JP2008267637A - Refrigerating air-conditioning device - Google Patents

Refrigerating air-conditioning device Download PDF

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JP2008267637A
JP2008267637A JP2007108300A JP2007108300A JP2008267637A JP 2008267637 A JP2008267637 A JP 2008267637A JP 2007108300 A JP2007108300 A JP 2007108300A JP 2007108300 A JP2007108300 A JP 2007108300A JP 2008267637 A JP2008267637 A JP 2008267637A
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heat exchanger
air
propeller fan
refrigerating
conditioning apparatus
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JP4794498B2 (en
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Yasuaki Kato
康明 加藤
Hisafumi Ikeda
尚史 池田
Masato Yosomiya
正人 四十宮
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating air-conditioning device of low noise, while optimizing a size and costs of a heat exchanger. <P>SOLUTION: The heat exchanger is constituted of a first heat exchanger 8 disposed on the upstream side of airflow and a second heat exchanger 9 disposed at a downstream side of airflow; the first heat exchanger 8 and the second heat exchanger 9 are made to overlap each other, the first heat exchanger 8 and the second heat exchanger 9 have different sizes; and a boundary of the overlapping portion of the first heat exchanger 8 and the second heat exchanger 9 is located at a position not opposed to an upper fan motor 5a and a lower fan motor 5b. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は冷凍空調装置に関し、特に複数台の送風機を備えた冷凍空調装置に関するものである。   The present invention relates to a refrigeration air conditioner, and more particularly to a refrigeration air conditioner including a plurality of fans.

従来の冷凍空調装置としては、例えば「ユニット本体１は、前面部、後板および底板を一体に組合わせた筐体である。この前面部にはベルマウス２が設けられ、熱交換空気の吹出し口３が形成される。背面部と一方の側面部には熱交換空気の吸込み口４，５が設けられる。ユニット本体１内には、吸込み口４，５に沿うようにして室外熱交換器６が配置される。上記室外熱交換器６は、背面部と側面部の外気吸込み口４，５に対向するよう平面視で略Ｌ字状に折り曲げ形成される第１の熱交換器７と、この第１の熱交換器における背面部外気吸込み口４に沿う直状部分に並行で、かつ背面部外気吸込み口側に沿って配置される直状の第２の熱交換器８とから構成される。」（例えば特許文献１参照）というものが提案されている。   As a conventional refrigerating and air-conditioning apparatus, for example, “the unit main body 1 is a housing in which a front portion, a rear plate and a bottom plate are integrally combined. A bell mouth 2 is provided on the front portion, and a blowout of heat exchange air is performed. A port 3 is formed, and heat exchange air suction ports 4 and 5 are provided on the back surface and one side surface of the unit body 1. An outdoor heat exchanger is provided in the unit body 1 along the suction ports 4 and 5. The outdoor heat exchanger 6 includes a first heat exchanger 7 that is bent and formed in a substantially L shape in plan view so as to face the outdoor air suction ports 4 and 5 on the back surface portion and the side surface portion. The first heat exchanger includes a straight second heat exchanger 8 disposed in parallel with the straight portion along the back surface outside air suction port 4 and along the back surface outside air suction port side. Has been proposed (for example, see Patent Document 1).

また、例えば「第１熱交換器８１と第２熱交換器８２の全体形状は、室外機５の背面から向かって左側面に折り曲げられた平面視略Ｌ字形状でかつ略同一形状に構成されている。第１熱交換器８１と第２熱交換器８２とは、上下方向に所定距離ずらせることにより、上下方向中間の一部が重合するように配置されている。たとえば、ケーシングの外気吸い込み口の形状に対応して上下方向の長さ２４０ｍｍの熱交換器を構成する場合、上下方向の長さ２４０ｍｍに１列の伝熱管を設けた熱交換器では熱交換能力が不十分であり、２列の伝熱管を設けた熱交換器では熱交換能力に余裕がありすぎる場合には、図５に示すように、上下方向の長さが２００ｍｍの第１熱交換器８１および第２熱交換器８２を用いて、中間の重合部分８８のサイズを１６０ｍｍとし、下部非重合部８９および上部非重合部９０のサイズをそれぞれ４０ｍｍに設定する。このことにより、室外熱交換器４０の上下方向の全体的なサイズを２４０ｍｍとし、かつ熱交換能力を１列の場合と２列の場合との中間サイズのものに設定できる。」（例えば特許文献２参照）というものが提案されている。   Further, for example, “the overall shapes of the first heat exchanger 81 and the second heat exchanger 82 are substantially L-shaped in a plan view bent from the back surface of the outdoor unit 5 toward the left side surface, and substantially the same shape. The first heat exchanger 81 and the second heat exchanger 82 are arranged so that a part of the middle in the vertical direction is overlapped by being shifted by a predetermined distance in the vertical direction, for example, outside air of the casing. When configuring a heat exchanger with a vertical length of 240 mm corresponding to the shape of the suction port, the heat exchanger provided with a row of heat transfer tubes with a vertical length of 240 mm has insufficient heat exchange capacity. If the heat exchanger provided with the two rows of heat transfer tubes has too much heat exchange capacity, as shown in FIG. 5, the first heat exchanger 81 and the second heat having a vertical length of 200 mm are used. Using the exchanger 82, the size of the intermediate polymerization portion 88 is reduced. 60 mm, and the size of each of the lower non-polymerized portion 89 and the upper non-polymerized portion 90 is set to 40 mm, whereby the overall size of the outdoor heat exchanger 40 in the vertical direction is set to 240 mm, and the heat exchange capacity is 1 It can be set to an intermediate size between the case of a row and the case of a row of 2 ”(see, for example, Patent Document 2).

特開平８−２７０９８５号公報（段落番号００２８〜００３０、図１）JP-A-8-270985 (paragraph numbers 0028 to 0030, FIG. 1) 特開２００３−１１４０６５号公報（段落番号００２４、図４，５）Japanese Unexamined Patent Publication No. 2003-114065 (paragraph number 0024, FIGS. 4 and 5)

一般的に、冷凍空調装置は、共通の本体サイズによって熱交換能力の異なる複数の機種に対応することで、意匠の統一化、部品の共通化、又は製造ラインの共有化などによるコストダウンが図られている。このようなコストダウンを実現するため、冷凍空調装置本体に配置される熱交換器の列数（伝熱管の列数）を必要な熱交換能力に応じて１列、２列、又は３列など複数列にする構成としている。また、熱交換器の列数の変更だけでは最適なコストで適当な熱交換能力を備えることが困難であるとして、従来より提案されているものの中には、列により大きさの異なる熱交換器を配置しているものもある（例えば、特許文献１、特許文献２参照）。
しかしながら、従来の冷凍空調装置では、熱交換能力の最適化は改善されているが、送風機の特性の適正化までは図られていなかった。つまり、熱交換器の列数が異なる範囲を通過するそれぞれの空気流れは流速が異なり、この流速差によって生じる乱流に起因する送風騒音が増加するという問題点があった。また、送風機に要求される昇圧特性と風量のバランスが送風機の特性に対して適性でないという問題点があった。 In general, refrigeration and air-conditioning systems support multiple models with different heat exchange capacities depending on a common body size, thereby reducing costs by unifying designs, sharing parts, or sharing production lines. It has been. In order to realize such cost reduction, the number of rows of heat exchangers arranged in the refrigeration air conditioner body (number of rows of heat transfer tubes) is 1 row, 2 rows, 3 rows, etc. depending on the required heat exchange capacity It is configured to have multiple columns. In addition, it is difficult to provide an appropriate heat exchange capacity at an optimal cost only by changing the number of rows of heat exchangers. Among those conventionally proposed, heat exchangers having different sizes depending on the rows Some of them are arranged (see, for example, Patent Document 1 and Patent Document 2).
However, in the conventional refrigeration air conditioner, the optimization of the heat exchange capacity has been improved, but the optimization of the characteristics of the blower has not been achieved. That is, there is a problem in that airflows passing through ranges with different numbers of rows of heat exchangers have different flow rates, and blowing noise due to turbulent flow caused by this flow rate difference increases. In addition, there is a problem that the balance between the boosting characteristics and the air volume required for the blower is not suitable for the blower characteristics.

この発明は、上記のよう課題を解決するためになされたものであり、熱交換器のサイズとコストを最適とした上で低騒音の冷凍空調装置を得るものである。   The present invention has been made to solve the above-described problems, and provides a low noise refrigeration air conditioner while optimizing the size and cost of a heat exchanger.

この発明に係る冷凍空調装置は、空気の吸込み口と吹出し口が形成された本体と、前記吸込み口から空気を吸引し、前記吹出し口から空気を排出させる複数の送風機と、前記吸込み口と前記送風機との間に配置された熱交換器とを備えた冷凍空調装置において、前記熱交換器は、空気流れ上流側に配置された第一熱交換器と、空気流れ下流側に配置された第二熱交換器とからなり、前記第一熱交換器と前記第二熱交換器は重合して設けられ、前記第一熱交換器と前記第二熱交換器は大きさが異なり、前記第一熱交換器と前記第二熱交換器との重合部境界が、前記送風機と対向しない位置にあるものである。   The refrigerating and air-conditioning apparatus according to the present invention includes a main body in which an air suction port and an air outlet are formed, a plurality of blowers that suck air from the air inlet and exhaust air from the air outlet, the air inlet, and the air In the refrigerating and air-conditioning apparatus including the heat exchanger disposed between the blower, the heat exchanger includes a first heat exchanger disposed on the upstream side of the air flow and a first heat exchanger disposed on the downstream side of the air flow. The first heat exchanger and the second heat exchanger are provided by polymerization, the first heat exchanger and the second heat exchanger are different in size, and The superposition | polymerization part boundary of a heat exchanger and said 2nd heat exchanger exists in the position which does not oppose the said air blower.

この発明においては、第一熱交換器と第二熱交換器との重合部境界が、送風機と対向しない位置にあるので、第一熱交換器または第二熱交換器の一方のみを通過する空気流れと、第一熱交換器と第二熱交換器との重合部を通過する空気流れがそれぞれ干渉して乱れることが抑制される。そのため、熱交換器のサイズとコストを最適とした上で低騒音の冷凍空調装置を得ることができる。   In this invention, since the overlapping portion boundary between the first heat exchanger and the second heat exchanger is in a position not facing the blower, air that passes through only one of the first heat exchanger and the second heat exchanger It is suppressed that a flow and the air flow which passes the superposition | polymerization part of a 1st heat exchanger and a 2nd heat exchanger interfere with each other, and are disturb | confused. Therefore, a low-noise refrigeration air conditioner can be obtained while optimizing the size and cost of the heat exchanger.

実施の形態１．
図１は、この発明の実施の形態１における冷凍空調装置の室外機の外観斜視図である。また、図２は図１におけるＡ−Ａ断面模式図である。この図１及び図２を用いて、本実施形態１における冷凍空調装置の室外機の構成について説明する。
室外機本体１は、設置床面積を小さくするため、また空気の吹き出し面積や熱交換器の面積を広く取るために上下方向に長さが長い略直方体の箱型形状をしている。この室外機本体１の側面１ａには、上下方向２箇所に略円形の吹出し口（上部吹出し口２ａ、下部吹出し口２ｂ）が設けられている。上部吹出し口２ａには上部ベルマウス３ａが形成されており、この上部ベルマウス３ａと対向して、上部プロペラファン４ａ及び上部プロペラファン４ａを回転駆動するための上部ファンモータ５ａが設けられている。下部吹出し口２ｂには下部ベルマウス３ｂが形成されており、この下部ベルマウス３ｂと対向して、下部プロペラファン４ｂ及び下部プロペラファン４ｂを回転駆動するための下部ファンモータ５ｂが設けられている。これら上部プロペラファン４ａ及び上部ファンモータ５ａと下部プロペラファン４ｂ及び下部ファンモータ５ｂは、それぞれ本発明の送風機に相当する。上部プロペラファン４ａの外径Ｄ１よりも下部プロペラファン４ｂの外径Ｄ２の方が小さい構成となっている。上部ファンモータ５ａ及び下部ファンモータ５ｂは各々モータサポート（図示せず）によって所定の位置に保持されている。また、上部吹出し口２ａ及び下部吹出し口２ｂは、上部プロペラファン４ａ及び下部プロペラファン４ｂに手等が接触することを防止するため、それぞれ上部ファンガード６ａ及び下部ファンガード６ｂで覆われている。 Embodiment 1 FIG.
1 is an external perspective view of an outdoor unit of a refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention. FIG. 2 is a schematic cross-sectional view taken along the line AA in FIG. The configuration of the outdoor unit of the refrigerating and air-conditioning apparatus according to Embodiment 1 will be described with reference to FIGS. 1 and 2.
The outdoor unit main body 1 has a substantially rectangular parallelepiped box shape that is long in the vertical direction in order to reduce the installation floor area and to increase the air blowing area and the heat exchanger area. The side surface 1a of the outdoor unit body 1 is provided with substantially circular outlets (upper outlet 2a and lower outlet 2b) at two locations in the vertical direction. An upper bell mouth 3a is formed at the upper outlet 2a, and an upper propeller fan 4a and an upper fan motor 5a for rotationally driving the upper propeller fan 4a are provided facing the upper bell mouth 3a. . A lower bell mouth 3b is formed in the lower outlet 2b, and a lower propeller fan 4b and a lower fan motor 5b for rotationally driving the lower propeller fan 4b are provided facing the lower bell mouth 3b. . These upper propeller fan 4a and upper fan motor 5a, lower propeller fan 4b and lower fan motor 5b correspond to the blower of the present invention. The outer diameter D2 of the lower propeller fan 4b is smaller than the outer diameter D1 of the upper propeller fan 4a. The upper fan motor 5a and the lower fan motor 5b are each held in a predetermined position by a motor support (not shown). Further, the upper outlet 2a and the lower outlet 2b are covered with an upper fan guard 6a and a lower fan guard 6b, respectively, in order to prevent a hand or the like from coming into contact with the upper propeller fan 4a and the lower propeller fan 4b.

室外機本体１の側面１ｂと側面１ｃには、それぞれ吸込み口７ａ及び吸込み口７ｂが設けられている。吸込み口７ａは、その高さ寸法は側面１ｂの高さ寸法よりやや短く、その幅寸法は側面１ｂの幅寸法よりやや短い長方形状に形成されている。吸込み口７ｂは、その高さ寸法は側面１ｃの高さ寸法よりやや短く、その幅寸法は側面１ｃの幅寸法よりやや短い長方形状に形成されている。室外機本体１内には、この吸込み口７ａ及び吸込み口７ｂを覆うように横断面略Ｌ型形状の第一熱交換器８が配置されている。また、第一熱交換器８の内側（吸込み口７ａ及び吸込み口７ｂと反対側）側面の下側には、第一熱交換器８よりも高さ寸法が短い横断面略Ｌ型形状の第二熱交換器９が第一熱交換器８と重合して配置されている。この第一熱交換器８及び第二熱交換器９が本発明の熱交換器に相当する。第一熱交換器８及び第二熱交換器９は、例えばフィンチューブ型熱交換器である。   The side surface 1b and the side surface 1c of the outdoor unit main body 1 are provided with a suction port 7a and a suction port 7b, respectively. The suction port 7a is formed in a rectangular shape whose height is slightly shorter than the height of the side surface 1b and whose width is slightly shorter than the width of the side surface 1b. The suction port 7b is formed in a rectangular shape whose height is slightly shorter than the height of the side surface 1c and whose width is slightly shorter than the width of the side surface 1c. In the outdoor unit main body 1, a first heat exchanger 8 having a substantially L-shaped cross section is disposed so as to cover the suction port 7a and the suction port 7b. In addition, on the inner side of the first heat exchanger 8 (on the side opposite to the suction port 7a and the suction port 7b), on the lower side of the first heat exchanger 8, there is a first L having a substantially L-shaped cross section whose height dimension is shorter than the first heat exchanger 8. Two heat exchangers 9 are arranged in superposition with the first heat exchanger 8. The first heat exchanger 8 and the second heat exchanger 9 correspond to the heat exchanger of the present invention. The first heat exchanger 8 and the second heat exchanger 9 are, for example, fin tube heat exchangers.

図２に示すように、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａの下端高さＨ１と下部プロペラファン４ｂの上端高さＨ２との間に位置する。つまり、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａ及び下部プロペラファン４ｂと対向しない位置にある。また、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）から、上部プロペラファン４ａの下端高さＨ１と下部プロペラファン４ｂの上端高さＨ２との間にかけて、空気の流れを上下で分離する分離板１０が設けられている。分離板１０は、第二熱交換器９側へ下るように傾斜して設けられている。   As shown in FIG. 2, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is equal to the lower end height H1 of the upper propeller fan 4a. It is located between the upper end height H2 of the lower propeller fan 4b. That is, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is in a position not facing the upper propeller fan 4a and the lower propeller fan 4b. . Further, the lower end height H1 of the upper propeller fan 4a and the lower propeller fan 4b are determined from the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9). A separation plate 10 is provided between the upper end height H2 and the upper and lower ends to separate the air flow vertically. The separation plate 10 is provided so as to be inclined toward the second heat exchanger 9 side.

空気の吸込みとなっていない室外機本体１の側面１ｄ側には、機械室板１１で仕切られた機械室１２が設けられている。この機械室１２には、圧縮機、膨張弁、及び冷媒分配器等の冷凍サイクルに必要な要素部品（図示せず）や、電気回路等（図示せず）が格納されている。また、第二熱交換器９より上部の機械室板１１には、上部プロペラファン４ａにより生じる空気流れの風路側に電気回路の放熱を行う冷却用フィン１３が取り付けられる。   A machine room 12 partitioned by a machine room plate 11 is provided on the side surface 1d side of the outdoor unit body 1 where air is not sucked. The machine room 12 stores component parts (not shown) necessary for the refrigeration cycle, such as a compressor, an expansion valve, and a refrigerant distributor, and an electric circuit (not shown). In addition, a cooling fin 13 that radiates heat from the electric circuit is attached to the machine room plate 11 above the second heat exchanger 9 on the air flow side of the air flow generated by the upper propeller fan 4a.

次に室外機本体１の空気流れについて説明する。上部ファンモータ５ａ及び下部ファンモータ５ｂによってそれぞれ回転する上部プロペラファン４ａ及び下部プロペラファン４ｂの昇圧作用によって、室外機本体１内の圧力が低下し、吸込み口７ａ及び吸込み口７ｂから外部の空気が室外機本体１内部に吸込まれる。室外機本体１内部に吸込まれた空気は、第一熱交換器８及び第二熱交換器９を通過する過程で熱交換を行う。例えば、第一熱交換器８及び第二熱交換器９が凝縮器として作用する場合（つまり、室内機が冷房運転時の場合）、熱は第一熱交換器８及び第二熱交換器９から空気へ移動する。また、第一熱交換器８及び第二熱交換器９が蒸発器として作用する場合（つまり、室内機が暖房運転時の場合）、熱は空気から第一熱交換器８及び第二熱交換器９へ移動する。室外機本体１に吸込まれた空気は、上部プロペラファン４ａ及び下部プロペラファン４ｂを介してそれぞれ上部吹出し口２ａ及び下部吹出し口２ｂから室外機本体１の外に排出される。   Next, the air flow of the outdoor unit body 1 will be described. The pressure inside the outdoor unit body 1 is reduced by the pressure-increasing action of the upper propeller fan 4a and the lower propeller fan 4b that are rotated by the upper fan motor 5a and the lower fan motor 5b, respectively, and external air is drawn from the suction port 7a and the suction port 7b. It is sucked into the outdoor unit body 1. The air sucked into the outdoor unit main body 1 performs heat exchange in the process of passing through the first heat exchanger 8 and the second heat exchanger 9. For example, when the first heat exchanger 8 and the second heat exchanger 9 act as a condenser (that is, when the indoor unit is in cooling operation), the heat is the first heat exchanger 8 and the second heat exchanger 9. Move from to the air. Further, when the first heat exchanger 8 and the second heat exchanger 9 act as an evaporator (that is, when the indoor unit is in a heating operation), heat is transferred from the air to the first heat exchanger 8 and the second heat exchanger. Move to vessel 9. The air sucked into the outdoor unit main body 1 is discharged out of the outdoor unit main body 1 through the upper propeller fan 4a and the lower propeller fan 4b from the upper outlet 2a and the lower outlet 2b, respectively.

外部の空気が室外機本体１内部に吸込まれる空気流れには、図２に示す経路Ａと経路Ｂの２経路がある。経路Ａは第一熱交換器８のみを通過して室外機本体１内部に吸込まれる経路である。経路Ｂは第一熱交換器８及び第二熱交換器９、つまり第一熱交換器８と第二熱交換器９の重合部を通過して室外機本体１内部に吸込まれる経路である。経路Ａと比較して、経路Ｂは第二熱交換器９を通過する分だけ通風抵抗が大きくなる。   The air flow into which the external air is sucked into the outdoor unit main body 1 has two paths, a path A and a path B shown in FIG. The path A is a path that passes through only the first heat exchanger 8 and is sucked into the outdoor unit body 1. The path B is a path through which the first heat exchanger 8 and the second heat exchanger 9, that is, the first heat exchanger 8 and the second heat exchanger 9 are overlapped and sucked into the outdoor unit body 1. . Compared with the path A, the path B has a larger ventilation resistance by passing through the second heat exchanger 9.

仮に、分離板１０が無く、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）が上部プロペラファン４ａの下端高さＨ１よりも高い、又は下部プロペラファン４ｂの上端高さＨ２よりも低いと仮定する。第一熱交換器８を通過した時点での経路Ａの圧力と、第二熱交換器９を通過した時点での経路Ｂの圧力とが同じ場合、経路Ａの流速は経路Ｂの流速よりも速くなる。つまり、経路Ａの流速と経路Ｂの流速は異なる。上部プロペラファン４ａ又は下部プロペラファン４ｂの一方に流速の異なる経路Ａと経路Ｂの空気が流入すると、空気流れの乱れに起因する騒音が増加してしまう。   If the separation plate 10 is not provided, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is lower than the lower end height H1 of the upper propeller fan 4a. Is also higher or lower than the upper end height H2 of the lower propeller fan 4b. When the pressure of the path A when passing through the first heat exchanger 8 and the pressure of the path B when passing through the second heat exchanger 9 are the same, the flow rate of the path A is higher than the flow rate of the path B. Get faster. That is, the flow rate of the route A and the flow rate of the route B are different. When the air of the path | route A and the path | route B from which the flow velocity differs into one of the upper propeller fan 4a or the lower propeller fan 4b flows, the noise resulting from disturbance of an air flow will increase.

しかし、本実施形態１における室外機本体１では、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａの下端高さＨ１と下部プロペラファン４ｂの上端高さＨ２との間に位置する。つまり、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａ及び下部プロペラファン４ｂと対向しない位置にある。このため、経路Ａ及び経路Ｂの空気は、それぞれ上部プロペラファン４ａ及び下部プロペラファン４ｂに分かれて流入する。したがって、空気流れの乱れに起因する騒音を抑制することができる。
また、本実施形態１における室外機本体１には、分離板１０が配置されているので、上部プロペラファン４ａ又は下部プロペラファン４ｂの一方に流速の異なる経路Ａと経路Ｂの空気が流入することをさらに抑制できる。したがって、プロペラファン４ａ及び下部プロペラファン４ｂへ流入する空気流れは乱れが小さく、騒音の小さな室外機とすることができる。 However, in the outdoor unit main body 1 according to the first embodiment, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is the upper propeller fan 4a. Is located between the lower end height H1 and the upper end height H2 of the lower propeller fan 4b. That is, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is in a position not facing the upper propeller fan 4a and the lower propeller fan 4b. . For this reason, the air of the path | route A and the path | route B flows in into the upper propeller fan 4a and the lower propeller fan 4b, respectively. Therefore, noise caused by air flow disturbance can be suppressed.
In addition, since the separation plate 10 is disposed in the outdoor unit main body 1 according to the first embodiment, the air of the path A and the path B having different flow speeds flows into one of the upper propeller fan 4a and the lower propeller fan 4b. Can be further suppressed. Accordingly, the air flow flowing into the propeller fan 4a and the lower propeller fan 4b is less disturbed and can be an outdoor unit with less noise.

分離板１０は、経路Ａ及び経路Ｂの空気の流れを上下で分離する効果の他にも低騒音化に効果を発揮する。一般的に、プロペラファンが回転すると室外機本体内の空気の速度、圧力が変動する。複数台のプロペラファンを有する場合には、一方のプロペラファンに起因する速度、圧力の変動が別のプロペラファンへ影響を及ぼし騒音を増加させる。しかしながら、分離板１０は、室外機本体１内を上部プロペラファン４ａが設けられた上部空間と、下部プロペラファン４ｂが設けられた下部空間に分離するため、上部プロペラファン４ａと下部プロペラファン４ｂが互いに影響を及ぼし騒音を増加させることを抑制する。また、上部吹出し口２ａから室外機本体１内に侵入する雨水等から下部のファンモータを保護する役目も果し、耐候性を高めることができる。さらに、分離板１０は第二熱交換器９側へ下るように傾斜して設けられているので、進入した水は第一熱交換器８及び第二熱交換器９を通じて速やかに排水される。したがって、水が室外機本体１内部に留まり凍結やさび等の腐食の要因となることを防ぐ効果を有する。   The separation plate 10 exhibits an effect of reducing noise in addition to the effect of separating the air flows of the route A and the route B vertically. Generally, when the propeller fan rotates, the speed and pressure of air in the outdoor unit main body fluctuate. In the case of having a plurality of propeller fans, fluctuations in speed and pressure caused by one propeller fan affect another propeller fan and increase noise. However, since the separation plate 10 separates the interior of the outdoor unit main body 1 into an upper space provided with the upper propeller fan 4a and a lower space provided with the lower propeller fan 4b, the upper propeller fan 4a and the lower propeller fan 4b are separated from each other. Suppresses increasing noise by affecting each other. In addition, it also serves to protect the lower fan motor from rainwater and the like entering the outdoor unit main body 1 from the upper outlet 2a, and weather resistance can be improved. Furthermore, since the separating plate 10 is inclined so as to descend toward the second heat exchanger 9, the water that has entered is quickly drained through the first heat exchanger 8 and the second heat exchanger 9. Therefore, it has the effect of preventing water from staying inside the outdoor unit body 1 and causing corrosion such as freezing and rust.

冷凍空調装置の空力騒音は搭載したファンの騒音特性の影響が大きい。つまり、本実施形態１における冷凍空調装置の室外機においては、上部プロペラファン４ａ及び下部プロペラファン４ｂの騒音特性の影響が大きい。一般的に、プロペラファンの騒音特性は、風量と静圧のバランスで整理されることが多い。所要の風量及び静圧に対して、騒音は、（騒音）＝（比騒音）＋ｌｏｇ（（風量）×（静圧2.5 ））で整理される。この式の中の比騒音は、静圧と風量から定義される損失係数に応じて値が変化する。ここで、個々のプロペラファンにおける損失係数は（損失係数）＝（静圧）／（風量2 ）で表される。つまり、冷凍空調装置に必要な風量及び静圧に対して、比騒音の小さなファンを配置することが騒音の小さな冷凍空調装置を実現することになる。 The aerodynamic noise of a refrigeration air conditioner is greatly influenced by the noise characteristics of the installed fan. That is, in the outdoor unit of the refrigerating and air-conditioning apparatus according to Embodiment 1, the influence of the noise characteristics of the upper propeller fan 4a and the lower propeller fan 4b is large. In general, the noise characteristics of a propeller fan are often arranged by the balance between air volume and static pressure. For the required air volume and static pressure, the noise is organized as (noise) = (specific noise) + log ((air volume) × (static pressure 2.5 )). The value of the specific noise in this equation changes according to the loss coefficient defined by the static pressure and the air volume. Here, the loss coefficient in each propeller fan is expressed by (loss coefficient) = (static pressure) / (air flow 2 ). That is, disposing a fan with a small specific noise with respect to the air volume and static pressure required for the refrigeration air conditioner realizes a refrigeration air conditioner with low noise.

図３は、本実施形態１における上部プロペラファン４ａ及び下部プロペラファン４ｂの空力特性図であり、（ａ）は風量−比騒音特性図、（ｂ）は風量−静圧特性図である。（ｂ）に示す上部プロペラファン４ａの風量−静圧特性図は、例えばファン外径４００ｍｍであり、回転数が８００ｒｐｍのものである。また、（ｂ）に示す下部プロペラファン４ｂの風量−静圧特性図は、例えば３５０ｍｍであり、回転数が１０４０ｒｐｍのものである。なお、上部プロペラファン４ａ及び下部プロペラファン４ｂは外径は異なるが、類似のファン形状のものを用いている。
上述したように、経路Ａと比較して、経路Ｂは第二熱交換器９を通過する分だけ通風抵抗が大きくなる。このため、同量の風量を得るためには、経路Ａと比較して経路Ｂの方が静圧が高くなり、図３（ｂ）に示すように負荷曲線は経路Ａと経路Ｂで異なるものとなる。例えば、経路Ａにおいて必要な風量が３０ｍ3 ／ｍｉｎ、必要な静圧が２５Ｐａとすると、このときの上部プロペラファン４ａの比騒音は約１２ｄＢであり最も比騒音の低い使い方ができている。経路Ｂにおいて必要な風量が２６ｍ3 ／ｍｉｎ、必要な静圧が３２Ｐａとすると、仮に下部プロペラファン４ｂに上部プロペラファン４ａと同じプロペラファンを用いた場合、比騒音は約１７ｄＢとなる。一方、ファン外径３５０ｍｍの下部プロペラファン４ｂでは比騒音は約１２ｄＢとなり、ファン外径４００ｍｍの場合と比べて約５ｄＢ低い運転とすることができる。 FIG. 3 is an aerodynamic characteristic diagram of the upper propeller fan 4a and the lower propeller fan 4b according to the first embodiment, (a) is an air volume-specific noise characteristic diagram, and (b) is an air volume-static pressure characteristic diagram. The flow rate-static pressure characteristic diagram of the upper propeller fan 4a shown in FIG. 5B is, for example, a fan outer diameter of 400 mm and a rotation speed of 800 rpm. Moreover, the air volume-static pressure characteristic diagram of the lower propeller fan 4b shown in (b) is, for example, 350 mm and the rotational speed is 1040 rpm. Although the upper propeller fan 4a and the lower propeller fan 4b have different outer diameters, they have similar fan shapes.
As described above, compared with the path A, the path B has an increased ventilation resistance by the amount that passes through the second heat exchanger 9. For this reason, in order to obtain the same amount of airflow, the static pressure is higher in the route B than in the route A, and the load curve is different between the route A and the route B as shown in FIG. It becomes. For example, if the required air volume in the path A is 30 m 3 / min and the required static pressure is 25 Pa, the specific noise of the upper propeller fan 4a at this time is about 12 dB, and the usage with the lowest specific noise is achieved. Assuming that the required air volume in the path B is 26 m 3 / min and the required static pressure is 32 Pa, if the same propeller fan as the upper propeller fan 4a is used for the lower propeller fan 4b, the specific noise is about 17 dB. On the other hand, in the lower propeller fan 4b having a fan outer diameter of 350 mm, the specific noise is about 12 dB, and the operation can be reduced by about 5 dB compared to the case of the fan outer diameter of 400 mm.

このように、通風抵抗の大きい経路Ｂの空気、つまり第一熱交換器８と第二熱交換器９の重合部を通過が流入する下部プロペラファン４ｂに、通風抵抗の小さい経路Ａの空気が流入する上部プロペラファン４ａよりも静圧が大きい状態で比騒音が最小となるプロペラファンを用いることで、より騒音の小さい冷凍空調装置とすることができる。   In this way, the air in the path B having a small ventilation resistance is introduced into the air in the path B having a large ventilation resistance, that is, the lower propeller fan 4b passing through the overlapping portion of the first heat exchanger 8 and the second heat exchanger 9. By using a propeller fan that has a minimum specific noise in a state where the static pressure is larger than that of the upper propeller fan 4a that flows in, a refrigeration air conditioner with less noise can be obtained.

なお、本実施形態では下部プロペラファン４ｂに上部プロペラファン４ａよりもファン外径が小さいプロペラファンを用いることで、下部プロペラファン４ｂが上部プロペラファン４ａよりも静圧が大きい状態で比騒音が最小となるプロペラファンとした。しかし、これに限らずファン幅やファン形状を変更して、下部プロペラファン４ｂが上部プロペラファン４ａよりも静圧が大きい状態で比騒音が最小となるプロペラファンとしてもよい。また、上部プロペラファン４ａ及び下部プロペラファン４ｂの少なくとも一方を遠心ファン等の他の送風機にすることも可能である。   In the present embodiment, a propeller fan having a smaller fan outer diameter than the upper propeller fan 4a is used as the lower propeller fan 4b, so that the specific noise is minimized when the lower propeller fan 4b has a higher static pressure than the upper propeller fan 4a. Propeller fan. However, the present invention is not limited to this, and the fan width and the fan shape may be changed so that the lower propeller fan 4b has a higher static pressure than the upper propeller fan 4a and the propeller fan has a minimum specific noise. Further, at least one of the upper propeller fan 4a and the lower propeller fan 4b can be used as another blower such as a centrifugal fan.

また、図１では図４（Ａ）のように第一熱交換器８、第二熱交換器９ともに横断面略Ｌ型形状をしているが、（Ｂ）のように第二熱交換器９を平面形状にしてもよく、（Ｃ）のように第一熱交換器８、第二熱交換器９ともに平面形状状としてもよい。冷凍空調装置が要求される熱交換能力に応じて、熱交換器のサイズとコストを最適化を図ることができる適切な形態を選択できる。   In FIG. 1, both the first heat exchanger 8 and the second heat exchanger 9 have a substantially L-shaped cross section as shown in FIG. 4A, but the second heat exchanger as shown in FIG. 9 may have a planar shape, and both the first heat exchanger 8 and the second heat exchanger 9 may have a planar shape as shown in FIG. Depending on the heat exchange capacity required by the refrigeration air conditioner, an appropriate form that can optimize the size and cost of the heat exchanger can be selected.

このように構成された冷凍空調装置の室外機においては、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａ及び下部プロペラファン４ｂと対向しない位置にある。このため、経路Ａ及び経路Ｂの空気は、それぞれ上部プロペラファン４ａ及び下部プロペラファン４ｂに分かれて流入する。したがって、空気流れの乱れに起因する騒音を抑制することができる。そのため、熱交換器のサイズとコストを最適とした上で低騒音の冷凍空調装置を得ることができる。   In the outdoor unit of the refrigerating and air-conditioning apparatus configured as described above, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is the upper propeller. It is in the position which does not oppose the fan 4a and the lower propeller fan 4b. For this reason, the air of the path | route A and the path | route B flows in into the upper propeller fan 4a and the lower propeller fan 4b, respectively. Therefore, noise caused by air flow disturbance can be suppressed. Therefore, a low-noise refrigeration air conditioner can be obtained while optimizing the size and cost of the heat exchanger.

第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）から、上部プロペラファン４ａの下端高さＨ１と下部プロペラファン４ｂの上端高さＨ２との間にかけて、空気の流れを上下で分離する分離板１０が設けられているので、上部プロペラファン４ａ又は下部プロペラファン４ｂの一方に流速の異なる経路Ａと経路Ｂの空気が流入することをさらに抑制できる。したがって、プロペラファン４ａ及び下部プロペラファン４ｂへ流入する空気流れは乱れが小さく、騒音の小さな室外機とすることができる。   From the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9), the lower end height H1 of the upper propeller fan 4a and the upper end height of the lower propeller fan 4b. Since the separation plate 10 that separates the air flow from top to bottom is provided between the upper and lower propeller fans 4a and 4b, the air of the path A and the path B having different flow velocities flows into one of the upper propeller fan 4a and the lower propeller fan 4b. This can be further suppressed. Accordingly, the air flow flowing into the propeller fan 4a and the lower propeller fan 4b is less disturbed and can be an outdoor unit with less noise.

分離板１０は、室外機本体１内を上部プロペラファン４ａが設けられた上部空間と、下部プロペラファン４ｂが設けられた下部空間に分離するため、上部プロペラファン４ａと下部プロペラファン４ｂが互いに影響を及ぼし騒音を増加させることを抑制する。また、上部吹出し口２ａから室外機本体１内に侵入する雨水等から下部のファンモータを保護する役目も果し、耐候性を高めることができる。さらに、分離板１０は水平方向に傾斜しており、第二熱交換器９側が低くなっているので、進入した水は第一熱交換器８及び第二熱交換器９を通じて速やかに排水される。したがって、水が室外機本体１内部に留まり凍結やさび等の腐食の要因となることを防ぐ効果を有する。   Since the separation plate 10 separates the interior of the outdoor unit main body 1 into an upper space provided with the upper propeller fan 4a and a lower space provided with the lower propeller fan 4b, the upper propeller fan 4a and the lower propeller fan 4b influence each other. To suppress the increase of noise. In addition, it also serves to protect the lower fan motor from rainwater and the like entering the outdoor unit main body 1 from the upper outlet 2a, and weather resistance can be improved. Further, since the separation plate 10 is inclined in the horizontal direction and the second heat exchanger 9 side is lowered, the water that has entered is quickly drained through the first heat exchanger 8 and the second heat exchanger 9. . Therefore, it has the effect of preventing water from staying inside the outdoor unit body 1 and causing corrosion such as freezing and rust.

通風抵抗の小さい上部プロペラファン４ａにより生じる経路Ａの風路側に電気回路の放熱を行う冷却用フィン１３が取り付けられているので、放熱に必要な風速をモータ入力の小さい上部プロペラファン４ａから得ることができる。したがって、消費電力の小さい冷凍空調装置とすることができる。   Since the cooling fin 13 for radiating the electric circuit is attached to the air path side of the path A generated by the upper propeller fan 4a having a small ventilation resistance, the wind speed necessary for the heat radiation can be obtained from the upper propeller fan 4a having a small motor input. Can do. Therefore, a refrigeration air conditioner with low power consumption can be obtained.

通風抵抗の大きい経路Ｂの空気が流入する下部プロペラファン４ｂに、通風抵抗の小さい経路Ａの空気が流入する上部プロペラファン４ａよりも静圧が大きい状態で比騒音が最小となるプロペラファンを用いることで、より騒音の小さい冷凍空調装置とすることができる。   For the lower propeller fan 4b into which the air in the path B having a large ventilation resistance flows, a propeller fan having a minimum specific noise in a state where the static pressure is larger than that in the upper propeller fan 4a into which the air in the path A having a small ventilation resistance flows is used. Thus, a refrigeration air conditioner with less noise can be obtained.

実施の形態２．
実施の形態１では、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）から、上部プロペラファン４ａの下端高さＨ１と下部プロペラファン４ｂの上端高さＨ２との間にかけて、空気の流れを上下で分離する分離板１０が設けられていたが、本実施形態２では分離板１０のない冷凍空調装置の室外機について説明する。なお、本実施形態２において、特に記述しない項目については実施の形態１と同様とし、同一機能については同一の符号を用いて述べることとする。 Embodiment 2. FIG.
In the first embodiment, the lower end height H1 and lower portion of the upper propeller fan 4a are determined from the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9). The separation plate 10 that separates the air flow vertically is provided between the upper end height H2 of the propeller fan 4b. In the second embodiment, an outdoor unit of a refrigeration air conditioner without the separation plate 10 will be described. . In the second embodiment, items not particularly described are the same as those in the first embodiment, and the same functions are described using the same reference numerals.

図５は、本実施形態１における冷凍空調装置の室外機の断面模式図である。本実施形態２においても第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａの下端高さＨ１と下部プロペラファン４ｂの上端高さＨ２との間に位置しているが、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、上部プロペラファン４ａの下端高さＨ１に近い位置となっている。   FIG. 5 is a schematic cross-sectional view of the outdoor unit of the refrigeration air-conditioning apparatus according to the first embodiment. Also in the second embodiment, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is equal to the lower end height H1 of the upper propeller fan 4a and the lower portion. Although it is located between the upper end height H2 of the propeller fan 4b, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is The upper propeller fan 4a is close to the lower end height H1.

経路Ａの流速は経路Ｂの流速よりも速くなるために、経路Ａを流れる空気は第一熱交換器８を通過した時点で経路Ｂ側へ広がる。このため、第二熱交換器９の上端高さＨａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）を上部プロペラファン４ａの下端高さＨ１に近い位置とすることにより、経路Ａ及び経路Ｂの空気は、それぞれ上部プロペラファン４ａ及び下部プロペラファン４ｂに分かれて流入する。したがって、空気流れの乱れに起因する騒音を抑制することができる。そのため、熱交換器のサイズとコストを最適とした上で低騒音の冷凍空調装置を得ることができる。   Since the flow rate of the route A is faster than the flow rate of the route B, the air flowing through the route A spreads toward the route B when it passes through the first heat exchanger 8. For this reason, the upper end height Ha of the second heat exchanger 9 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is set to a position close to the lower end height H1 of the upper propeller fan 4a. Thus, the air in the path A and the path B flows into the upper propeller fan 4a and the lower propeller fan 4b, respectively. Therefore, noise caused by air flow disturbance can be suppressed. Therefore, a low-noise refrigeration air conditioner can be obtained while optimizing the size and cost of the heat exchanger.

実施の形態３．
図６は、この発明の実施の形態３における冷凍空調装置の室内機の外観斜視図である。また、図７は図６におけるＢ−Ｂ断面模式図である。この図６及び図７を用いて、本実施形態３における冷凍空調装置の室内機の構成について説明する。 Embodiment 3 FIG.
FIG. 6 is an external perspective view of the indoor unit of the refrigerating and air-conditioning apparatus according to Embodiment 3 of the present invention. FIG. 7 is a schematic cross-sectional view taken along the line BB in FIG. The configuration of the indoor unit of the refrigerating and air-conditioning apparatus according to Embodiment 3 will be described with reference to FIGS. 6 and 7.

室内の天井等に設置される室内機本体２１は、室内の床面を有効に活用するため、また床から室内機本体２１までの距離を確保するため、水平方向に長さが長い略直方体の箱型形状をしている。この室内機本体２１の側面１ａには、水平方向２箇所に略円形の吹出し口（左部吹出し口２２ａ、右部吹出し口２２ｂ）が設けられている。左部吹出し口２２ａには左部ベルマウス２３ａが形成されており、この左部ベルマウス２３ａと対向して、本発明の送風機に相当する左部プロペラファン２４ａ及び左部プロペラファン２４ａを回転駆動するための左部ファンモータ２５ａが設けられている。右部吹出し口２２ｂには右部ベルマウス２３ｂが形成されており、この右部ベルマウス２３ｂと対向して、本発明の送風機に相当する右部プロペラファン２４ｂ及び右部プロペラファン２４ｂを回転駆動するための右部ファンモータ２５ｂが設けられている。上部プロペラファン４ａ及び下部プロペラファン４ｂは外径は異なるが、類似のファン形状のものを用いている。また、左部プロペラファン２４ａの外径Ｄ３よりも右部プロペラファン２４ｂの外径Ｄ４の方が小さい構成となっている。左部ファンモータ２５ａ及び右部ファンモータ２５ｂは各々モータサポート（図示せず）によって所定の位置に保持されている。また、左部吹出し口２２ａ及び右部吹出し口２２ｂは、左部プロペラファン２４ａ及び右部プロペラファン２４ｂに手等が接触することを防止するため、それぞれ左部ファンガード２６ａ及び右部ファンガード２６ｂで覆われている。   The indoor unit main body 21 installed on the indoor ceiling or the like is a substantially rectangular parallelepiped having a long length in the horizontal direction in order to effectively utilize the indoor floor surface and to secure a distance from the floor to the indoor unit main body 21. It has a box shape. The side surface 1a of the indoor unit body 21 is provided with substantially circular outlets (left outlet 22a and right outlet 22b) at two locations in the horizontal direction. A left bell mouth 23a is formed in the left outlet 22a, and the left propeller fan 24a and the left propeller fan 24a corresponding to the blower of the present invention are rotationally driven to face the left bell mouth 23a. A left fan motor 25a is provided. A right bell mouth 23b is formed in the right outlet port 22b, and the right propeller fan 24b and the right propeller fan 24b corresponding to the blower of the present invention are rotationally driven to face the right bell mouth 23b. A right fan motor 25b is provided. Although the upper propeller fan 4a and the lower propeller fan 4b have different outer diameters, they have similar fan shapes. Further, the outer diameter D4 of the right propeller fan 24b is smaller than the outer diameter D3 of the left propeller fan 24a. Each of the left fan motor 25a and the right fan motor 25b is held at a predetermined position by a motor support (not shown). Further, the left outlet 22a and the right outlet 22b are respectively provided with a left fan guard 26a and a right fan guard 26b to prevent the left propeller fan 24a and the right propeller fan 24b from coming into contact with hands. Covered with.

室内機本体２１の側面１ｂには、吸込み口２７ａが設けられている。吸込み口２７ａは、その高さ寸法は側面１ｂの高さ寸法よりやや短く、その幅寸法は側面１ｂの幅寸法よりやや短い長方形状に形成されている。室内機本体２１内には、この吸込み口２７ａを覆うように平面形状の第一熱交換器２８が配置されている。また、第一熱交換器２８の内側（吸込み口２７ａと反対側）側面の右側には、第一熱交換器２８よりも幅寸法（水平方向の寸法）が短い平面形状の第二熱交換器２９が、第一熱交換器２８と重合して配置されている。この第一熱交換器２８及び第二熱交換器２９が本発明の熱交換器に相当する。第一熱交換器２８及び第二熱交換器２９は、例えばフィンチューブ型熱交換器である。   A suction port 27 a is provided on the side surface 1 b of the indoor unit main body 21. The suction port 27a is formed in a rectangular shape whose height is slightly shorter than the height of the side surface 1b and whose width is slightly shorter than the width of the side surface 1b. A planar first heat exchanger 28 is arranged in the indoor unit body 21 so as to cover the suction port 27a. In addition, on the right side of the side surface on the inner side (opposite to the suction port 27a) of the first heat exchanger 28, a planar second heat exchanger having a shorter width dimension (horizontal dimension) than the first heat exchanger 28. 29 is arranged in superposition with the first heat exchanger 28. The first heat exchanger 28 and the second heat exchanger 29 correspond to the heat exchanger of the present invention. The first heat exchanger 28 and the second heat exchanger 29 are, for example, fin tube heat exchangers.

図７に示すように、第二熱交換器２９の左端Ｗａ（つまり第一熱交換器２８と第二熱交換器２９の重合部境界）は、左部プロペラファン２４ａの右端Ｗ１と右部プロペラファン２４ｂの左端Ｗ２との間に位置する。つまり、第二熱交換器２９の左端Ｗａ（つまり第一熱交換器８と第二熱交換器９の重合部境界）は、左部プロペラファン２４ａ及び右部プロペラファン２４ｂと対向しない位置にある。また、第二熱交換器２９の左端Ｗａ（つまり第一熱交換器２８と第二熱交換器２９の重合部境界）から、左部プロペラファン２４ａの右端Ｗ１と右部プロペラファン２４ｂの左端Ｗ２との間にかけて、空気の流れを左右で分離する分離板３０が設けられている。   As shown in FIG. 7, the left end Wa of the second heat exchanger 29 (that is, the overlapping portion boundary between the first heat exchanger 28 and the second heat exchanger 29) is the right end W1 of the left propeller fan 24a and the right propeller. It is located between the left end W2 of the fan 24b. That is, the left end Wa of the second heat exchanger 29 (that is, the overlapping portion boundary between the first heat exchanger 8 and the second heat exchanger 9) is in a position not facing the left propeller fan 24a and the right propeller fan 24b. . Further, from the left end Wa of the second heat exchanger 29 (that is, the overlapping portion boundary between the first heat exchanger 28 and the second heat exchanger 29), the right end W1 of the left propeller fan 24a and the left end W2 of the right propeller fan 24b. Is provided with a separation plate 30 that separates the air flow on the left and right.

次に室内機本体２１の空気流れについて説明する。左部ファンモータ２５ａ及び右部ファンモータ２５ｂによってそれぞれ回転する左部プロペラファン２４ａ及び右部プロペラファン２４ｂの昇圧作用によって、室内機本体２１内の圧力が低下し、吸込み口７ａから室内機本体２１の外部の空気が室内機本体２１内部に吸込まれる。室内機本体２１内部に吸込まれた空気は、第一熱交換器２８及び第二熱交換器２９を通過する過程で熱交換を行う。例えば、第一熱交換器２８及び第二熱交換器２９が凝縮器として作用する場合（つまり、室内機が暖房運転時の場合）、熱は第一熱交換器２８及び第二熱交換器２９から空気へ移動する。また、第一熱交換器２８及び第二熱交換器２９が蒸発器として作用する場合（つまり、室内機が冷房運転時の場合）、熱は空気から第一熱交換器２８及び第二熱交換器２９へ移動する。室内機本体２１に吸込まれた空気は、左部プロペラファン２４ａ及び右部プロペラファン２４ｂを介してそれぞれ左部吹出し口２２ａ及び右部吹出し口２２ｂから室内機本体２１の外に排出される。   Next, the air flow of the indoor unit body 21 will be described. The pressure in the indoor unit main body 21 is lowered by the pressure-increasing action of the left propeller fan 24a and the right propeller fan 24b that are rotated by the left fan motor 25a and the right fan motor 25b, respectively. Outside air is sucked into the indoor unit body 21. The air sucked into the indoor unit main body 21 performs heat exchange in the process of passing through the first heat exchanger 28 and the second heat exchanger 29. For example, when the first heat exchanger 28 and the second heat exchanger 29 act as a condenser (that is, when the indoor unit is in a heating operation), the heat is the first heat exchanger 28 and the second heat exchanger 29. Move from to the air. Further, when the first heat exchanger 28 and the second heat exchanger 29 act as an evaporator (that is, when the indoor unit is in a cooling operation), heat is transferred from the air to the first heat exchanger 28 and the second heat exchanger. Move to vessel 29. The air sucked into the indoor unit main body 21 is discharged out of the indoor unit main body 21 from the left outlet port 22a and the right outlet port 22b via the left propeller fan 24a and the right propeller fan 24b, respectively.

室内機本体２１の外部の空気が室内機本体２１内部に吸込まれる空気流れには、図７に示す経路Ａと経路Ｂの２経路がある。経路Ａは、第一熱交換器２８のみを通過して室内機本体２１内部に吸込まれる経路である。経路Ｂは、第一熱交換器２８及び第二熱交換器２９、つまり第一熱交換器２８と第二熱交換器２９の重合部を通過して室内機本体２１内部に吸込まれる経路である。経路Ａと比較して、経路Ｂは第二熱交換器２９を通過する分だけ通風抵抗が大きくなる。   The air flow in which the air outside the indoor unit main body 21 is sucked into the indoor unit main body 21 has two paths, a path A and a path B shown in FIG. The path A is a path that passes through only the first heat exchanger 28 and is sucked into the indoor unit main body 21. The path B is a path that passes through the first heat exchanger 28 and the second heat exchanger 29, that is, the overlapping portion of the first heat exchanger 28 and the second heat exchanger 29 and is sucked into the indoor unit body 21. is there. Compared with the path A, the ventilation resistance of the path B is increased by the amount that passes through the second heat exchanger 29.

仮に、分離板３０が無く、第二熱交換器２９の左端Ｗａ（つまり第一熱交換器２８と第二熱交換器２９の重合部境界）が左部プロペラファン２４ａの右端Ｗ１よりも左側、又は右部プロペラファン２４ｂの左端Ｗ２よりも右側にあると仮定する。第一熱交換器２８を通過した時点での経路Ａの圧力と、第二熱交換器２９を通過した時点での経路Ｂの圧力とが同じ場合、経路Ａの流速は経路Ｂの流速よりも速くなる。つまり、経路Ａの流速と経路Ｂの流速は異なる。左部プロペラファン２４ａ又は右部プロペラファン２４ｂの一方に流速の異なる経路Ａと経路Ｂの空気が流入すると、空気流れの乱れに起因する騒音が増加してしまう。   If the separation plate 30 is not provided, the left end Wa of the second heat exchanger 29 (that is, the overlapping portion boundary between the first heat exchanger 28 and the second heat exchanger 29) is on the left side of the right end W1 of the left propeller fan 24a. Alternatively, it is assumed that the right propeller fan 24b is on the right side of the left end W2. When the pressure of the path A when passing through the first heat exchanger 28 and the pressure of the path B when passing through the second heat exchanger 29 are the same, the flow rate of the path A is higher than the flow rate of the path B. Get faster. That is, the flow rate of the route A and the flow rate of the route B are different. If the air of the path | route A and the path | route B from which the flow velocity differs into one of the left part propeller fan 24a or the right part propeller fan 24b flows, the noise resulting from disturbance of an air flow will increase.

しかし、本実施形態３における室内機本体２１では、第二熱交換器２９の左端Ｗａ（つまり第一熱交換器２８と第二熱交換器２９の重合部境界）は、左部プロペラファン２４ａの右端Ｗ１と右部プロペラファン２４ｂの左端Ｗ２との間に位置する。つまり、第二熱交換器２９の左端Ｗａ（つまり第一熱交換器２８と第二熱交換器２９の重合部境界）は、左部プロペラファン２４ａ及び右部プロペラファン２４ｂと対向しない位置にある。このため、経路Ａ及び経路Ｂの空気は、それぞれ左部プロペラファン２４ａ及び右部プロペラファン２４ｂに分かれて流入する。したがって、空気流れの乱れに起因する騒音を抑制することができる。また、本実施形態３における室内機本体２１では、分離板３０が配置されているので、左部プロペラファン２４ａ又は右部プロペラファン２４ｂの一方に流速の異なる経路Ａと経路Ｂの空気が流入することをさらに抑制できる。したがって、プロペラファン４ａ及び右部プロペラファン２４ｂへ流入する空気流れは乱れが小さく、騒音の小さな室外機とすることができる。   However, in the indoor unit main body 21 according to the third embodiment, the left end Wa of the second heat exchanger 29 (that is, the overlapping portion boundary between the first heat exchanger 28 and the second heat exchanger 29) is the left propeller fan 24a. It is located between the right end W1 and the left end W2 of the right propeller fan 24b. That is, the left end Wa of the second heat exchanger 29 (that is, the overlapping portion boundary between the first heat exchanger 28 and the second heat exchanger 29) is in a position not facing the left propeller fan 24a and the right propeller fan 24b. . For this reason, the air of the path | route A and the path | route B flows in into the left part propeller fan 24a and the right part propeller fan 24b, respectively. Therefore, noise caused by air flow disturbance can be suppressed. Further, in the indoor unit main body 21 according to the third embodiment, since the separation plate 30 is arranged, the air of the path A and the path B having different flow speeds flows into one of the left propeller fan 24a and the right propeller fan 24b. This can be further suppressed. Therefore, the air flow flowing into the propeller fan 4a and the right propeller fan 24b is less disturbed and can be an outdoor unit with less noise.

分離板３０は、経路Ａ及び経路Ｂの空気の流れを上下で分離する効果の他にも低騒音化に効果を発揮する。複数台のプロペラファンを有する場合には、一方のプロペラファンに起因する速度、圧力の変動が別のプロペラファンへ影響を及ぼし騒音を増加させるが、分離板３０は、室内機本体２１内を左部プロペラファン２４ａが設けられた左部空間と、右部プロペラファン２４ｂが設けられた右部空間に分離するため、左部プロペラファン２４ａと右部プロペラファン２４ｂが互いに影響を及ぼし騒音を増加させることを抑制する。   In addition to the effect of separating the air flows in the path A and the path B up and down, the separation plate 30 is effective in reducing noise. In the case of having a plurality of propeller fans, speed and pressure fluctuations caused by one propeller fan affect another propeller fan and increase noise. However, the separation plate 30 is left in the indoor unit body 21. Since the left propeller fan 24a and the right propeller fan 24b are separated into a left space and a right propeller fan 24b, the left propeller fan 24a and the right propeller fan 24b affect each other to increase noise. To suppress that.

本実施形態３においても、実施の形態１及び２と同様に、通風抵抗の大きい経路Ｂの空気が流入する下部プロペラファン４ｂに、通風抵抗の小さい経路Ａの空気が流入する上部プロペラファン４ａよりも静圧が大きい状態で比騒音が最小となるプロペラファンを用いることで、より騒音の小さい冷凍空調装置とすることができる。   Also in the third embodiment, as in the first and second embodiments, the lower propeller fan 4b into which the air in the path B having a large ventilation resistance flows flows into the lower propeller fan 4a into which the air in the path A having a small ventilation resistance flows. However, by using a propeller fan that minimizes the specific noise in a state where the static pressure is large, a refrigeration air conditioner with less noise can be obtained.

この発明の実施の形態１における冷凍空調装置の室外機を示す斜視図である。It is a perspective view which shows the outdoor unit of the refrigerating air conditioning apparatus in Embodiment 1 of this invention. この発明の実施の形態１における図１のＡ−Ａ断面を示す断面模式図である。It is a cross-sectional schematic diagram which shows the AA cross section of FIG. 1 in Embodiment 1 of this invention. この発明の実施の形態１における上部プロペラファン４ａ及び下部プロペラファン４ｂの空力特性図であり、（ａ）は風量−比騒音特性図、（ｂ）は風量−静圧特性図である。It is an aerodynamic characteristic figure of upper propeller fan 4a and lower propeller fan 4b in Embodiment 1 of this invention, (a) is an air volume-specific noise characteristic figure, and (b) is an air volume-static pressure characteristic figure. この発明の実施の形態１における冷凍空調装置の熱交換器形態の一例を示す斜視図である。It is a perspective view which shows an example of the heat exchanger form of the refrigerating air conditioning apparatus in Embodiment 1 of this invention. この発明の実施の形態２における冷凍空調装置の室外機を示す断面模式図である。It is a cross-sectional schematic diagram which shows the outdoor unit of the refrigerating and air-conditioning apparatus in Embodiment 2 of this invention. この発明の実施の形態３における冷凍空調装置の室外機を示す斜視図である。It is a perspective view which shows the outdoor unit of the refrigerating air conditioning apparatus in Embodiment 3 of this invention. この発明の実施の形態３における図６のＢ−Ｂ断面を示す断面模式図である。It is a cross-sectional schematic diagram which shows the BB cross section of FIG. 6 in Embodiment 3 of this invention.

符号の説明Explanation of symbols

１ 室外機本体、１ａ〜ｄ 側面、２ａ 上部吹出し口、２ｂ 下部吹出し口、３ａ 上部ベルマウス、３ｂ 下部ベルマウス、４ａ 上部プロペラファン、４ｂ 下部プロペラファン、５ａ 上部ファンモータ、５ｂ 下部ファンモータ、６ａ 上部ファンガード、６ｂ 下部ファンガード、７ａ 吸込み口、７ｂ 吸込み口、８ 第一熱交換器、９ 第二熱交換器、１０ 分離板、１１ 機械室板、１２ 機械室、１３ 冷却用フィン、２１ 室内機本体、２１ａ，ｂ 側面、２２ａ 左部吹出し口、２２ｂ 右部吹出し口、２３ａ 左部ベルマウス、２３ｂ 右部ベルマウス、２４ａ 左部プロペラファン、２４ｂ 右部プロペラファン、２５ａ 左部ファンモータ、２５ｂ 右部ファンモータ、２６ａ 左部ファンガード、２６ｂ 右部ファンガード、２７ａ 吸込み口、２８ 第一熱交換器、２９ 第二熱交換器、３０ 分離板、Ａ 経路、Ｂ 経路。   DESCRIPTION OF SYMBOLS 1 Outdoor unit main body, 1a-d side surface, 2a Upper outlet, 2b Lower outlet, 3a Upper bell mouth, 3b Lower bell mouth, 4a Upper propeller fan, 4b Lower propeller fan, 5a Upper fan motor, 5b Lower fan motor, 6a Upper fan guard, 6b Lower fan guard, 7a Suction port, 7b Suction port, 8 First heat exchanger, 9 Second heat exchanger, 10 Separation plate, 11 Machine room plate, 12 Machine room, 13 Cooling fin, 21 indoor unit main body, 21a, b side surface, 22a left outlet, 22b right outlet, 23a left bell mouth, 23b right bell mouth, 24a left propeller fan, 24b right propeller fan, 25a left fan Motor, 25b Right fan motor, 26a Left fan guard, 26b Right fan guard, 27 a suction port, 28 first heat exchanger, 29 second heat exchanger, 30 separator plate, A path, B path

Claims (9)

空気の吸込み口と吹出し口が形成された本体と、
前記吸込み口から空気を吸引し、前記吹出し口から空気を排出させる複数の送風機と、
前記吸込み口と前記送風機との間に配置された熱交換器と、
を備えた冷凍空調装置において、
前記熱交換器は、
空気流れ上流側に配置された第一熱交換器と、空気流れ下流側に配置された第二熱交換器とからなり、
前記第一熱交換器と前記第二熱交換器は重合して設けられ、
前記第一熱交換器と前記第二熱交換器は大きさが異なり、
前記第一熱交換器と前記第二熱交換器との重合部境界が、
前記送風機と対向しない位置にあることを特徴とする冷凍空調装置。 A main body formed with an air inlet and outlet;
A plurality of blowers for sucking air from the suction port and discharging air from the blowout port;
A heat exchanger disposed between the suction port and the blower;
In the refrigeration air conditioner with
The heat exchanger is
The first heat exchanger disposed on the upstream side of the air flow and the second heat exchanger disposed on the downstream side of the air flow,
The first heat exchanger and the second heat exchanger are provided by polymerization,
The first heat exchanger and the second heat exchanger are different in size,
The overlapping part boundary between the first heat exchanger and the second heat exchanger is
A refrigerating and air-conditioning apparatus, wherein the refrigerating and air-conditioning apparatus is in a position not facing the blower. 前記複数の送風機は上下方向に設けられ、
前記第一熱交換器と前記第二熱交換器は上下方向長さが異なることを特徴とする請求項１に記載の冷凍空調装置。 The plurality of blowers are provided in the vertical direction,
The refrigerating and air-conditioning apparatus according to claim 1, wherein the first heat exchanger and the second heat exchanger have different vertical lengths. 前記重合部境界から、
前記複数の送風機間にかけて、
分離板が設けられたことを特徴とする請求項２に記載の冷凍空調装置。 From the overlap portion boundary,
Between the plurality of blowers,
The refrigerating and air-conditioning apparatus according to claim 2, wherein a separation plate is provided. 前記分離板は、
前記熱交換器側へ下るように傾斜して設けられたことを特徴とする請求項３に記載の冷凍空調装置。 The separation plate is
The refrigerating and air-conditioning apparatus according to claim 3, wherein the refrigerating and air-conditioning apparatus is provided so as to be inclined toward the heat exchanger side. 前記複数の送風機は左右方向に設けられ、
前記第一熱交換器と前記第二熱交換器は左右方向長さが異なることを特徴とする請求項１に記載の冷凍空調装置。 The plurality of fans are provided in the left-right direction,
The refrigerating and air-conditioning apparatus according to claim 1, wherein the first heat exchanger and the second heat exchanger have different lengths in the left-right direction. 前記重合部境界から、
前記複数の送風機間にかけて、
分離板が設けられたことを特徴とする請求項５に記載の冷凍空調装置。 From the overlap portion boundary,
Between the plurality of blowers,
The refrigerating and air-conditioning apparatus according to claim 5, further comprising a separation plate. 前記複数の送風機のうち、
前記第一熱交換器と前記第二熱交換器との重合部に対向して設けられた送風機は、
前記第一熱交換器と前記第二熱交換器とが重合しない範囲に対向して設けられた送風機と比較して、
静圧が大きい状態で比騒音が最小となる送風機を用いたことを特徴とする請求項１〜請求項６のいずれかに記載の冷凍空調装置。 Among the plurality of blowers,
A blower provided to face the overlapping portion of the first heat exchanger and the second heat exchanger,
Compared to the blower provided facing the range where the first heat exchanger and the second heat exchanger do not overlap,
The refrigerating and air-conditioning apparatus according to any one of claims 1 to 6, wherein a blower that minimizes specific noise in a state where the static pressure is large is used. 前記複数の送風機のうち、
前記第一熱交換器と前記第二熱交換器との重合部に対向して設けられた送風機と、
前記第一熱交換器と前記第二熱交換器とが重合しない範囲に対向して設けられた送風機は、
それぞれファン形状が相似するプロペラファンを用い、
前記第一熱交換器と前記第二熱交換器との重合部に対向して設けられた該プロペラファンは、
前記第一熱交換器と前記第二熱交換器とが重合しない範囲に対向して設けられた前記プロペラファンと比較して、
ファン外径が小さいことを特徴とする請求項７に記載の冷凍空調装置。 Among the plurality of blowers,
A blower provided to face the overlapping portion of the first heat exchanger and the second heat exchanger;
The blower provided facing the range where the first heat exchanger and the second heat exchanger do not overlap,
Propeller fans with similar fan shapes are used,
The propeller fan provided facing the overlapping portion of the first heat exchanger and the second heat exchanger is,
Compared to the propeller fan provided facing the range where the first heat exchanger and the second heat exchanger are not polymerized,
The refrigerating and air-conditioning apparatus according to claim 7, wherein a fan outer diameter is small. 前記第一熱交換器または前記第二熱交換器の一方のみを通過する空気流れの風路に冷却用フィンを設置したことを特徴とする請求項１〜請求項８のいずれかに記載の冷凍空調装置。   The refrigeration according to any one of claims 1 to 8, wherein a cooling fin is installed in an air flow path of an air flow passing through only one of the first heat exchanger or the second heat exchanger. Air conditioner.
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011252673A (en) * 2010-06-03 2011-12-15 Mitsubishi Electric Corp Outdoor unit of refrigerating cycle device
JP2014194306A (en) * 2013-03-29 2014-10-09 Hitachi Appliances Inc Heat exchange device and heat pump water heater
CN108534239A (en) * 2018-06-12 2018-09-14 珠海格力电器股份有限公司 Indoor unit and air conditioner
CN114992799A (en) * 2022-05-05 2022-09-02 青岛海尔空调电子有限公司 Air conditioner outdoor unit and control method of air conditioner
CN114992799B (en) * 2022-05-05 2024-06-07 青岛海尔空调电子有限公司 Air conditioner outdoor unit and control method of air conditioner

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JPH07158902A (en) * 1993-12-10 1995-06-20 Mitsubishi Electric Corp Outdoor unit for air-conditioning machine and assembling method thereof
JPH08270985A (en) * 1995-04-03 1996-10-18 Toshiba Corp Outdoor unit for air conditioner

Patent Citations (2)

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JPH07158902A (en) * 1993-12-10 1995-06-20 Mitsubishi Electric Corp Outdoor unit for air-conditioning machine and assembling method thereof
JPH08270985A (en) * 1995-04-03 1996-10-18 Toshiba Corp Outdoor unit for air conditioner

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011252673A (en) * 2010-06-03 2011-12-15 Mitsubishi Electric Corp Outdoor unit of refrigerating cycle device
JP2014194306A (en) * 2013-03-29 2014-10-09 Hitachi Appliances Inc Heat exchange device and heat pump water heater
CN108534239A (en) * 2018-06-12 2018-09-14 珠海格力电器股份有限公司 Indoor unit and air conditioner
CN114992799A (en) * 2022-05-05 2022-09-02 青岛海尔空调电子有限公司 Air conditioner outdoor unit and control method of air conditioner
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