアピンチューブ
２ＣＵベント
２Ｅ，２Ｅ´ エンドプレート
２Ｆフィン
２Ｇ欠込み
２Ｐ取付片
２Ｒ戻り側接続管
２Ｓ往き側接続管
３Ｄ，４Ｄダクト管
３Ｆダクトファン
３Ｇ吸気グリル
４Ａ粘性断熱材
４Ｔ気密テープ
６Ｐプラスチック樹脂パイプ
８Ａドレンパイプ
８Ｂ排水パイプ
８Ｒ止水板
９Ａ洗浄ノズル
１０Ａ噴霧ノズル
１１継手部材
１１Ｆ垂直辺
１１Ｊ接続パイプ部
１１Ｓ円錐部
１１Ｔ嵌合部
ｂｔ風偏向板
ｂ１ボルト
Ｃ天井
Ｆｄ下端縁
Ｆｕ上端縁
Ｈ１挿入用孔
Ｈ２貫入用孔
ｎ１，ｎ２ねじ
Ｓｄ下面空間
Ｓｕ上面空間 1,13 Air heat exchanger 1A, 13A Tube body 1B, 13B Bottom plate 1D, 13D Lower box 1F, 13F Side plate 1G Rubber plate 1R Supply side 1S Intake side 1T, 13T Top plate 1U, 13U Upper case 2 Cold / hot water Coil 2A Circulation pipe 2B Hairpin tube 2C U vent 2E, 2E 'End plate 2F Fin 2G Notch 2P Mounting piece 2R Return side connecting pipe 2S Outward side connecting pipe 3D, 4D Duct pipe 3F Duct fan 3G Intake grill 4A Viscous insulation 4T Airtight tape 6P Plastic resin pipe 8A Drain pipe 8B Drain pipe 8R Water stop plate 9A Washing nozzle 10A Spray nozzle 11 Joint member 11F Vertical side 11J Connection pipe portion 11S Conical portion 11T Fitting portion bt Wind deflection plate b1 Bolt C Ceiling Fd Lower end edge Fu upper edge H1 insertion hole H2 penetration hole n1, n2 screw Sd lower surface Between Su top space

Claims

In the circulation pipe (2A), a long chilled / hot water coil (2) in which fins (2F) are arranged orthogonally in a parallel dense form while maintaining an air-flow interval is provided, and the fin (2F) is provided in the cylinder body (1A). in a form orthogonal to the longitudinal direction of the main body (1A), and placed in the longitudinal direction, the upper surface of the suction air flow entering into the cylinder body from the intake side (1S) (1A) (a3) is cold and hot water coil (2) Cold and hot water is guided by a group of wind deflectors (bt) that are guided to the space (Su) and are arranged in the cylinder body (1A) so that the passing air volume decreases sequentially from the intake side (1S) to the supply side (1R). The air flow is sequentially deflected and guided from the upper surface space (Su) of the coil (2) to the lower surface space (Sd) of the cold / hot water coil (2) to guide through the gaps of the fins (2F) group of the cold / hot water coil (2). From the supply side (1R), the empty space from the lower surface space (Sd) of the cold / hot water coil (2) Air heat exchanger, characterized in that to flow out as stream (a4).

A group of cleaning nozzles (9A) is spaced from the upper surface of the cylinder main body (1A), and a spray nozzle (10A) for humidification is arranged from the front upper surface of the cylinder main body (1A). The air heat exchanger according to claim 1, wherein a water stop plate (8R) is disposed on the inner bottom surface of the rear end, and a drain pipe (8A) is suspended from the front portion of the water stop plate (8R).

The cylinder body (1A) has a square cross section in which the upper box (1U) and the lower box (1D) are connected and integrated vertically, and the wind deflector (bt) group is arranged on both sides of the upper box (1U). The hot / cold water coil (2) is arranged in a passing form between the plates (1F), and the upper surface of the fin (2F) group is aligned with the upper end edge (Fu) of the lower box (1D). 2. The air heat exchanger according to 2.

Both side plates (1F) of the upper box (1U) are inclined so that the side plate (1F) reduces the vertical width from the intake side (1S) to the supply side (1R), and both sides of the lower box (1D). The plate (1F) has an inclined form that increases the vertical width from the intake side (1S) to the supply side (1R), and the cold / hot water coil (2) has both upper plates on the upper side in the lower box (1D). (1F) is arranged in alignment with the upper edge (Fu), and a wind deflector plate (bt) group that slopes up to the intake side (1S) is passed between the side plates (1F) of the upper box (1U). The air heat exchanger according to claim 3 arranged in a shape.

The lower surface and both side surfaces of the front end of the cold / hot water coil (2), and the upper surface and both side surfaces of the rear end of the cold / hot water coil (2) are provided with rubber plates (1G) and the front end of the lower surface space (Sd) and the upper surface space. (Su) The rear end is airtightly treated, and the water stop plate (8R) is rearward from the bottom plate (1B) of the lower box (1D) to a height of 35 ± 5% of the height of the cylinder body (1A). The air heat exchanger according to claim 4, wherein the air heat exchanger is inclined upward.