JP5312512B2 - Heat exchanger and air conditioner equipped with the heat exchanger - Google Patents

Heat exchanger and air conditioner equipped with the heat exchanger Download PDF

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JP5312512B2
JP5312512B2 JP2011092001A JP2011092001A JP5312512B2 JP 5312512 B2 JP5312512 B2 JP 5312512B2 JP 2011092001 A JP2011092001 A JP 2011092001A JP 2011092001 A JP2011092001 A JP 2011092001A JP 5312512 B2 JP5312512 B2 JP 5312512B2
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heat transfer
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transfer tubes
heat exchanger
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JP2012225545A (en
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晃 石橋
拓也 松田
相武 李
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Mitsubishi Electric Corp
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Description

本発明は、熱交換器及びこの熱交換器を備えた空気調和機に関する。   The present invention relates to a heat exchanger and an air conditioner equipped with the heat exchanger.

従来より、空気が通過する隙間を置いて複数積層された矩形状フィンと、これら矩形状フィンと直交し、内部を作動流体が通過する伝熱管とを備えたフィンチューブ型熱交換器が知られている（例えば、特許文献１参照）。   2. Description of the Related Art Conventionally, a finned tube heat exchanger has been known that includes a plurality of rectangular fins stacked with a gap through which air passes and heat transfer tubes that are orthogonal to the rectangular fins and through which a working fluid passes. (For example, refer to Patent Document 1).

特開平１１−５１４１２号公報（図１）Japanese Patent Laid-Open No. 11-51412 (FIG. 1)

しかしながら、従来のフィンチューブ型熱交換器は、配管間の距離が遠く、一まとめにできないという難点があり、パス数が増大する傾向にあった。   However, the conventional fin tube type heat exchanger has a disadvantage that the distance between the pipes is long and cannot be integrated, and the number of passes tends to increase.

本発明の技術的課題は、伝熱管を集約し、パス数を低減できるようにすることにある。   A technical problem of the present invention is to collect heat transfer tubes and reduce the number of paths.

本発明に係る熱交換器は、下記の構成からなるものである。すなわち、空気が通過する隙間を置いて複数積層された矩形状フィンと、これら矩形状フィンと直交し、内部を作動流体が通過する伝熱管とを備え、矩形状フィンは、前記隙間の空気導入部となる側の積層面が空気流れ方向に直交する向きに配置され、伝熱管は、矩形状フィンの長手方向を段方向として複数段設けられるとともに、空気流れ方向を列方向として複数列設けられてなる熱交換器であって、各列及び各段毎に、列方向に複数の伝熱管を配し、かつこれら複数の伝熱管の、前記積層された矩形状フィンを貫通した両端部の少なくとも一方に、これら複数の伝熱管を束ねて段毎に合流又は分配する段専用集合管を設け、段専用集合管の合流管部を、その軸線が空気流れの上流寄りとなるように形成したものである。 The heat exchanger according to the present invention has the following configuration. That is, a plurality of stacked rectangular fins with gaps through which air passes, and heat transfer tubes that are orthogonal to the rectangular fins and through which the working fluid passes, and the rectangular fins introduce air into the gaps. The heat transfer tubes are provided in a plurality of rows with the longitudinal direction of the rectangular fins as the step direction, and in a plurality of rows with the air flow direction as the row direction. A plurality of heat transfer tubes arranged in the row direction for each row and each stage, and at least at both ends of the plurality of heat transfer tubes penetrating the stacked rectangular fins On the other hand, a stage-only collecting pipe that bundles or distributes these heat transfer pipes for each stage is provided , and the joining pipe portion of the stage-only collecting pipe is formed so that its axis is closer to the upstream side of the air flow. It is.

本発明に係る熱交換器においては、各列及び各段毎に、列方向に複数の伝熱管を配し、かつこれら複数の伝熱管の、前記積層された矩形状フィンを貫通した両端部の少なくとも一方に、これら複数の伝熱管を束ねて段毎に合流又は分配する段専用集合管を設けたので、各列及び各段毎に列方向に複数設けた伝熱管を、実質的に１本の配管として扱って冷媒パスを構成することが可能となり、パス数を低減させることができ、熱交換性能を向上させることができる。さらに、段専用集合管の合流管部を、その軸線が空気流れの上流寄りとなるように形成したので、この熱交換器を例えば空気調和機の凝縮器に適用した場合、液冷媒の慣性力を利用して、熱負荷の大きい空気流れ方向上流側の伝熱管に冷媒を多く流すことができる。このため、２相冷媒を用いる場合、空気流れ方向上流側と下流側の伝熱管間の乾き度を一様にすることができ、熱交換性能が向上する。 In the heat exchanger according to the present invention, for each row and each stage, a plurality of heat transfer tubes are arranged in the row direction, and both ends of the plurality of heat transfer tubes passing through the stacked rectangular fins. Since at least one of the plurality of heat transfer tubes is bundled and a stage-dedicated collecting pipe that joins or distributes each stage is provided, there is substantially one heat transfer pipe provided in the row direction for each row and each row. It is possible to construct a refrigerant path by treating it as a pipe, reducing the number of passes and improving the heat exchange performance. Furthermore, since the junction pipe portion of the stage-only collecting pipe is formed so that the axis thereof is closer to the upstream side of the air flow, when this heat exchanger is applied to a condenser of an air conditioner, for example, the inertial force of the liquid refrigerant Can be used to flow a large amount of refrigerant through the heat transfer tube on the upstream side in the air flow direction with a large heat load. For this reason, when using a two-phase refrigerant | coolant, the dryness between the heat exchanger tubes of the air flow direction upstream and downstream can be made uniform, and heat exchange performance improves.

本発明の実施形態１に係る熱交換器の構成を示す断面図である。It is sectional drawing which shows the structure of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施形態１に係る熱交換器の伝熱管配置の変形例を示す断面図である。It is sectional drawing which shows the modification of the heat exchanger tube arrangement | positioning of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施形態１に係る熱交換器の接続配管、段専用集合管（三方管）、及び伝熱管の関係を示す正面図である。It is a front view which shows the connection piping of the heat exchanger which concerns on Embodiment 1 of this invention, the stage exclusive collection pipe (three-way pipe), and the relationship of a heat exchanger tube. 本発明の実施形態１に係る熱交換器の接続配管、段専用集合管（三方管）、伝熱管、及び矩形状フィンと、空気流れ方向の関係を示す正面図である。It is a front view which shows the connection piping of the heat exchanger which concerns on Embodiment 1 of this invention, the stage exclusive collection pipe (three-way pipe), a heat exchanger tube, and a rectangular fin, and the relationship of an air flow direction. 本発明の実施形態１に係る熱交換器の段専用集合管（三方管）とＵベンドの関係を示す側面図である。It is a side view which shows the relationship between the stage exclusive collection pipe (three-way pipe) and U bend of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施形態１に係る熱交換器を伝熱管のヘアピン側より示す側面図である。It is a side view which shows the heat exchanger which concerns on Embodiment 1 of this invention from the hairpin side of a heat exchanger tube. 本発明の実施形態１に係る熱交換器の三方管の変形例を示す正面図である。It is a front view which shows the modification of the three-way pipe | tube of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施形態２に係る空気調和機の冷凍サイクルの冷媒回路図である。It is a refrigerant circuit figure of the refrigerating cycle of the air conditioner concerning Embodiment 2 of the present invention.

実施形態１．
図１は本発明の実施形態１に係る熱交換器の構成を示す断面図である。
本発明の実施形態１に係る熱交換器は、図１のように空気が通過する隙間を置いて複数積層された２列の矩形状フィン１ａ，１ｂと、これら矩形状フィン１ａ，１ｂのそれぞれに直交し、内部を作動流体が通過する２列の伝熱管２ａ，２ｂとを備えている。すなわち、矩形状フィン１ａ，１ｂは、隙間の空気導入部となる側の積層面が空気流れ方向に直交する向きに配置されている。伝熱管２ａ，２ｂは、矩形状フィン１ａ，１ｂの長手方向を段方向として複数段設けられるとともに、空気流れ方向を列方向として複数列設けられている。また、伝熱管２ａ，２ｂは、各列及び各段毎に設けられ、それぞれが列方向（空気流れ方向）に平行に配置されている。さらに、各列及び各段毎に設けられている伝熱管２ａ，２ｂは、隣接する列側の伝熱管２ａ，２ｂとの位置関係で見ると段方向にずらせて配置されていて、互いに千鳥状に配列されている。ここで、伝熱管２ａ，２ｂの管径は５.０mmであり、矩形状フィン１ａ，１ｂの空気流れ方向のフィン幅は２２mm、各列における伝熱管２ａ，２ｂの段方向のピッチは２１mmである。また、各列における伝熱管２ａ，２ｂの中心軸の空気流れ方向のピッチは１０mmである。 Embodiment 1. FIG.
FIG. 1 is a cross-sectional view showing a configuration of a heat exchanger according to Embodiment 1 of the present invention.
The heat exchanger according to Embodiment 1 of the present invention includes two rows of rectangular fins 1a and 1b stacked with a gap through which air passes as shown in FIG. 1, and each of these rectangular fins 1a and 1b. And two rows of heat transfer tubes 2a and 2b through which the working fluid passes. That is, the rectangular fins 1a and 1b are arranged in a direction in which the laminated surface on the side serving as the air introduction portion of the gap is orthogonal to the air flow direction. The heat transfer tubes 2a and 2b are provided in a plurality of stages with the longitudinal direction of the rectangular fins 1a and 1b as the step direction, and are provided in a plurality of rows with the air flow direction as the column direction. The heat transfer tubes 2a and 2b are provided for each row and each stage, and are arranged in parallel to the row direction (air flow direction). Furthermore, the heat transfer tubes 2a and 2b provided for each row and each step are arranged in a staggered manner when viewed from the positional relationship with the heat transfer tubes 2a and 2b on the adjacent row side. Is arranged. Here, the tube diameter of the heat transfer tubes 2a and 2b is 5.0 mm, the fin width in the air flow direction of the rectangular fins 1a and 1b is 22 mm, and the pitch in the step direction of the heat transfer tubes 2a and 2b in each row is 21 mm. is there. Further, the pitch in the air flow direction of the central axis of the heat transfer tubes 2a and 2b in each row is 10 mm.

図１のように、各列及び各段毎に、複数の伝熱管２ａ，２ｂを設け、かつこれら伝熱管２ａ，２ｂは、空気流れ方向に平行に配置することで、空気側の通風抵抗を増やすことなく伝熱管の本数を増加させることができる。   As shown in FIG. 1, a plurality of heat transfer tubes 2a and 2b are provided for each row and each stage, and these heat transfer tubes 2a and 2b are arranged in parallel to the air flow direction to reduce the air-side ventilation resistance. The number of heat transfer tubes can be increased without increasing the number.

さらに、各列及び各段毎に設けられている伝熱管２ａ，２ｂを、隣接する列間で見て千鳥状に配列することで、伝熱性能を向上させることができる。   Furthermore, the heat transfer performance can be improved by arranging the heat transfer tubes 2a and 2b provided for each row and each stage in a staggered manner as seen between adjacent rows.

図２は本発明の実施形態１に係る熱交換器の伝熱管配置の変形例を示す断面図である。図２においては、各列及び各段毎に設けられている伝熱管２ａ，２ｂが、空気流れ方向に対して伝熱管投影面分（伝熱管外径分）、段方向に偏倚して配置されている。   FIG. 2 is a cross-sectional view showing a modification of the heat transfer tube arrangement of the heat exchanger according to Embodiment 1 of the present invention. In FIG. 2, the heat transfer tubes 2 a and 2 b provided for each row and each step are arranged so as to be deviated in the step direction by the heat transfer tube projection surface (heat transfer tube outer diameter) with respect to the air flow direction. ing.

図２のように各列及び各段毎に設けられている伝熱管２ａ，２ｂを互いに段方向に偏倚して配置し、空気流れの下流側に配置されている伝熱管２ｂが、空気流れの上流側に配置されている伝熱管２ａの後流の影響を受けないようにすることで、伝熱性能を向上させることができる。   As shown in FIG. 2, the heat transfer tubes 2a and 2b provided for each row and each stage are arranged so as to be offset in the step direction, and the heat transfer tubes 2b arranged on the downstream side of the air flow The heat transfer performance can be improved by avoiding the influence of the wake of the heat transfer tube 2a arranged on the upstream side.

図３は本発明の実施形態１に係る熱交換器の接続配管、段専用集合管（三方管）、及び伝熱管の関係を示す正面図である。図４は本発明の実施形態１に係る熱交換器の接続配管、段専用集合管（三方管）、伝熱管、及び矩形状フィンと、空気流れ方向の関係を示す正面図である。図５は本発明の実施形態１に係る熱交換器の段専用集合管（三方管）とＵベンドの関係を示す側面図である。図６は本発明の実施形態１に係る熱交換器を伝熱管のヘアピン側より示す側面図である。   FIG. 3 is a front view showing the relationship among the connection pipe, the stage-only collecting pipe (three-way pipe), and the heat transfer pipe of the heat exchanger according to Embodiment 1 of the present invention. FIG. 4 is a front view showing the relationship between the connection pipe, the stage-only collecting pipe (three-way pipe), the heat transfer pipe, and the rectangular fins of the heat exchanger according to Embodiment 1 of the present invention and the air flow direction. FIG. 5 is a side view showing the relationship between the stage-only collecting pipe (three-way pipe) and the U-bend of the heat exchanger according to Embodiment 1 of the present invention. FIG. 6 is a side view showing the heat exchanger according to Embodiment 1 of the present invention from the hairpin side of the heat transfer tube.

図３乃至図６のように各列及び各段毎に設けられている伝熱管２ａ，２ｂの、積層された矩形状フィン１ａや１ｂを貫通した両端部の一方に、これら複数の伝熱管２ａ，２ｂを束ねて段毎に合流又は分配する段専用集合管すなわち三方管３が設けられている。三方管３の入口又は出口となる合流管部３ａは、その直径が７mmであり、その軸線が空気流れ方向上流側の伝熱管２ａ寄りに配置されている。ここでは、図３のように三方管３の合流管部３ａの軸線と空気流れ方向上流側の伝熱管２ａの軸線とがほぼ一致するように構成されている。このように三方管３の合流管部３ａを空気流れ方向上流側に配置することにより、本実施形態の熱交換器を空気調和機の凝縮器に適用した場合、液冷媒の慣性力を利用して、熱負荷の大きい空気流れ方向上流側の伝熱管２ａに冷媒を多く流すことができる。このため、２相冷媒を用いる場合、空気流れ方向上流側と下流側の伝熱管２ａ，２ｂ間の乾き度を一様にすることができ、熱交換性能が向上する。   As shown in FIG. 3 to FIG. 6, the heat transfer tubes 2a and 2b provided in each row and each stage have a plurality of heat transfer tubes 2a on one of both end portions penetrating the stacked rectangular fins 1a and 1b. , 2b are bundled, or a stage-dedicated collecting pipe, that is, a three-way pipe 3 is provided to join or distribute each stage. The confluence tube portion 3a serving as the inlet or the outlet of the three-way tube 3 has a diameter of 7 mm, and its axis is disposed closer to the heat transfer tube 2a on the upstream side in the air flow direction. Here, as shown in FIG. 3, the axis of the merging pipe portion 3 a of the three-way pipe 3 is configured to substantially coincide with the axis of the heat transfer pipe 2 a on the upstream side in the air flow direction. As described above, by arranging the merge pipe portion 3a of the three-way pipe 3 on the upstream side in the air flow direction, when the heat exchanger of the present embodiment is applied to the condenser of the air conditioner, the inertial force of the liquid refrigerant is used. Thus, a large amount of refrigerant can flow through the heat transfer pipe 2a on the upstream side in the air flow direction with a large heat load. For this reason, when using a two-phase refrigerant | coolant, the dryness between the heat exchanger tubes 2a and 2b of the air flow direction upstream and downstream can be made uniform, and heat exchange performance improves.

したがって、冷媒は、凝縮器の場合、図５及び図６のように空気流れ方向下流側の矩形状フィン１ｂの列の入口から流入し、三方管３により矩形状フィン１ｂの最上段に位置する伝熱管２ａ，２ｂに分配される。次いで、矩形状フィン１ｂで熱交換され、伝熱管２ａ，２ｂのそれぞれのヘアピン部を通過し、再び矩形状フィン１ｂで熱交換された後、二段目の三方管３により伝熱管２ａ，２ｂは合流される。次いで、段間Ｕベンド５で下段（三段目）に流入し、下段（三段目）の三方管３に流入後、伝熱管２ａ，２ｂに分配される。これを、空気流れ方向下流側の矩形状フィン１ｂで繰り返した後、列間Ｕベンド６で上流側に流入し、空気流れ方向上流側の矩形状フィン１ａの最下段の三方管３に流入する。   Therefore, in the case of the condenser, the refrigerant flows in from the inlet of the row of the rectangular fins 1b on the downstream side in the air flow direction as shown in FIGS. 5 and 6, and is positioned at the uppermost stage of the rectangular fins 1b by the three-way pipe 3. The heat transfer tubes 2a and 2b are distributed. Next, heat is exchanged by the rectangular fins 1b, passes through the respective hairpin portions of the heat transfer tubes 2a and 2b, and is again heat exchanged by the rectangular fins 1b, and then the heat transfer tubes 2a and 2b by the second three-way tube 3 Are merged. Next, the air flows into the lower stage (third stage) through the interstage U-bend 5, flows into the lower (third stage) three-way pipe 3, and is then distributed to the heat transfer pipes 2a and 2b. After this is repeated at the rectangular fin 1b on the downstream side in the air flow direction, it flows into the upstream side by the inter-row U-bend 6 and flows into the lowest three-way pipe 3 of the rectangular fin 1a at the upstream side in the air flow direction. .

次に、矩形状フィン１ａの最下段の三方管３により伝熱管２ａ，２ｂに分配され、矩形状フィン１ａで熱交換され、ヘアピンを通過し、再び矩形状フィン１ａで熱交換される。その後、下から二段目の三方管３により伝熱管２ａ，２ｂは合流される。次いで、段間Ｕベンド５で上段（下から三段目）に流入し、下から三段目の三方管３に流入後、伝熱管２ａ，２ｂに分配される。これを、空気流れ方向上流側の矩形状フィン１ａで繰り返した後、最上段の三方管３の合流管部３ａ、つまり冷媒出口より接続配管４（図４）へ流出する。   Next, the heat is transferred to the heat transfer tubes 2a and 2b by the lowermost three-way tube 3 of the rectangular fin 1a, exchanges heat with the rectangular fin 1a, passes through the hairpin, and again exchanges heat with the rectangular fin 1a. Thereafter, the heat transfer tubes 2a and 2b are joined by the three-way tube 3 in the second stage from the bottom. Next, the air flows into the upper stage (third stage from the bottom) at the interstage U-bend 5, and after flowing into the three-way pipe 3 at the third stage from the bottom, it is distributed to the heat transfer tubes 2a and 2b. This is repeated at the rectangular fin 1a on the upstream side in the air flow direction, and then flows out from the junction pipe portion 3a of the uppermost three-way pipe 3, that is, from the refrigerant outlet to the connection pipe 4 (FIG. 4).

このように、各列及び各段毎に設けられている複数の伝熱管２ａ，２ｂを束ねて段毎に合流又は分配する三方管３により、各列及び各段毎に設けられている複数の伝熱管２ａ，２ｂを実質的に１本の配管として扱い、冷媒パスを構成しているので、冷媒パス数を半減できる。   In this way, the plurality of heat transfer tubes 2a and 2b provided for each row and each stage are bundled and the three-way pipe 3 that joins or distributes for each step provides a plurality of each of the rows and each stage. Since the heat transfer tubes 2a and 2b are substantially handled as one pipe and constitute a refrigerant path, the number of refrigerant paths can be halved.

図７は本発明の実施形態１に係る熱交換器の三方管の変形例を示す正面図である。この三方管３Ａは、伝熱管２ａ，２ｂとの接続部が、合流管部３ａの軸線を挟むように設けられている。このような三方管３Ａの場合、空気流れ方向上流側に配置される伝熱管２ａと空気流れ方向下流側に配置される伝熱管２ｂをストレート状に接続した場合、これら伝熱管２ａ，２ｂには液冷媒が均等に流れる。このため、熱負荷の大きい空気流れ方向上流側の伝熱管２ａに冷媒を多く流すことはできない。   FIG. 7 is a front view showing a modification of the three-way pipe of the heat exchanger according to the first embodiment of the present invention. The three-way pipe 3A is provided so that the connection part with the heat transfer pipes 2a and 2b sandwiches the axis of the joining pipe part 3a. In the case of such a three-way pipe 3A, when the heat transfer tube 2a disposed on the upstream side in the air flow direction and the heat transfer tube 2b disposed on the downstream side in the air flow direction are connected in a straight shape, the heat transfer tubes 2a and 2b include Liquid refrigerant flows evenly. For this reason, a large amount of refrigerant cannot flow through the heat transfer pipe 2a on the upstream side in the air flow direction with a large heat load.

したがって、このような三方管３Ａを用いる場合は、空気流れ方向下流側に配置される伝熱管２ｂを、図７のように三方管３Ａの接続部まで空気流れ方向上流側に折り曲げて、三方管３Ａに接続する形態を採る。これにより、空気流れ方向下流側に配置される伝熱管２ｂに圧損を付けることができて、空気流れ方向上流側の伝熱管２ａにより多くの液冷媒を流すことができる。このため、２相冷媒を用いる場合、空気流れ方向上流側と下流側の伝熱管２ａ，２ｂ間の乾き度を一様にすることができ、熱交換性能が向上する。   Therefore, when such a three-way pipe 3A is used, the heat transfer pipe 2b arranged on the downstream side in the air flow direction is bent to the upstream side in the air flow direction to the connection portion of the three-way pipe 3A as shown in FIG. The form which connects to 3A is taken. As a result, pressure loss can be applied to the heat transfer tube 2b arranged on the downstream side in the air flow direction, and a larger amount of liquid refrigerant can flow through the heat transfer tube 2a on the upstream side in the air flow direction. For this reason, when using a two-phase refrigerant | coolant, the dryness between the heat exchanger tubes 2a and 2b of the air flow direction upstream and downstream can be made uniform, and heat exchange performance improves.

なお、ここでは各列及び各段毎に設けられている複数の伝熱管２ａ，２ｂの、積層された矩形状フィン１ａ，１ｂを貫通した両端部の内の一方に、これら複数の伝熱管２ａ，２ｂを束ねて段毎に合流又は分配する段専用集合管すなわち三方管３又は３Ａを設け、伝熱管２ａ，２ｂの両端部の内の他方は、これら伝熱管２ａ，２ｂを折り返すヘアピンとして構成したものを例に挙げて説明したが、これに限るものではない。すなわち、三方管３又は３Ａは、伝熱管２ａ，２ｂの、積層された矩形状フィン１ａ，１ｂを貫通した両端部の両方に設けてもよいものである。この場合は、各伝熱管２ａ，２ｂが合流するまでの長さを短くすることができるため、熱負荷の影響を受けなくなり、乾き度分布を少なくでき、熱交換性能が向上する。   Here, a plurality of heat transfer tubes 2a and 2b provided in each row and each stage are provided on one of both end portions penetrating the stacked rectangular fins 1a and 1b. , 2b are bundled to each stage to join or distribute, that is, a three-way pipe 3 or 3A is provided, and the other of both ends of the heat transfer tubes 2a, 2b is configured as a hairpin that turns back the heat transfer tubes 2a, 2b. However, the present invention is not limited to this. That is, the three-way tube 3 or 3A may be provided at both ends of the heat transfer tubes 2a and 2b penetrating the stacked rectangular fins 1a and 1b. In this case, since the length until the heat transfer tubes 2a and 2b join can be shortened, the heat load is not affected, the dryness distribution can be reduced, and the heat exchange performance is improved.

また、ここでは、各列及び各段毎に、列方向に２つの伝熱管２ａ，２ｂを配し、段専用集合管すなわち三方管３又は３Ａにてこれら２つの伝熱管２ａ，２ｂを束ねて段毎に合流又は分配するようにしたものを例に挙げて説明したが、これに限るものではない。例えば、各列及び各段毎に、列方向に３つ以上の伝熱管を配し、段専用集合管にてこれら３つ以上の伝熱管を束ねて段毎に合流又は分配するようにしてもよいものである。   Further, here, for each row and each stage, two heat transfer tubes 2a and 2b are arranged in the row direction, and these two heat transfer tubes 2a and 2b are bundled by a stage-dedicated collecting pipe, that is, the three-way pipe 3 or 3A. Although an example has been described in which each stage is joined or distributed, the present invention is not limited to this. For example, for each row and each stage, three or more heat transfer tubes are arranged in the row direction, and these three or more heat transfer tubes are bundled in a stage-dedicated collecting pipe to be merged or distributed for each stage. It ’s good.

実施形態２．
図８は前述の熱交換器を備えた本発明の実施形態２に係る空気調和機の冷凍サイクルの冷媒回路図である。 Embodiment 2. FIG.
FIG. 8 is a refrigerant circuit diagram of a refrigeration cycle of an air conditioner according to Embodiment 2 of the present invention including the above-described heat exchanger.

本発明の実施形態２に係る空気調和機は、図８のように圧縮機３３、凝縮器３４、絞り装置３５、蒸発器３６、凝縮器用送風機３７ａ及びその駆動用モーター３８ａ、蒸発器用送風機３７ｂ及びその駆動用モーター３８ｂにより構成されている。前述の実施形態１に係る熱交換器を凝縮器３４または蒸発器３６、もしくは両方に用いることにより、エネルギー効率の高い空調冷凍装置を実現することができる。ここで、エネルギー効率は、次式（１）（２）で求められるものである。
暖房エネルギー効率＝室内熱交換器（凝縮器）能力／全入力‥‥‥‥‥‥（１）
冷房エネルギー効率＝室内熱交換器（蒸発器）能力／全入力‥‥‥‥‥‥（２） As shown in FIG. 8, the air conditioner according to Embodiment 2 of the present invention includes a compressor 33, a condenser 34, a throttling device 35, an evaporator 36, a condenser blower 37a and its driving motor 38a, an evaporator blower 37b, and The drive motor 38b is used. By using the heat exchanger according to the first embodiment for the condenser 34, the evaporator 36, or both, an air-conditioning refrigeration apparatus with high energy efficiency can be realized. Here, energy efficiency is calculated | required by following Formula (1) (2).
Heating energy efficiency = indoor heat exchanger (condenser) capacity / all inputs (1)
Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / all inputs (2)

なお、前述の実施形態１で述べた熱交換器及びこの熱交換器を備えた空気調和機については、ＨＣＦＣ（Ｒ２２）やＨＦＣ（Ｒ１１６、Ｒ１２５、Ｒ１３４ａ、Ｒ１４、Ｒ１４３ａ、Ｒ１５２ａ、Ｒ２２７ｅａ、Ｒ２３、Ｒ２３６ｅａ、Ｒ２３６ｆａ、Ｒ２４５ｃａ、Ｒ２４５ｆａ、Ｒ３２、Ｒ４１，ＲＣ３１８などや、これら冷媒の数種の混合冷媒Ｒ４０７Ａ、Ｒ４０７Ｂ、Ｒ４０７Ｃ、Ｒ４０７Ｄ、Ｒ４０７Ｅ、Ｒ４１０Ａ、Ｒ４１０Ｂ、Ｒ４０４Ａ、Ｒ５０７Ａ、Ｒ５０８Ａ、Ｒ５０８Ｂなど）、ＨＣ（ブタン、イソブタン、エタン、プロパン、プロピレンなどや、これら冷媒の数種混合冷媒）、自然冷媒（空気、炭酸ガス、アンモニアなどや、これら冷媒の数種の混合冷媒）、ＨＦＯ１２３４yf等の低ＧＷＰ冷媒、またこれら冷媒の数種の混合冷媒など、どんな種類の冷媒を用いても、その効果を達成することができる。   In addition, about the heat exchanger described in above-mentioned Embodiment 1, and an air conditioner provided with this heat exchanger, HCFC (R22) and HFC (R116, R125, R134a, R14, R143a, R152a, R227ea, R23, R236ea, R236fa, R245ca, R245fa, R32, R41, RC318, etc., and mixed refrigerants R407A, R407B, R407C, R407D, R407E, R410A, R410B, R404A, R507A, R508A, HCB, etc. Low GWP refrigerants such as butane, isobutane, ethane, propane, propylene, etc., some mixed refrigerants of these refrigerants, natural refrigerants (air, carbon dioxide, ammonia, etc., several mixed refrigerants of these refrigerants), HFO1234yf, These refrigerants A mixed refrigerant type, be used any type of refrigerant, can achieve its effect.

また、作動流体として、ここでは空気と冷媒の例を示したが、他の気体、液体、気液混合流体を用いても、同様の効果を奏する。   Moreover, although the example of air and a refrigerant | coolant was shown here as a working fluid, even if it uses other gas, liquid, and gas-liquid mixed fluid, there exists the same effect.

伝熱管２ａ，２ｂと矩形状フィン１ａ，１ｂは、異なった材料を用いることが一般的である。しかし、伝熱管２ａ，２ｂと矩形状フィン１ａ，１ｂの材料として、銅やアルミ等、同じ材料を用いることで、矩形状フィン１ａ，１ｂと伝熱管２ａ，２ｂのロウ付けが可能となる。この場合には、矩形状フィン１ａ，１ｂと伝熱管２ａ，２ｂの接触熱伝達率が飛躍的に向上し、熱交換能力が大幅に向上する。また、リサイクル性も向上させることができる。   Generally, different materials are used for the heat transfer tubes 2a and 2b and the rectangular fins 1a and 1b. However, by using the same material such as copper or aluminum as the material of the heat transfer tubes 2a and 2b and the rectangular fins 1a and 1b, the rectangular fins 1a and 1b and the heat transfer tubes 2a and 2b can be brazed. In this case, the contact heat transfer coefficient between the rectangular fins 1a and 1b and the heat transfer tubes 2a and 2b is dramatically improved, and the heat exchange capability is greatly improved. Moreover, recyclability can also be improved.

また、伝熱管２ａ，２ｂと矩形状フィン１ａ，１ｂを密着させる方法として、炉中ロウ付けを行う場合、炉中ロウ付けの後に、矩形状フィン１ａ，１ｂに親水材を塗布するようにすれば、親水材の焼け落ちを防ぐことができる。   In addition, when performing brazing in the furnace as a method for bringing the heat transfer tubes 2a, 2b and the rectangular fins 1a, 1b into close contact, a hydrophilic material is applied to the rectangular fins 1a, 1b after brazing in the furnace. If so, it is possible to prevent the hydrophilic material from burning off.

また、前述の実施形態１で説明した熱交換器を室外機で用いた場合においても同様な効果を奏する。   Further, the same effect can be obtained when the heat exchanger described in the first embodiment is used in an outdoor unit.

なお、前述の実施形態１で述べた熱交換器及びそれを用いた実施形態２の空調冷凍装置については、鉱油系、アルキルベンゼン油系、エステル油系、エーテル油系、フッ素油系など、冷媒と油が溶ける溶けないに拘わらず、どんな冷凍機油についても、その効果を達成することができる。   For the heat exchanger described in the first embodiment and the air-conditioning refrigeration apparatus of the second embodiment using the heat exchanger, a mineral oil, an alkylbenzene oil system, an ester oil system, an ether oil system, a fluorine oil system, or the like can be used. The effect can be achieved with any refrigeration oil, regardless of whether the oil is soluble or not.

本発明の活用例として、熱交換性能を向上し、省エネルギー性能を向上することが必要なヒートポンプ装置の熱交換器に使用することができる。   As an application example of the present invention, it can be used in a heat exchanger of a heat pump apparatus that requires improved heat exchange performance and improved energy saving performance.

１ａ，１ｂ 矩形状フィン、２ａ，２ｂ 伝熱管、３，３Ａ 三方管（段専用集合管）、３ａ 合流管部、４ 接続配管、５ 段間Ｕベンド、６ 列間Ｕベンド、３３ 圧縮機、３４ 凝縮器、３５ 絞り装置、３６ 蒸発器、３７ａ 凝縮器用送風機、３７ｂ 蒸発器用送風機、３８ａ，３８ｂ 駆動用モーター。   1a, 1b Rectangular fin, 2a, 2b Heat transfer tube, 3, 3A Three-way tube (collection tube dedicated to the stage), 3a Merge pipe part, 4 Connection pipe, 5 Interstage U-bend, 6 Interrow U-bend, 33 Compressor, 34 condenser, 35 throttle device, 36 evaporator, 37a condenser blower, 37b evaporator blower, 38a, 38b drive motor.

Claims (7)

空気が通過する隙間を置いて複数積層された矩形状フィンと、これら矩形状フィンと直交し、内部を作動流体が通過する伝熱管とを備え、前記矩形状フィンは、前記隙間の空気導入部となる側の積層面が空気流れ方向に直交する向きに配置され、前記伝熱管は、前記矩形状フィンの長手方向を段方向として複数段設けられるとともに、空気流れ方向を列方向として複数列設けられてなる熱交換器であって、
各列及び各段毎に、列方向に複数の伝熱管を配し、かつこれら複数の伝熱管の、前記積層された矩形状フィンを貫通した両端部の少なくとも一方に、これら複数の伝熱管を束ねて段毎に合流又は分配する段専用集合管を設け、
前記段専用集合管の合流管部を、その軸線が空気流れの上流寄りとなるように形成したことを特徴とする熱交換器。 A plurality of rectangular fins stacked with a gap through which air passes, and a heat transfer tube perpendicular to the rectangular fins and through which a working fluid passes, the rectangular fin being an air introduction portion of the gap And the heat transfer tubes are provided in a plurality of stages with the longitudinal direction of the rectangular fins as the step direction, and provided in a plurality of rows with the air flow direction as the column direction. A heat exchanger,
For each row and each stage, a plurality of heat transfer tubes are arranged in the row direction, and at least one of the plurality of heat transfer tubes penetrating the stacked rectangular fins is provided with the plurality of heat transfer tubes. A stage-only collecting pipe that bundles and joins or distributes for each stage is provided,
Heat exchanger you, characterized in that the collecting pipe portion of the stage only collecting pipe, the axis is formed such that the upstream side of the air flow. 段専用集合管の合流管部の軸線と空気流れ方向上流側の伝熱管の軸線とがほぼ一致するように構成したことを特徴とする請求項１記載の熱交換器。 The heat exchanger of claim 1, wherein the stage dedicated collector pipe collecting pipe portion of the axis and the axis of the air flow upstream side heat transfer tubes is configured to substantially coincide. 空気が通過する隙間を置いて複数積層された矩形状フィンと、これら矩形状フィンと直交し、内部を作動流体が通過する伝熱管とを備え、前記矩形状フィンは、前記隙間の空気導入部となる側の積層面が空気流れ方向に直交する向きに配置され、前記伝熱管は、前記矩形状フィンの長手方向を段方向として複数段設けられるとともに、空気流れ方向を列方向として複数列設けられてなる熱交換器であって、
各列及び各段毎に、列方向に複数の伝熱管を配し、かつこれら複数の伝熱管の、前記積層された矩形状フィンを貫通した両端部の少なくとも一方に、これら複数の伝熱管を束ねて段毎に合流又は分配する段専用集合管を設け、
前記段専用集合管は、前記複数の伝熱管との接続部が、当該段専用集合管の合流管部の軸線を挟むように設けられており、前記複数の伝熱管の内、空気流れ方向上流側の伝熱管は、前記段専用集合管の前記接続部の一方にストレートに接続され、空気流れ方向下流側の伝熱管は、空気流れ方向上流側に折り曲げられて前記段専用集合管の前記接続部の他方に接続されてなることを特徴とする熱交換器。 A plurality of rectangular fins stacked with a gap through which air passes, and a heat transfer tube perpendicular to the rectangular fins and through which a working fluid passes, the rectangular fin being an air introduction portion of the gap And the heat transfer tubes are provided in a plurality of stages with the longitudinal direction of the rectangular fins as the step direction, and provided in a plurality of rows with the air flow direction as the column direction. A heat exchanger,
For each row and each stage, a plurality of heat transfer tubes are arranged in the row direction, and at least one of the plurality of heat transfer tubes penetrating the stacked rectangular fins is provided with the plurality of heat transfer tubes. A stage-only collecting pipe that bundles and joins or distributes for each stage is provided,
The stage-dedicated collecting pipe is provided so that a connection portion with the plurality of heat transfer tubes sandwiches the axis of the merging pipe portion of the stage-dedicated collecting pipe, and the upstream of the plurality of heat transfer tubes in the air flow direction The heat transfer tube on the side is straightly connected to one of the connecting portions of the stage-dedicated collecting pipe, and the heat transfer tube on the downstream side in the air flow direction is bent toward the upstream side in the air flow direction to connect the connection of the stage-dedicated collecting pipe heat exchanger characterized by comprising connected to the other parts. 空気が通過する隙間を置いて複数積層された矩形状フィンと、これら矩形状フィンと直交し、内部を作動流体が通過する伝熱管とを備え、前記矩形状フィンは、前記隙間の空気導入部となる側の積層面が空気流れ方向に直交する向きに配置され、前記伝熱管は、前記矩形状フィンの長手方向を段方向として複数段設けられるとともに、空気流れ方向を列方向として複数列設けられてなる熱交換器であって、
各列及び各段毎に、列方向に複数の伝熱管を配し、かつこれら複数の伝熱管の、前記積層された矩形状フィンを貫通した両端部の少なくとも一方に、これら複数の伝熱管を束ねて段毎に合流又は分配する段専用集合管を設け、
前記伝熱管の少なくとも一端部の段間接続を、段方向で隣接する前記段専用集合管相互を段間Ｕベンドにて接続することで行うことを特徴とする熱交換器。 A plurality of rectangular fins stacked with a gap through which air passes, and a heat transfer tube perpendicular to the rectangular fins and through which a working fluid passes, the rectangular fin being an air introduction portion of the gap And the heat transfer tubes are provided in a plurality of stages with the longitudinal direction of the rectangular fins as the step direction, and provided in a plurality of rows with the air flow direction as the column direction. A heat exchanger,
For each row and each stage, a plurality of heat transfer tubes are arranged in the row direction, and at least one of the plurality of heat transfer tubes penetrating the stacked rectangular fins is provided with the plurality of heat transfer tubes. A stage-only collecting pipe that bundles and joins or distributes for each stage is provided,
At least between one end of the stage connection, the heat exchanger shall be the characterized in that by connecting the stage dedicated collecting pipe mutually adjacent in the interstage U-bend in the column direction of the heat transfer tube. 前記列及び各段毎に、列方向に複数設けた伝熱管を、互いに段方向に偏倚させて配置したことを特徴とする請求項１乃至請求項４のいずれかに記載の熱交換器。   The heat exchanger according to any one of claims 1 to 4, wherein a plurality of heat transfer tubes provided in the row direction are arranged so as to be biased in the row direction for each row and each row. 伝熱管の少なくとも一端部の列間接続を、列方向で隣接する前記段専用集合管相互を列間Ｕベンドにて接続することで行うことを特徴とする請求項１乃至請求項５のいずれかに記載の熱交換器。 Between rows of at least one end portion of the heat transfer tube connection, one of claims 1 to 5, characterized in that performed by connecting the stage dedicated collecting pipe mutually adjacent in the column direction at the column between the U-bend The heat exchanger as described in. 作動流体に冷媒を用い、蒸発器及び凝縮器の両者又はいずれか一方に、前記請求項１乃至請求項６のいずれかの熱交換器を用いたことを特徴とする空気調和機。 An air conditioner using a refrigerant as a working fluid and using the heat exchanger according to any one of claims 1 to 6 for both or one of an evaporator and a condenser.
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JP2008076025A (en) * 2006-09-25 2008-04-03 Matsushita Electric Ind Co Ltd Refrigerant divider and air conditioner using the same
JP4982401B2 (en) * 2008-02-06 2012-07-25 日立アプライアンス株式会社 Air conditioner outdoor unit
KR101172572B1 (en) * 2009-06-08 2012-08-08 엘지전자 주식회사 Distributor and air conditioner including the same

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