JP4624146B2 - Air conditioner indoor unit - Google Patents

Air conditioner indoor unit Download PDF

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JP4624146B2
JP4624146B2 JP2005072369A JP2005072369A JP4624146B2 JP 4624146 B2 JP4624146 B2 JP 4624146B2 JP 2005072369 A JP2005072369 A JP 2005072369A JP 2005072369 A JP2005072369 A JP 2005072369A JP 4624146 B2 JP4624146 B2 JP 4624146B2
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heat exchanger
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heat
transfer tube
heat transfer
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竜太 大西
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Sharp Corp
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Description

本発明は空気調和機の室内機に関し、より特定的には、フィン付き熱交換器を備えている空気調和機の室内機に関する。   The present invention relates to an indoor unit for an air conditioner, and more particularly to an indoor unit for an air conditioner including a finned heat exchanger.

近年、空気調和機の省エネルギー化の進行とともに、空気調和機を構成するフィン付き熱交換器の高効率化が要求されてきている。高効率化の１つの手段として、熱交換器を多段に折り曲げることや円弧状にすることにより、限られた空間内での伝熱交換可能な面積を増加させて、熱交換器の高性能化が図られている。また、別の手段として、熱交換器の風上側に過冷却促進用補助熱交換器を設けることにより、暖房運転時における熱交換器の高性能化が図られている。   In recent years, with the progress of energy saving of air conditioners, there has been a demand for higher efficiency of heat exchangers with fins constituting the air conditioners. As one means of increasing efficiency, the heat exchanger can be bent in multiple stages or formed into an arc shape to increase the heat transfer exchange area in a limited space and improve the performance of the heat exchanger. Is planned. Further, as another means, by providing an auxiliary heat exchanger for promoting supercooling on the windward side of the heat exchanger, the heat exchanger is improved in performance during heating operation.

また、熱交換器を構成する伝熱管等を工夫することにより、熱交換器の高効率化が図られている。熱交換器の伝熱管の管径と管配列に着目して高効率化を図る空気調和機は、たとえば特開２００１−１７４０４７号公報（特許文献１）に開示されている。風速分布に着目して高効率化を図る空気調和機は、たとえば特開平９−２６４５５５号公報（特許文献２）に開示されている。   In addition, the efficiency of the heat exchanger is improved by devising the heat transfer tubes and the like constituting the heat exchanger. An air conditioner that achieves high efficiency by paying attention to the diameter and arrangement of heat transfer tubes of a heat exchanger is disclosed in, for example, Japanese Patent Application Laid-Open No. 2001-174047 (Patent Document 1). An air conditioner that achieves high efficiency by paying attention to the wind speed distribution is disclosed in, for example, Japanese Patent Application Laid-Open No. 9-264555 (Patent Document 2).

図１０は、特許文献１に開示された空気調和機の室内機を示す概略側面図である。図１０を参照して、空気調和機の室内機１００は、送風機１５２と、フィン群と伝熱管群から構成される３台の熱交換器１２１とを備えている。熱交換器１２１は多段に折り曲げられて送風機１５２を囲むように配置されている。通風抵抗の最も高い前面部熱交換器１２２を送風機１５２の最も近い前面部に、次に通風抵抗が高い中央部熱交換器１２３を前面部熱交換器１２２の上位に位置する中央部に、最も通風抵抗の低い背面部熱交換器１２４を中央部熱交換器１２３の背面に配置している。前面部熱交換器１２２、中央部熱交換器１２３、および背面部熱交換器１２４は、径の異なる複数の伝熱管を用いている。これにより、通風抵抗の均一化による送風効率が改善されている。また、暖房運転時に冷媒を最太径伝熱管Ａから順次、中間径伝熱管Ｂ、最細径伝熱管Ｃへ流動させることにより、冷媒側の熱伝達率が向上されている。   FIG. 10 is a schematic side view showing an indoor unit of an air conditioner disclosed in Patent Document 1. Referring to FIG. 10, an indoor unit 100 of an air conditioner includes a blower 152 and three heat exchangers 121 including a fin group and a heat transfer tube group. The heat exchanger 121 is arranged so as to be bent in multiple stages and surround the blower 152. The front heat exchanger 122 with the highest ventilation resistance is placed closest to the front face of the blower 152, and the central heat exchanger 123 with the next highest ventilation resistance is placed at the center located above the front heat exchanger 122. A rear heat exchanger 124 having low ventilation resistance is disposed on the rear surface of the central heat exchanger 123. The front surface heat exchanger 122, the center heat exchanger 123, and the back surface heat exchanger 124 use a plurality of heat transfer tubes having different diameters. Thereby, the ventilation efficiency by the uniform ventilation resistance is improved. Further, by causing the refrigerant to flow sequentially from the thickest heat transfer tube A to the intermediate heat transfer tube B and the thinnest heat transfer tube C during the heating operation, the heat transfer coefficient on the refrigerant side is improved.

図１１は、特許文献２に開示された空気調和機の熱交換器の空気調和機組込時の断面図である。図１１を参照して、空気調和機の熱交換器２００は、フィン２０４と伝熱管２０３から構成される前面側熱交換器２０１と、後面側熱交換器２０２とを備えている。熱交換器２００は、多段に折り曲げられ、前面側熱交換器２０１および後面側熱交換器２０２の一部における伝熱管２０３の列数を、後面側熱交換器２０２の他の部分における伝熱管２０３の列数より少なくしている。これにより、通風抵抗が削減でき、熱交換効率が低下した分を送風効率で補うことで性能を維持しながらコスト低減を図っている。
特開２００１−１７４０４７号公報 特開平９−２６４５５５号公報 FIG. 11 is a cross-sectional view of the air conditioner heat exchanger disclosed in Patent Document 2 when the air conditioner is assembled. Referring to FIG. 11, the heat exchanger 200 of the air conditioner includes a front side heat exchanger 201 including a fin 204 and a heat transfer tube 203, and a rear side heat exchanger 202. The heat exchanger 200 is bent in multiple stages, and the number of rows of the heat transfer tubes 203 in a part of the front side heat exchanger 201 and the rear side heat exchanger 202 is set as the number of rows of the heat transfer tubes 203 in the other part of the rear side heat exchanger 202. The number of columns is less. Thereby, ventilation resistance can be reduced, and cost reduction is aimed at maintaining performance by supplementing the part which heat exchange efficiency fell with ventilation efficiency.
JP 2001-174047 A JP-A-9-264555

しかしながら、特許文献１に開示された空気調和機の室内機１００は、伝熱管の管径と管配列を工夫する必要があるので、前面部熱交換器１２２および背面部熱交換器１２４内における伝熱管の管径が異なっている。また、前面部熱交換器１２２、中央部熱交換器１２３、および背面部熱交換器１２４における伝熱管の配列が異なっているため、特殊なフィンや特殊な伝熱管を製造する必要がある。よって、生産効率が低下し、コストが上昇する。   However, since the indoor unit 100 of the air conditioner disclosed in Patent Document 1 needs to devise the tube diameter and the tube arrangement of the heat transfer tubes, the heat transfer in the front surface heat exchanger 122 and the back surface heat exchanger 124 is required. The diameter of the heat pipe is different. Moreover, since the arrangement | sequence of the heat exchanger tube in the front part heat exchanger 122, the center part heat exchanger 123, and the back surface heat exchanger 124 differs, it is necessary to manufacture a special fin and a special heat exchanger tube. Thus, production efficiency is reduced and costs are increased.

また、特許文献２に開示された空気調和機の熱交換器２００は、伝熱管２０３の列数を少なくしているので熱交換可能な伝熱面積が減少する。よって、熱交換器の高性能化が図れない。   Moreover, since the heat exchanger 200 of the air conditioner disclosed in Patent Document 2 has a reduced number of rows of the heat transfer tubes 203, the heat transfer area capable of heat exchange is reduced. Therefore, the performance of the heat exchanger cannot be improved.

それゆえ本発明の目的は、高性能化が図れると共に、生産効率が上昇し、コスト低減を図ることのできる空気調和機の室内機を提供することである。   SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide an air conditioner indoor unit that can achieve high performance, increase production efficiency, and reduce costs.

この発明に従った空気調和機の室内機は、送風機と、少なくとも３台の熱交換器とを備えている。熱交換器は、送風機の周囲に配置され、互いに間隔をへだてて配置されたフィン群と、フィン群に接続されて内部を冷媒が流動する伝熱管群とを有している。各熱交換器が有しているそれぞれの伝熱管群の管径は熱交換器毎に略同じである。少なくとも３台の熱交換器は、少なくとも２台の熱交換器からなる第１熱交換器グループと、第１熱交換器グループの熱交換器における伝熱管群の管径より大きい管径を有する伝熱管群を含む少なくとも１台の熱交換器からなる第２熱交換器グループとにより構成される。第２熱交換器グループを、第１熱交換器グループよりも送風機に近い位置に配置したことを特徴とする。フィン群を伝熱管群が貫通し、伝熱管群が貫通するフィン群の主表面における伝熱管群の貫通位置は、ある方向に整列した１以上の列を構成するように配置され、フィン群の主表面における列の延在方向に垂直な方向における幅を、列の数で割った値を伝熱管群の１列分のフィンの幅とし、第１熱交換器グループにおける伝熱管群の１列分のフィンの幅が、第２熱交換器グループにおける伝熱管群の１列分のフィンの幅より小さく、第１熱交換器グループの伝熱管群の列の数が、第２熱交換器グループの伝熱管群の列の数より多いことを特徴とする。 The indoor unit of an air conditioner according to the present invention includes a blower and at least three heat exchangers. The heat exchanger includes a fin group disposed around the blower and spaced apart from each other, and a heat transfer tube group that is connected to the fin group and in which the refrigerant flows. The tube diameter of each heat exchanger tube group which each heat exchanger has is substantially the same for every heat exchanger. At least three heat exchangers have a pipe diameter larger than the pipe diameter of the first heat exchanger group including at least two heat exchangers and the heat transfer pipe group in the heat exchanger of the first heat exchanger group. And a second heat exchanger group including at least one heat exchanger including a heat tube group. The second heat exchanger group is arranged at a position closer to the blower than the first heat exchanger group. The heat transfer tube group penetrates the fin group, and the penetration position of the heat transfer tube group on the main surface of the fin group through which the heat transfer tube group penetrates is arranged to constitute one or more rows aligned in a certain direction, A value obtained by dividing the width in the direction perpendicular to the extending direction of the rows on the main surface by the number of rows is defined as the fin width for one row of the heat transfer tube group, and one row of the heat transfer tube group in the first heat exchanger group The width of the minute fin is smaller than the width of the fin for one row of the heat transfer tube group in the second heat exchanger group, and the number of rows of the heat transfer tube group in the first heat exchanger group is the second heat exchanger group. More than the number of rows of heat transfer tube groups.

本発明の空気調和機の室内機によれば、第１熱交換器グループの伝熱管群の管径が細い熱交換器は通風抵抗が少なくなるため、熱交換器を通過する空気の風量が増加できる。そのため、熱交換器での空気と冷媒の熱交換量が向上し、熱交換器全体として効率が向上し、空気調和機の室内機の高性能化を果たすことができる。   According to the indoor unit of the air conditioner of the present invention, a heat exchanger with a thin tube diameter of the heat transfer tube group of the first heat exchanger group has a reduced ventilation resistance, and thus the air volume passing through the heat exchanger increases. it can. Therefore, the amount of heat exchange between the air and the refrigerant in the heat exchanger is improved, the efficiency of the entire heat exchanger is improved, and the performance of the indoor unit of the air conditioner can be improved.

また、各熱交換器が有しているそれぞれの伝熱管群の管径は熱交換器毎に略同じであるため、生産効率を上昇し、コストの低減を図ることができる。   Moreover, since the tube diameter of each heat exchanger tube group which each heat exchanger has is substantially the same for every heat exchanger, production efficiency can be raised and cost reduction can be aimed at.

以下、図面に基づいて本発明の実施の形態を説明する。なお、以下の図面において同一または相当する部分には同一の参照番号を付し、その説明は繰り返さない。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.

（実施の形態１）
図１は、本発明の実施の形態１による空気調和機の室内機を示す側面図である。図１を参照して、実施の形態１による空気調和機の室内機を説明する。実施の形態１による空気調和機１０は、たとえば、図１に示すように、３台の熱交換器１１ａ、１１ｂ、１１ｃと、送風機１４とを備えている。３台の熱交換器１１ａ、１１ｂ、１１ｃは、それぞれ互いに間隔をへだてて配置されたフィン群１２ａ、１２ｂ、１２ｃと、フィン群１２ａ、１２ｂ、１２ｃに接続されて内部を冷媒が流動する伝熱管群１３ａ、１３ｂ、１３ｃとを有している。 (Embodiment 1)
FIG. 1 is a side view showing an indoor unit of an air conditioner according to Embodiment 1 of the present invention. With reference to FIG. 1, the indoor unit of the air conditioner by Embodiment 1 is demonstrated. The air conditioner 10 according to Embodiment 1 includes, for example, three heat exchangers 11a, 11b, and 11c and a blower 14, as shown in FIG. The three heat exchangers 11a, 11b, and 11c are respectively connected to the fin groups 12a, 12b, and 12c spaced apart from each other, and the heat transfer tubes that are connected to the fin groups 12a, 12b, and 12c and in which the refrigerant flows. Groups 13a, 13b and 13c.

熱交換器１１ａが有している伝熱管群１３ａの管径は、略同じである。同様に、熱交換器１１ｂが有している伝熱管群１３ｂの管径は略同じであり、熱交換器１１ｃが有している伝熱管群１３ｃの管径は略同じである。また、伝熱管群１３ｃの管径は、伝熱管群１３ａ、１３ｂの管径よりも大きい。   The tube diameter of the heat transfer tube group 13a included in the heat exchanger 11a is substantially the same. Similarly, the tube diameter of the heat transfer tube group 13b included in the heat exchanger 11b is substantially the same, and the tube diameter of the heat transfer tube group 13c included in the heat exchanger 11c is approximately the same. The tube diameter of the heat transfer tube group 13c is larger than the tube diameters of the heat transfer tube groups 13a and 13b.

第１熱交換器グループは、熱交換器１１ａと、熱交換器１１ｂからなる。第２熱交換器グループは、熱交換器１１ｃからなる。すなわち、第１熱交換器グループは少なくとも２台の熱交換器からなり、第２熱交換器グループは、第１熱交換器グループを構成する熱交換器の伝熱管群の管径より大きい管径の伝熱管群を有する熱交換器からなる。   The first heat exchanger group includes a heat exchanger 11a and a heat exchanger 11b. The second heat exchanger group includes a heat exchanger 11c. That is, the first heat exchanger group is composed of at least two heat exchangers, and the second heat exchanger group has a tube diameter larger than the tube diameter of the heat transfer tube group of the heat exchanger constituting the first heat exchanger group. It consists of a heat exchanger having a heat transfer tube group.

図１に示すように、熱交換器１１ａ、１１ｂ、１１ｃは、送風機１４の周囲に、送風機１４と近い順にそれぞれ配置されている。また、熱交換器１１ａ、１１ｂ、１１ｃにおいて、伝熱管群１３ａ、１３ｂ、１３ｃは、フィン群１２ａ、１２ｂ、１２ｃをそれぞれ貫通し、冷媒が伝熱管群１３ａ、１３ｂ、１３ｃの内部を流動する。熱交換器１１ａ、１１ｂ、１１ｃにおいて、送風機１４から送られた空気は、フィン群１２ａ、１２ｂ、１２ｃの間をそれぞれ流動する。   As shown in FIG. 1, the heat exchangers 11 a, 11 b, and 11 c are arranged around the blower 14 in the order close to the blower 14. In the heat exchangers 11a, 11b, and 11c, the heat transfer tube groups 13a, 13b, and 13c pass through the fin groups 12a, 12b, and 12c, respectively, and the refrigerant flows through the heat transfer tube groups 13a, 13b, and 13c. In the heat exchangers 11a, 11b, and 11c, the air sent from the blower 14 flows between the fin groups 12a, 12b, and 12c.

次に、空気調和機の室内機１０の動作方法について説明する。図１を参照して、送風機１４を運転して、熱交換器１１ａ、１１ｂ、１１ｃに空気を送り込む。また、冷媒を伝熱管群１３ａ、１３ｂ、１３ｃに流動させる。よって、熱交換器１１ａ、１１ｂ、１１ｃに送り込まれた空気は、伝熱管群１３ａ、１３ｂ、１３ｃを流れる冷媒により、冷却または過熱される。なお、熱交換器１１ａ、１１ｂ、１１ｃを通過した風量を風量１５ａ、１５ｂ、１５ｃと示し、冷媒の流路は図示していない。   Next, an operation method of the indoor unit 10 of the air conditioner will be described. With reference to FIG. 1, the air blower 14 is operated and air is sent into the heat exchangers 11a, 11b, and 11c. Further, the refrigerant is caused to flow through the heat transfer tube groups 13a, 13b, and 13c. Therefore, the air sent to the heat exchangers 11a, 11b, and 11c is cooled or overheated by the refrigerant flowing through the heat transfer tube groups 13a, 13b, and 13c. In addition, the air volume which passed heat exchanger 11a, 11b, 11c is shown as air volume 15a, 15b, 15c, and the flow path of a refrigerant | coolant is not shown in figure.

以上説明したように、実施の形態１に係る空気調和機の室内機１０によれば、第１熱交換器グループの２台の熱交換器１１ａ、１１ｂにおける伝熱管群の管径より大きい管径を有する伝熱管群を含む１台の熱交換器からなる第２熱交換器グループとにより構成される。よって、伝熱管群の管径が細い熱交換器１１ａ、１１ｂは通風抵抗が少なくなる。そのため、熱交換器１１ａ、１１ｂを通過する空気の風量１５ａ、１５ｂは増加できるので、熱交換器１１ａ、１１ｂでの空気と冷媒の熱交換量が向上する。したがって、熱交換器全体として効率が向上する。その結果、空気調和機の室内機１０は、高性能化を果たすことができる。   As described above, according to the indoor unit 10 of the air conditioner according to Embodiment 1, the pipe diameter larger than the pipe diameter of the heat transfer tube group in the two heat exchangers 11a and 11b of the first heat exchanger group. And a second heat exchanger group composed of one heat exchanger including a heat transfer tube group having Therefore, the heat exchangers 11a and 11b having a thin tube diameter of the heat transfer tube group have low ventilation resistance. Therefore, since the air volume 15a, 15b of the air passing through the heat exchangers 11a, 11b can be increased, the amount of heat exchange between the air and the refrigerant in the heat exchangers 11a, 11b is improved. Therefore, the efficiency of the heat exchanger as a whole is improved. As a result, the indoor unit 10 of the air conditioner can achieve high performance.

また、３台の熱交換器１１ａ、１１ｂ、１１ｃが有しているそれぞれの伝熱管群１３ａ、１３ｂ、１３ｃの管径が熱交換器毎に略同じである。よって、熱交換器において管径の異なる伝熱管群を配置する場合より、熱交換器の生産効率を上昇させることができる。その結果、空気調和機の室内機１０は、コストの低減を図ることができる。   Moreover, the tube diameter of each heat exchanger tube group 13a, 13b, 13c which the three heat exchangers 11a, 11b, 11c have is substantially the same for every heat exchanger. Therefore, the production efficiency of the heat exchanger can be increased as compared with the case where heat transfer tube groups having different tube diameters are arranged in the heat exchanger. As a result, the air conditioner indoor unit 10 can achieve cost reduction.

（実施の形態２）
図２は、本発明の実施の形態２における空気調和機の室内機を示す側面図である。図２を参照して、実施の形態２による空気調和機の室内機を説明する。図２を参照して、実施の形態２による空気調和機の室内機２０の構成は、基本的には図１に示した本発明の実施の形態１と同様であるが、管径の太い伝熱管群１３ｃより構成されている第２熱交換器グループを構成する熱交換器１１ｃを送風機１４に最も近い前面部に配置している点において異なる。 (Embodiment 2)
FIG. 2 is a side view showing the indoor unit of the air conditioner according to Embodiment 2 of the present invention. With reference to FIG. 2, the indoor unit of the air conditioner by Embodiment 2 is demonstrated. Referring to FIG. 2, the configuration of air conditioner indoor unit 20 according to the second embodiment is basically the same as that of the first embodiment of the present invention shown in FIG. The difference is that the heat exchanger 11c constituting the second heat exchanger group constituted by the heat tube group 13c is arranged on the front surface portion closest to the blower 14.

次に、空気調和機の室内機２０の動作方法について説明する。図２を参照して、送風機１４を運転して、熱交換器１１ａ、１１ｂ、１１ｃに空気を送り込む。また、冷媒を伝熱管群１３ａ、１３ｂ、１３ｃに流動させる。よって、熱交換器１１ａ、１１ｂ、１１ｃに送り込まれた空気は、伝熱管群１３ａ、１３ｂ、１３ｃを流れる冷媒により、冷却または過熱される。   Next, an operation method of the indoor unit 20 of the air conditioner will be described. With reference to FIG. 2, the air blower 14 is operated and air is sent into the heat exchangers 11a, 11b, and 11c. Further, the refrigerant is caused to flow through the heat transfer tube groups 13a, 13b, and 13c. Therefore, the air sent to the heat exchangers 11a, 11b, and 11c is cooled or overheated by the refrigerant flowing through the heat transfer tube groups 13a, 13b, and 13c.

以上説明したように、実施の形態２に係る空気調和機の室内機２０によれば、第２熱交換器グループを構成する熱交換器１１ｃを送風機の最も近い前面部に配置している。よって、熱交換器１１ｃの伝熱管群１３ｃの管径が大きいことから、熱交換器１１ｃは、３台の熱交換器１１ａ、１１ｂ、１１ｃのうち最も通風抵抗が大きい。最も通風抵抗が大きい熱交換器１１ｃを送風機１４における最も風速の早い前面部分に配置しているので、熱交換器１１ａ、１１ｂ、１１ｃに送り込まれる空気の風量１５ａ、１５ｂ、１５ｃは略同一となる。そのため、３台の熱交換器１１ａ、１１ｂ、１１ｃにおける風速分布が均一となり、３台の熱交換器１１ａ、１１ｂ、１１ｃのそれぞれが熱交換に有効に寄与することができる。その結果、空気調和機の室内機２０は、さらに高性能化を果たすことができる。   As explained above, according to the indoor unit 20 of the air conditioner according to Embodiment 2, the heat exchanger 11c constituting the second heat exchanger group is arranged on the front surface portion closest to the blower. Therefore, since the tube diameter of the heat transfer tube group 13c of the heat exchanger 11c is large, the heat exchanger 11c has the largest ventilation resistance among the three heat exchangers 11a, 11b, and 11c. Since the heat exchanger 11c having the highest ventilation resistance is disposed in the front portion of the blower 14 with the fastest wind speed, the air flow rates 15a, 15b, and 15c of the air fed into the heat exchangers 11a, 11b, and 11c are substantially the same. . Therefore, the wind speed distribution in the three heat exchangers 11a, 11b, and 11c is uniform, and each of the three heat exchangers 11a, 11b, and 11c can contribute to heat exchange effectively. As a result, the indoor unit 20 of the air conditioner can achieve higher performance.

（実施の形態３）
図３は、本発明の実施の形態３における空気調和機の室内機を示す側面図である。図３を参照して、実施の形態３による空気調和機の室内機を説明する。図３を参照して、実施の形態３による空気調和機の室内機３０の構成は、基本的には図２に示した本発明の実施の形態２と同様であるが、冷房運転時冷媒流入部３６ａと、暖房時冷媒流出部３６ｂと、冷房運転時冷媒流出部３７ａと、暖房時冷媒流入部３７ｂと、冷媒の流路３７ｃとを設けている点において異なる。 (Embodiment 3)
FIG. 3 is a side view showing an indoor unit of an air conditioner according to Embodiment 3 of the present invention. With reference to FIG. 3, the indoor unit of the air conditioner by Embodiment 3 is demonstrated. Referring to FIG. 3, the configuration of air conditioner indoor unit 30 according to the third embodiment is basically the same as that of the second embodiment of the present invention shown in FIG. The difference is that a portion 36a, a heating refrigerant outflow portion 36b, a cooling operation refrigerant outflow portion 37a, a heating refrigerant inflow portion 37b, and a refrigerant flow path 37c are provided.

具体的には、暖房運転時には、第２熱交換器グループを構成する熱交換器１１ｃに暖房時冷媒流入部３７ｂを設けると共に、第１熱交換器グループを構成する熱交換器１１ａに暖房時冷媒流出部３６ｂを設けている。一方、冷房運転時には、第１熱交換器グループを構成する熱交換器１１ａに冷房時冷媒流入部３６ａを設けると共に、第２熱交換器グループを構成する熱交換器１１ｃに冷房時冷媒流出部３７ａを設けている。   Specifically, during the heating operation, the heating refrigerant inflow portion 37b is provided in the heat exchanger 11c constituting the second heat exchanger group, and the heating refrigerant is provided in the heat exchanger 11a constituting the first heat exchanger group. An outflow portion 36b is provided. On the other hand, at the time of cooling operation, the cooling-time refrigerant inflow portion 36a is provided in the heat exchanger 11a constituting the first heat exchanger group, and the cooling-time refrigerant outflow portion 37a is provided in the heat exchanger 11c constituting the second heat exchanger group. Is provided.

また、空気調和機の室内機３０では、第１熱交換器グループを構成する熱交換器１１ａ、１１ｂは、それぞれの伝熱管群１３ａ、１３ｂの管径が互いに異なる構成としている。本実施の形態では、たとえば、熱交換器１１ａの伝熱管群１３ａの管径は、熱交換器１１ｂの管径よりも細い構成としている。   Moreover, in the indoor unit 30 of the air conditioner, the heat exchangers 11a and 11b constituting the first heat exchanger group are configured such that the tube diameters of the heat transfer tube groups 13a and 13b are different from each other. In the present embodiment, for example, the tube diameter of the heat transfer tube group 13a of the heat exchanger 11a is configured to be thinner than the tube diameter of the heat exchanger 11b.

なお、冷媒流入部とは、冷媒を伝熱管群に流すために冷媒を投入するための部材を意味し、冷媒流出部とは、伝熱管群を流れた冷媒を排出するための部材を意味する。   Note that the refrigerant inflow portion means a member for charging the refrigerant to flow the refrigerant to the heat transfer tube group, and the refrigerant outflow portion means a member for discharging the refrigerant that has flowed through the heat transfer tube group. .

暖房運転時の冷媒の流路３７ｃは、暖房時冷媒流入部３７ｂから冷媒が流入され、伝熱管群の管径が太い順に熱交換器１１ｃ、１１ｂ、１１ａにおける伝熱管群１３ｃ、１３ｂ、１３ａへと順次流れ、暖房時冷媒流出部３６ｂから排出されるように冷媒回路を構成している。   In the refrigerant flow path 37c during the heating operation, the refrigerant flows in from the refrigerant inflow portion 37b during heating, and the heat transfer tube groups 13c, 13b, and 13a in the heat exchangers 11c, 11b, and 11a are arranged in descending order. The refrigerant circuit is configured so as to flow sequentially and discharged from the refrigerant outflow portion 36b during heating.

一方、冷房運転時の冷媒の流路３７ｃは、冷房時冷媒流入部３６aから冷媒が流入され、伝熱管群の管径が細い順に熱交換器１１ａ、１１ｂ、１１ｃにおける伝熱管群１３ａ、１３ｂ、１３ｃへと順次流れ、冷房時冷媒流出部３７ａから排出されるように冷媒回路を構成している。   On the other hand, in the refrigerant flow path 37c during the cooling operation, the refrigerant is introduced from the cooling refrigerant inflow portion 36a, and the heat transfer tube groups 13a, 13b, 13b in the heat exchangers 11a, 11b, 11c The refrigerant circuit is configured so as to flow sequentially to 13c and be discharged from the refrigerant outflow portion 37a during cooling.

次に、空気調和機の室内機３０の動作方法について説明する。図３を参照して、送風機１４を運転して、熱交換器１１ａ、１１ｂ、１１ｃに空気を送り込む。   Next, an operation method of the indoor unit 30 of the air conditioner will be described. With reference to FIG. 3, the air blower 14 is operated to send air into the heat exchangers 11a, 11b, and 11c.

暖房運転時には、冷媒が暖房時冷媒流入部３７ｂから流入され、流路３７ｃを流れ、暖房時冷媒流出部３６ｂから排出される。よって、熱交換器１１ｃ、１１ｂ、１１ａに送り込まれた空気は、流路３７ｃを構成する伝熱管群１３ｃ、１３ｂ、１３ａを流れる冷媒により加熱される。   During the heating operation, the refrigerant flows in from the heating refrigerant inflow portion 37b, flows through the flow path 37c, and is discharged from the heating refrigerant inflow portion 36b. Therefore, the air sent into the heat exchangers 11c, 11b, and 11a is heated by the refrigerant flowing through the heat transfer tube groups 13c, 13b, and 13a constituting the flow path 37c.

暖房運転時における暖房時冷媒流入部３７ｂでの冷媒の状態は、高温高圧の気体状態である。熱交換器１１ｃ、１１ｂ、１１ａの流路３７ｃを構成する伝熱管群１３ｃ、１３ｂ、１３ａ内を流動する際に、冷媒は空気と熱交換する。その際、冷媒は空気により冷却されるため、流路３７ｃの途中で気液二相状態となり、暖房時冷媒流出部３６ｂでは冷媒は低温高圧の液体へと変化する。   The state of the refrigerant in the heating refrigerant inflow portion 37b during the heating operation is a high-temperature and high-pressure gas state. When flowing in the heat transfer tube groups 13c, 13b, 13a constituting the flow path 37c of the heat exchangers 11c, 11b, 11a, the refrigerant exchanges heat with air. At this time, since the refrigerant is cooled by air, the refrigerant enters a gas-liquid two-phase state in the middle of the flow path 37c, and the refrigerant changes into a low-temperature and high-pressure liquid in the refrigerant outlet portion 36b during heating.

暖房運転時において、冷媒の流路３７ｃ中の冷媒は、暖房時冷媒流出部３６ｂに近づくにしたがって、二相状態の冷媒における液状態の比率が上昇していく。そのため、冷媒の流速は低下していき、空気と伝熱管群との熱伝達が低下していく。   During the heating operation, the ratio of the liquid state in the refrigerant in the two-phase state increases as the refrigerant in the refrigerant passage 37c approaches the heating refrigerant outflow portion 36b. Therefore, the flow rate of the refrigerant decreases, and heat transfer between the air and the heat transfer tube group decreases.

しかしながら、空気調和機の室内機３０では、暖房時冷媒流出部３６ｂを構成する熱交換器１１ａ、１１ｂの伝熱管群１３ａ、１３ｂの管径は、相対的に伝熱管群１３ｃの管径より細い。そのため、液状態の比率が上昇している過冷却状態の冷媒の流速低下が抑制され、暖房時冷媒流出部３６ｂ付近における冷媒と伝熱管群内の熱伝達が促進される。   However, in the indoor unit 30 of the air conditioner, the tube diameters of the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b constituting the heating refrigerant outflow portion 36b are relatively smaller than the tube diameter of the heat transfer tube group 13c. . Therefore, a decrease in the flow rate of the supercooled refrigerant in which the ratio of the liquid state is increased is suppressed, and heat transfer between the refrigerant and the heat transfer tube group in the vicinity of the refrigerant outlet portion 36b during heating is promoted.

一方、冷房運転時には、冷媒が冷房時冷媒流入部３６ａから流入され、冷媒の流路３７ｃを流れ、冷房時冷媒流出部３７ａから排出される。よって、熱交換器１１ａ、１１ｂ、１１ｃを流れる冷媒により、空気は冷却される。   On the other hand, during the cooling operation, the refrigerant flows in from the cooling refrigerant inflow portion 36a, flows through the refrigerant flow path 37c, and is discharged from the cooling refrigerant outflow portion 37a. Therefore, the air is cooled by the refrigerant flowing through the heat exchangers 11a, 11b, and 11c.

冷房時における冷房時冷媒流入部３６ａでの冷媒の状態は、低温低圧の液比率の高い二相状態である。流路３７ｃを構成する熱交換器１１ａ、１１ｂ、１１ｃにおける伝熱管群１３ａ、１３ｂ、１３ｃ内を流動する際に、冷媒は空気と熱交換する。その際、冷媒は空気により過熱されるため、冷房時冷媒流出部３７ａでは冷媒は低温低圧の気体冷媒へと変化する。   The state of the refrigerant in the cooling refrigerant inflow portion 36a during cooling is a two-phase state in which the liquid ratio of low temperature and low pressure is high. When flowing in the heat transfer tube groups 13a, 13b, and 13c in the heat exchangers 11a, 11b, and 11c constituting the flow path 37c, the refrigerant exchanges heat with air. At that time, since the refrigerant is superheated by air, the refrigerant changes into a low-temperature and low-pressure gaseous refrigerant in the cooling-time refrigerant outflow portion 37a.

冷房運転時において、流路３７ｃ中の冷媒は、冷房時冷媒流出部３７ａに近づくにしたがって、二相状態の冷媒における気体状態の比率が上昇していく。そのため、流路３７ｃを構成する伝熱管群１３ａ、１３ｂ、１３ｃを進むにつれ、その中での圧力損失が増大していく。その結果、熱交換器全体としての熱伝達率が低下していく。   During the cooling operation, the ratio of the gas state in the refrigerant in the two-phase state increases as the refrigerant in the flow path 37c approaches the cooling outflow portion 37a. Therefore, as the heat transfer tube groups 13a, 13b, and 13c constituting the flow path 37c are advanced, the pressure loss therein increases. As a result, the heat transfer coefficient as a whole heat exchanger decreases.

しかしながら、空気調和機の室内機３０では、冷房時冷媒流出部３７ａを構成する熱交換器１１ｃの伝熱管群１３ｃの管径は太い。そのため、気体状態の比率が上昇している過熱状態の冷媒の圧力損失の増大が抑制され、熱伝達率の低下が抑制できる。   However, in the indoor unit 30 of the air conditioner, the tube diameter of the heat transfer tube group 13c of the heat exchanger 11c constituting the cooling refrigerant outflow portion 37a is large. Therefore, an increase in the pressure loss of the superheated refrigerant in which the gas state ratio is increasing can be suppressed, and a decrease in the heat transfer coefficient can be suppressed.

また、除湿運転時には、冷媒の流路３７ｃは冷房運転時と同様である。具体的には、風量を抑え、湿度を優先的に取り除くサイクル、すなわち弱冷房運転とする。よって、冷媒の流動状態も冷房運転時と同様である。   In the dehumidifying operation, the refrigerant flow path 37c is the same as in the cooling operation. Specifically, a cycle in which the air volume is suppressed and humidity is preferentially removed, that is, a weak cooling operation is performed. Therefore, the flow state of the refrigerant is the same as in the cooling operation.

なお、冷房運転時冷媒流入部３６ａと暖房時冷媒流出部３６ｂは、冷媒の流入および排出を兼用する１の配管としても良いし、２の配管としても良い。同様に、冷房運転時冷媒流出部３７ａと暖房時冷媒流入部３７ｂは、冷媒の流入および排出を兼用する１の配管としても良いし、２の配管としても良い。   Note that the refrigerant inflow portion 36a during cooling operation and the refrigerant outflow portion 36b during heating may be one pipe that also serves as the refrigerant inflow and exhaust, or may be two pipes. Similarly, the refrigerant outflow portion 37a during cooling operation and the refrigerant inflow portion 37b during heating may be one pipe that also serves as the refrigerant inflow and exhaust, or may be two pipes.

以上説明したように、実施の形態３における空気調和機の室内機３０によれば、暖房運転時には、第２熱交換器グループを構成する熱交換器の少なくとも１つに暖房時冷媒流入部３７ｂを設けると共に、第１熱交換器グループを構成する熱交換器の少なくとも１つに暖房時冷媒流出部３６ｂを設けている。そして、第２熱交換器グループを構成する熱交換器１１ｃから、第１熱交換器グループを構成する熱交換器１１ｂ、１１ａへ冷媒を流動させている。また、第１熱交換器グループのうち相対的に伝熱管群の管径の大きな熱交換器１１ｂから相対的に伝熱管群の管径の小さな熱交換器１１ａに順次流動させている。よって、高温高圧の冷媒が、流路３７ｃを進むにつれて低温高圧に変化しても、伝熱管群の管径が細くなるので、流速低下が抑制される。その結果、空気調和機の室内機３０は、高性能化を図ることができる。   As described above, according to the indoor unit 30 of the air conditioner in Embodiment 3, the heating-time refrigerant inflow portion 37b is provided in at least one of the heat exchangers constituting the second heat exchanger group during the heating operation. At the same time, at least one of the heat exchangers constituting the first heat exchanger group is provided with a heating refrigerant outflow portion 36b. And the refrigerant is made to flow from heat exchanger 11c which constitutes the 2nd heat exchanger group to heat exchangers 11b and 11a which constitute the 1st heat exchanger group. Moreover, it is made to flow sequentially from the heat exchanger 11b with a relatively large diameter of the heat transfer tube group to the heat exchanger 11a with a relatively small diameter of the heat transfer tube group in the first heat exchanger group. Therefore, even if the high-temperature and high-pressure refrigerant changes to low-temperature and high-pressure as it travels through the flow path 37c, the pipe diameter of the heat transfer tube group becomes thin, so that a decrease in flow rate is suppressed. As a result, the indoor unit 30 of the air conditioner can achieve high performance.

また、冷房運転時には、第１熱交換器グループを構成する熱交換器の少なくとも１つに冷房時冷媒流入部３６ａを設けると共に、第２熱交換器グループを構成する熱交換器の少なくとも１つに冷房時冷媒流出部３７ａを設けている。そして、第１熱交換器グループを構成する熱交換器１１ａ、１１ｂから、第２熱交換器グループを構成する熱交換器１１ｃへ冷媒を流動させている。また、第１熱交換器グループのうち相対的に伝熱管群の管径の小さな熱交換器１１ａから相対的に伝熱管群の管径の大きな熱交換器１１ｂに順次流動させている。よって、低温低圧の液比率の高い二相状態の冷媒が流路３７ｃを進むにつれて、気体比率が高くなる場合であっても、伝熱管群の管径が太くなるので、伝熱管群内での圧力損失の増大を抑制できる。その結果、空気調和機の室内機３０は、高性能化を図ることができる。   Further, during cooling operation, at least one of the heat exchangers constituting the first heat exchanger group is provided with a cooling refrigerant inflow portion 36a, and at least one of the heat exchangers constituting the second heat exchanger group is provided. A cooling refrigerant outflow portion 37a is provided. And the refrigerant is made to flow from heat exchanger 11a, 11b which constitutes the 1st heat exchanger group to heat exchanger 11c which constitutes the 2nd heat exchanger group. Moreover, it is made to flow sequentially from the heat exchanger 11a with a relatively small diameter of the heat transfer tube group to the heat exchanger 11b with a relatively large diameter of the heat transfer tube group in the first heat exchanger group. Accordingly, as the refrigerant in a two-phase state with a high liquid ratio of low temperature and low pressure advances through the flow path 37c, the tube diameter of the heat transfer tube group becomes thick even if the gas ratio becomes high. Increase in pressure loss can be suppressed. As a result, the indoor unit 30 of the air conditioner can achieve high performance.

（実施の形態４）
図４は、本発明の実施の形態４における空気調和機の室内機を示す側面図である。図４を参照して、実施の形態４による空気調和機の室内機を説明する。図４を参照して、実施の形態４による空気調和機の室内機４０の構成は、基本的には図３に示した本発明の実施の形態３と同様であるが、第１熱交換器グループと第２熱交換器グループとを接続する冷媒の流路３７ｃに絞り手段４８を設けている点において異なる。 (Embodiment 4)
FIG. 4 is a side view showing an indoor unit of an air conditioner according to Embodiment 4 of the present invention. With reference to FIG. 4, the indoor unit of the air conditioner by Embodiment 4 is demonstrated. Referring to FIG. 4, the configuration of the indoor unit 40 of the air conditioner according to the fourth embodiment is basically the same as that of the third embodiment of the present invention shown in FIG. 3, but the first heat exchanger The difference is that a throttle means 48 is provided in the refrigerant flow path 37c connecting the group and the second heat exchanger group.

具体的には、第１熱交換器グループを構成している、フィン群１２ｂの幅がＬｂである熱交換器１１ｂの伝熱管群１３ｂと、第２熱交換器グループを構成している、フィン群１２ｃの幅がＬｃである熱交換器１１ｃの伝熱管群１３ｃとの間に絞り手段４８を設けている。   Specifically, the heat transfer tube group 13b of the heat exchanger 11b in which the width of the fin group 12b is Lb, which constitutes the first heat exchanger group, and the fins that constitute the second heat exchanger group A throttle means 48 is provided between the group 12c and the heat transfer tube group 13c of the heat exchanger 11c whose width is Lc.

次に、空気調和機の室内機４０の動作方法について説明する。暖房運転時および冷房運転時については、実施の形態３における空気調和機の室内機３０と同様であるので、その説明は繰り返さない。なお、暖房運転時および冷房運転時においては、絞り手段４８は作用させない。以下、空気調和機の室内機４０の再熱除湿運転時について説明する。   Next, an operation method of the indoor unit 40 of the air conditioner will be described. Since the heating operation and the cooling operation are the same as those of the indoor unit 30 of the air conditioner according to Embodiment 3, the description thereof will not be repeated. It should be noted that the throttle means 48 does not act during heating operation and cooling operation. Hereinafter, the reheat dehumidifying operation of the indoor unit 40 of the air conditioner will be described.

再熱除湿運転時には、送風機１４を運転して、熱交換器１１ａ、１１ｂ、１１ｃに空気を送り込む。冷媒は、冷房時冷媒流入部３６ａから流入され、伝熱管群１３ａ、１３ｂを流れ、絞り手段４８を通過して、伝熱管群１３ｃを流れ、冷房時冷媒流出部３７ａから排出される。そして、熱交換器１１ａ、１１ｂ、１１ｃを流れる冷媒と、送り込まれた空気との間で熱交換が行なわれる。   During the reheat dehumidifying operation, the blower 14 is operated to send air into the heat exchangers 11a, 11b, and 11c. The refrigerant flows from the cooling refrigerant inflow portion 36a, flows through the heat transfer tube groups 13a and 13b, passes through the throttle means 48, flows through the heat transfer tube group 13c, and is discharged from the cooling refrigerant outflow portion 37a. And heat exchange is performed between the refrigerant | coolant which flows through heat exchanger 11a, 11b, 11c, and the sent air.

次に、再熱除湿運転時における冷媒の流れについて説明する。再熱除湿運転時には、冷媒は、圧縮機、室外熱交換器などを経て高温高圧とされる。そして、高温高圧とされた冷媒は冷房時冷媒流入部３６ａより流入し、伝熱管群の管径の細い第１熱交換器グループを構成する熱交換器１１ａ、１１ｂを流動する。次いで、絞り手段４８を通過する際に、絞り手段４８により冷媒は減圧され低温低圧の状態になる。その後、第２熱交換器グループを構成する伝熱管群の管径の太い熱交換器１１ｃへ冷媒は流入し、冷房時冷媒流出部３７ａより流出する。すなわち、除湿運転時には、第１熱交換器グループ内では冷媒は高温であるため、第１熱交換器グループが凝縮部として作用し、第２熱交換器グループ内では冷媒は低温であるため、第２熱交換器グループが蒸発部として作用するように冷媒を流動させる。   Next, the flow of the refrigerant during the reheat dehumidification operation will be described. During the reheat dehumidifying operation, the refrigerant is brought to a high temperature and pressure through a compressor, an outdoor heat exchanger, and the like. And the refrigerant | coolant made into the high temperature / high pressure flows in from the refrigerant | coolant inflow part 36a at the time of a cooling, and flows through the heat exchangers 11a and 11b which comprise the 1st heat exchanger group with a thin pipe diameter of a heat exchanger tube group. Next, when passing through the throttle means 48, the refrigerant is depressurized by the throttle means 48 and becomes a low temperature and low pressure state. Thereafter, the refrigerant flows into the heat exchanger 11c having the large diameter of the heat transfer tube group constituting the second heat exchanger group, and flows out from the cooling refrigerant outflow portion 37a. That is, during the dehumidifying operation, since the refrigerant is hot in the first heat exchanger group, the first heat exchanger group acts as a condensing unit, and since the refrigerant is low in the second heat exchanger group, The refrigerant is caused to flow so that the two heat exchanger groups act as an evaporation section.

熱交換器に送り込まれた空気は、熱交換器１１ｃでは、冷媒が低温低圧であるので除湿される。一方、熱交換器１１ａ、１１ｂでは、冷媒が高温高圧であるので、空気は過熱される。よって、第２熱交換器グループで冷却、除湿された空気は、第１熱交換器グループにより温められた空気と混合され、空気全体として温度を低下させることなく除湿を行わせる。   The air sent to the heat exchanger is dehumidified in the heat exchanger 11c because the refrigerant is at low temperature and low pressure. On the other hand, in the heat exchangers 11a and 11b, since the refrigerant is high temperature and pressure, the air is overheated. Therefore, the air cooled and dehumidified by the second heat exchanger group is mixed with the air warmed by the first heat exchanger group, and the entire air is dehumidified without lowering the temperature.

なお、絞り手段４８とは、再熱除湿運転時に第１熱交換器グループから第２熱交換器グループへ流れる冷媒を減圧する部材を意味する。絞り手段４８は、たとえば、電磁弁、キャピラリチューブ等で構成されている。   The throttle means 48 means a member that depressurizes the refrigerant flowing from the first heat exchanger group to the second heat exchanger group during the reheat dehumidifying operation. The throttle means 48 is constituted by, for example, an electromagnetic valve, a capillary tube or the like.

以上説明したように、実施の形態４における空気調和機の室内機４０によれば、第１熱交換器グループと第２熱交換器グループとを接続する冷媒の流路３７ｃに絞り手段４８を設けている。そのため、絞り手段４８を作用させることにより、再熱除湿運転が可能となる。   As described above, according to the indoor unit 40 of the air conditioner in the fourth embodiment, the throttle means 48 is provided in the refrigerant flow path 37c that connects the first heat exchanger group and the second heat exchanger group. ing. Therefore, the reheat dehumidifying operation can be performed by operating the throttle means 48.

また、除湿運転時には、第１熱交換器グループが凝縮部で、第２熱交換器グループが蒸発部として作用するように冷媒を流動させている。よって、冷媒を第１熱交換器グループでは高温高圧とし、第２熱交換器グループでは低温低圧とすることができる。そして、凝縮部を構成する第１熱交換器グループは伝熱管群の管径が細いため、実施の形態３で示したように凝縮側の熱伝達率は向上する。一方、蒸発部を構成する第２熱交換器グループは伝熱管群の管径が太いため、同様に、蒸発側の熱伝達率は向上する。その結果、空気調和機の室内機４０は、大幅に除湿性能を向上させることが可能となり、さらに高性能化を図ることができる。   Further, during the dehumidifying operation, the refrigerant is caused to flow so that the first heat exchanger group acts as a condenser and the second heat exchanger group acts as an evaporator. Therefore, the refrigerant can be set to a high temperature and a high pressure in the first heat exchanger group, and to a low temperature and a low pressure in the second heat exchanger group. And since the 1st heat exchanger group which comprises a condensation part has the thin pipe diameter of a heat exchanger tube group, as shown in Embodiment 3, the heat transfer rate by the side of a condensation improves. On the other hand, since the second heat exchanger group constituting the evaporator section has a large heat transfer tube group, the heat transfer coefficient on the evaporation side is improved. As a result, the indoor unit 40 of the air conditioner can greatly improve the dehumidifying performance, and can achieve higher performance.

次に、実施の形態４における空気調和機の室内機４０の変形例を説明する。図５は、本発明の実施の形態４における空気調和機の室内機４０の変形例における熱交換器１１ａおよび１１ｃの側面図である。   Next, the modification of the indoor unit 40 of the air conditioner in Embodiment 4 is demonstrated. FIG. 5 is a side view of heat exchangers 11a and 11c in a modification of indoor unit 40 of the air conditioner according to Embodiment 4 of the present invention.

図５を参照して、熱交換器１１ａ、１１ｃでは、フィン群１２ａ、１２ｃを伝熱管群１３ａ、１３ｃが貫通し、フィン群１２ａ、１２ｃの主表面における伝熱管群１３ａ、１３ｃの貫通位置は、ある方向（図において縦方向）に２列に並ぶように構成されている。   Referring to FIG. 5, in heat exchangers 11a and 11c, heat transfer tube groups 13a and 13c pass through fin groups 12a and 12c, and the through-hole positions of heat transfer tube groups 13a and 13c on the main surfaces of fin groups 12a and 12c are as follows. These are arranged in two rows in a certain direction (vertical direction in the figure).

フィン群１２ａ、１２ｃの主表面における列の延在方向に垂直な方向（図において横方向）における幅を、列の数で割った値を伝熱管群１３ａ、１３ｃの１列分のフィンの幅とする。図５に示すように、熱交換器１１ａ、１１ｃの一列分のフィン１２ａ、１２ｃの幅は、それぞれＬc／２、Ｌa／２となる。本変形例では、それぞれの一列分のフィンの幅は、Ｌc／２＞Ｌa／２となる関係が成立している。   Fin width of one row of heat transfer tube groups 13a and 13c, which is obtained by dividing the width in the direction perpendicular to the extending direction of the rows (lateral direction in the figure) on the main surface of fin groups 12a and 12c by the number of rows And As shown in FIG. 5, the widths of the fins 12a and 12c for one row of the heat exchangers 11a and 11c are Lc / 2 and La / 2, respectively. In the present modification, the relationship that the widths of the fins for one row are Lc / 2> La / 2 is established.

本変形例によれば、フィン群を伝熱管群が貫通し、伝熱管群が貫通するフィン群の主表面における伝熱管群の貫通位置は、ある方向に整列した１以上の列を構成するように配置され、第１熱交換器グループにおける伝熱管群の１列分のフィンの幅が、第２熱交換器グループにおける伝熱管群の１列分のフィンの幅より小さくしている。すなわち、送風機１４から近くに位置し、風速が早く、伝熱管群１３ｃの管径が太い第２熱交換器グループを構成する熱交換器１１ｃにおける一列分のフィンの幅を大きくしている。そのため、熱交換器１１ｃの熱伝達効率を向上させることが可能となる。一方、送風機１４から比較的遠くに位置し、風速が遅く、伝熱管群１３ａの管径が細い第１熱交換器グループを構成する熱交換器１１ａの一列分のフィンの幅を小さくしている。そのため、通風抵抗を低減し、送風機動力を削減することができ、送風機効率を改善することが可能となる。その結果、熱交換器全体としての効率を向上させることが可能となる。   According to this modification, the heat transfer tube group penetrates the fin group, and the penetration position of the heat transfer tube group on the main surface of the fin group through which the heat transfer tube group penetrates constitutes one or more rows aligned in a certain direction. The width of the fins for one row of the heat transfer tube group in the first heat exchanger group is smaller than the width of the fins for one row of the heat transfer tube group in the second heat exchanger group. That is, the fin width for one row in the heat exchanger 11c that constitutes the second heat exchanger group that is located close to the blower 14, has a high wind speed, and has a large tube diameter of the heat transfer tube group 13c is increased. Therefore, it becomes possible to improve the heat transfer efficiency of the heat exchanger 11c. On the other hand, the fin width for one row of the heat exchanger 11a constituting the first heat exchanger group that is positioned relatively far from the blower 14, the wind speed is slow, and the tube diameter of the heat transfer tube group 13a is small. . Therefore, ventilation resistance can be reduced, fan power can be reduced, and fan efficiency can be improved. As a result, the efficiency of the entire heat exchanger can be improved.

（実施の形態５）
図６は、本発明の実施の形態５における空気調和機の室内機を示す側面図である。図６を参照して、実施の形態５による空気調和機の室内機を説明する。図６を参照して、実施の形態５による空気調和機の室内機５０の構成は、基本的には図４に示した本発明の実施の形態４と同様であるが、第１熱交換器グループを構成する熱交換器１１ａ、１１ｂにおける伝熱管群１３ａ、１３ｂの列の数を２列から３列に増やしている点において異なる。 (Embodiment 5)
FIG. 6 is a side view showing an indoor unit of an air conditioner according to Embodiment 5 of the present invention. With reference to FIG. 6, the indoor unit of the air conditioner by Embodiment 5 is demonstrated. Referring to FIG. 6, the configuration of air conditioner indoor unit 50 according to the fifth embodiment is basically the same as that of the fourth embodiment of the present invention shown in FIG. The difference is that the number of rows of the heat transfer tube groups 13a and 13b in the heat exchangers 11a and 11b constituting the group is increased from two rows to three rows.

具体的には、図６に示すように、伝熱管群の管径が細い熱交換器１１ａ、１１ｂでは伝熱管群１３ａ、１３ｂの列の数が３列となっており、伝熱管群の管径が太い熱交換器１１ｃでは伝熱管群１３ｃの列の数が２列となっている。流路３７ｃは、基本的には実施の形態４による空気調和機の室内機４０と同様であるが、熱交換器１１ａ、１１ｂで列の数を１列ずつ増やした分が長くなる。なお、熱交換器１１ａ、１１ｂは、列の数を３列としているが、実施の形態４の変形例で示したように、フィン１２ａ、１２ｂの１列分の幅は、フィン１２ｃの１列分の幅より狭い点においては同様である。   Specifically, as shown in FIG. 6, in the heat exchangers 11 a and 11 b where the tube diameter of the heat transfer tube group is thin, the number of rows of the heat transfer tube groups 13 a and 13 b is three, and the tubes of the heat transfer tube group In the heat exchanger 11c having a large diameter, the number of rows of the heat transfer tube groups 13c is two. The flow path 37c is basically the same as the indoor unit 40 of the air conditioner according to Embodiment 4, but the amount of increase in the number of rows by one in the heat exchangers 11a and 11b becomes longer. The heat exchangers 11a and 11b have three rows. However, as shown in the modification of the fourth embodiment, the width of one row of the fins 12a and 12b is one row of the fins 12c. The same is true for points narrower than the minute width.

空気調和機の室内機５０の動作方法については、暖房運転時、冷房運転時、再熱除湿運転時については、実施の形態４における空気調和機の室内機４０と同様であるので、その説明は繰り返さない。   About the operation method of the indoor unit 50 of an air conditioner, since it is the same as that of the indoor unit 40 of the air conditioner in Embodiment 4 about the heating operation, the cooling operation, and the reheat dehumidification operation, the description Do not repeat.

なお、上述したように、流路３７ｃは、熱交換器１１ａ、１１ｂにおいて列の数が増えた分だけ長くなる。   As described above, the flow path 37c becomes longer as the number of rows in the heat exchangers 11a and 11b increases.

以上説明したように、実施の形態５における空気調和機の室内機５０によれば、第１熱交換器グループの伝熱管群の列の数が、第２熱交換器グループの伝熱管群の列の数より多い構成としている。よって、列の数を増やした分だけ熱交換可能な表面積を増加させることが可能となる。その結果、熱伝達率をさらに向上させることができる。   As explained above, according to the indoor unit 50 of the air conditioner in the fifth embodiment, the number of rows of the heat transfer tube groups in the first heat exchanger group is equal to the row of the heat transfer tube groups in the second heat exchanger group. More than the number. Therefore, it is possible to increase the heat exchangeable surface area by the number of rows increased. As a result, the heat transfer rate can be further improved.

また、列の数を増やしても、第１熱交換器グループにおける伝熱管群の１列分のフィンの幅が、第２熱交換機グループにおける伝熱管群の１列分のフィンの幅より小さくしている。よって、列の数を増加しても、大きく通風抵抗を悪化させることがない。その結果、空気調和機の室内機５０は、さらに高性能化を図ることができる。   Even if the number of rows is increased, the width of the fins for one row of the heat transfer tube group in the first heat exchanger group is made smaller than the width of the fins for one row of the heat transfer tube group in the second heat exchanger group. ing. Therefore, even if the number of rows is increased, the ventilation resistance is not greatly deteriorated. As a result, the indoor unit 50 of the air conditioner can achieve higher performance.

（実施の形態６）
図７は、本発明の実施の形態６における空気調和機の室内機を示す側面図である。図７を参照して、実施の形態６による空気調和機の室内機を説明する。図７を参照して、実施の形態６による空気調和機の室内機６０の構成は、基本的には図６に示した本発明の実施の形態５と同様であるが、冷房運転時冷媒流入部６６ａと、暖房時冷媒流出部６６ｂとを、第１熱交換器グループを構成している熱交換器１１ａ、１１ｂの全てに設けている点において異なる。 (Embodiment 6)
FIG. 7 is a side view showing an indoor unit of an air conditioner according to Embodiment 6 of the present invention. With reference to FIG. 7, the indoor unit of the air conditioner by Embodiment 6 is demonstrated. Referring to FIG. 7, the configuration of air conditioner indoor unit 60 according to the sixth embodiment is basically the same as that of the fifth embodiment of the present invention shown in FIG. It differs in the point which has provided the part 66a and the refrigerant | coolant outflow part 66b at the time of heating in all the heat exchangers 11a and 11b which comprise the 1st heat exchanger group.

具体的には、冷媒の流路３７ｃにおいて、冷媒が、第１熱交換器グループに流入または第１熱交換器グループから流出されるときに、第１熱交換器グループを構成する熱交換器１１ａ、１１ｂの双方から流入または流出できるようにしている。すなわち、冷房運転時冷媒流入部６６ａと、暖房時冷媒流出部６６ｂとを、第１熱交換器グループを構成する熱交換器１１ａ、１１ｂの双方に設けている。   Specifically, in the refrigerant flow path 37c, when the refrigerant flows into the first heat exchanger group or flows out of the first heat exchanger group, the heat exchanger 11a constituting the first heat exchanger group. , 11b from both sides. That is, the cooling operation refrigerant inflow portion 66a and the heating operation refrigerant outflow portion 66b are provided in both of the heat exchangers 11a and 11b constituting the first heat exchanger group.

次に、空気調和機の室内機６０の動作方法について説明する。暖房運転時、冷房運転時、再熱除湿運転時において、基本的には同様であるので、同様の説明は繰り返さないで、異なる点である暖房運転時の冷媒の状態について説明する。   Next, an operation method of the indoor unit 60 of the air conditioner will be described. Since it is basically the same during the heating operation, the cooling operation, and the reheat dehumidification operation, the same description will not be repeated, and the state of the refrigerant during the heating operation, which is a different point, will be described.

暖房運転時には、暖房時冷媒流入部３７ｂより、高温高圧の冷媒が、伝熱管群の管径の太い熱交換器１１ｃから流入する。フィン群１２ｃを介し空気と熱交換することで、冷媒は凝縮液化していき、伝熱管群の管径が細い熱交換器１１ａ、１１ｂの出口部分で合流し、暖房時冷媒流出部６６ｂから流出する。   During the heating operation, high-temperature and high-pressure refrigerant flows from the heat exchanger 11c having a large diameter of the heat transfer tube group from the heating refrigerant inflow portion 37b. By exchanging heat with the air through the fin group 12c, the refrigerant condenses and condenses, and merges at the outlet portions of the heat exchangers 11a and 11b where the tube diameter of the heat transfer tube group is small, and flows out from the refrigerant outflow portion 66b during heating. To do.

その際、流路３７ｃの後半における熱交換器１１ａ、１１ｂでは、冷媒は液化していき、冷媒の温度は低下していく。冷媒が液化している領域である過冷却域は、流速が低下し、熱伝達率も低下する。   At that time, in the heat exchangers 11a and 11b in the latter half of the flow path 37c, the refrigerant is liquefied and the temperature of the refrigerant is lowered. In the supercooling region, which is a region where the refrigerant is liquefied, the flow velocity is decreased and the heat transfer coefficient is also decreased.

しかしながら、空気調和機の室内機６０では、熱交換器１１ａ、１１ｂの双方の伝熱管群１３ａ、１３ｂの端部に暖房時冷媒流出部６６ｂを設けているので、過冷却域は熱交換器１１ａ、１１ｂにおける暖房時冷媒流出部６６ｂの近傍の一列の伝熱管群６７ａ、６７ｂである。そのため、暖房運転時に過冷却域が存在しても、熱交換器１１ａ、１１ｂの送風機に近い２列は過冷却域とはならない。よって、熱交換効率の大幅な低下を抑制できる。   However, in the indoor unit 60 of the air conditioner, since the heating-time refrigerant outflow portion 66b is provided at the ends of the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b, the supercooling region is the heat exchanger 11a. , 11b, a row of heat transfer tube groups 67a, 67b in the vicinity of the refrigerant outlet portion 66b during heating. Therefore, even if a supercooling zone exists during heating operation, the two rows close to the blowers of the heat exchangers 11a and 11b do not become supercooling zones. Thus, a significant decrease in heat exchange efficiency can be suppressed.

以上説明したように、実施の形態５における空気調和機の室内機６０によれば、暖房運転時には、第１熱交換器グループを構成する熱交換器の全てに、暖房時冷媒流出部を設けている。そのため、過冷却域を増加させることがなくなり、熱交換器全体の熱伝達率が向上する。その結果、さらに高性能な空気調和機の室内機とすることができる。   As described above, according to the indoor unit 60 of the air conditioner in the fifth embodiment, during the heating operation, all the heat exchangers constituting the first heat exchanger group are provided with the heating refrigerant outflow portion. Yes. Therefore, the supercooling region is not increased and the heat transfer coefficient of the entire heat exchanger is improved. As a result, the indoor unit of a higher performance air conditioner can be obtained.

（実施の形態７）
図８は、本発明の実施の形態７における空気調和機の室内機を示す側面図である。図８を参照して、実施の形態７による空気調和機の室内機を説明する。図８を参照して、実施の形態７による空気調和機の室内機７０の構成は、基本的には図７に示した本発明の実施の形態６と同様であるが、第２熱交換器グループを構成する熱交換器１１ａ、１１ｂの伝熱管群１３ａ、１３ｂにおける冷媒の流動経路が２列に並列に接続された流動経路部分を有している点において異なる。 (Embodiment 7)
FIG. 8 is a side view showing an indoor unit of an air conditioner according to Embodiment 7 of the present invention. With reference to FIG. 8, the indoor unit of the air conditioner by Embodiment 7 is demonstrated. Referring to FIG. 8, the configuration of air conditioner indoor unit 70 according to the seventh embodiment is basically the same as that of the sixth embodiment of the present invention shown in FIG. The difference is that the refrigerant flow paths in the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b constituting the group include flow path portions connected in parallel in two rows.

具体的には、熱交換器１１ａ、１１ｂにおいて、冷媒の流路３７ｃは分岐して合流する経路をそれぞれ有している。したがって、第１熱交換器グループとしては、熱交換器１１ａ、１１ｂのそれぞれにおいて２列に並列に接続された流動経路部分を有している。すなわち、第１熱交換器グループを構成する熱交換器１１ａ、１１ｂの伝熱管群１３ａ、１３ｂにおける冷媒の流動経路は４列に並列に接続された流動経路部分を有している。なお、第２熱交換器グループを構成する熱交換器１１ｃの伝熱管群１３ｃにおける冷媒の流動経路が２列に並列に接続されている点においては、実施の形態６と同様である。   Specifically, in the heat exchangers 11a and 11b, the refrigerant flow paths 37c have paths that branch and merge. Therefore, the first heat exchanger group has flow path portions connected in parallel in two rows in each of the heat exchangers 11a and 11b. In other words, the refrigerant flow paths in the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b constituting the first heat exchanger group have flow path portions connected in parallel in four rows. In addition, it is the same as that of Embodiment 6 in the point that the flow path of the refrigerant | coolant in the heat exchanger tube group 13c of the heat exchanger 11c which comprises a 2nd heat exchanger group is connected in parallel with 2 rows.

また、第１熱交換器グループを構成する伝熱管群１３ａ、１３ｂの管径を４ｍｍ以上６ｍｍ以下とし、第２熱交換器グループを構成する伝熱管群１３ｃの管径を７ｍｍ以上１３ｍｍ以下としている。伝熱管群１３ａ、１３ｂの管径を４ｍｍより小さくすると、ロウ付け作業時の詰まり等の生産性に問題が生じたり、伝熱管群の肉厚が減少して耐圧に問題を生じるからである。一方、伝熱管群１３ｃの管径を１３ｍｍより大きくすると、空気調和機の室内機７０に用いる上で、搭載可能な熱交換器１１ａ、１１ｂの大きさより制約されるからである。   Further, the tube diameters of the heat transfer tube groups 13a and 13b constituting the first heat exchanger group are 4 mm or more and 6 mm or less, and the tube diameter of the heat transfer tube group 13c constituting the second heat exchanger group is 7 mm or more and 13 mm or less. . This is because if the tube diameters of the heat transfer tube groups 13a and 13b are smaller than 4 mm, problems such as clogging during brazing work will occur, and the thickness of the heat transfer tube group will decrease, resulting in problems with pressure resistance. On the other hand, if the tube diameter of the heat transfer tube group 13c is larger than 13 mm, it is restricted by the size of the heat exchangers 11a and 11b that can be mounted in the indoor unit 70 of the air conditioner.

次に、空気調和機の室内機７０の動作方法について説明する。図８を参照して、送風機１４を運転して、熱交換器１１ａ、１１ｂ、１１ｃに空気を送り込む。   Next, an operation method of the indoor unit 70 of the air conditioner will be described. With reference to FIG. 8, the air blower 14 is operated to send air into the heat exchangers 11a, 11b, and 11c.

暖房運転時においては暖房時冷媒流入部３７ｂより高温高圧の気体冷媒が伝熱管群の管径が太い熱交換器１１ｃに流入し、流路３７ｃで空気と熱交換する。その後、伝熱管群の管径が細い熱交換器１１ａ、１１ｂにおいて気液二相状態から液体の一相状態へと冷媒は変化し、暖房時冷媒流出部６６ｂより低温高圧の液冷媒として流出される。   During the heating operation, high-temperature and high-pressure gaseous refrigerant flows from the heating refrigerant inflow portion 37b into the heat exchanger 11c having a large diameter of the heat transfer tube group, and exchanges heat with air through the flow path 37c. Thereafter, in the heat exchangers 11a and 11b having the thin tube diameters of the heat transfer tube group, the refrigerant changes from the gas-liquid two-phase state to the liquid one-phase state, and flows out as low-temperature and high-pressure liquid refrigerant from the heating refrigerant outflow portion 66b. The

その際、上述したように、冷媒が液化している過冷却域では、流速が低下し、伝熱管群内の熱伝達率も低下する。   At that time, as described above, in the supercooling region where the refrigerant is liquefied, the flow velocity is reduced, and the heat transfer coefficient in the heat transfer tube group is also reduced.

しかしながら、空気調和機の室内機７０では、伝熱管群の管径が細い熱交換器１１ａ、１１ｂの出口に近い部分のそれぞれの合計の流路数が４流路から２流路へと減少しているため、過冷却域での冷媒の流速低下を抑制することが可能となり、伝熱管群内の熱伝達率を向上させることができる。   However, in the indoor unit 70 of the air conditioner, the total number of channels in the portions close to the outlets of the heat exchangers 11a and 11b where the tube diameter of the heat transfer tube group is small decreases from 4 channels to 2 channels. Therefore, it is possible to suppress a decrease in the flow rate of the refrigerant in the supercooling region, and it is possible to improve the heat transfer coefficient in the heat transfer tube group.

一方、冷房運転時には、冷房時冷媒流入部６６ａより低温低圧の二相状態の冷媒が、伝熱管群の管径が細い熱交換器１１ａ、１１ｂにそれぞれ流入し、フィン１２ａ、１２ｂを介して空気と熱交換を行う。熱交換が行なわれると、冷媒は徐々に気化し、管径の太い熱交換器１１ｃへと流入し、冷房時冷媒流出部３７ａより乾き度の進行した冷媒が排出される。   On the other hand, during the cooling operation, the low-temperature and low-pressure refrigerant in the two-phase state flows from the cooling refrigerant inflow portion 66a into the heat exchangers 11a and 11b having a small diameter of the heat transfer tube group, respectively, and air flows through the fins 12a and 12b. And heat exchange. When heat exchange is performed, the refrigerant gradually evaporates and flows into the heat exchanger 11c having a large pipe diameter, and the refrigerant whose dryness has progressed is discharged from the cooling refrigerant outflow portion 37a.

その際、冷媒は気化が進行すると、冷媒内の気体成分により伝熱管群内の圧力損失を増大させ、冷媒の循環量を低下させる。   At that time, when the vaporization of the refrigerant proceeds, the pressure loss in the heat transfer tube group is increased by the gas component in the refrigerant, and the circulation amount of the refrigerant is decreased.

しかしながら、空気調和機の室内機７０では、伝熱管群の管径の細い熱交換器１１ａ、１１ｂ内での流路数をそれぞれ２流路で合計４流路に拡大させている。したがって、熱交換器１１ａ、１１ｂ内での冷媒の気化による圧力損失の増大を抑制することが可能となる。その結果、冷房時の冷媒循環量の低下を抑制することが可能となり、冷房能力の向上が図れる。   However, in the indoor unit 70 of the air conditioner, the number of channels in the heat exchangers 11a and 11b having a small diameter of the heat transfer tube group is expanded to a total of 4 channels with 2 channels each. Therefore, it is possible to suppress an increase in pressure loss due to the vaporization of the refrigerant in the heat exchangers 11a and 11b. As a result, it is possible to suppress a decrease in the refrigerant circulation amount during cooling, and the cooling capacity can be improved.

以上説明したように、実施の形態７における空気調和機の室内機７０によれば、第１熱交換器グループを構成する熱交換器の伝熱管群における冷媒の流動経路が２〜４列の範囲内の２列に平行に接続された流動経路部分を有しており、第２熱交換器グループを構成する伝熱管群における冷媒の流動経路が２列に並列に接続された流動経路部分を有している。そのため、どの運転時においても、熱交換器全体の熱伝達率をさらに向上させることが可能となる。その結果、さらに高性能な空気調和機の室内機とすることができる。   As described above, according to the indoor unit 70 of the air conditioner in the seventh embodiment, the flow path of the refrigerant in the heat transfer tube group of the heat exchanger constituting the first heat exchanger group is in the range of 2 to 4 rows. The flow path portions are connected in parallel to the two rows, and the flow paths of the refrigerant in the heat transfer tube group constituting the second heat exchanger group have the flow path portions connected in parallel to the two rows. is doing. Therefore, in any operation, it becomes possible to further improve the heat transfer coefficient of the entire heat exchanger. As a result, the indoor unit of a higher performance air conditioner can be obtained.

（実施の形態８）
図９は、本発明の実施の形態８における空気調和機の室内機を示す側面図である。図９を参照して、実施の形態８による空気調和機の室内機を説明する。図９を参照して、実施の形態８による空気調和機の室内機８０の構成は、基本的には図８に示した本発明の実施の形態７と同様であるが、伝熱管群の管径が細い第１熱交換器グループを構成している熱交換器１１ａ、１１ｂの流路構成、およびベンドの配置が統一されている点において異なる。 (Embodiment 8)
FIG. 9 is a side view showing an indoor unit of an air conditioner according to Embodiment 8 of the present invention. With reference to FIG. 9, the indoor unit of the air conditioner by Embodiment 8 is demonstrated. Referring to FIG. 9, the configuration of indoor unit 80 of the air conditioner according to the eighth embodiment is basically the same as that of the seventh embodiment of the present invention shown in FIG. The difference is that the flow path configurations of the heat exchangers 11a and 11b constituting the first heat exchanger group having a small diameter and the arrangement of the bends are unified.

なお、流路構成は、熱交換器１１ａ、１１ｂにおける冷媒が流れる流路３７ｃを意味する。具体的には、熱交換器１１ａ、１１ｂにおける冷媒が流れる流路３７ｃは、２流路に分岐する点および１流路に合流する点が略同じであり、その流路も略同一である。   The channel configuration means the channel 37c through which the refrigerant in the heat exchangers 11a and 11b flows. Specifically, the flow path 37c through which the refrigerant flows in the heat exchangers 11a and 11b is substantially the same in that it is branched into two flow paths and merged into one flow path, and the flow paths are also substantially the same.

次に、空気調和機の室内機７０の動作方法については、実施の形態６における空気調和機の室内機６０と同様であるので、その説明は繰り返さない。   Next, since the operation method of the indoor unit 70 of the air conditioner is the same as that of the indoor unit 60 of the air conditioner in Embodiment 6, the description thereof will not be repeated.

以上説明したように、実施の形態８における空気調和機の室内機７０によれば、第１熱交換器グループを構成する熱交換器の全てにおいて、冷媒が流動する流路構成が略同じである。そのため、熱交換器１１ａ、１１ｂを同一に生産することが可能となり、生産時に混同したり、間違えたりすることを防止できる。その結果、生産効率の改善を図ることが可能となる。   As described above, according to the indoor unit 70 of the air conditioner in the eighth embodiment, the flow path configuration in which the refrigerant flows is substantially the same in all of the heat exchangers constituting the first heat exchanger group. . Therefore, it is possible to produce the heat exchangers 11a and 11b in the same manner, and it is possible to prevent confusion or mistakes during production. As a result, it is possible to improve production efficiency.

今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は上記した実施の形態ではなくて特許請求の範囲によって示され、特許請求の範囲と均等な意味および範囲内でのすべての変更点が含まれることが意図される。   The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above-described embodiment but by the scope of claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

本発明の実施の形態１における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 1 of this invention. 本発明の実施の形態２における空位調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the sky level conditioner in Embodiment 2 of this invention. 本発明の実施の形態３における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 3 of this invention. 本発明の実施の形態４における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 4 of this invention. 実施の形態４の変形例における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in the modification of Embodiment 4. 本発明の実施の形態５における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 5 of this invention. 本発明の実施の形態６における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 6 of this invention. 本発明の実施の形態７における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 7 of this invention. 本発明の実施の形態８における空気調和機の室内機を示す側面図である。It is a side view which shows the indoor unit of the air conditioner in Embodiment 8 of this invention. 特許文献１に開示された空気調和機の室内機を示す概略側面図である。It is a schematic side view which shows the indoor unit of the air conditioner disclosed by patent document 1. FIG. 特許文献２に開示された空気調和機の熱交換器の空気調和機組込時の断面図である。It is sectional drawing at the time of the air conditioner built-in of the heat exchanger of the air conditioner disclosed by patent document 2. FIG.

符号の説明Explanation of symbols

１０ 空気調和機の室内機、１１ａ 熱交換器、１１ｂ 熱交換器、１１ｃ 熱交換器、１２ａ フィン群、１２ｂ フィン群、１２ｃ フィン群、１３ａ 伝熱管群、１３ｂ 伝熱管群、１３ｃ 伝熱管群、１４ 送風機、１５ａ 風量、１５ｂ 風量、１５ｃ 風量、２０ 空気調和機の室内機、３０ 空気調和機の室内機、３６ａ 冷房時冷媒流入部、３６ｂ 暖房時冷媒流出部、３７ａ 冷房時冷媒流出部、３７ｂ 暖房時冷媒流入部、３７ｃ 流路、４０ 空気調和機の室内機、４８ 絞り手段、５０ 空気調和機の室内機、６０ 空気調和機の室内機、６６ａ 冷房時冷媒流入部、６６ｂ 暖房時冷媒流出部、６７ａ 伝熱管群、７０ 空気調和機の室内機、８０ 空気調和機の室内機。   10 air conditioner indoor units, 11a heat exchanger, 11b heat exchanger, 11c heat exchanger, 12a fin group, 12b fin group, 12c fin group, 13a heat transfer tube group, 13b heat transfer tube group, 13c heat transfer tube group, 14 Blower, 15a Air volume, 15b Air volume, 15c Air volume, 20 Air conditioner indoor unit, 30 Air conditioner indoor unit, 36a Cooling refrigerant inflow part, 36b Heating refrigerant outflow part, 37a Cooling refrigerant outflow part, 37b Refrigerant inflow part during heating, 37c flow path, 40 indoor unit of air conditioner, 48 throttle means, 50 indoor unit of air conditioner, 60 indoor unit of air conditioner, 66a refrigerant inflow part during cooling, 66b refrigerant outflow during heating Part, 67a heat transfer tube group, 70 indoor unit of air conditioner, 80 indoor unit of air conditioner.

Claims (4)

送風機と、
前記送風機の周囲に配置され、互いに間隔をへだてて配置されたフィン群と、前記フィン群に接続されて内部を冷媒が流動する伝熱管群とを有する少なくとも３台の熱交換器とを備え、
前記各熱交換器が有しているそれぞれの前記伝熱管群の管径が熱交換器毎に略同じで、
前記少なくとも３台の熱交換器は、
少なくとも２台の熱交換器からなる第１熱交換器グループと、
前記第１熱交換器グループの前記熱交換器における前記伝熱管群の管径より大きい管径を有する前記伝熱管群を含む少なくとも１台の熱交換器からなる第２熱交換器グループとにより構成され、
前記第２熱交換器グループを、前記第１熱交換器グループよりも前記送風機に近い位置に配置したことを特徴とし、
前記フィン群を前記伝熱管群が貫通し、前記伝熱管群が貫通する前記フィン群の主表面における前記伝熱管群の貫通位置は、ある方向に整列した１以上の列を構成するように配置され、
前記フィン群の主表面における前記列の延在方向に垂直な方向における幅を、前記列の数で割った値を前記伝熱管群の１列分のフィンの幅とし、
前記第１熱交換器グループにおける前記伝熱管群の１列分のフィンの幅が、前記第２熱交換器グループにおける前記伝熱管群の１列分のフィンの幅より小さく、
前記第１熱交換器グループの前記伝熱管群の前記列の数が、前記第２熱交換器グループの前記伝熱管群の前記列の数より多いことを特徴とする、空気調和機の室内機。 A blower,
A fin group disposed around the blower and spaced apart from each other; and at least three heat exchangers having a heat transfer tube group connected to the fin group and in which a refrigerant flows;
The tube diameter of each of the heat transfer tube groups that each of the heat exchangers has is substantially the same for each heat exchanger,
The at least three heat exchangers are:
A first heat exchanger group comprising at least two heat exchangers;
And a second heat exchanger group including at least one heat exchanger including the heat transfer tube group having a tube diameter larger than that of the heat transfer tube group in the heat exchanger of the first heat exchanger group. And
The second heat exchanger group is arranged at a position closer to the blower than the first heat exchanger group ,
The heat transfer tube group penetrates the fin group, and the penetration position of the heat transfer tube group on the main surface of the fin group through which the heat transfer tube group penetrates is arranged to form one or more rows aligned in a certain direction. And
The width in the direction perpendicular to the extending direction of the rows on the main surface of the fin group is a value obtained by dividing the width by the number of rows as the width of the fins for one row of the heat transfer tube group,
The width of the fin for one row of the heat transfer tube group in the first heat exchanger group is smaller than the width of the fin for one row of the heat transfer tube group in the second heat exchanger group,
The indoor unit of an air conditioner , wherein the number of the rows of the heat transfer tube groups of the first heat exchanger group is greater than the number of the rows of the heat transfer tube groups of the second heat exchanger group . 暖房運転時には、前記第２熱交換器グループを構成する前記熱交換器から、前記第１熱交換器グループを構成する前記熱交換器へ冷媒を流動させることを特徴とする、請求項１に記載の空気調和機の室内機。   2. The refrigerant according to claim 1, wherein during the heating operation, the refrigerant flows from the heat exchanger constituting the second heat exchanger group to the heat exchanger constituting the first heat exchanger group. Air conditioner indoor unit. 冷房運転時には、前記第１熱交換器グループを構成する前記熱交換器の少なくとも１つに冷房時冷媒流入部を設けると共に、前記第２熱交換器グループを構成する前記熱交換器の少なくとも１つに冷房時冷媒流出部を設けたことを特徴とする、請求項１または２に記載の空気調和機の室内機。   During cooling operation, at least one of the heat exchangers constituting the first heat exchanger group is provided with a cooling refrigerant inflow portion, and at least one of the heat exchangers constituting the second heat exchanger group The air conditioner indoor unit according to claim 1, wherein a cooling refrigerant outflow portion is provided in the air conditioner. 前記第１熱交換器グループを構成する前記伝熱管群の管径を４ｍｍ以上６ｍｍ以下とし、前記第２熱交換器グループを構成する前記伝熱管群の管径を７ｍｍ以上１３ｍｍ以下とすることを特徴とする、請求項１〜３のいずれかに記載の空気調和機の室内機。 The tube diameter of the heat transfer tube group constituting the first heat exchanger group is 4 mm or more and 6 mm or less, and the tube diameter of the heat transfer tube group constituting the second heat exchanger group is 7 mm or more and 13 mm or less. The air conditioner indoor unit according to any one of claims 1 to 3 , wherein the indoor unit is an air conditioner.
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JP6371046B2 (en) * 2013-09-03 2018-08-08 日立ジョンソンコントロールズ空調株式会社 Air conditioner and heat exchanger for air conditioner
JP6253513B2 (en) * 2014-05-26 2017-12-27 三菱電機株式会社 Air conditioner indoor unit
JP2022124548A (en) * 2021-02-16 2022-08-26 パナソニックＩｐマネジメント株式会社 Heat exchanger

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JPH10160266A (en) * 1996-11-28 1998-06-19 Hitachi Ltd Heat exchanger for air conditioner
JP2000088476A (en) * 1998-09-16 2000-03-31 Daikin Ind Ltd Heat exchanger
JP2001174047A (en) * 1999-12-17 2001-06-29 Matsushita Electric Ind Co Ltd Indoor unit of air conditioner
JP2001330309A (en) * 2000-05-22 2001-11-30 Hitachi Ltd Air conditioner
JP2003021485A (en) * 2001-07-11 2003-01-24 Toshiba Kyaria Kk Fin tube heat exchanger

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JPH02128015U (en) * 1989-03-29 1990-10-22
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JPH10132372A (en) * 1996-10-31 1998-05-22 Daikin Ind Ltd Air conditioner
JPH10160266A (en) * 1996-11-28 1998-06-19 Hitachi Ltd Heat exchanger for air conditioner
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JP2001174047A (en) * 1999-12-17 2001-06-29 Matsushita Electric Ind Co Ltd Indoor unit of air conditioner
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