WO2011077484A1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
WO2011077484A1
WO2011077484A1 PCT/JP2009/007170 JP2009007170W WO2011077484A1 WO 2011077484 A1 WO2011077484 A1 WO 2011077484A1 JP 2009007170 W JP2009007170 W JP 2009007170W WO 2011077484 A1 WO2011077484 A1 WO 2011077484A1
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Prior art keywords
heat exchanger
air conditioner
air
cross flow
flow fan
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PCT/JP2009/007170
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French (fr)
Japanese (ja)
Inventor
篠崎健
山田彰二
迫田健一
松本崇
若本慎一
加賀邦彦
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2009/007170 priority Critical patent/WO2011077484A1/en
Priority to JP2011547076A priority patent/JP5506821B2/en
Publication of WO2011077484A1 publication Critical patent/WO2011077484A1/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
    • F24F1/0025—Cross-flow or tangential 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
    • F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air

Definitions

  • the present invention relates to an air conditioner equipped with a cross flow fan used as a blowing means.
  • Some conventional air conditioners are provided with a flow rate control member such as a mesh member between the heat exchanger and the crossflow fan in order to appropriately adjust the airflow flowing into the heat exchanger.
  • a flow rate control member such as a mesh member between the heat exchanger and the crossflow fan in order to appropriately adjust the airflow flowing into the heat exchanger.
  • An air inlet is formed in the front portion of the casing of the air conditioner, and an air outlet is formed in the lower portion of the front.
  • a filter, a heat exchanger, a semi-cylindrical mesh member, and a cross-flow fan are sequentially arranged from the upstream side to the downstream side of the air flow path from the air inlet port to the air outlet port. ing.
  • the heat exchanger is composed of a refrigerant pipe and a plurality of fins arranged in parallel across the refrigerant pipe, and is located behind the air suction port.
  • the semi-cylindrical mesh member has an arc shape equidistant from the central axis of the cross flow fan over the entire air suction port formed by the casing side rear guide and the drain pan side tongue of the cross flow fan. Is provided.
  • the cross flow fan is disposed at a position downstream of the heat exchanger and the mesh member corresponding to the installation shape of the air flow passage.
  • a pressure loss body such as a mesh member is provided between the heat exchanger and the cross flow fan in order to slow down the wind speed in the vicinity of the tongue.
  • a pressure loss body flow velocity control member
  • problems such as an increase in cost and an increase in power consumption of the fan motor due to an increase in input of the fan motor.
  • the present invention solves the above-mentioned conventional problems, and flows into the heat exchanger at the lower front side without providing a separate pressure loss body on the secondary side of the heat exchanger (between the heat exchanger and the cross flow fan).
  • An object of the present invention is to provide an air conditioner that effectively reduces the wind speed and has sufficient heat exchange capability without impairing the cooling and heating capability.
  • an air conditioner includes a main body, an air passage provided so that air passes through the main body, a heat exchanger and a cloth disposed in the air passage.
  • the heat exchanger has a front lower heat exchanger located at a lower front side with respect to the cross flow fan, The tongue is extended along the rotational direction of the cross flow fan from the tip of a drain pan located below the front lower heat exchanger so that the wind speed flowing into the front lower heat exchanger is reduced. It is the structure.
  • the tongue central angle which is an angle formed by a line connecting the center of the cross flow fan and the tip of the tongue, and a line connecting the center of the cross flow fan and the tip of the drain pan, is ⁇
  • the cross flow fan When the angle between the line extending horizontally from the center of the front lower heat exchanger and the line connecting the center of the crossflow fan and the tip of the drain pan is ⁇ , The ⁇ is 0.5 ⁇ ⁇ ⁇ ⁇ 1.05 ⁇ , preferably 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ . It is the range of these.
  • the tongue portion is configured to extend along the rotation direction of the cross flow fan, so that a pressure loss member is not separately provided between the heat exchanger and the cross flow fan as in the prior art.
  • the wind speed flowing into the heat exchanger can be effectively reduced, and sufficient heat exchange capability can be ensured.
  • tongue part center angle (theta) is 95 degree
  • FIG. 1 is a cross-sectional side view showing an air conditioner according to Embodiment 1 of the present invention.
  • An air conditioner 10 according to Embodiment 1 includes a main body 1 made of a box-shaped casing, a heat exchanger 2 and a cross flow fan 3 disposed in an air passage 4 formed in the main body 1. ing.
  • the heat exchanger 2 indicated by 2 as a whole is constituted by a three-part cross-fin tube heat exchanger in this example. In other words, the heat exchanger 2 is vertically sectioned as shown in the drawing and viewed from the side, the front lower heat exchanger 2c located on the drain pan 14 and located on the front side of the cross flow fan 3 is shown.
  • a front heat exchanger 2b which is disposed on the upper side of the lower front heat exchanger 2c and whose upper end is inclined rearward, and a rear heat which is connected on the upper side of the front heat exchanger 2b and inclined lower rearward.
  • the heat exchangers 2a to 2c of these three parts are connected in an inverted V shape so that the refrigerant flows continuously. Further, the heat exchangers 2a to 2c of each part are configured by repeatedly reciprocating the refrigerant pipe 5 through a large number of fins arranged in parallel in the lateral direction (direction perpendicular to the drawing sheet).
  • a top air inlet 6 and a front air inlet 7 are formed on the upper surface and lower front of the main body 1 (below the front panel 11 on the front), respectively, and an air blower opening toward the front is formed on the lower portion of the main body 1.
  • An outlet 8 is formed.
  • the upper surface air inlet 6, the front air inlet 7 and the air outlet 8 form an air passage 4 through which air passes through the main body 1.
  • An air cleaning filter 9, the heat exchanger 2, and the cross flow fan 3 are disposed in the air path 4 in order from the upstream side.
  • a tongue 12 and a rear guide 13 are provided around the cross flow fan 3 in order to form an air suction port of the cross flow fan 3.
  • the tongue 12 is extended along the rotation direction of the cross flow fan 3 (arrow direction shown in the drawing) so that the wind speed flowing into the front lower heat exchanger 2c decreases. Moreover, the tongue part 12 is arrange
  • the air conditioner 10 when the cross flow fan 3 is rotationally driven, air is sucked from the upper surface air inlet 6 and the front air inlet 7, and the sucked air is heat-exchanged with the refrigerant in the heat exchanger 2.
  • the air that has become cold air or warm air is blown into the room from the air outlet 8.
  • the air outlet 8 is equipped with a louver (not shown) for changing the direction of the blown air.
  • FIG. 2 is a cross-sectional side view showing the main part of the present invention, for explaining the positional relationship among the crossflow fan 3, the tongue 12 and the front lower heat exchanger 2c of the air conditioner according to Embodiment 1. It is a schematic diagram.
  • the center of the crossflow fan 3 is O
  • a line extending horizontally from the center O toward the lower front heat exchanger 2c is 30, and the center O of the crossflow fan 3 and the tip 12a of the tongue 12 are connected.
  • the tongue 31 is a line
  • 32 is a line connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14
  • the angle between the line 30 and the line 32 is ⁇
  • the angle between the line 31 and the line 32 (hereinafter referred to as the tongue)
  • the tongue central angle ⁇ is 0.5 ⁇ ⁇ ⁇ ⁇ 1.05 ⁇ , preferably 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ .
  • the height position of 12a is set.
  • the position of the center O of the crossflow fan 3 is disposed at a substantially intermediate position of the height dimension L (the height below the bent portion) of the front lower heat exchanger 2c.
  • ⁇ is set in the range of 60 to 70 degrees.
  • the flow that flows into the impeller crosses the impeller in the diametrical direction, that is, the flow first flows inward in the radial direction of the impeller and then flows outward. It has the feature of passing through twice.
  • the crossflow fan 3 is installed in the main body 1, the air that flows in from the front side of the crossflow fan 3 is sucked in most. Therefore, the wind speed passing through the front lower heat exchanger 2c tends to be faster than the wind speed passing through the other heat exchangers 2b and 2a. For this reason, there exists a problem that heat exchange performance falls easily.
  • FIG. 3 is a diagram showing the air flow when ⁇ is 25 degrees.
  • FIG. 4 is a view when ⁇ is 95 degrees
  • FIG. 5 is a view showing an air flow when ⁇ is 60 degrees.
  • the tongue center angle ⁇ in the above range, that is, 0.5 ⁇ ⁇ ⁇ ⁇ 1.05 ⁇ , preferably 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ , the front surface as shown in FIG. Since the amount of air flowing into the cross flow fan 3 from the lower heat exchanger 2c is reduced and the wind speed is effectively reduced, a sufficient heat exchange capability can be ensured. Further, since the vortex 40 is generated at a position closer to the tongue portion 12 so as to widen the through-flow width, the blowing wind speed is reduced and the noise is also reduced.
  • FIG. 6 (a) shows a ratio of heat exchange capacity to a conventional air conditioner (conventional machine) when the tongue center angle ⁇ is changed.
  • the solid line in the figure indicates the heat exchange capacity of the conventional machine as “1”, the vertical axis in the figure represents the ratio of the heat exchange capacity to the conventional machine, and the horizontal axis in the figure represents the central angle of the tongue. It shows the change of ⁇ . Further, the central angle ⁇ of the tongue in the conventional machine is 20 degrees to 25 degrees.
  • the table in FIG. 6 (b) shows the coordinate positions of the points A to J in FIG. 6 (a).
  • the points A, C to E, G and J are actual experimental values, and the points B, F, H, and I are the coordinate positions of each point on the approximate curve 50 that passes through these experimental values.
  • the heat exchange capacity is higher than that of the conventional machine within the range of 0.45 ⁇ ⁇ ⁇ 1.07 ⁇ , and in particular, the heat exchange capacity ratio is within the range of 0.5 ⁇ ⁇ ⁇ ⁇ 1.05 ⁇ . It can be seen that the heat exchange capacity is 1.02 or more, and more preferably in the range of 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ , the heat exchange capacity is improved by 1.1 times or more than the conventional machine.
  • the tongue 12 has a tongue center angle ⁇ satisfying the range of 0.45 ⁇ ⁇ ⁇ 1.07 ⁇ , particularly 0.5 ⁇ ⁇ ⁇ ⁇ 1.05 ⁇ .
  • the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced, and sufficient heat exchange capability can be ensured. .
  • noise can be reduced.
  • the cost can be reduced.
  • FIG. FIG. 7 is a cross-sectional view showing an air conditioner according to Embodiment 2 of the present invention.
  • the refrigerant pipe 5 of the lower front heat exchanger 2c is configured with a smaller number than the other heat exchangers 2a and 2b in the depth direction of the air conditioner. That is, for example, the point that the number of rows of the refrigerant pipes 5 of the front lower heat exchanger 2c is reduced as compared with the other heat exchangers 2a and 2b is different from the first embodiment in that the air conditioner main body is made thinner.
  • Other configurations are the same as those of the first embodiment.
  • the wind speed distribution of the heat exchanger 2 has a low air resistance due to its configuration.
  • the wind speed is extremely unbalanced.
  • the position of the tip 12a of the tongue 12 is such that the line 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, and the center O of the crossflow fan 3 and the tongue.
  • 12 is a line in which the tongue center angle ⁇ , which is an angle formed with the line 31 connecting the tip 12a of the twelve, extends horizontally from the center O of the crossflow fan 3 toward the front lower heat exchanger 2c, The angle is 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ , which is 70% or more of the angle ⁇ formed by the line 32 connecting the center O of the fan 3 and the tip 14 a of the drain pan 14.
  • the position of the center O of the cross flow fan 3 is arranged at a substantially middle position of the height dimension L of the front lower heat exchanger 2c. ⁇ is set in the range of 60 to 70 degrees.
  • the tongue center angle ⁇ is set to be less than 0.7 ⁇ , the pressure loss on the front side of the cross flow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be secured, and when it is set to 1.05 ⁇ or more, as shown by the thick solid line in FIG. Experimental results have been obtained that the heat exchange capacity is also reduced due to the decrease in air flow and the air blowing performance. Therefore, when the wind speed of the heat exchanger 2 has an unbalanced distribution, by setting the tongue central angle ⁇ to the range 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ , the front lower heat exchanger as shown in FIG. Since the amount of air flowing in from 2c is reduced and the wind speed is effectively reduced, sufficient heat exchange capability can be ensured. Also, noise can be reduced.
  • the tongue center angle ⁇ is 0.7 ⁇ ⁇ ⁇ ⁇ .
  • FIG. 8 is a cross-sectional view showing an air conditioner according to Embodiment 3 of the present invention.
  • the air conditioner 10 ⁇ / b> B according to the third embodiment is provided with a suction port 6 only on the upper surface of the main body 1 made of a box-shaped casing, and in an inverted V shape upstream of the cross flow fan 3.
  • positioned smaller was different from Embodiment 1 and Embodiment 2.
  • Other configurations are the same as those of the second embodiment.
  • the air suction port 7 on the front surface side is eliminated and only the air suction port 6 on the upper surface side of the main body 1 is used, and the heat exchanger 2 is the same as that of the front heat exchanger 2b.
  • the air conditioner main body is made thin by making the angle of the inverted V-shaped portion with the rear heat exchanger 2a that is connected to the upper side and inclined rearward and lower than the configuration of the first and second embodiments. It has become. Therefore, the wind speed distribution of the heat exchanger 2 becomes an unbalanced distribution in which the wind speed is extremely high in the front lower heat exchanger 2c with a small pressure loss due to the thinning of the air conditioner body.
  • the position of the tip 12a of the tongue 12 is such that the line 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, and the center O of the crossflow fan 3 and the tongue.
  • 12 is a line in which the tongue center angle ⁇ , which is an angle formed with the line 31 connecting the tip 12a of the twelve, extends horizontally from the center O of the crossflow fan 3 toward the front lower heat exchanger 2c, The angle is 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ , which is 70% or more of the angle ⁇ formed by the line 32 connecting the center O of the fan 3 and the tip 14 a of the drain pan 14.
  • the position of the center O of the cross flow fan 3 is arranged at a substantially middle position of the height dimension L of the front lower heat exchanger 2c. ⁇ is set in the range of 60 to 70 degrees.
  • the tongue center angle ⁇ is set to be less than 0.7 ⁇ , the pressure loss on the front side of the cross flow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be ensured, and when it is set to 1.05 ⁇ or more, as shown by the thick solid line in FIG. Experimental results have been obtained that the heat exchange capacity is also reduced due to the decrease in air flow and the air blowing performance. Therefore, when the wind speed of the heat exchanger 2 has an unbalanced distribution, by setting the tongue central angle ⁇ to the range 0.7 ⁇ ⁇ ⁇ ⁇ 0.98 ⁇ , the front lower heat exchanger as shown in FIG. Since the amount of air flowing in from 2c is reduced and the wind speed is effectively reduced, sufficient heat exchange capability can be ensured.
  • the tongue center angle ⁇ is set to 0.7 ⁇ ⁇ ⁇ .
  • the reverse V-shaped heat exchanger 2 has been described.
  • the heat exchanger according to the present invention is not limited to this, and for example, the heat exchanger 2a on the back side.
  • the heat exchangers 2b and 2c on the front side may be used.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

Disclosed is an air conditioner provided with: a main body (1); an air passage (4) provided within the main body; a heat exchanger (2) and a cross flow fan (3), which are disposed in the air passage (4); and a tongue portion (12) and a rear guide (13), which are provided around the cross flow fan (3). The heat exchanger (2) has a front lower heat exchanger (2c) positioned at the front lower portion with respect to the cross flow fan (3), and the tongue portion (12) extends in the rotational direction of the cross flow fan (3) from the tip (14a) of a drain pan (14) positioned below the front lower heat exchanger (2c) so that the speed of the air flowing into the front lower heat exchanger (2c) is reduced. If the tongue portion center angle between a line joining the center of the fan to the tip of the tongue portion and a line joining the center of the fan to the tip of the drain pan is designated as θ, and if the angle between a line horizontally extending from the center of the fan toward the front lower heat exchanger and a line joining the center of the fan to the tip of the drain pan is designated as α, θ satisfies 0.45α<θ<1.07α, preferably, 0.5α≤θ<1.05α, and more preferably, 0.7α≤θ≤0.98α.

Description

空気調和機Air conditioner
　本発明は、送風手段として用いられるクロスフローファンを備えた空気調和機に関するものである。 The present invention relates to an air conditioner equipped with a cross flow fan used as a blowing means.
　従来の空気調和機においては、熱交換器に流入する風量を適正に調節するために、熱交換器とクロスフローファンとの間に、例えばメッシュ部材のような流速制御部材を設けたものがある（例えば、特許文献１参照）。
　ここで、前記クロスフローファンを備えた従来の空気調和機の構造について記述する。
　空気調和機のケーシングの前面部分には空気吸込口が、また前面下方部分には空気吹出口が各々形成されている。そして、ケーシング内には、空気吸込口から空気吹出口に至る空気流通路の上流側から下流側にかけて、フィルター、熱交換器、半筒体状のメッシュ部材、クロスフローファンがそれぞれ順番に配置されている。
　そして、この熱交換器は、冷媒配管と該冷媒配管にクロスして多数枚並設されたフィンからなり、前記空気吸込口の背後に位置して設置されている。また半筒体状のメッシュ部材は、クロスフローファンのケーシング側リアガイドとドレンパン側舌部とにより形成される空気吸込口の全体に亘りクロスフローファンの中心軸から等距離の円弧状になるように設けられている。さらに、クロスフローファンは、空気流通路の設置形状に対応して、上記熱交換器およびメッシュ部材の背後下流に位置して配設されている。
　そして、冷暖房時において前記クロスフローファンが駆動されると、室内の空気は空気吸込口から熱交換器に供給されて熱交換（加熱又は冷却）される。その後、熱交換された空気は、クロスフローファンを介して空気吹出口より室内に適宜所定の角度で吹き出される。 Some conventional air conditioners are provided with a flow rate control member such as a mesh member between the heat exchanger and the crossflow fan in order to appropriately adjust the airflow flowing into the heat exchanger. (For example, refer to Patent Document 1).
Here, the structure of a conventional air conditioner including the cross flow fan will be described.
An air inlet is formed in the front portion of the casing of the air conditioner, and an air outlet is formed in the lower portion of the front. In the casing, a filter, a heat exchanger, a semi-cylindrical mesh member, and a cross-flow fan are sequentially arranged from the upstream side to the downstream side of the air flow path from the air inlet port to the air outlet port. ing.
The heat exchanger is composed of a refrigerant pipe and a plurality of fins arranged in parallel across the refrigerant pipe, and is located behind the air suction port. The semi-cylindrical mesh member has an arc shape equidistant from the central axis of the cross flow fan over the entire air suction port formed by the casing side rear guide and the drain pan side tongue of the cross flow fan. Is provided. Further, the cross flow fan is disposed at a position downstream of the heat exchanger and the mesh member corresponding to the installation shape of the air flow passage.
When the cross-flow fan is driven during cooling and heating, indoor air is supplied from the air suction port to the heat exchanger and heat exchange (heating or cooling) is performed. Thereafter, the heat-exchanged air is blown out from the air outlet through the cross flow fan into the room at a predetermined angle as appropriate.
特開平６－３１７３３４号公報（第２－３頁、図１）JP-A-6-317334 (page 2-3, FIG. 1)
　しかしながら、前記従来の空気調和機の構成では、舌部近傍における風速を遅くするために、熱交換器とクロスフローファンとの間にメッシュ部材のごとき圧損体（流速制御部材）を設けているため、コストアップとなり、また、ファンモーターの入力が大きくなってファンモーターの消費電力が大きくなる、等の課題を有している。 However, in the configuration of the conventional air conditioner, a pressure loss body (flow velocity control member) such as a mesh member is provided between the heat exchanger and the cross flow fan in order to slow down the wind speed in the vicinity of the tongue. However, there are problems such as an increase in cost and an increase in power consumption of the fan motor due to an increase in input of the fan motor.
　本発明は、前記従来の課題を解決するもので、熱交換器の2次側（熱交換器とクロスフローファンの間）に別途圧損体を設けることなく、前面下部の熱交換器に流入する風速を効果的に低下させ、冷暖房能力を損なわず十分な熱交換能力を有する空気調和機を提供することを目的とする。 The present invention solves the above-mentioned conventional problems, and flows into the heat exchanger at the lower front side without providing a separate pressure loss body on the secondary side of the heat exchanger (between the heat exchanger and the cross flow fan). An object of the present invention is to provide an air conditioner that effectively reduces the wind speed and has sufficient heat exchange capability without impairing the cooling and heating capability.
　前記従来の課題を解決するために、本発明に係る空気調和機は、本体と、本体内を空気が通過するように設けられた風路と、風路に配設された熱交換器およびクロスフローファンと、クロスフローファンの周囲に設けられた舌部とリアガイドとを備えた空気調和機において、
　前記熱交換器は、前記クロスフローファンに対して前方下部に位置する前面下部熱交換器を有し、
　前記前面下部熱交換器に流入する風速が低下するように、前記舌部が、前記前面下部熱交換器の下方に位置するドレンパンの先端から、前記クロスフローファンの回転方向に沿って延長された構成となっていることを特徴とする。 In order to solve the above-described conventional problems, an air conditioner according to the present invention includes a main body, an air passage provided so that air passes through the main body, a heat exchanger and a cloth disposed in the air passage. In an air conditioner equipped with a flow fan, a tongue provided around the cross flow fan, and a rear guide,
The heat exchanger has a front lower heat exchanger located at a lower front side with respect to the cross flow fan,
The tongue is extended along the rotational direction of the cross flow fan from the tip of a drain pan located below the front lower heat exchanger so that the wind speed flowing into the front lower heat exchanger is reduced. It is the structure.
　また、前記クロスフローファンの中心が前記前面下部熱交換器の高さ寸法の略中間位置に配置された空気調和機において、
　前記クロスフローファンの中心と前記舌部の先端とを結ぶ線と、前記クロスフローファンの中心と前記ドレンパンの先端とを結ぶ線とのなす角度である舌部中心角をθ、前記クロスフローファンの中心から前記前面下部熱交換器に向かって水平に延ばした線と、前記クロスフローファンの中心と前記ドレンパンの先端とを結ぶ線とのなす角度をαとするとき、
　前記θは、０．５α≦θ＜１．０５α、好ましくは、０．７α≦θ≦０．９８α
の範囲であることを特徴とする。 Moreover, in the air conditioner in which the center of the cross flow fan is disposed at a substantially middle position of the height dimension of the front lower heat exchanger,
The tongue central angle, which is an angle formed by a line connecting the center of the cross flow fan and the tip of the tongue, and a line connecting the center of the cross flow fan and the tip of the drain pan, is θ, and the cross flow fan When the angle between the line extending horizontally from the center of the front lower heat exchanger and the line connecting the center of the crossflow fan and the tip of the drain pan is α,
The θ is 0.5α ≦ θ <1.05α, preferably 0.7α ≦ θ ≦ 0.98α.
It is the range of these.
　本発明によれば、舌部をクロスフローファンの回転方向に沿って延長する構成とすることによって、従来のように熱交換器とクロスフローファンの間に圧損体を別途設けることなく前面下部の熱交換器に流入する風速を効果的に低下させることができ、十分な熱交換能力を確保することができる。 According to the present invention, the tongue portion is configured to extend along the rotation direction of the cross flow fan, so that a pressure loss member is not separately provided between the heat exchanger and the cross flow fan as in the prior art. The wind speed flowing into the heat exchanger can be effectively reduced, and sufficient heat exchange capability can be ensured.
本発明の実施の形態１に係る空気調和機の構成を示す断面側面図である。It is a section side view showing the composition of the air harmony machine concerning Embodiment 1 of the present invention. 本発明の実施の形態１に係る空気調和機におけるクロスフローファンと舌部と前面下部熱交換との位置関係を説明するための模式図である。It is a schematic diagram for demonstrating the positional relationship of the crossflow fan, tongue part, and front lower part heat exchange in the air conditioner which concerns on Embodiment 1 of this invention. 舌部中心角θが３０度のときの空気の流れを示す図である。It is a figure which shows the flow of air when the tongue part center angle | corner (theta) is 30 degree | times. 舌部中心角θが９５度のときの図である。It is a figure when tongue part center angle (theta) is 95 degree | times. 舌部中心角θが６０度のときの空気の流れを示す図である。It is a figure which shows the flow of air when tongue part center angle | corner (theta) is 60 degree | times. 舌部中心角θの変化による熱交換能力比の変化を示すグラフである。It is a graph which shows the change of the heat exchange capability ratio by the change of tongue part center angle (theta). 本発明の実施の形態２に係る空気調和機の構成を示す断面側面図である。It is a cross-sectional side view which shows the structure of the air conditioner which concerns on Embodiment 2 of this invention. 本発明の実施の形態３に係る空気調和機の構成を示す断面側面図である。It is a cross-sectional side view which shows the structure of the air conditioner which concerns on Embodiment 3 of this invention.
　以下、本発明の実施の形態について、図面を参照しながら説明する。なお、本発明は、図示の実施の形態に限定されるものではない。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the illustrated embodiment.
実施の形態１．
　図１は、本発明の実施の形態１に係る空気調和機を示す断面側面図である。
　この実施の形態１に係る空気調和機１０は、箱形のケーシングよりなる本体１と、本体１内に形成された風路４に配設された熱交換器２およびクロスフローファン３とを備えている。
　全体符号を２で示された熱交換器２は、本例では３つの部分のクロスフィンチューブ式熱交換器により構成されている。すなわち、この熱交換器２は、図のように縦に断面して側方からみると、クロスフローファン３の前方側に位置してドレンパン１４上に配設されている前面下部熱交換器２ｃと、この前面下部熱交換器２ｃの上側に配置されてその上端側が後方へ傾斜する前面熱交換器２ｂと、この前面熱交換器２ｂの上側で連接され、かつ後方下側へ傾斜した背面熱交換器２ａとを有し、これら３つの部分の熱交換器２ａ～２ｃは冷媒が連続して流れるように逆Ｖ字状に連接して構成されている。さらに、各部分の熱交換器２ａ～２ｃは横方向（図の紙面に垂直な方向）に並列配置した多数のフィンに冷媒配管５を繰り返し往復し貫通させて構成されている。 Embodiment 1 FIG.
1 is a cross-sectional side view showing an air conditioner according to Embodiment 1 of the present invention.
An air conditioner 10 according to Embodiment 1 includes a main body 1 made of a box-shaped casing, a heat exchanger 2 and a cross flow fan 3 disposed in an air passage 4 formed in the main body 1. ing.
The heat exchanger 2 indicated by 2 as a whole is constituted by a three-part cross-fin tube heat exchanger in this example. In other words, the heat exchanger 2 is vertically sectioned as shown in the drawing and viewed from the side, the front lower heat exchanger 2c located on the drain pan 14 and located on the front side of the cross flow fan 3 is shown. And a front heat exchanger 2b which is disposed on the upper side of the lower front heat exchanger 2c and whose upper end is inclined rearward, and a rear heat which is connected on the upper side of the front heat exchanger 2b and inclined lower rearward. The heat exchangers 2a to 2c of these three parts are connected in an inverted V shape so that the refrigerant flows continuously. Further, the heat exchangers 2a to 2c of each part are configured by repeatedly reciprocating the refrigerant pipe 5 through a large number of fins arranged in parallel in the lateral direction (direction perpendicular to the drawing sheet).
　本体１の上面と前面下部（正面の前面パネル１１の下側）に、それぞれ上面空気吸込口６と前面空気吸込口７が形成され、本体１の下部には前面側に向けて開口する空気吹出口８が形成されている。これら上面空気吸込口６、前面空気吸込口７および空気吹出口８により本体１内を空気が通過する風路４が形成されている。風路４には上流側より順に空気清浄化用のフィルター９、上記の熱交換器２、およびクロスフローファン３が配設されている。そして、クロスフローファン３の空気吸込口を形成するために、クロスフローファン３の周囲には舌部１２とリアガイド１３が設けられている。さらにこの舌部１２は、前面下部熱交換器２ｃに流入する風速が低下するように、クロスフローファン３の回転方向（図示の矢印方向）に沿って延長されている。また、舌部１２は、前面下部熱交換器２ｃの下方に配置され、熱交換器２ｂ、２ｃより滴下するドレン水を受けるためのドレンパン１４と一体的に形成されている。 A top air inlet 6 and a front air inlet 7 are formed on the upper surface and lower front of the main body 1 (below the front panel 11 on the front), respectively, and an air blower opening toward the front is formed on the lower portion of the main body 1. An outlet 8 is formed. The upper surface air inlet 6, the front air inlet 7 and the air outlet 8 form an air passage 4 through which air passes through the main body 1. An air cleaning filter 9, the heat exchanger 2, and the cross flow fan 3 are disposed in the air path 4 in order from the upstream side. A tongue 12 and a rear guide 13 are provided around the cross flow fan 3 in order to form an air suction port of the cross flow fan 3. Further, the tongue 12 is extended along the rotation direction of the cross flow fan 3 (arrow direction shown in the drawing) so that the wind speed flowing into the front lower heat exchanger 2c decreases. Moreover, the tongue part 12 is arrange | positioned under the front lower heat exchanger 2c, and is integrally formed with the drain pan 14 for receiving the drain water dripped from the heat exchangers 2b and 2c.
　この空気調和機１０において、クロスフローファン３を回転駆動すると、上面空気吸込口６および前面空気吸込口７から空気を吸い込み、吸い込まれた空気は熱交換器２で冷媒との間で熱交換され、冷気または暖気となった空気が空気吹出口８から室内へ吹き出されることになる。なお、空気吹出口８には、吹出空気の方向変換用のルーバー（図示省略）が装着されている。 In the air conditioner 10, when the cross flow fan 3 is rotationally driven, air is sucked from the upper surface air inlet 6 and the front air inlet 7, and the sucked air is heat-exchanged with the refrigerant in the heat exchanger 2. The air that has become cold air or warm air is blown into the room from the air outlet 8. The air outlet 8 is equipped with a louver (not shown) for changing the direction of the blown air.
　図２は、本発明の要部を示す断面側面図で、実施の形態１に係る空気調和機のクロスフローファン３と舌部１２と前面下部熱交換器２ｃとの位置関係を説明するための模式図である。
　図２において、クロスフローファン３の中心をＯ、中心Ｏから前面下部熱交換器２ｃに向けて水平に延ばした線を３０、クロスフローファン３の中心Ｏと舌部１２の先端１２ａとを結ぶ線を３１、クロスフローファン３の中心Ｏとドレンパン１４の先端１４ａとを結ぶ線を３２とし、線３０と線３２とのなす角度をα、線３１と線３２とのなす角度（以下、舌部中心角という）をθとすると、舌部中心角θは、０．５α≦θ＜１．０５α、好ましくは、０．７α≦θ≦０．９８αの範囲になるように舌部１２の先端１２ａの高さ位置を設定している。なお、クロスフローファン３の中心Ｏの位置は前面下部熱交換器２ｃの高さ寸法Ｌ（折れ曲がり部より下方の高さ）の略中間位置に配置されている。また、αは６０度～７０度の範囲に設定している。 FIG. 2 is a cross-sectional side view showing the main part of the present invention, for explaining the positional relationship among the crossflow fan 3, the tongue 12 and the front lower heat exchanger 2c of the air conditioner according to Embodiment 1. It is a schematic diagram.
In FIG. 2, the center of the crossflow fan 3 is O, a line extending horizontally from the center O toward the lower front heat exchanger 2c is 30, and the center O of the crossflow fan 3 and the tip 12a of the tongue 12 are connected. 31 is a line, 32 is a line connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, the angle between the line 30 and the line 32 is α, and the angle between the line 31 and the line 32 (hereinafter referred to as the tongue) Where the tongue central angle θ is 0.5α ≦ θ <1.05α, preferably 0.7α ≦ θ ≦ 0.98α. The height position of 12a is set. In addition, the position of the center O of the crossflow fan 3 is disposed at a substantially intermediate position of the height dimension L (the height below the bent portion) of the front lower heat exchanger 2c. Α is set in the range of 60 to 70 degrees.
　クロスフローファン３は、羽根車の内部に流入した流れが羽根車を直径方向に横切る、つまり始めは羽根車の半径方向内向きに流入し、次に外向きに流出して、流れは羽根車を２度通り抜けるという特徴を有している。特に、クロスフローファン３は、本体１内に設置するとクロスフローファン３の前面側から流入する空気を最も多く吸い込む。そのため、前面下部熱交換器２ｃを通る風速が他の部分の熱交換器２ｂ、２ａを通る風速よりも速くなる傾向にある。このため、熱交換性能が低下しやすいという問題がある。 In the cross flow fan 3, the flow that flows into the impeller crosses the impeller in the diametrical direction, that is, the flow first flows inward in the radial direction of the impeller and then flows outward. It has the feature of passing through twice. In particular, when the crossflow fan 3 is installed in the main body 1, the air that flows in from the front side of the crossflow fan 3 is sucked in most. Therefore, the wind speed passing through the front lower heat exchanger 2c tends to be faster than the wind speed passing through the other heat exchangers 2b and 2a. For this reason, there exists a problem that heat exchange performance falls easily.
　この問題について図面を用いて説明する。図３は、θが２５度のときの空気の流れを示す図である。また、図４は、θが９５度のときの図であり、図５は、θが６０度のときの空気の流れを示す図である。
　舌部中心角θを０．５α未満に設定した場合には、クロスフローファン３の前面側の圧力損失が小さくなり、図３に示すように、前面下部熱交換器２ｃから流入する風量が増加して風速が速くなるために十分な熱交換能力が確保できない。また、渦４０が舌部１２近傍から吐出風路４ａ側へ向けて延びるように発生するため、クロスフローファン３を貫流する空気の貫流幅が小さくなり、吹き出し風速が増加することから騒音発生の原因ともなる。
　一方、舌部中心角θを１．５α以上に設定すると、クロスフローファン３の実質的な吸込み面積領域３５（図４に太い実線で示す領域）が減少し送風性能が低下するため、熱交換能力も低下するという実験結果が得られている。 This problem will be described with reference to the drawings. FIG. 3 is a diagram showing the air flow when θ is 25 degrees. FIG. 4 is a view when θ is 95 degrees, and FIG. 5 is a view showing an air flow when θ is 60 degrees.
When the tongue center angle θ is set to less than 0.5α, the pressure loss on the front side of the crossflow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c is increased as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be secured. Further, since the vortex 40 is generated so as to extend from the vicinity of the tongue portion 12 toward the discharge air passage 4a, the flow width of the air flowing through the cross flow fan 3 is reduced, and the blowing air speed is increased, so that noise is generated. It can also be a cause.
On the other hand, when the tongue center angle θ is set to 1.5α or more, the substantial suction area region 35 (the region indicated by the thick solid line in FIG. 4) of the cross flow fan 3 is reduced and the air blowing performance is lowered. Experimental results have shown that ability is also reduced.
　そこで、舌部中心角θを上に示した範囲、すなわち、０．５α≦θ＜１．０５α、好ましくは、０．７α≦θ≦０．９８αとすることで、図５に示すように前面下部熱交換器２ｃからクロスフローファン３に流入する風量が減少し風速が効果的に低下するため、十分な熱交換能力を確保することができる。また、渦４０は貫流幅を広げるように、舌部１２に、より接近する位置に発生するため、吹き出し風速が低下し騒音も低下する。 Therefore, by setting the tongue center angle θ in the above range, that is, 0.5α ≦ θ <1.05α, preferably 0.7α ≦ θ ≦ 0.98α, the front surface as shown in FIG. Since the amount of air flowing into the cross flow fan 3 from the lower heat exchanger 2c is reduced and the wind speed is effectively reduced, a sufficient heat exchange capability can be ensured. Further, since the vortex 40 is generated at a position closer to the tongue portion 12 so as to widen the through-flow width, the blowing wind speed is reduced and the noise is also reduced.
　図６（ａ）に、舌部中心角θを変化させたときの、従来の空気調和機（従来機）に対する熱交換能力の比を示す。同図中の実線は、従来機の熱交換能力を「１」として示しており、同図中の縦軸は従来機に対する熱交換能力の比を、同図中の横軸は舌部中心角θの変化をあらわしている。また、従来機における舌部中心角θは２０度～２５度である。図6（ｂ）の表は、図６（ａ）における各点Ａ～Ｊの座標位置を示すものであり、点Ａ、Ｃ～Ｅ、ＧおよびＪは実際の実験値であり、点Ｂ、Ｆ、ＨおよびＩは、それら実験値を通る近似曲線５０上の各点の座標位置である。
　図６のグラフから、０．４５α＜θ＜１．０７αの範囲内において熱交換能力が従来機よりも高くなり、特に、０．５α≦θ＜１．０５αの範囲内において熱交換能力比が従来比１．０２以上となり、さらに好ましくは、０．７α≦θ≦０．９８αの範囲のものでは従来機よりも熱交換能力が１．１倍以上に向上していることが分かる。 FIG. 6 (a) shows a ratio of heat exchange capacity to a conventional air conditioner (conventional machine) when the tongue center angle θ is changed. The solid line in the figure indicates the heat exchange capacity of the conventional machine as “1”, the vertical axis in the figure represents the ratio of the heat exchange capacity to the conventional machine, and the horizontal axis in the figure represents the central angle of the tongue. It shows the change of θ. Further, the central angle θ of the tongue in the conventional machine is 20 degrees to 25 degrees. The table in FIG. 6 (b) shows the coordinate positions of the points A to J in FIG. 6 (a). The points A, C to E, G and J are actual experimental values, and the points B, F, H, and I are the coordinate positions of each point on the approximate curve 50 that passes through these experimental values.
From the graph of FIG. 6, the heat exchange capacity is higher than that of the conventional machine within the range of 0.45α <θ <1.07α, and in particular, the heat exchange capacity ratio is within the range of 0.5α ≦ θ <1.05α. It can be seen that the heat exchange capacity is 1.02 or more, and more preferably in the range of 0.7α ≦ θ ≦ 0.98α, the heat exchange capacity is improved by 1.1 times or more than the conventional machine.
　以上のように、本実施の形態においては、舌部中心角θが０．４５α＜θ＜１．０７αの範囲内、特に０．５α≦θ＜１．０５αの範囲を満たすように舌部１２をクロスフローファン３の回転方向に沿って延長する構成とすることによって、前面下部熱交換器２ｃへ流入する風速を効果的に低下させることができ、十分な熱交換能力を確保することができる。また、騒音も低下させることができる。また、従来のような圧損体も必要としないのでコスト低減ができる。 As described above, in the present embodiment, the tongue 12 has a tongue center angle θ satisfying the range of 0.45α <θ <1.07α, particularly 0.5α ≦ θ <1.05α. Is configured to extend along the rotation direction of the cross flow fan 3, the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced, and sufficient heat exchange capability can be ensured. . Also, noise can be reduced. In addition, since a pressure loss body as in the prior art is not required, the cost can be reduced.
実施の形態２．
　図７は、本発明の実施の形態２に係る空気調和機を示す断面図である。
　この実施の形態２に係る空気調和機１０Ａは、前面下部熱交換器２ｃの冷媒配管５を前記空気調和機の奥行き方向に対して他の熱交換器２ａ、２ｂより少ない本数で構成することにより、すなわち、例えば、前面下部熱交換器２ｃの冷媒配管５の列数を他の熱交換器２ａ、２ｂよりも減じて空気調和機本体を薄型化している点が実施の形態１と相違し、その他の構成は実施の形態１と同様である。
　このように、前面下部熱交換器２ｃの冷媒配管５の本数すなわち列数を減らすことで空気調和機本体を薄型化した場合、その構成上、熱交換器２の風速分布は、空気抵抗の小さい前面下部熱交換器２ｃで風速が極端に速いアンバランスな分布になる。 Embodiment 2. FIG.
FIG. 7 is a cross-sectional view showing an air conditioner according to Embodiment 2 of the present invention.
In the air conditioner 10A according to the second embodiment, the refrigerant pipe 5 of the lower front heat exchanger 2c is configured with a smaller number than the other heat exchangers 2a and 2b in the depth direction of the air conditioner. That is, for example, the point that the number of rows of the refrigerant pipes 5 of the front lower heat exchanger 2c is reduced as compared with the other heat exchangers 2a and 2b is different from the first embodiment in that the air conditioner main body is made thinner. Other configurations are the same as those of the first embodiment.
Thus, when the air conditioner main body is thinned by reducing the number of refrigerant pipes 5 of the front lower heat exchanger 2c, that is, the number of rows, the wind speed distribution of the heat exchanger 2 has a low air resistance due to its configuration. In the front lower heat exchanger 2c, the wind speed is extremely unbalanced.
　このため、舌部１２の先端１２ａの位置は、図２に示すように、クロスフローファン３の中心Ｏとドレンパン１４の先端１４ａとを結ぶ線３２と、クロスフローファン３の中心Ｏと舌部１２の先端１２ａとを結ぶ線３１とのなす角度である舌部中心角θが、クロスフローファン３の中心Ｏから前面下部熱交換器２ｃに向けて水平に延ばした線を３０と、クロスフローファン３の中心Ｏとドレンパン１４の先端１４ａとを結ぶ線３２とのなす角度αの７０％以上となる角度０．７α≦θ≦０．９８αの範囲になるように構成している。なお、クロスフローファン３の中心Ｏの位置は前面下部熱交換器２ｃの高さ寸法Ｌの略中間位置に配置されている。また、αは６０度～７０度の範囲に設定している。 For this reason, as shown in FIG. 2, the position of the tip 12a of the tongue 12 is such that the line 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, and the center O of the crossflow fan 3 and the tongue. 12 is a line in which the tongue center angle θ, which is an angle formed with the line 31 connecting the tip 12a of the twelve, extends horizontally from the center O of the crossflow fan 3 toward the front lower heat exchanger 2c, The angle is 0.7α ≦ θ ≦ 0.98α, which is 70% or more of the angle α formed by the line 32 connecting the center O of the fan 3 and the tip 14 a of the drain pan 14. In addition, the position of the center O of the cross flow fan 3 is arranged at a substantially middle position of the height dimension L of the front lower heat exchanger 2c. Α is set in the range of 60 to 70 degrees.
　ここで、舌部中心角θを０．７α未満に設定した場合には、クロスフローファン３の前面側の圧力損失が小さくなり、図３に示すように前面下部熱交換器２ｃから流入する風量が増加し風速が速くなるために十分な熱交換能力が確保できず、また１．０5α以上に設定すると、図４の太い実線で示すように、クロスフローファン３の実質的な吸込み面積領域３５が減少し送風性能が低下するため熱交換能力も低下するという実験結果を得ている。そこで、熱交換器２の風速がアンバランスな分布となるときには、舌部中心角θを前記範囲０．７α≦θ≦０．９８αとすることで、図５に示すように前面下部熱交換器２ｃから流入する風量が減少し風速が効果的に低下するため、十分な熱交換能力を確保することができる。また、騒音も低下させることができる。 Here, when the tongue center angle θ is set to be less than 0.7α, the pressure loss on the front side of the cross flow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be secured, and when it is set to 1.05α or more, as shown by the thick solid line in FIG. Experimental results have been obtained that the heat exchange capacity is also reduced due to the decrease in air flow and the air blowing performance. Therefore, when the wind speed of the heat exchanger 2 has an unbalanced distribution, by setting the tongue central angle θ to the range 0.7α ≦ θ ≦ 0.98α, the front lower heat exchanger as shown in FIG. Since the amount of air flowing in from 2c is reduced and the wind speed is effectively reduced, sufficient heat exchange capability can be ensured. Also, noise can be reduced.
　以上のように、本実施の形態においては、空気調和機本体の薄型化に伴い熱交換器２の風速がアンバランスな分布となる場合には、舌部中心角θが０．７α≦θ≦０．９８αの範囲を満たすように舌部１２をクロスフローファン３の回転方向に沿って延長する構成とすることによって、前面下部熱交換器２ｃへ流入する風速を効果的に低下させることができ、十分な熱交換能力を確保することができる。また、騒音も低下させることができる。また、従来のような圧損体も必要としないのでコスト低減ができる。 As described above, in the present embodiment, when the air speed of the heat exchanger 2 has an unbalanced distribution as the air conditioner body becomes thinner, the tongue center angle θ is 0.7α ≦ θ ≦. By configuring the tongue 12 to extend along the rotational direction of the crossflow fan 3 so as to satisfy the range of 0.98α, the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced. Sufficient heat exchange capacity can be ensured. Also, noise can be reduced. In addition, since a pressure loss body as in the prior art is not required, the cost can be reduced.
実施の形態３．
　図８は、本発明の実施の形態３に係る空気調和機を示す断面図である。
　この実施の形態３に係る空気調和機１０Ｂは、箱形のケーシングよりなる本体１の上面のみに吸込口６を設けた点、および、クロスフローファン３に対して上流側に逆Ｖ字状に配置される熱交換器２の鋭角をより小さくして空気調和機本体を薄型化した点が実施の形態１及び実施の形態２と相違する。本例では、前面に配置される前面パネル１１の下端がドレンパン１４と連結されて図１に示した前面空気吸込口７が閉じられた形態となっている。その他の構成は実施の形態２と同様である。 Embodiment 3 FIG.
FIG. 8 is a cross-sectional view showing an air conditioner according to Embodiment 3 of the present invention.
The air conditioner 10 </ b> B according to the third embodiment is provided with a suction port 6 only on the upper surface of the main body 1 made of a box-shaped casing, and in an inverted V shape upstream of the cross flow fan 3. The point which made the air conditioner main body thin by making the acute angle of the heat exchanger 2 arrange | positioned smaller was different from Embodiment 1 and Embodiment 2. FIG. In this example, the lower end of the front panel 11 disposed on the front surface is connected to the drain pan 14 and the front air inlet 7 shown in FIG. 1 is closed. Other configurations are the same as those of the second embodiment.
　本実施の形態の空気調和機１０Ｂでは、前面側の空気吸込口７を無くし空気吸込口を本体１の上面側の空気吸込口６のみとし、熱交換器２については、前面熱交換器２ｂの上側と連設され、且つ後方下側へ傾斜した背面熱交換器２ａとの逆Ｖ字型部分の角度を実施の形態１、２の構成よりも鋭角とすることで、空気調和機本体を薄型化している。したがって、かかる空気調和機本体の薄型化による構成上、熱交換器２の風速分布は、圧力損失の小さい前面下部熱交換器２ｃで風速が極端に速いアンバランスな分布になる。 In the air conditioner 10B of the present embodiment, the air suction port 7 on the front surface side is eliminated and only the air suction port 6 on the upper surface side of the main body 1 is used, and the heat exchanger 2 is the same as that of the front heat exchanger 2b. The air conditioner main body is made thin by making the angle of the inverted V-shaped portion with the rear heat exchanger 2a that is connected to the upper side and inclined rearward and lower than the configuration of the first and second embodiments. It has become. Therefore, the wind speed distribution of the heat exchanger 2 becomes an unbalanced distribution in which the wind speed is extremely high in the front lower heat exchanger 2c with a small pressure loss due to the thinning of the air conditioner body.
　このため、舌部１２の先端１２ａの位置は、図２に示すように、クロスフローファン３の中心Ｏとドレンパン１４の先端１４ａとを結ぶ線３２と、クロスフローファン３の中心Ｏと舌部１２の先端１２ａとを結ぶ線３１とのなす角度である舌部中心角θが、クロスフローファン３の中心Ｏから前面下部熱交換器２ｃに向けて水平に延ばした線を３０と、クロスフローファン３の中心Ｏとドレンパン１４の先端１４ａとを結ぶ線３２とのなす角度αの７０％以上となる角度０．７α≦θ≦０．９８αの範囲になるように構成している。なお、クロスフローファン３の中心Ｏの位置は前面下部熱交換器２ｃの高さ寸法Ｌの略中間位置に配置されている。また、αは６０度～７０度の範囲に設定している。 For this reason, as shown in FIG. 2, the position of the tip 12a of the tongue 12 is such that the line 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, and the center O of the crossflow fan 3 and the tongue. 12 is a line in which the tongue center angle θ, which is an angle formed with the line 31 connecting the tip 12a of the twelve, extends horizontally from the center O of the crossflow fan 3 toward the front lower heat exchanger 2c, The angle is 0.7α ≦ θ ≦ 0.98α, which is 70% or more of the angle α formed by the line 32 connecting the center O of the fan 3 and the tip 14 a of the drain pan 14. In addition, the position of the center O of the cross flow fan 3 is arranged at a substantially middle position of the height dimension L of the front lower heat exchanger 2c. Α is set in the range of 60 to 70 degrees.
　ここで、舌部中心角θを０．７α未満に設定した場合には、クロスフローファン３の前面側の圧力損失が小さくなり、図３に示すように前面下部熱交換器２ｃから流入する風量が増加し風速が速くなるために十分な熱交換能力が確保できず、また１．０５α以上に設定すると、図４の太い実線で示すように、クロスフローファン３の実質的な吸込み面積領域３５が減少し送風性能が低下するため熱交換能力も低下するという実験結果を得ている。そこで、熱交換器２の風速がアンバランスな分布となるときには、舌部中心角θを前記範囲０．７α≦θ≦０．９８αとすることで、図５に示すように前面下部熱交換器２ｃから流入する風量が減少し風速が効果的に低下するため、十分な熱交換能力を確保することができる。 Here, when the tongue center angle θ is set to be less than 0.7α, the pressure loss on the front side of the cross flow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be ensured, and when it is set to 1.05α or more, as shown by the thick solid line in FIG. Experimental results have been obtained that the heat exchange capacity is also reduced due to the decrease in air flow and the air blowing performance. Therefore, when the wind speed of the heat exchanger 2 has an unbalanced distribution, by setting the tongue central angle θ to the range 0.7α ≦ θ ≦ 0.98α, the front lower heat exchanger as shown in FIG. Since the amount of air flowing in from 2c is reduced and the wind speed is effectively reduced, sufficient heat exchange capability can be ensured.
　以上のように、本実施の形態においては、空気調和機本体の薄型化に伴い熱交換器２の風速がアンバランスな分布となる場合には、前記舌部中心角θを０．７α≦θ≦０．９８αの範囲を満たすように舌部１２をクロスフローファン３の回転方向に沿って延長する構成とすることによって、前面下部熱交換器２ｃへ流入する風速を効果的に低下させることができ、十分な熱交換能力を確保することができる。また、騒音も低下させることができる。また、従来のような圧損体も必要としないのでコスト低減ができる。 As described above, in the present embodiment, when the air speed of the heat exchanger 2 has an unbalanced distribution as the air conditioner body becomes thinner, the tongue center angle θ is set to 0.7α ≦ θ. By setting the tongue 12 to extend along the rotation direction of the cross flow fan 3 so as to satisfy the range of ≦ 0.98α, the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced. And sufficient heat exchange capability can be secured. Also, noise can be reduced. In addition, since a pressure loss body as in the prior art is not required, the cost can be reduced.
　なお、以上の実施の形態１～３では逆Ｖ字状の熱交換器２について説明したが、本発明における熱交換器はこれに限定されるものではなく、例えば、背面側の熱交換器２ａは無くてもよく、前面側の熱交換器２ｂ、２ｃのみでもよいものである。 In the above first to third embodiments, the reverse V-shaped heat exchanger 2 has been described. However, the heat exchanger according to the present invention is not limited to this, and for example, the heat exchanger 2a on the back side. The heat exchangers 2b and 2c on the front side may be used.
　１　本体、２　熱交換器、２a　背面熱交換器、２b　前面熱交換器、２c　前面下部熱交換器、３　クロスフローファン、４　風路、４ａ　吹出風路、５　冷媒配管、６　上面空気吸込口、７　前面空気吸込口、８　空気吹出口、９　フィルター、１０、１０Ａ、１０Ｂ　空気調和機、１１　前面パネル、１２　舌部、１３　リアガイド、１４　ドレンパン、３０　クロスフローファン３の中心Ｏから前面下部熱交換器２ｃに向けて水平に延ばした線、３１　クロスフローファン３の中心Ｏと舌部１２の先端１２ａとを結ぶ線、３２　クロスフローファン３の中心Ｏとドレンパン１４の先端１４ａとを結ぶ線、３５　吸込み面積領域、４０　渦。 1 Main body, 2 Heat exchanger, 2a Rear heat exchanger, 2b Front heat exchanger, 2c Front lower heat exchanger, 3 Cross flow fan, 4 Air channel, 4a Air outlet, 5 Refrigerant piping, 6 Top air inlet , 7 Front air inlet, 8 Air outlet, 9 Filter, 10, 10A, 10B Air conditioner, 11 Front panel, 12 Tongue, 13 Rear guide, 14 Drain pan, 30 Cross flow fan 3 from center O to lower front A line extending horizontally toward the heat exchanger 2c, 31 a line connecting the center O of the crossflow fan 3 and the tip 12a of the tongue 12, and 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14 Line, 35 suction area, 40 vortex.

Claims (8)

  1. 　本体と、本体内を空気が通過するように設けられた風路と、風路に配設された熱交換器およびクロスフローファンと、クロスフローファンの周囲に設けられた舌部とリアガイドとを備えた空気調和機において、
    　前記熱交換器は、前記クロスフローファンに対して前方下部に位置する前面下部熱交換器を有し、
    　前記前面下部熱交換器に流入する風速が低下するように、前記舌部が、前記前面下部熱交換器の下方に位置するドレンパンの先端から、前記クロスフローファンの回転方向に沿って延長された構成となっていることを特徴とする空気調和機。     A main body, an air passage provided to allow air to pass through the main body, a heat exchanger and a cross flow fan disposed in the air passage, a tongue and a rear guide provided around the cross flow fan, In an air conditioner equipped with
    The heat exchanger has a front lower heat exchanger located at a lower front side with respect to the cross flow fan,
    The tongue is extended along the rotational direction of the cross flow fan from the tip of a drain pan located below the front lower heat exchanger so that the wind speed flowing into the front lower heat exchanger is reduced. An air conditioner characterized by having a configuration.
  2. 　前記クロスフローファンの中心が前記前面下部熱交換器の高さ寸法の略中間位置に配置された空気調和機において、
    　前記クロスフローファンの中心と前記舌部の先端とを結ぶ線と、前記クロスフローファンの中心と前記ドレンパンの先端とを結ぶ線とのなす角度である舌部中心角をθ、前記クロスフローファンの中心から前記前面下部熱交換器に向かって水平に延ばした線と、前記クロスフローファンの中心と前記ドレンパンの先端とを結ぶ線とのなす角度をαとするとき、
    　前記θは、０．４５α＜θ＜１．０７α
    の範囲であることを特徴とする請求項１記載の空気調和機。     In the air conditioner in which the center of the cross flow fan is disposed at a substantially middle position of the height dimension of the front lower heat exchanger,
    The tongue central angle, which is an angle formed by a line connecting the center of the cross flow fan and the tip of the tongue, and a line connecting the center of the cross flow fan and the tip of the drain pan, is θ, and the cross flow fan When the angle between the line extending horizontally from the center of the front lower heat exchanger and the line connecting the center of the crossflow fan and the tip of the drain pan is α,
    The θ is 0.45α <θ <1.07α.
    The air conditioner according to claim 1, wherein the air conditioner falls within the range.
  3. 　前記θは、０．５α≦θ＜１．０５α
    の範囲であることを特徴とする請求項２記載の空気調和機。     The θ is 0.5α ≦ θ <1.05α.
    The air conditioner according to claim 2, wherein the air conditioner falls within the range.
  4. 　前記θは、０．７α≦θ≦０．９８α
    の範囲であることを特徴とする請求項２記載の空気調和機。     The θ is 0.7α ≦ θ ≦ 0.98α.
    The air conditioner according to claim 2, wherein the air conditioner falls within the range.
  5. 　前記αは、６０度以上９０度以下である特徴とする請求項２～４のいずれかに記載の空気調和機。 The air conditioner according to any one of claims 2 to 4, wherein the α is not less than 60 degrees and not more than 90 degrees.
  6. 　請求項２～４のいずれかに記載の空気調和機において、
    　前記本体には上面と前面下部に前記風路の入口を構成する空気吸込口がそれぞれ設けられ、
    　前記熱交換器は、前面下部熱交換器を含む３つの部分の熱交換を有し、前記クロスフローファンに対し上流側に逆Ｖ字状に配置されていることを特徴とする空気調和機。     The air conditioner according to any one of claims 2 to 4,
    The main body is provided with an air inlet that constitutes the inlet of the air passage on the upper surface and the lower front surface, respectively.
    The said heat exchanger has heat exchange of three parts including a front lower heat exchanger, and is arrange | positioned in the reverse V shape upstream from the said crossflow fan, The air conditioner characterized by the above-mentioned.
  7. 　請求項４に記載の空気調和機において、
    　前記本体には上面と前面下部に前記風路の入口を構成する空気吸込口がそれぞれ設けられ、
    　前記熱交換器は、前面下部熱交換器を含む３つの部分の熱交換を有し、前記クロスフローファンに対し上流側に逆Ｖ字状に配置され、かつ、前面下部熱交換器の冷媒配管の本数が他の２つの部分の熱交換器よりも少ない構成としたことを特徴とする空気調和機。     The air conditioner according to claim 4,
    The main body is provided with an air inlet that constitutes the inlet of the air passage on the upper surface and the lower front surface, respectively.
    The heat exchanger has heat exchange of three parts including a front lower heat exchanger, is arranged in an inverted V shape upstream of the cross flow fan, and is a refrigerant pipe of the front lower heat exchanger The air conditioner is characterized in that the number of the is less than the heat exchangers of the other two parts.
  8. 　請求項４に記載の空気調和機において、
    　前記本体には上面に前記風路の入口を構成する空気吸込口が設けられ、
    　前記熱交換器は、前面下部熱交換器を含む３つの部分の熱交換を有し、前記クロスフローファンに対し上流側に逆Ｖ字状に配置されていることを特徴とする空気調和機。     The air conditioner according to claim 4,
    The main body is provided with an air inlet that forms the inlet of the air passage on the upper surface,
    The said heat exchanger has heat exchange of three parts including a front lower heat exchanger, and is arrange | positioned in the reverse V shape upstream from the said crossflow fan, The air conditioner characterized by the above-mentioned.
PCT/JP2009/007170 2009-12-24 2009-12-24 Air conditioner WO2011077484A1 (en)

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JP2015124986A (en) * 2013-12-27 2015-07-06 ダイキン工業株式会社 Air-conditioner indoor unit
CN104791910A (en) * 2015-04-03 2015-07-22 广东美的制冷设备有限公司 Refrigeration equipment and heat exchange assembly for same
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