JP7005355B2 - Air conditioner - Google Patents

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JP7005355B2
JP7005355B2 JP2018007218A JP2018007218A JP7005355B2 JP 7005355 B2 JP7005355 B2 JP 7005355B2 JP 2018007218 A JP2018007218 A JP 2018007218A JP 2018007218 A JP2018007218 A JP 2018007218A JP 7005355 B2 JP7005355 B2 JP 7005355B2
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flat surface
straightening vane
surface portion
radial direction
fan
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JP2019124437A (en
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昌和 伊藤
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Priority to JP2018007218A priority Critical patent/JP7005355B2/en
Priority to AU2018402616A priority patent/AU2018402616B2/en
Priority to ES18901027T priority patent/ES2969560T3/en
Priority to CN201880086535.1A priority patent/CN111602006A/en
Priority to PCT/JP2018/041713 priority patent/WO2019142466A1/en
Priority to EP18901027.5A priority patent/EP3739268B1/en
Publication of JP2019124437A publication Critical patent/JP2019124437A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0022—Centrifugal or radial fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/02—Ducting arrangements
    • F24F13/06—Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser
    • F24F2013/0616—Outlets that have intake openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
    • F24F13/082—Grilles, registers or guards
    • F24F2013/088—Air-flow straightener

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Air-Flow Control Members (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Description

本発明は、熱交換器の内周側に取り付けられる複数の整流板を備える空気調和機に関するものである。 The present invention relates to an air conditioner provided with a plurality of straightening vanes attached to the inner peripheral side of a heat exchanger.

従来、遠心ファンの周囲にフィンチューブ形の熱交換器を設けた天井埋込型の空気調和機が知られている（例えば、特許文献１参照）。
特許文献１に開示される空気調和機は、方形状の熱交換器の四辺の内側の中央に、それぞれ３枚の導風板を配置したものである。導風板は、遠心ファンの回転方向と反対方向に傾斜し、内側に膨出した曲面状に形成されている。特許文献１の空気調和機は、３枚の導風板の狭い空間に吹き出し風を流入させて吹き出し風の向きをフィンの方向に変化させることにより、吹き出し風がフィンに衝突して発生する送風騒音を減少させる。 Conventionally, a ceiling-embedded air conditioner in which a fin tube type heat exchanger is provided around a centrifugal fan is known (see, for example, Patent Document 1).
The air conditioner disclosed in Patent Document 1 has three baffle plates arranged in the center of the inside of each of the four sides of a rectangular heat exchanger. The baffle plate is formed in a curved surface shape that is inclined in the direction opposite to the rotation direction of the centrifugal fan and bulges inward. The air conditioner of Patent Document 1 causes the blown air to flow into the narrow space of the three baffle plates and changes the direction of the blown air toward the fins, so that the blown air collides with the fins and is generated. Reduce noise.

特開２００１－９９４３６号公報Japanese Unexamined Patent Publication No. 2001-99436

しかしながら、特許文献１の空気調和機は、方形状の熱交換器の四辺の内側の中央にそれぞれ３枚の導風板を配置している。また、導風板が遠心ファンの回転方向と反対方向に傾斜して内側に膨出した曲面状に形成されている。そのため、導風板を配置することにより、通風抵抗が大きく上昇してしまう。 However, in the air conditioner of Patent Document 1, three baffle plates are arranged in the center inside the four sides of the rectangular heat exchanger. Further, the baffle plate is formed in a curved surface shape that is inclined in the direction opposite to the rotation direction of the centrifugal fan and bulges inward. Therefore, by arranging the baffle plate, the ventilation resistance is greatly increased.

本発明は、このような事情に鑑みてなされたものであって、通風抵抗を大きく上昇させることなく吹き出し風がフィンに衝突して発生する送風騒音を減少させることが可能な空気調和機を提供することを目的とする。 INDUSTRIAL APPLICABILITY The present invention has been made in view of such circumstances, and provides an air conditioner capable of reducing the ventilation noise generated by the blown wind colliding with the fins without significantly increasing the ventilation resistance. The purpose is to do.

上記課題を解決するために、本発明の空気調和機は以下の手段を採用する。
本発明の一態様に係る空気調和機は、回転軸の軸線方向に沿って流入する空気を前記軸線方向と交差する半径方向に流出させるファンと、前記ファンの外周を取り囲むように配置されるとともに伝熱管と該伝熱管に取り付けられる複数のフィンとを有する熱交換器と、前記熱交換器の内周側に取り付けられるとともに前記回転軸と平行な軸線に沿って延びて前記回転軸に向けて直線状に突出する複数の整流板と、を備え、前記熱交換器は、前記ファンとの最近接位置において前記半径方向と直交する平面に沿って配置される複数の平面部と、前記複数の平面部を連結する複数の曲面部と、を有し、前記複数の平面部の少なくともいずれか一つには、前記最近接位置よりも前記ファンの回転方向の上流側の第１所定位置に第１の前記整流板が取り付けられ、前記最近接位置よりも前記ファンの回転方向の下流側の第２所定位置に第２の前記整流板が取り付けられ、前記第１の整流板と前記第２の整流板とが隣接して配置される。 In order to solve the above problems, the air conditioner of the present invention employs the following means.
The air conditioner according to one aspect of the present invention is arranged so as to surround a fan that causes air flowing in along the axial direction of the rotating shaft to flow out in the radial direction intersecting the axial direction, and an outer periphery of the fan. A heat exchanger having a heat transfer tube and a plurality of fins attached to the heat transfer tube, and a heat exchanger attached to the inner peripheral side of the heat exchanger and extending along an axis parallel to the rotation axis toward the rotation axis. The heat exchanger comprises a plurality of linearly projecting rectifying plates, and the heat exchanger includes a plurality of flat surface portions arranged along a plane orthogonal to the radial direction at a position closest to the fan, and the plurality of flat surface portions. It has a plurality of curved surface portions connecting the flat surface portions, and at least one of the plurality of flat surface portions is located at a first predetermined position on the upstream side in the rotation direction of the fan from the closest position. The rectifying plate of 1 is attached, and the second rectifying plate is attached to a second predetermined position on the downstream side in the rotation direction of the fan from the closest position, and the first rectifying plate and the second rectifying plate are attached. The rectifying plate is arranged adjacent to it.

本発明の一態様に係る空気調和機によれば、熱交換器の複数の平面部の少なくともいずれか一つには、ファンとの最近接位置よりもファンの回転方向の上流側の第１所定位置に第１の整流板が取り付けられる。そのため、吹き出し風の回転方向の速度成分が、最近接位置に到達する前に第１の整流板で発生する乱流により減少し、最近接位置で吹き出し風がフィンに衝突して発生する送風騒音が減少する。
また、本発明の一態様に係る空気調和機によれば、熱交換器の複数の平面部の少なくともいずれか一つには、ファンとの最近接位置よりもファンの回転方向の下流側の第２所定位置に第２の整流板が取り付けられる。そのため、最近接位置よりもファンの回転方向の下流側で吹き出し風の回転方向の速度成分が再び上昇することが抑制され、吹き出し風がフィンに衝突して発生する送風騒音が減少する。 According to the air conditioner according to one aspect of the present invention, at least one of the plurality of flat surfaces of the heat exchanger has a first predetermined position on the upstream side in the rotation direction of the fan with respect to the position closest to the fan. A first straightening vane is attached at the position. Therefore, the velocity component in the rotation direction of the blown wind is reduced by the turbulent flow generated in the first straightening vane before reaching the closest position, and the blown air is generated by the blown wind colliding with the fins at the closest position. Decreases.
Further, according to the air conditioner according to one aspect of the present invention, at least one of the plurality of flat surface portions of the heat exchanger is located on the downstream side in the rotation direction of the fan with respect to the position closest to the fan. 2 A second rectifying plate is attached at a predetermined position. Therefore, it is suppressed that the velocity component in the rotation direction of the blown wind rises again on the downstream side in the rotation direction of the fan from the closest position, and the blowing noise generated by the blown wind colliding with the fins is reduced.

さらに、本発明の一態様に係る空気調和機によれば、整流板がファンの回転軸と平行な軸線に沿って延びて回転軸に向けて直線状に突出する形状となっているため、ファンの回転方向と反対方向に傾斜して内側に膨出した曲面状に形成される場合に比べて通風抵抗が減少する。また、第１の整流板と第２の整流板が最近接位置を挟んでファンの回転方向の上流側と下流側に隣接して配置されるため、最近接位置を含めた３枚の整流板を配置する場合に比べて通風抵抗が減少する。
このように、本発明の一態様に係る空気調和機によれば、通風抵抗を大きく上昇させることなく吹き出し風がフィンに衝突して発生する送風騒音を減少させることができる。 Further, according to the air conditioner according to one aspect of the present invention, the straightening vane extends along the axis parallel to the rotation axis of the fan and protrudes linearly toward the rotation axis. Ventilation resistance is reduced as compared with the case where it is formed in a curved shape that is inclined in the direction opposite to the direction of rotation and bulges inward. Further, since the first straightening vane and the second straightening vane are arranged adjacent to the upstream side and the downstream side in the rotation direction of the fan with the closest contacting position in between, the three straightening vanes including the closest contacting position are arranged adjacent to each other. Ventilation resistance is reduced compared to the case of arranging.
As described above, according to the air conditioner according to one aspect of the present invention, it is possible to reduce the blowing noise generated by the blown wind colliding with the fins without significantly increasing the ventilation resistance.

本発明の一態様に係る空気調和機において、前記第１所定位置は、前記平面部の前記最近接位置を通過する前記半径方向と前記第１の整流板の先端を通過する前記半径方向とがなす角が３度以上かつ７度以下の範囲となる位置である。より好ましくは、５度となる位置である。
このようにすることで、最近接位置における吹き出し風の回転方向の速度成分を適切に減少させることができる。 In the air conditioner according to one aspect of the present invention, the first predetermined position includes the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the first straightening vane. It is a position where the angle between the two is 3 degrees or more and 7 degrees or less. More preferably, it is a position of 5 degrees.
By doing so, it is possible to appropriately reduce the velocity component in the rotation direction of the blown wind at the closest position.

本発明の一態様に係る空気調和機において、前記第２所定位置は、前記平面部の前記最近接位置を通過する前記半径方向と前記第２の整流板の先端を通過する前記半径方向とがなす角が１５度以上かつ２０度以下の範囲となる位置である。
このようにすることで、最近接位置よりもファンの回転方向の下流側で吹き出し風の回転方向の速度成分が再び上昇すること適切に抑制することができる。 In the air conditioner according to one aspect of the present invention, the second predetermined position includes the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the second straightening vane. It is a position where the angle formed is within the range of 15 degrees or more and 20 degrees or less.
By doing so, it is possible to appropriately suppress that the velocity component in the rotation direction of the blown wind rises again on the downstream side in the rotation direction of the fan from the closest position.

本発明の一態様に係る空気調和機において、前記第１の整流板及び前記第２の整流板が取り付けられる前記平面部の前記最近接位置における前記ファンと前記熱交換器との前記半径方向の距離をＬとし、前記第１の整流板の前記回転軸へ向けて突出する長さをｌとした場合、Ｌ／ｌ≧３．５かつｌ≧７ｍｍを満たすようにしてもよい。
ファンと熱交換器との半径方向の距離Ｌを第１の整流板の回転軸へ向けて突出する長さｌの３．５倍以上とすることで、第１の整流板による通風抵抗の上昇を十分に抑制することができる。また、ｌを７ｍｍ以上とすることで、第１の整流板で適切に乱流を発生させ、最近接位置における吹き出し風の回転方向の速度成分を減少させることができる。 In the air conditioner according to one aspect of the present invention, in the radial direction of the fan and the heat exchanger at the closest position of the flat surface portion to which the first straightening vane and the second straightening vane are attached. When the distance is L and the length of the first straightening vane protruding toward the rotation axis is l, L / l ≧ 3.5 and l ≧ 7 mm may be satisfied.
By setting the radial distance L between the fan and the heat exchanger to 3.5 times or more the length l protruding toward the rotation axis of the first straightening vane, the ventilation resistance of the first straightening vane increases. Can be sufficiently suppressed. Further, by setting l to 7 mm or more, it is possible to appropriately generate turbulence in the first straightening vane and reduce the velocity component in the rotation direction of the blown wind at the closest position.

本発明によれば、通風抵抗を大きく上昇させることなく吹き出し風がフィンに衝突して発生する送風騒音を減少させることが可能な空気調和機を提供することができる。 According to the present invention, it is possible to provide an air conditioner capable of reducing the blowing noise generated by the blown wind colliding with the fins without significantly increasing the ventilation resistance.

本発明の一実施形態に係る空気調和機の斜視図である。It is a perspective view of the air conditioner which concerns on one Embodiment of this invention. 図１に示す空気調和機の室内機の縦断面図である。It is a vertical sectional view of the indoor unit of the air conditioner shown in FIG. 図２に示すファン及び室内熱交換器を開口側からみた図である。It is a figure which looked at the fan and the room heat exchanger shown in FIG. 2 from the opening side. 図２に示す室内熱交換器及び整流板の部分拡大図である。FIG. 3 is a partially enlarged view of the indoor heat exchanger and the straightening vane shown in FIG. 2. 図３に示す第１平面部の最近接位置の近傍の部分拡大図である。FIG. 3 is a partially enlarged view of the vicinity of the closest position of the first plane portion shown in FIG. 室内機で発生する騒音の音圧レベルを示すグラフである。It is a graph which shows the sound pressure level of the noise generated in an indoor unit.

以下に、本発明に係る空気調和機１の一実施形態について、図面を参照して説明する。
図１には、本実施形態に係る天井埋込み型の空気調和機１の斜視図が示され、図２には、その縦断面図が示されている。ここでは、室外機２に対して１台の室内機３が接続された天井埋込み型の空気調和機１の例が示されている。 Hereinafter, an embodiment of the air conditioner 1 according to the present invention will be described with reference to the drawings.
FIG. 1 shows a perspective view of the ceiling-embedded air conditioner 1 according to the present embodiment, and FIG. 2 shows a vertical sectional view thereof. Here, an example of a ceiling-embedded air conditioner 1 in which one indoor unit 3 is connected to the outdoor unit 2 is shown.

空気調和機１は、室内機３が室内の天井等に吊下げ設置され、冷媒配管４および電気配線５を介して屋外の設置された室外機２と接続されて使用されるものである。室外機２には、冷媒圧縮機６、室外熱交換器７、室外ファン８、コントロールボックス９、図示省略の四方切換弁等の機器類が設置されている。この室外機２は、室内機３側に設けられる後述の室内熱交換器１８と共に冷凍サイクルを構成し、室内機３に供給する冷媒の調整機能を担うものである。 The air conditioner 1 is used by suspending the indoor unit 3 from the ceiling or the like in the room and connecting it to the outdoor unit 2 installed outdoors via the refrigerant pipe 4 and the electric wiring 5. The outdoor unit 2 is provided with equipment such as a refrigerant compressor 6, an outdoor heat exchanger 7, an outdoor fan 8, a control box 9, and a four-way switching valve (not shown). The outdoor unit 2 constitutes a refrigeration cycle together with the indoor heat exchanger 18 provided on the indoor unit 3 side, and is responsible for adjusting the refrigerant supplied to the indoor unit 3.

室内機３は、下方部が開口されているキャビネット１０と、このキャビネット１０の下方部位に取り付けられる略四角形状の天井パネル１１とを備えている。キャビネット１０内の下方部位には、空気吸込口１２を形成するベルマウス１３と、ドレンパン１４とが設置されており、ドレンパン１４の一部により風路１５が形成されている。また、キャビネット１０の天板中央部位には、ファンモータ１６により回転駆動されるターボファン１７が設置されており、このターボファン１７の外周を取り囲むように、四角形状に折り曲げ形成されている室内熱交換器１８が図示省略のブラケットを介して天板側に固定設置されている。 The indoor unit 3 includes a cabinet 10 having an open lower portion and a substantially square ceiling panel 11 attached to a lower portion of the cabinet 10. A bell mouth 13 forming an air suction port 12 and a drain pan 14 are installed in a lower portion of the cabinet 10, and an air passage 15 is formed by a part of the drain pan 14. Further, a turbofan 17 that is rotationally driven by a fan motor 16 is installed in the central portion of the top plate of the cabinet 10, and the indoor heat is formed by bending in a square shape so as to surround the outer periphery of the turbofan 17. The exchanger 18 is fixedly installed on the top plate side via a bracket (not shown).

キャビネット１０内には、空気吸込口１２を形成するベルマウス１３を介してターボファン１７に室内空気を導き、ターボファン１７により昇圧されてラジアル方向に吹出された空気を、その外周を取り囲むように配設されている室内熱交換器１８を通して、キャビネット１０の内面とドレンパン１４の外周面とで形成される風路１５へと流通させる空気流通路１９が構成されている。 Inside the cabinet 10, indoor air is guided to the turbofan 17 via the bell mouth 13 forming the air suction port 12, and the air boosted by the turbofan 17 and blown out in the radial direction surrounds the outer periphery thereof. An air flow passage 19 is configured to flow through the indoor heat exchanger 18 arranged to the air passage 15 formed by the inner surface of the cabinet 10 and the outer peripheral surface of the drain pan 14.

四方形状の天井パネル１１には、その四辺に沿って空調風を吹出す長方形状の空気吹出口２０が風路１５と連通すように設けられているとともに、中央部に室内空気を吸込むための開口２１が設けられている。この開口２１には、エアフィルタ２２等を設置した吸込グリル２３が、図１に示されるように、ワイヤ２４等を介して昇降自在に設けられている。また、各空気吹出口２０には、空気吹出口２０から吹出される空調風の風向を調整するための風向調整ルーバ２５が、それぞれ個別にスイング可能に設置されている。 The rectangular ceiling panel 11 is provided with a rectangular air outlet 20 for blowing air-conditioned air along its four sides so as to communicate with the air passage 15, and for sucking indoor air into the central portion. An opening 21 is provided. As shown in FIG. 1, a suction grill 23 on which an air filter 22 or the like is installed is provided in the opening 21 so as to be able to move up and down via a wire 24 or the like. Further, at each air outlet 20, a wind direction adjusting louver 25 for adjusting the wind direction of the conditioned air blown from the air outlet 20 is individually swingably installed.

ターボファン１７は、中心部にファンモータ１６の回転軸１６Ａを固定するためのハブ２６が設けられている主板２７と、主板２７に対向配設されている流体流路２８を形成するためのシュラウド２９と、シュラウド２９と主板２７との間に配設されている複数枚のブレード３０とから構成されている。このターボファン１７は、シュラウド２９側がベルマウス１３の空気吸込口１２に対向配置されており、ベルマウス１３の一部がシュラウド２９の内周にオーバーラップされ、その間にターボファン１７の吹出風の一部をベルマウス１３の裏面に沿ってベルマウス１３とシュラウド２９とのオーバーラップ部の隙間からシュラウド２９の内面２９Ａ側に循環させる再循環路３１が形成されている。 The turbofan 17 has a main plate 27 provided with a hub 26 for fixing the rotating shaft 16A of the fan motor 16 in the center thereof, and a shroud for forming a fluid flow path 28 opposed to the main plate 27. It is composed of 29 and a plurality of blades 30 arranged between the shroud 29 and the main plate 27. In this turbofan 17, the shroud 29 side is arranged to face the air suction port 12 of the bell mouth 13, and a part of the bell mouth 13 overlaps the inner circumference of the shroud 29, during which the blown wind of the turbo fan 17 is blown. A recirculation path 31 is formed in which a part of the bell mouth 13 is circulated along the back surface of the shroud 29 from the gap of the overlapping portion between the bell mouth 13 and the shroud 29 to the inner surface 29A side of the shroud 29.

ターボファン１７は、ファンモータ１６の回転軸１６Ａ回りに回転するファンであり、回転軸１６Ａの軸線方向に沿って流入する空気を回転軸１６Ａの軸線方向と交差する半径方向に流出させる。ここで、回転軸１６Ａの軸線方向は鉛直方向と一致しており、軸線方向と交差する半径方向は水平方向と一致している。 The turbofan 17 is a fan that rotates around the rotating shaft 16A of the fan motor 16 and causes the air flowing in along the axial direction of the rotating shaft 16A to flow out in the radial direction intersecting the axial direction of the rotating shaft 16A. Here, the axial direction of the rotating shaft 16A coincides with the vertical direction, and the radial direction intersecting the axial direction coincides with the horizontal direction.

ここで、図３を参照して、室内熱交換器１８について説明する。図３は、図２に示すターボファン１７及び室内熱交換器１８を開口２１からみた図である。
図３に示すように、室内熱交換器１８は、ターボファン１７の外周を取り囲むように配置されるとともに伝熱管１８ａと伝熱管１８ａに取り付けられる複数のフィン１８ｂとを有する。図３に示すように、室内熱交換器１８は、第１平面部１８Ａ，第２平面部１８Ｂ，第３平面部１８Ｃ，第４平面部１８Ｄ，第５平面部１８Ｅと、第１曲面部１８Ｆ，第２曲面部１８Ｇ，第３曲面部１８Ｈ，第４曲面部１８Ｉとを有する。 Here, the indoor heat exchanger 18 will be described with reference to FIG. FIG. 3 is a view of the turbofan 17 and the indoor heat exchanger 18 shown in FIG. 2 as viewed from the opening 21.
As shown in FIG. 3, the indoor heat exchanger 18 is arranged so as to surround the outer periphery of the turbofan 17, and has a heat transfer tube 18a and a plurality of fins 18b attached to the heat transfer tube 18a. As shown in FIG. 3, the indoor heat exchanger 18 includes a first flat surface portion 18A, a second flat surface portion 18B, a third flat surface portion 18C, a fourth flat surface portion 18D, a fifth flat surface portion 18E, and a first curved surface portion 18F. , A second curved surface portion 18G, a third curved surface portion 18H, and a fourth curved surface portion 18I.

第１平面部１８Ａは、ターボファン１７のブレード３０との最近接位置Ｐ１において半径方向と直交する平面に沿って配置される部分である。第２平面部１８Ｂは、ターボファン１７のブレード３０との最近接位置Ｐ２において半径方向と直交する平面に沿って配置される部分である。第３平面部１８Ｃは、ターボファン１７のブレード３０との最近接位置Ｐ３において半径方向と直交する平面に沿って配置される部分である。第４平面部１８Ｄは、ターボファン１７のブレード３０との最近接位置Ｐ３において半径方向と直交する平面に沿って配置される部分である。第５平面部１８Ｅは、ターボファン１７のブレード３０との最近接位置Ｐ５において半径方向と直交する平面に沿って配置される部分である。 The first plane portion 18A is a portion arranged along a plane orthogonal to the radial direction at the position P1 closest to the blade 30 of the turbofan 17. The second plane portion 18B is a portion arranged along a plane orthogonal to the radial direction at the position P2 closest to the blade 30 of the turbofan 17. The third plane portion 18C is a portion arranged along a plane orthogonal to the radial direction at the position P3 closest to the blade 30 of the turbofan 17. The fourth plane portion 18D is a portion arranged along a plane orthogonal to the radial direction at the position P3 closest to the blade 30 of the turbofan 17. The fifth plane portion 18E is a portion arranged along a plane orthogonal to the radial direction at the position P5 closest to the blade 30 of the turbofan 17.

第１曲面部１８Ｆは第１平面部１８Ａと第２平面部１８Ｂとを連結する部分であり、第２曲面部１８Ｇは第２平面部１８Ｂと第３平面部１８Ｃとを連結する部分であり、第３曲面部１８Ｈは第３平面部１８Ｃと第４平面部１８Ｄとを連結する部分であり、第４曲面部１８Ｉは第４平面部１８Ｄと第５平面部１８Ｅとを連結する部分である。 The first curved surface portion 18F is a portion connecting the first flat surface portion 18A and the second flat surface portion 18B, and the second curved surface portion 18G is a portion connecting the second flat surface portion 18B and the third flat surface portion 18C. The third curved surface portion 18H is a portion connecting the third flat surface portion 18C and the fourth flat surface portion 18D, and the fourth curved surface portion 18I is a portion connecting the fourth flat surface portion 18D and the fifth flat surface portion 18E.

次に、図２から図５を参照して、室内熱交換器１８の内周側に取り付けられる複数の整流板３２について説明する。図４は、図２に示す室内熱交換器１８及び整流板３２の部分拡大図である。図５は、図３の第１平面部１８Ａの最近接位置Ｐ１の近傍の部分拡大図である。
図２に示すように、室内熱交換器１８の内周側には、回転軸１６Ａと平行な軸線Ｘ１に沿って延びる整流板３２と、回転軸１６Ａと平行な軸線Ｘ２に沿って延びる整流板３２とが取り付けられている。 Next, with reference to FIGS. 2 to 5, a plurality of straightening vanes 32 attached to the inner peripheral side of the indoor heat exchanger 18 will be described. FIG. 4 is a partially enlarged view of the indoor heat exchanger 18 and the straightening vane 32 shown in FIG. FIG. 5 is a partially enlarged view of the vicinity of the closest position P1 of the first plane portion 18A of FIG.
As shown in FIG. 2, on the inner peripheral side of the indoor heat exchanger 18, a rectifying plate 32 extending along the axis X1 parallel to the rotation shaft 16A and a rectifying plate extending along the axis X2 parallel to the rotation shaft 16A. 32 and are attached.

図３に示すように、第１平面部１８Ａの内周側には２つの整流板３２が取り付けられており、第２平面部１８Ｂの内周側には２つの整流板３２が取り付けられており、第３平面部１８Ｃの内周側には２つの整流板３２が取り付けられている。第４平面部１８Ｄの内周側には１つの整流板３２が取り付けられており、第５平面部１８Ｅの内周側には１つの整流板３２が取り付けられている。 As shown in FIG. 3, two straightening vanes 32 are attached to the inner peripheral side of the first flat surface portion 18A, and two straightening vanes 32 are attached to the inner peripheral side of the second flat surface portion 18B. , Two straightening vanes 32 are attached to the inner peripheral side of the third flat surface portion 18C. One straightening vane 32 is attached to the inner peripheral side of the fourth flat surface portion 18D, and one straightening vane 32 is attached to the inner peripheral side of the fifth flat surface portion 18E.

図４に示すように、整流板３２は、ターボファン１７の半径方向と直交する平面に沿って配置される基部３２ａと、基部３２ａから回転軸１６Ａに向けて直線状に突出する板部３２ｂと、基部３２ａから板部３２ｂの反対方向に突出する一対の保持部３２ｃと、基部３２ａから板部３２ｂの反対方向に突出する支持部３２ｄと、を有する。整流板３２は、支持部３２ｄを伝熱管１８ａに支持させた状態で一対の保持部３２ｃで伝熱管１８ａを保持させることにより、室内熱交換器１８に取り付けられる。 As shown in FIG. 4, the rectifying plate 32 includes a base portion 32a arranged along a plane orthogonal to the radial direction of the turbofan 17, and a plate portion 32b protruding linearly from the base portion 32a toward the rotation axis 16A. It has a pair of holding portions 32c protruding from the base portion 32a in the opposite direction of the plate portion 32b, and a support portion 32d protruding from the base portion 32a in the opposite direction to the plate portion 32b. The straightening vane 32 is attached to the indoor heat exchanger 18 by holding the heat transfer tube 18a with a pair of holding portions 32c in a state where the support portion 32d is supported by the heat transfer tube 18a.

図４に示すように、整流板３２を室内熱交換器１８に取り付けた状態で、整流板３２の基部３２ａの上端は、室内熱交換器１８のフィン１８ｂの上端と一致する。このような位置関係となっているため、作業者は、整流板３２の基部３２ａの上端がフィン１８ｂの上端と一致するように位置合わせすることで、整流板３２を容易に室内熱交換器１８に取り付けることができる。 As shown in FIG. 4, with the straightening vane 32 attached to the indoor heat exchanger 18, the upper end of the base portion 32a of the straightening vane coincides with the upper end of the fins 18b of the indoor heat exchanger 18. Since of such a positional relationship, the operator can easily align the straightening vane 32 with the indoor heat exchanger 18 by aligning the upper end of the base portion 32a of the straightening vane 32 so as to coincide with the upper end of the fins 18b. Can be attached to.

図５に示すように、第１平面部１８Ａには、整流板３２Ａ（第１の整流板）と、整流板３２Ｂ（第２の整流板）とが隣接して配置された状態で取り付けられている。整流板３２Ａは、ターボファン１７の回転方向Ｒｄの上流側の第１所定位置に取り付けられている。ここで、第１所定位置とは、第１平面部１８Ａの最近接位置Ｐ１を通過する半径方向と整流板３２Ａの先端を通過する半径方向とがなす角θ１が、３度以上かつ７度以下の範囲となる位置である。第１所定位置は、更に望ましくはθ１が５度となる位置である。このようにすることで、最近接位置Ｐ１におけるターボファン１７からの吹き出し風の回転方向Ｒｄの速度成分を適切に減少させることができる。 As shown in FIG. 5, the straightening vane 32A (first straightening vane) and the straightening vane 32B (second straightening vane) are attached to the first flat surface portion 18A in a state of being arranged adjacent to each other. There is. The straightening vane 32A is attached to a first predetermined position on the upstream side of the rotation direction Rd of the turbofan 17. Here, the first predetermined position means that the angle θ1 formed by the radial direction passing through the closest position P1 of the first plane portion 18A and the radial direction passing through the tip of the straightening vane 32A is 3 degrees or more and 7 degrees or less. It is a position within the range of. The first predetermined position is more preferably a position where θ1 is 5 degrees. By doing so, the velocity component of the rotation direction Rd of the blown wind from the turbofan 17 at the closest position P1 can be appropriately reduced.

整流板３２Ｂは、ターボファン１７の回転方向Ｒｄの下流側の第２所定位置に取り付けられている。ここで、第２所定位置とは、第１平面部１８Ａの最近接位置Ｐ１を通過する半径方向と整流板３２Ｂの先端を通過する半径方向とがなす角θ２が、１５度以上かつ２０度以下の範囲となる位置である。このようにすることで、最近接位置Ｐ１よりもターボファン１７の回転方向Ｒｄの下流側で吹き出し風の回転方向Ｒｄの速度成分が再び上昇すること適切に抑制することができる。 The straightening vane 32B is attached to a second predetermined position on the downstream side of the rotation direction Rd of the turbofan 17. Here, the second predetermined position means that the angle θ2 formed by the radial direction passing through the closest position P1 of the first plane portion 18A and the radial direction passing through the tip of the straightening vane 32B is 15 degrees or more and 20 degrees or less. It is a position within the range of. By doing so, it is possible to appropriately suppress that the velocity component of the rotation direction Rd of the blown wind rises again on the downstream side of the rotation direction Rd of the turbofan 17 from the closest position P1.

図５において、距離Ｌは、整流板３２Ａ及び整流板３２Ｂが取り付けられる第１平面部１８Ａの最近接位置Ｐ１におけるターボファン１７と室内熱交換器１８との半径方向の距離である。また、距離ｌは、整流板３２Ａ及び整流板３２Ｂの回転軸１６Ａへ向けて突出する長さである。本実施形態において、距離Ｌと距離ｌとは、以下の式（１）及び式（２）の関係を満たす。
Ｌ／ｌ≧３．５ （１）
ｌ≧７ｍｍ （２）
式（１）は、整流板３２Ａによる通風抵抗の上昇を抑制するための条件である。また、式（２）は、最近接位置Ｐ１におけるターボファン１７の吹き出し風の回転方向Ｒｄの速度成分を減少させるための条件である。 In FIG. 5, the distance L is the radial distance between the turbofan 17 and the indoor heat exchanger 18 at the closest position P1 of the first flat surface portion 18A to which the straightening vane 32A and the straightening vane 32B are attached. Further, the distance l is a length that projects toward the rotating shaft 16A of the straightening vane 32A and the straightening vane 32B. In the present embodiment, the distance L and the distance l satisfy the relations of the following equations (1) and (2).
L / l ≧ 3.5 (1)
l ≧ 7mm (2)
Equation (1) is a condition for suppressing an increase in ventilation resistance due to the straightening vane 32A. Further, the equation (2) is a condition for reducing the velocity component of the rotation direction Rd of the blown wind of the turbofan 17 at the closest position P1.

なお、以上においては、第１平面部１８Ａに取り付けられる２つの整流板３２について説明したが、第２平面部１８Ｂに取り付けられる２つの整流板３２も、第１平面部１８Ａに取り付けられる２つの整流板３２と同様の配置となる。また、第３平面部１８Ｃに取り付けられる２つの整流板３２も、第１平面部１８Ａに取り付けられる２つの整流板３２と同様の配置となる。 Although the two straightening vanes 32 attached to the first flat surface portion 18A have been described above, the two straightening vanes 32 attached to the second flat surface portion 18B also have two straightening vanes attached to the first flat surface portion 18A. The arrangement is the same as that of the plate 32. Further, the two straightening vanes 32 attached to the third flat surface portion 18C have the same arrangement as the two straightening vanes 32 attached to the first flat surface portion 18A.

なお、第１平面部１８Ａ，第２平面部１８Ｂ，第３平面部１８Ｃには、それぞれ２つの整流板３２が取り付けられる一方で、第４平面部１８Ｄ，第５平面部１８Ｅには、それぞれ１つずつの整流板３２が取り付けられる。これは、第４平面部１８Ｄ，第５平面部１８Ｅの長さが第１平面部１８Ａ，第２平面部１８Ｂ，第３平面部１８Ｃに比べて短く、最近接位置Ｐ４，Ｐ５における吹き出し風の回転方向Ｒｄの速度成分が小さいからである。 Two straightening vanes 32 are attached to the first flat surface portion 18A, the second flat surface portion 18B, and the third flat surface portion 18C, respectively, while one is attached to the fourth flat surface portion 18D and the fifth flat surface portion 18E, respectively. Each straightening vane 32 is attached. This is because the lengths of the 4th flat surface portion 18D and the 5th flat surface portion 18E are shorter than those of the 1st flat surface portion 18A, the 2nd flat surface portion 18B, and the 3rd flat surface portion 18C, and the blowout wind at the closest positions P4 and P5 This is because the velocity component in the rotation direction Rd is small.

次に、本実施形態の空気調和機１の室内機３で発生する騒音の音圧レベルとその比較例について説明する。図６は、本実施形態の室内機３で発生する騒音の音圧レベルを示すグラフである。図６において、実線は本実施形態の図３に示すように室内熱交換器１８の内周側に複数の整流板３２を配置した場合の音圧レベルを示し、破線は図３に示す複数の整流板３２の全てを配置しない場合の音圧レベルを示す。図６は、１／３オクターブバンド中心周波数（Ｈｚ）と音圧レベル（ｄＢ）との関係を示すものである。 Next, the sound pressure level of the noise generated in the indoor unit 3 of the air conditioner 1 of the present embodiment and a comparative example thereof will be described. FIG. 6 is a graph showing the sound pressure level of noise generated in the indoor unit 3 of the present embodiment. In FIG. 6, the solid line shows the sound pressure level when a plurality of straightening vanes 32 are arranged on the inner peripheral side of the indoor heat exchanger 18 as shown in FIG. 3 of the present embodiment, and the broken line shows the plurality of sound pressure levels shown in FIG. The sound pressure level when not all of the straightening vane 32 is arranged is shown. FIG. 6 shows the relationship between the 1/3 octave band center frequency (Hz) and the sound pressure level (dB).

図６の実験結果に示すように、本実施形態の空気調和機１は、比較例に比べて、騒音として認識されやすい高周波数領域（２ｋＨｚ～４ｋＨｚ）の音圧レベルが低くなっている。これは、最近接位置Ｐ１，Ｐ２，Ｐ３よりもターボファン１７の回転方向Ｒｄの上流側の第１所定位置に整流板３２が取り付けられているため、吹き出し風の回転方向Ｒｄの速度成分が、最近接位置Ｐ１，Ｐ２，Ｐ３に到達する前に整流板３２で発生する乱流により減少していることが要因であると考えられる。 As shown in the experimental results of FIG. 6, the air conditioner 1 of the present embodiment has a lower sound pressure level in the high frequency region (2 kHz to 4 kHz), which is easily recognized as noise, as compared with the comparative example. This is because the straightening vane 32 is attached to the first predetermined position on the upstream side of the rotation direction Rd of the turbofan 17 from the closest positions P1, P2, P3, so that the velocity component of the rotation direction Rd of the blown wind is increased. It is considered that the factor is that it is reduced due to the turbulent flow generated in the straightening vane 32 before reaching the closest positions P1, P2 and P3.

また、ターボファン１７との最近接位置Ｐ１，Ｐ２，Ｐ３よりもターボファン１７の回転方向Ｒｄの下流側の第２所定位置に整流板３２が取り付けられているため、最近接位置Ｐ１，Ｐ２，Ｐ３よりもターボファン１７の回転方向Ｒｄの下流側で吹き出し風の回転方向Ｒｄの速度成分が再び上昇することが抑制されていることが要因であると考えられる。 Further, since the rectifying plate 32 is attached to the second predetermined position on the downstream side of the rotation direction Rd of the turbofan 17 from the closest positions P1, P2 and P3 with the turbofan 17, the closest positions P1, P2 and P2. It is considered that the reason is that the velocity component of the rotation direction Rd of the blown wind is suppressed from rising again on the downstream side of the rotation direction Rd of the turbofan 17 than P3.

以上説明した本実施形態の空気調和機１が奏する作用及び効果について説明する。
本実施形態の空気調和機１によれば、室内熱交換器１８の第１平面部１８Ａ，第２平面部１８Ｂ、第３平面部１８Ｃには、ターボファン１７のブレード３０との最近接位置Ｐ１，Ｐ２，Ｐ３よりもターボファン１７の回転方向Ｒｄの上流側の第１所定位置に整流板３２が取り付けられる。そのため、吹き出し風の回転方向Ｒｄの速度成分が、最近接位置Ｐ１，Ｐ２，Ｐ３に到達する前に整流板３２で発生する乱流により減少し、最近接位置Ｐ１，Ｐ２，Ｐ３で吹き出し風がフィン１８ｂに衝突して発生する送風騒音が減少する。 The operation and effect of the air conditioner 1 of the present embodiment described above will be described.
According to the air conditioner 1 of the present embodiment, the first flat surface portion 18A, the second flat surface portion 18B, and the third flat surface portion 18C of the indoor heat exchanger 18 are in close contact with the blade 30 of the turbofan 17. , P2, P3, the rectifying plate 32 is attached to the first predetermined position on the upstream side of the rotation direction Rd of the turbofan 17. Therefore, the velocity component of the rotation direction Rd of the blown wind is reduced by the turbulent flow generated in the rectifying plate 32 before reaching the closest positions P1, P2, P3, and the blown wind is generated at the closest positions P1, P2, P3. The blowing noise generated by colliding with the fin 18b is reduced.

ここで、第１所定位置は、第１平面部１８Ａ（第２平面部１８Ｂ，第３平面部１８Ｃ）の最近接位置Ｐ１（Ｐ２，Ｐ３）を通過する半径方向と整流板３２Ａの先端を通過する半径方向とがなす角θ１が３度以上かつ７度以下の範囲となる位置である。より好ましくは、５度となる位置である。 Here, the first predetermined position passes through the radial direction passing through the closest position P1 (P2, P3) of the first flat surface portion 18A (second flat surface portion 18B, third flat surface portion 18C) and the tip of the straightening vane 32A. It is a position where the angle θ1 formed by the radial direction is within a range of 3 degrees or more and 7 degrees or less. More preferably, it is a position of 5 degrees.

また、本実施形態の空気調和機１によれば、室内熱交換器１８の第１平面部１８Ａ，第２平面部１８Ｂ、第３平面部１８Ｃには、ターボファン１７のブレード３０との最近接位置Ｐ１，Ｐ２，Ｐ３よりもターボファン１７の回転方向Ｒｄの下流側の第２所定位置に整流板３２が取り付けられる。そのため、最近接位置Ｐ１，Ｐ２，Ｐ３よりもターボファン１７の回転方向Ｒｄの下流側で吹き出し風の回転方向Ｒｄの速度成分が再び上昇することが抑制され、吹き出し風がフィン１８ｂに衝突して発生する送風騒音が減少する。 Further, according to the air conditioner 1 of the present embodiment, the first flat surface portion 18A, the second flat surface portion 18B, and the third flat surface portion 18C of the indoor heat exchanger 18 are in close contact with the blade 30 of the turbofan 17. The rectifying plate 32 is attached to a second predetermined position on the downstream side of the rotation direction Rd of the turbofan 17 from the positions P1, P2, and P3. Therefore, it is suppressed that the velocity component of the rotation direction Rd of the blown wind rises again on the downstream side of the rotation direction Rd of the turbofan 17 from the closest positions P1, P2, P3, and the blown wind collides with the fins 18b. The generated ventilation noise is reduced.

ここで、第２所定位置は、第１平面部１８Ａ（第２平面部１８Ｂ，第３平面部１８Ｃ）の最近接位置Ｐ１（Ｐ２，Ｐ３）を通過する半径方向と整流板３２Ｂの先端を通過する半径方向とがなす角θ２が１５度以上かつ２０度以下の範囲となる位置である。 Here, the second predetermined position passes through the radial direction passing through the closest position P1 (P2, P3) of the first flat surface portion 18A (the second flat surface portion 18B, the third flat surface portion 18C) and the tip of the straightening vane 32B. It is a position where the angle θ2 formed by the radial direction is within a range of 15 degrees or more and 20 degrees or less.

さらに、本実施形態の空気調和機１によれば、整流板３２がターボファン１７の回転軸１６Ａと平行な軸線Ｘ１，Ｘ２に沿って延びて回転軸１６Ａに向けて直線状に突出する形状となっているため、ターボファン１７の回転方向Ｒｄと反対方向に傾斜して内側に膨出した曲面状に形成される場合に比べて通風抵抗が減少する。また、２つの整流板３２が最近接位置Ｐ１，Ｐ２，Ｐ３を挟んでターボファン１７の回転方向Ｒｄの上流側と下流側に隣接して配置されるため、最近接位置Ｐ１，Ｐ２，Ｐ３を含めた３枚の整流板を配置する場合に比べて通風抵抗が減少する。
このように、本実施形態の空気調和機１によれば、通風抵抗を大きく上昇させることなく吹き出し風がフィン１８ｂに衝突して発生する送風騒音を減少させることができる。 Further, according to the air conditioner 1 of the present embodiment, the straightening vane 32 extends along the axes X1 and X2 parallel to the rotation shaft 16A of the turbofan 17 and protrudes linearly toward the rotation shaft 16A. Therefore, the ventilation resistance is reduced as compared with the case where the turbofan 17 is formed in a curved shape that is inclined in the direction opposite to the rotation direction Rd and bulges inward. Further, since the two straightening vanes 32 are arranged adjacent to the upstream side and the downstream side of the rotation direction Rd of the turbofan 17 with the closest positions P1, P2 and P3 sandwiched between them, the closest positions P1, P2 and P3 are arranged. The ventilation resistance is reduced as compared with the case where the three straightening vanes including the one are arranged.
As described above, according to the air conditioner 1 of the present embodiment, it is possible to reduce the blowing noise generated by the blown wind colliding with the fins 18b without significantly increasing the ventilation resistance.

本実施形態の空気調和機１において、整流板３２Ａ及び整流板３２Ｂが取り付けられる第１平面部１８Ａ（第２平面部１８Ｂ、第３平面部１８Ｃ）の最近接位置Ｐ１（Ｐ２，Ｐ３）におけるターボファン１７と室内熱交換器１８との半径方向の距離をＬとし、整流板３２Ａの回転軸１６Ａへ向けて突出する長さをｌとした場合、Ｌ／ｌ≧３．５かつｌ≧７ｍｍを満たす。 In the air conditioner 1 of the present embodiment, the turbo at the closest position P1 (P2, P3) of the first flat surface portion 18A (second flat surface portion 18B, third flat surface portion 18C) to which the rectifying plate 32A and the rectifying plate 32B are attached. When the distance between the fan 17 and the indoor heat exchanger 18 in the radial direction is L and the length of the rectifying plate 32A protruding toward the rotating shaft 16A is l, L / l ≧ 3.5 and l ≧ 7 mm. Fulfill.

ターボファン１７と室内熱交換器１８との半径方向の距離Ｌを整流板３２Ａ及び整流板３２Ｂの回転軸１６Ａへ向けて突出する長さｌの３．５倍以上とすることで、整流板３２Ａ及び整流板３２Ｂによる通風抵抗の上昇を十分に抑制することができる。また、ｌを７ｍｍ以上とすることで、整流板３２Ａで適切に乱流を発生させ、最近接位置Ｐ１（Ｐ２，Ｐ３）における吹き出し風の回転方向Ｒｄの速度成分を減少させることができる。 By setting the radial distance L between the turbo fan 17 and the indoor heat exchanger 18 to be 3.5 times or more the length l of the straightening vane 32A and the straightening vane 32B protruding toward the rotating shaft 16A, the straightening vane 32A And the increase in ventilation resistance due to the straightening vane 32B can be sufficiently suppressed. Further, by setting l to 7 mm or more, turbulence can be appropriately generated in the straightening vane 32A, and the velocity component of the rotation direction Rd of the blown wind at the closest position P1 (P2, P3) can be reduced.

１ 空気調和機
２ 室外機
３ 室内機
４ 冷媒配管
５ 電気配線
６ 冷媒圧縮機
７ 室外熱交換器
８ 室外ファン
９ コントロールボックス
１０ キャビネット
１１ 天井パネル
１２ 空気吸込口
１３ ベルマウス
１４ ドレンパン
１５ 風路
１６ ファンモータ
１６Ａ 回転軸
１７ ターボファン
１８ 室内熱交換器
１８ａ 伝熱管
１８ｂ フィン
１８Ａ 第１平面部
１８Ｂ 第２平面部
１８Ｃ 第３平面部
１８Ｄ 第４平面部
１８Ｅ 第５平面部
１８Ｆ 第１曲面部
１８Ｇ 第２曲面部
１８Ｈ 第３曲面部
１８Ｉ 第４曲面部
１９ 空気流通路
２０ 空気吹出口
２１ 開口
２２ エアフィルタ
２３ 吸込グリル
２４ ワイヤ
２５ 風向調整ルーバ
２６ ハブ
２７ 主板
２８ 流体流路
２９ シュラウド
３０ ブレード
３１ 再循環路
３２，３２Ａ，３２Ｂ 整流板
３２ａ 基部
３２ｂ 板部 1 Air conditioner 2 Outdoor unit 3 Indoor unit 4 Refrigerant piping 5 Electrical wiring 6 Refrigerant compressor 7 Outdoor heat exchanger 8 Outdoor fan 9 Control box 10 Cabinet 11 Ceiling panel 12 Air suction port 13 Bellmouth 14 Drain pan 15 Air passage 16 Fan Motor 16A Rotating shaft 17 Turbo fan 18 Indoor heat exchanger 18a Heat transfer tube 18b Fins 18A 1st flat surface part 18B 2nd flat surface part 18C 3rd flat surface part 18D 4th flat surface part 18E 5th flat surface part 18F 1st curved surface part 18G 2nd Curved surface 18H 3rd curved surface 18I 4th curved surface 19 Air flow passage 20 Air outlet 21 Opening 22 Air filter 23 Suction grill 24 Wire 25 Wind direction adjustment louver 26 Hub 27 Main plate 28 Fluid flow path 29 Shroud 30 Blade 31 Recirculation path 32, 32A, 32B Refrigerant plate 32a Base 32b Plate

Claims (3)

回転軸の軸線方向に沿って流入する空気を前記軸線方向と交差する半径方向に流出させるファンと、
前記ファンの外周を取り囲むように配置されるとともに伝熱管と該伝熱管に取り付けられる複数のフィンとを有する熱交換器と、
前記熱交換器の内周側に取り付けられるとともに前記回転軸と平行な軸線に沿って延びて前記回転軸に向けて直線状に突出する複数の整流板と、を備え、
前記熱交換器は、
前記ファンとの最近接位置において前記半径方向と直交する平面に沿って配置される複数の平面部と、
前記複数の平面部を連結する複数の曲面部と、を有し、
前記複数の平面部の少なくともいずれか一つには、前記最近接位置よりも前記ファンの回転方向の上流側の第１所定位置に第１の前記整流板が取り付けられ、前記最近接位置よりも前記ファンの回転方向の下流側の第２所定位置に第２の前記整流板が取り付けられ、
前記第１の整流板と前記第２の整流板とが隣接して配置され、
前記第１所定位置は、前記平面部の前記最近接位置を通過する前記半径方向と前記第１の整流板の先端を通過する前記半径方向とがなす角が３度以上かつ７度以下の範囲となる位置であり、
前記第２所定位置は、前記平面部の前記最近接位置を通過する前記半径方向と前記第２の整流板の先端を通過する前記半径方向とがなす角が１５度以上かつ２０度以下の範囲となる位置である空気調和機。 A fan that causes the air that flows in along the axis direction of the rotation axis to flow out in the radial direction that intersects the axis direction, and
A heat exchanger arranged so as to surround the outer periphery of the fan and having a heat transfer tube and a plurality of fins attached to the heat transfer tube.
A plurality of straightening vanes, which are attached to the inner peripheral side of the heat exchanger and extend along an axis parallel to the axis of rotation and project linearly toward the axis of rotation, are provided.
The heat exchanger is
A plurality of plane portions arranged along a plane orthogonal to the radial direction at the position closest to the fan, and
It has a plurality of curved surface portions that connect the plurality of flat surface portions, and has.
The first straightening vane is attached to at least one of the plurality of flat surfaces at a first predetermined position on the upstream side in the rotation direction of the fan from the closest position, and is more than the closest position. The second straightening vane is attached to a second predetermined position on the downstream side in the rotation direction of the fan.
The first straightening vane and the second straightening vane are arranged adjacent to each other .
The first predetermined position is in a range in which the angle formed by the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the first straightening vane is 3 degrees or more and 7 degrees or less. It is a position that becomes
The second predetermined position is in a range in which the angle formed by the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the second rectifying plate is 15 degrees or more and 20 degrees or less. The air conditioner that is the position to be . 前記第１所定位置は、前記平面部の前記最近接位置を通過する前記半径方向と前記第１の整流板の先端を通過する前記半径方向とがなす角が５度となる位置である請求項１に記載の空気調和機。 The first predetermined position is a position where the angle formed by the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the first rectifying plate is 5 degrees. The air conditioner according to 1 . 前記第１の整流板及び前記第２の整流板が取り付けられる前記平面部の前記最近接位置における前記ファンと前記熱交換器との前記半径方向の距離をＬとし、前記第１の整流板の前記回転軸へ向けて突出する長さをｌとした場合、Ｌ／ｌ≧３．５かつｌ≧７ｍｍを満たす請求項１または請求項２に記載の空気調和機。 Let L be the radial distance between the fan and the heat exchanger at the closest position of the flat surface to which the first straightening vane and the second straightening vane are attached, and let L be the distance of the first straightening vane. The air conditioner according to claim 1 or 2 , wherein the length protruding toward the rotation axis is l, and L / l ≧ 3.5 and l ≧ 7 mm are satisfied.
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