WO2023182025A1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
WO2023182025A1
WO2023182025A1 PCT/JP2023/009491 JP2023009491W WO2023182025A1 WO 2023182025 A1 WO2023182025 A1 WO 2023182025A1 JP 2023009491 W JP2023009491 W JP 2023009491W WO 2023182025 A1 WO2023182025 A1 WO 2023182025A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
cross
end protrusion
flow fan
air conditioner
Prior art date
Application number
PCT/JP2023/009491
Other languages
French (fr)
Japanese (ja)
Inventor
賢宣 和田
崇裕 大城
剛史 永田
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Publication of WO2023182025A1 publication Critical patent/WO2023182025A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • 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
    • 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

Definitions

  • the present disclosure mainly relates to a home air conditioner.
  • an air conditioner includes a cross flow fan having multiple blades, a stabilizer, a rear guider, and a heat exchanger within a housing.
  • the heat exchanger includes a front heat exchanger placed on the front side of the cross-flow fan and a back heat exchanger placed on the back side of the cross-flow fan.
  • This kind of air conditioner sucks air from the top side of the air conditioner housing, exchanges heat between the sucked air and the refrigerant flowing inside the heat exchanger, and then sucks air from the bottom side of the housing. It is configured to blow out. In this way, indoor air conditioning is achieved.
  • Patent Document 1 discloses an air conditioner that aims to suppress noise.
  • This air conditioner includes an air passage that communicates the air outlet and the suction port.
  • the air conditioner includes a cross flow fan, a rear guider, a stabilizer, a front heat exchanger, and a rear heat exchanger in the air passage.
  • a crossflow fan includes multiple blades.
  • the rear guider includes a proximal portion that faces and approaches the cross-flow fan and is separated from the cross-flow fan by a predetermined distance, and an upper end protrusion that extends from the proximal portion toward the upper side of the rear heat exchanger.
  • the front heat exchanger is placed in front of the crossflow fan, and the back heat exchanger is placed behind the crossflow fan.
  • the present disclosure provides an air conditioner that improves air blowing performance by rectifying airflow flowing into a cross-flow fan.
  • the air conditioner in the present disclosure includes a cross flow fan, a stabilizer, a rear guider, a front heat exchanger placed on the front side of the cross flow fan, and a back heat exchanger placed on the back side of the cross flow fan.
  • the rear guider includes a proximal portion that faces the cross-flow fan and is disposed close to the cross-flow fan at a predetermined distance, and an upper end protrusion that extends upward from the proximal portion.
  • the upper end protrusion of the rear guider has an arcuate portion circumscribing a straight line X perpendicular to the downstream surface of the back heat exchanger.
  • the air conditioner according to the present disclosure can improve air blowing performance by improving turbulence in the airflow flowing into the crossflow fan.
  • FIG. 1 is a longitudinal cross-sectional view of an air conditioner according to Embodiment 1 of the present disclosure.
  • FIG. 2 is a diagram showing a longitudinal cross-sectional configuration of the vicinity of the upper end protrusion of the air conditioner according to the first embodiment.
  • FIG. 3 is a streamline diagram showing the flow of air near the upper end protrusion of the air conditioner according to the first embodiment.
  • FIG. 4A is a diagram showing a change in the blowout air volume ratio with respect to D/T and the shape of the upper end protrusion of the air conditioner in the first embodiment.
  • FIG. 4B is a graph showing a change in the blowout air volume ratio with respect to D/T of the air conditioner in the first embodiment.
  • FIG. 5A is a diagram showing a change in the input of the crossflow fan and the shape of the upper end protrusion with respect to the D/T of the air conditioner in the first embodiment.
  • FIG. 5B is a graph showing a change in the input of the crossflow fan with respect to the D/T of the air conditioner in the first embodiment.
  • FIG. 6 is a longitudinal cross-sectional view of an air conditioner according to Patent Document 1.
  • FIG. 7 is a diagram showing a vertical cross-sectional configuration near the upper end protrusion of the air conditioner according to Patent Document 1.
  • FIG. 8 is a streamline diagram showing the flow of air near the upper end protrusion of the air conditioner according to Patent Document 1.
  • FIG. 6 is a longitudinal sectional view of the air conditioner 1 according to Patent Document 1.
  • FIG. 7 is a diagram showing a longitudinal cross-sectional configuration of the vicinity of the upper end protrusion 6b of the air conditioner 1.
  • FIG. 8 is a streamline diagram showing the flow of air near the upper end protrusion 6b of the air conditioner 1.
  • the air conditioner 1 includes an air passage 4 that communicates an air outlet 2 and an air inlet 3 with each other.
  • the air conditioner 1 includes a cross flow fan 5, a rear guider 6, and a stabilizer 7 in the air passage 4, a front heat exchanger 8 on the front side of the cross flow fan 5, and a rear heat exchanger on the back side of the cross flow fan 5. Equipped with 9.
  • the crossflow fan 5 includes a plurality of blades 5a.
  • the rear guider 6 includes a proximal portion 6a that faces the cross-flow fan 5 and approaches the cross-flow fan 5 at a predetermined distance.
  • the crossflow fan 5 includes an upper end protrusion 6b extending from the proximal portion 6a toward the upper side of the back heat exchanger 9.
  • the upper end projection 6b includes an upper end 6c of the upper end projection 6b, a surface 6d of the upper end projection 6b facing the back heat exchanger 9, and a surface 6e of the upper end projection 6b facing the cross flow fan 5.
  • the suction airflow that has passed through the portion of the upper end protrusion 6b located below the upper end 6c of the back heat exchanger 9 flows upward along the surface 6d of the upper end protrusion 6b facing the back heat exchanger 9, and flows upward through the upper end protrusion 6b. It turns toward the cross-flow fan 5 near the upper end of the portion 6b and flows into the cross-flow fan 5.
  • the suction airflow that has passed through the portion of the back heat exchanger 9 located above the upper end of the upper end protrusion 6b is transferred to the back heat exchanger located near the upper end of the upper end protrusion 6b and below the upper end of the upper end protrusion 6b. It merges with the suction airflow that has passed through the device 9 and flows into the crossflow fan 5.
  • a counterflow vortex that rotates in a direction opposite to the rotational direction of the crossflow fan 5 is generated in a space between the crossflow fan 5 and the surface 6e of the upper end protrusion 6b that faces the crossflow fan 5.
  • this backflow vortex is attached to the surface 6e of the upper end protrusion 6b facing the crossflow fan 5, and the vortex center of the backflow vortex is located upstream of the adjacent portion 6a, thereby preventing contact with the blades 5a.
  • the aim is to reduce interference and suppress noise.
  • FIG. 8 solid lines indicate streamlines of the airflow, and contours indicate the eddy viscosity coefficient of the airflow.
  • the upper end protrusion 6b has a uniform shape in the longitudinal direction parallel to the rotation axis of the cross flow fan 5.
  • the cross-sectional shape of the upper end of the upper end protrusion 6b in a cross section perpendicular to the rotation axis of the cross flow fan 5 is such that the surface of the upper end protrusion 6b facing the back heat exchanger 9 and the surface of the upper end protrusion 6b facing the cross flow fan 5 It is formed by an arc tangent to the surface.
  • a countercurrent vortex which is generated in the space between the crossflow fan 5 and the surface of the upper end protrusion 6b facing the crossflow fan 5 and rotates in a direction opposite to the rotational direction of the crossflow fan 5, flows into the arc of the upper end protrusion 6b.
  • the liquid flows along the upper end protrusion 6b toward the surface facing the back heat exchanger 9.
  • the suction airflow that has passed through the back heat exchanger 9 located below the upper end of the upper end protrusion 6b flows upward along the surface of the upper end protrusion 6b that faces the back heat exchanger 9, and
  • the liquid flows along the circular arc 6b toward the surface of the upper end protrusion 6b that faces the crossflow fan 5.
  • the present disclosure suppresses the collision between the suction airflow that has passed through the back heat exchanger and the backflow vortex generated in the space between the crossflow fan and the surface facing the crossflow fan of the upper end protrusion, and flows into the crossflow fan.
  • an air conditioner that can improve air blowing performance by improving airflow turbulence.
  • FIG. 1 is a longitudinal cross-sectional view of an air conditioner 100 in Embodiment 1 of the present disclosure.
  • FIG. 2 is a diagram showing a vertical cross-sectional configuration of the vicinity of the upper end protrusion 105b of the air conditioner 100.
  • FIG. 3 is a streamline diagram showing the flow of air near the upper end protrusion 105b of the air conditioner 100.
  • the left side in FIG. 1 will be described as the front side and the right side as the back side.
  • an air conditioner 100 includes a main body casing 103 having an inlet 101 and an outlet 102, a stabilizer 104, a rear guider 105, a cross flow fan 106, and a heat exchanger 107.
  • the rear guider 105 has a proximal portion 105a and an upper end protrusion 105b.
  • the proximal portion 105a is a portion that faces the cross-flow fan 106 and is close to the cross-flow fan 106 at a predetermined distance.
  • the upper end protrusion 105b is a portion extending upward from the proximal portion 105a.
  • the rear guider 105 is arranged between the crossflow fan 106 and a backside heat exchanger 107b, which will be described later.
  • the cross flow fan 106 has a rotating shaft and a plurality of blades 106a arranged in a cylindrical shape.
  • the heat exchanger 107 is composed of a front heat exchanger 107a and a back heat exchanger 107b.
  • Heat exchanger 107 may include an auxiliary heat exchanger.
  • the front heat exchanger 107a is arranged on the front side of the cross flow fan 106.
  • the back heat exchanger 107b is arranged on the back side of the cross flow fan 106.
  • the auxiliary heat exchanger is arranged, for example, on the surface of the rear heat exchanger 107b opposite to the surface where the cross flow fan 106 and the rear heat exchanger 107b face each other.
  • the auxiliary heat exchanger is arranged on the surface of the back heat exchanger 107b on the upstream side of the air flowing in from the suction port 101 when the crossflow fan rotates.
  • the heat exchanger 107 includes a plurality of fins 107c and a plurality of heat transfer tubes 107d passing through the plurality of fins 107c.
  • a point on the proximal portion 105a that is the shortest distance from the cross flow fan 106 is defined as a proximate point A.
  • a straight line X is a straight line perpendicular to the downstream surface of the back heat exchanger 107b.
  • the upper end protrusion 105b has a circular arc portion 105c that circumscribes the straight line X, and the point of contact between the straight line X and the circular arc portion 105c is a tip point B.
  • the tip point B is located closer to the cross flow fan 106 than the center line W of the upper end protrusion.
  • the upper end protrusion 105b is configured such that D/T ⁇ 0.6, where D is the diameter of the arcuate portion 105c and T is the thickness of the upper end protrusion 105b.
  • Point R is a point on the surface 105e of the upper end protrusion 105b facing the rear heat exchanger 107b, which is the shortest distance from point Q to the surface 105e of the upper end projection 105b facing the rear heat exchanger 107b.
  • the straight line connecting point Q and point R be straight line Z.
  • a straight line passing through the midpoint of the straight line Z and perpendicular to the straight line Z is defined as the center line W of the upper end protrusion.
  • the length of the line segment QR on the straight line Z be the thickness T of the upper end protrusion 105b.
  • the upper end protrusion 105b has a flat portion 105d that is tangential to the arcuate portion 105c and faces the back heat exchanger 107b.
  • the upper end protrusion 105b is configured such that U/T ⁇ 1.0, where U is the length of the flat portion 105d.
  • the cross flow fan 106 rotates, indoor air is sucked into the main body casing 103 from the suction port 101.
  • the indoor air sucked into the main body casing 103 passes through the front heat exchanger 107a and the back heat exchanger 107b, flows into the cross flow fan 106, and is blown out from the outlet 102 into the indoor space.
  • the cross flow fan 106 rotates clockwise.
  • the suction airflow that has passed through the portion of the rear heat exchanger 107b located below the upper end of the upper end protrusion 105b is caused to flow along the surface 105e of the upper end protrusion 105b facing the rear heat exchanger 107b. It flows upward, turns toward the cross-flow fan 106 near the upper end of the upper end protrusion 105b, and flows into the cross-flow fan 106.
  • the suction airflow passing through the portion located above the upper end of the upper end protrusion 105b in the back heat exchanger 107b is near the upper end of the upper end protrusion 105b, and is lower than the upper end of the upper end protrusion 105b in the back heat exchanger 107b. It merges with the suction airflow that has passed through the portion located at , and flows into the crossflow fan 106 .
  • a countercurrent vortex that rotates in a direction opposite to the rotational direction of the crossflow fan 106 is generated in the space between the crossflow fan 106 and the upper end protrusion 105b.
  • the backflow vortex adheres to the surface 105f of the upper end protrusion 105b facing the crossflow fan 106, and the vortex center of the backflow vortex is located above the proximal portion 105a.
  • the suction airflow passing through the portion of the back heat exchanger 107b that is located below the upper end of the upper end protrusion 105b flows upward along the surface 105e of the upper end protrusion 105b that faces the back heat exchanger 107b, and flows upward through the plane portion. Reach 105d. Due to the inertial force of the suction airflow, the suction airflow passing through the portion of the back heat exchanger 107b located below the upper end of the upper end protrusion 105b is flat with the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b. The upper end protrusion 105b is separated from the surface 105e facing the back heat exchanger 107b at the connection point S with the portion 105d.
  • the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b and the flat part 105d are not continuous, and the length U of the flat part 105d is equal to the thickness T of the upper end protrusion 105b. , U/T ⁇ 1.0. For this reason, the suction airflow separated from the surface 105e of the upper end protrusion 105b facing the back surface heat exchanger 107b does not re-adhere to the flat portion 105d, but joins the flow flowing into the cross-flow fan 106.
  • the backflow vortex flows upward along the surface 105f of the upper end protrusion 105b facing the crossflow fan 106, and reaches the arcuate portion 105c.
  • the tip point B of the arcuate portion 105c is located closer to the crossflow fan 106 than the centerline W of the upper end protrusion 105b, and the diameter D of the arcuate portion 105c is equal to the thickness of the upper end protrusion 105b. D/T ⁇ 0.6 for T.
  • the deflection radius is small and it is deflected sharply, but due to the inertia of the backflow vortex, it separates from the circular arc portion 105c and the cross flow fan 105 joins the flow flowing into the Furthermore, since the tip point B is located closer to the cross-flow fan 106 than the center line W of the upper end protrusion 105b, the backflow vortex separates from the arcuate portion 105c at a position close to the cross-flow fan 106, and the cross-flow fan 106 joins the flow flowing into the
  • FIG. 4A is a diagram showing changes in the blowout air volume ratio with respect to D/T of the air conditioner 100 and the shape of the upper end protrusion 105b.
  • FIG. 4B is a graph showing changes in the blowout air volume ratio with respect to D/T of the air conditioner 100.
  • FIG. 5A is a diagram showing the input change (change in input power) of the crossflow fan 106 with respect to the D/T of the air conditioner 100 and the shape of the upper end protrusion 105b.
  • FIG. 5B is a graph showing a change in input to the crossflow fan 106 (change in input power) with respect to D/T of the air conditioner 100.
  • the value of D/T is shown in the upper row
  • the air volume ratio is shown in the middle row
  • the shape of the upper end protrusion 105b is shown in the lower row.
  • the horizontal axis represents D/T
  • the vertical axis represents the air volume ratio to D/T.
  • the air volume ratio increases rapidly between D/T 1.0 and 0.6, while D/T When it becomes less than 0.6, the air volume ratio maintains a substantially constant value. That is, the air volume ratio increases rapidly when D/T is between 1.0 and 0.6, and reaches the upper limit when D/T reaches 0.6. Therefore, it can be said that when D/T is less than 0.6, the air volume ratio is improved and the air blowing performance is improved.
  • the value of D/T is shown in the upper row
  • the input ratio is shown in the middle row
  • the shape of the upper end protrusion 105b is shown in the lower row.
  • the horizontal axis represents D/T
  • the vertical axis represents input ratio.
  • the air conditioner 100 includes a main body casing 103 having an inlet 101 and an outlet 102, a stabilizer 104, a rear guider 105, a cross flow fan 106, and a front heat exchanger. 107a, and a back heat exchanger 107b.
  • the rear guider 105 includes a proximal portion 105a that faces the cross-flow fan 106 and is close to the cross-flow fan 106 by a predetermined dimension (distance), and an upper end protrusion 105b that extends upward from the proximal portion 105a.
  • the upper end protrusion 105b has an arcuate portion 105c, and the tip point B of the arcuate portion 105c is located closer to the cross flow fan 106 than the centerline W of the upper end protrusion 105b.
  • the upper end protrusion 105b is configured so that D/T ⁇ 0.6, where D is the diameter of the arcuate portion 105c and T is the thickness of the upper end protrusion 105b.
  • the tip point B of the arcuate portion 105c is located closer to the crossflow fan 106 than the centerline W of the upper end protrusion 105b, and D/T ⁇ 0.6, so the generated backflow vortex flows along the arcuate portion 105c.
  • the deflection radius is small and the flow is abruptly deflected, but the reverse flow vortex separates from the circular arc portion 105c due to the inertial force of the reverse flow vortex and joins the flow flowing into the cross flow fan 106.
  • the tip point B is located closer to the cross-flow fan 106 than the center line W of the upper end protrusion 105b, the backflow vortex separates from the arcuate portion 105c at a position close to the cross-flow fan 106, and the cross-flow fan 106 joins the flow flowing into the
  • the backflow vortex flows along the arcuate portion 105c of the upper end protrusion 105b to the surface of the upper end protrusion 105b facing the back heat exchanger 107b. Flowing toward 105e is suppressed. Therefore, the occurrence of collision between the backflow vortex and the suction airflow can be suppressed or alleviated. Therefore, by improving the turbulence of the airflow flowing into the cross-flow fan 106, the amount of air blown from the cross-flow fan 106 can be increased, and the power input to the cross-flow fan 106 can be reduced. Moreover, noise can be suppressed by improving the turbulence of the airflow flowing into the cross-flow fan 106.
  • the upper end protrusion 105b has a flat portion 105d, and is configured such that U/T ⁇ 1.0, where U is the length of the flat portion 105d.
  • U is the length of the flat portion 105d.
  • the suction airflow separates from the surface 105e of the upper end protrusion 105b facing the back surface heat exchanger 107b due to the inertial force of the suction airflow. Since the flat portion 105d is configured such that U/T ⁇ 1.0, the suction airflow separated from the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b is not reattached to the flat portion 105d. First, it joins the flow flowing into the crossflow fan 106.
  • the suction airflow flows toward the surface 105f of the upper end protrusion 105b facing the cross flow fan 106 along the arcuate part 105c of the upper end protrusion 105b. It is possible to suppress or alleviate the occurrence of collision with a backflow vortex. Therefore, by improving the turbulence of the airflow flowing into the cross-flow fan 106, the input power to the cross-flow fan 106 can be reduced and noise can be suppressed.
  • the outer diameter Dt of the heat exchanger tube 107d shown in this embodiment is only an example. It is sufficient if the heat exchanger tube 107d satisfies Dt ⁇ 5mm.
  • Dt the outer diameter of the heat transfer tube 107d
  • the amount of water flowing into the crossflow fan 106 By improving the turbulence of the airflow, the amount of air blown from the crossflow fan 106 can be increased, and the input power to the crossflow fan 106 can be reduced.
  • noise can be suppressed by improving the turbulence of the airflow flowing into the cross-flow fan 106.
  • the present disclosure can improve air blowing performance by suppressing or mitigating the collision between the intake airflow and the backflow vortex formed upstream of the vicinity of the rear guider, and improving the turbulence of the airflow flowing into the crossflow fan. Therefore, it can be suitably used for home air conditioning and commercial air conditioning.
  • Air conditioner 101 Suction port 102 Air outlet 103 Main body casing 104 Stabilizer 105 Rear guider 105a Proximity portion 105b Upper end protrusion 105c Arc portion 105d Plane portion 106 Cross flow fan 106a Blade 107 Heat exchanger 107a Front heat exchanger 107b Rear heat exchanger 107c Fin 107d Heat exchanger tube

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

This air conditioner comprises a cross-flow fan (106), a rear guider (105), and a back surface heat exchanger (107b). The rear guider (105) comprises an upper end protruding part (105b) that has an arc part (105c). A tip point B that is positioned on the arc part (105c) is positioned further to the cross-flow fan (106) side than a centerline W of the upper end protruding part (105b). When D is the diameter of the arc part (105c) and T is the shortest distance between a surface of the upper end protruding part (105b) that is on the cross-flow fan (106) side and a surface of the upper end protruding part (105b) that is on the back surface heat exchanger (107b) side, D/T<0.6.

Description

空気調和機air conditioner
　本開示は、主に家庭用の空気調和機に関する。 The present disclosure mainly relates to a home air conditioner.
　一般に、空気調和機は、筐体内に、複数のブレードを有するクロスフローファンと、スタビライザと、リアガイダと、熱交換器と、を備える。熱交換器は、クロスフローファンの前面側に配置される前面熱交換器と、クロスフローファンの背面側に配置される背面熱交換器とにより構成される。このような空気調和機は、空気調和機の筐体の天面側から空気を吸い込み、吸い込んだ空気と熱交換器の内部を流れる冷媒との熱交換をし、筐体の底面側から空気を吹き出すように構成される。これにより、室内の空気調和が行われる。 Generally, an air conditioner includes a cross flow fan having multiple blades, a stabilizer, a rear guider, and a heat exchanger within a housing. The heat exchanger includes a front heat exchanger placed on the front side of the cross-flow fan and a back heat exchanger placed on the back side of the cross-flow fan. This kind of air conditioner sucks air from the top side of the air conditioner housing, exchanges heat between the sucked air and the refrigerant flowing inside the heat exchanger, and then sucks air from the bottom side of the housing. It is configured to blow out. In this way, indoor air conditioning is achieved.
　特許文献１は、騒音抑制を図る空気調和機を開示する。この空気調和機は、吹出口と吸込口とを連通する送風路を備える。空気調和機は、送風路内に、クロスフローファンとリアガイダとスタビライザと前面熱交換器と背面熱交換器とを備える。クロスフローファンは複数のブレードを備える。リアガイダは、クロスフローファンに対向して近接して所定の寸法だけクロスフローファンから離れる近接部と、近接部から更に背面熱交換器の上部側へ向かって延設された上端突起部を備える。前面熱交換器はクロスフローファンの前方に配置されており、背面熱交換器はクロスフローファンの後方に配置されている。 Patent Document 1 discloses an air conditioner that aims to suppress noise. This air conditioner includes an air passage that communicates the air outlet and the suction port. The air conditioner includes a cross flow fan, a rear guider, a stabilizer, a front heat exchanger, and a rear heat exchanger in the air passage. A crossflow fan includes multiple blades. The rear guider includes a proximal portion that faces and approaches the cross-flow fan and is separated from the cross-flow fan by a predetermined distance, and an upper end protrusion that extends from the proximal portion toward the upper side of the rear heat exchanger. The front heat exchanger is placed in front of the crossflow fan, and the back heat exchanger is placed behind the crossflow fan.
特開２００１－１２４３６２号公報Japanese Patent Application Publication No. 2001-124362
　しかしながら、特許文献１に記載の空気調和機では、クロスフローファンの回転により生じる吸込気流と逆渦流とが衝突し、その乱れた気流がクロスフローファンに流入してしまうことにより、送風性能が低下してしまうという問題がある。 However, in the air conditioner described in Patent Document 1, the suction airflow generated by the rotation of the crossflow fan collides with the reverse vortex flow, and the turbulent airflow flows into the crossflow fan, resulting in a decrease in air blowing performance. The problem is that you end up doing it.
　本開示は、クロスフローファンに流入する気流を整流し、送風性能を向上した空気調和機を提供する。 The present disclosure provides an air conditioner that improves air blowing performance by rectifying airflow flowing into a cross-flow fan.
　本開示における空気調和機は、クロスフローファンと、スタビライザと、リアガイダと、クロスフローファンの前面側に配置される前面熱交換器と、クロスフローファンの背面側に配置される背面熱交換器を備える。リアガイダは、クロスフローファンに対向し、かつ所定の距離でクロスフローファンと近接して配置される近接部と、近接部から上方へ向かって延出した上端突起部を備える。クロスフローファンの回転軸と直交するリアガイダの断面視において、リアガイダの上端突起部は背面熱交換器の下流面に垂直な直線Ｘと外接する円弧部を有する。直線Ｘと円弧部の接点を先端点Ｂとしたときに先端点Ｂが上端突起部中心線よりもクロスフローファン側に位置し、円弧部の径をＤとし上端突起部の厚さをＴとしたときにＤ／Ｔ＜０.６となる。 The air conditioner in the present disclosure includes a cross flow fan, a stabilizer, a rear guider, a front heat exchanger placed on the front side of the cross flow fan, and a back heat exchanger placed on the back side of the cross flow fan. Be prepared. The rear guider includes a proximal portion that faces the cross-flow fan and is disposed close to the cross-flow fan at a predetermined distance, and an upper end protrusion that extends upward from the proximal portion. In a cross-sectional view of the rear guider perpendicular to the rotation axis of the cross-flow fan, the upper end protrusion of the rear guider has an arcuate portion circumscribing a straight line X perpendicular to the downstream surface of the back heat exchanger. When the point of contact between the straight line When this happens, D/T<0.6.
　本開示における空気調和機は、クロスフローファンに流入する気流の乱れを改善することで送風性能の向上を図ることができる。 The air conditioner according to the present disclosure can improve air blowing performance by improving turbulence in the airflow flowing into the crossflow fan.
図１は、本開示の実施の形態１における空気調和機の縦断面図である。FIG. 1 is a longitudinal cross-sectional view of an air conditioner according to Embodiment 1 of the present disclosure. 図２は、同実施の形態１における空気調和機の上端突起部近傍の縦断面構成を示す図である。FIG. 2 is a diagram showing a longitudinal cross-sectional configuration of the vicinity of the upper end protrusion of the air conditioner according to the first embodiment. 図３は、同実施の形態１における空気調和機の上端突起部近傍の空気の流れを示す流線図である。FIG. 3 is a streamline diagram showing the flow of air near the upper end protrusion of the air conditioner according to the first embodiment. 図４Ａは、同実施の形態１における空気調和機のＤ／Ｔに対する吹出風量比の変化および上端突起部の形状を示す図である。FIG. 4A is a diagram showing a change in the blowout air volume ratio with respect to D/T and the shape of the upper end protrusion of the air conditioner in the first embodiment. 図４Ｂは、同実施の形態１における空気調和機のＤ／Ｔに対する吹出風量比の変化を示すグラフである。FIG. 4B is a graph showing a change in the blowout air volume ratio with respect to D/T of the air conditioner in the first embodiment. 図５Ａは、同実施の形態１における空気調和機のＤ／Ｔに対するクロスフローファンの入力変化および上端突起部の形状を示す図である。FIG. 5A is a diagram showing a change in the input of the crossflow fan and the shape of the upper end protrusion with respect to the D/T of the air conditioner in the first embodiment. 図５Ｂは、同実施の形態１における空気調和機のＤ／Ｔに対するクロスフローファンの入力変化を示すグラフである。FIG. 5B is a graph showing a change in the input of the crossflow fan with respect to the D/T of the air conditioner in the first embodiment. 図６は、特許文献１に係る空気調和機の縦断面図である。FIG. 6 is a longitudinal cross-sectional view of an air conditioner according to Patent Document 1. 図７は、特許文献１に係る空気調和機の上端突起部近傍の縦断面構成を示す図である。FIG. 7 is a diagram showing a vertical cross-sectional configuration near the upper end protrusion of the air conditioner according to Patent Document 1. 図８は、特許文献１に係る空気調和機の上端突起部近傍の空気の流れを示す流線図である。FIG. 8 is a streamline diagram showing the flow of air near the upper end protrusion of the air conditioner according to Patent Document 1.
　（本開示の基礎となった知見等）
　発明者らが本開示に想到するに至った当時、空気調和機において、クロスフローファンとリアガイダの近接部の上流において周囲の気流を巻き込んで渦流が形成され、その渦流をブレードが通過することで干渉騒音が生じるという問題があった。この渦流は、クロスフローファンとリアガイダとの隙間において、クロスフローファンの回転方向と逆方向となる逆流が生じ、この逆流がクロスフローファンとリアガイダの近接部を通過することで発生する。この問題の解決策として、クロスフローファンの後方で上流と下流を仕切る近接部からクロスフローファンの上方に向かって設けられる上端突起部により、騒音抑制を図る技術がある。 (Findings, etc. that formed the basis of this disclosure)
At the time the inventors came up with the present disclosure, in an air conditioner, a vortex was formed upstream of the vicinity of the crossflow fan and the rear guider, drawing in the surrounding airflow, and the blades passing through the vortex. There was a problem that interference noise occurred. This vortex is generated by a backflow in a direction opposite to the rotational direction of the crossflow fan occurring in the gap between the crossflow fan and the rear guider, and this backflow passing through the vicinity of the crossflow fan and rear guider. As a solution to this problem, there is a technique for suppressing noise by using an upper end protrusion that is provided toward the top of the cross-flow fan from a proximal portion that partitions the upstream and downstream areas at the rear of the cross-flow fan.
　ここで、図６～図８を用いて、従来の空気調和機の一例として、特許文献１について説明する。図６は、特許文献１に係る空気調和機１の縦断面図である。図７は、空気調和機１の上端突起部６ｂ近傍の縦断面構成を示す図である。図８は、空気調和機１の上端突起部６ｂ近傍の空気の流れを示す流線図である。 Here, Patent Document 1 will be described as an example of a conventional air conditioner using FIGS. 6 to 8. FIG. 6 is a longitudinal sectional view of the air conditioner 1 according to Patent Document 1. FIG. 7 is a diagram showing a longitudinal cross-sectional configuration of the vicinity of the upper end protrusion 6b of the air conditioner 1. FIG. 8 is a streamline diagram showing the flow of air near the upper end protrusion 6b of the air conditioner 1.
　図６を用いて特許文献１に開示されている空気調和機１の構造を説明する。空気調和機１は、吹出口２と吸込口３とを連通する送風路４を備える。空気調和機１は、送風路４内にクロスフローファン５とリアガイダ６とスタビライザ７と、クロスフローファン５の前面側に前面熱交換器８、クロスフローファンの５の背面側に背面熱交換器９を備える。クロスフローファン５は複数のブレード５ａを備える。リアガイダ６は、クロスフローファン５に対向してクロスフローファン５と所定の距離で近接する近接部６ａを備える。クロスフローファン５は、近接部６ａから更に背面熱交換器９の上部側へ向かって延設された上端突起部６ｂを備える。 The structure of the air conditioner 1 disclosed in Patent Document 1 will be explained using FIG. 6. The air conditioner 1 includes an air passage 4 that communicates an air outlet 2 and an air inlet 3 with each other. The air conditioner 1 includes a cross flow fan 5, a rear guider 6, and a stabilizer 7 in the air passage 4, a front heat exchanger 8 on the front side of the cross flow fan 5, and a rear heat exchanger on the back side of the cross flow fan 5. Equipped with 9. The crossflow fan 5 includes a plurality of blades 5a. The rear guider 6 includes a proximal portion 6a that faces the cross-flow fan 5 and approaches the cross-flow fan 5 at a predetermined distance. The crossflow fan 5 includes an upper end protrusion 6b extending from the proximal portion 6a toward the upper side of the back heat exchanger 9.
　図７を用いて特許文献１に開示されている空気調和機１の空気の流れを説明する。上端突起部６ｂは上端突起部６ｂの上端６ｃと、上端突起部６ｂの背面熱交換器９に対向する面６ｄと、上端突起部６ｂのクロスフローファン５に対向する面６ｅを備える。背面熱交換器９における上端突起部６ｂの上端６ｃ下方に位置する部分を通過した吸込気流は、上端突起部６ｂの背面熱交換器９に対向する面６ｄに沿って上方へ流動し、上端突起部６ｂの上端近傍でクロスフローファン５へ向けて旋回し、クロスフローファン５へ流入する。また、背面熱交換器９における上端突起部６ｂの上端より上方に位置する部分を通過した吸込気流は、上端突起部６ｂの上端近傍で、上端突起部６ｂの上端より下方に位置する背面熱交換器９を通過した吸込気流と合流して、クロスフローファン５へ流入する。クロスフローファン５と上端突起部６ｂのクロスフローファン５に対向する面６ｅとの間の空間に、クロスフローファン５の回転方向と逆方向に回転する逆流渦が生じる。空気調和機１では、この逆流渦を上端突起部６ｂのクロスフローファン５に対向する面６ｅに付着させ、逆流渦の渦中心を近接部６ａよりも上流に位置させることで、ブレード５ａとの干渉を緩和して騒音抑制できると目論んでいる。 The air flow in the air conditioner 1 disclosed in Patent Document 1 will be explained using FIG. 7. The upper end projection 6b includes an upper end 6c of the upper end projection 6b, a surface 6d of the upper end projection 6b facing the back heat exchanger 9, and a surface 6e of the upper end projection 6b facing the cross flow fan 5. The suction airflow that has passed through the portion of the upper end protrusion 6b located below the upper end 6c of the back heat exchanger 9 flows upward along the surface 6d of the upper end protrusion 6b facing the back heat exchanger 9, and flows upward through the upper end protrusion 6b. It turns toward the cross-flow fan 5 near the upper end of the portion 6b and flows into the cross-flow fan 5. In addition, the suction airflow that has passed through the portion of the back heat exchanger 9 located above the upper end of the upper end protrusion 6b is transferred to the back heat exchanger located near the upper end of the upper end protrusion 6b and below the upper end of the upper end protrusion 6b. It merges with the suction airflow that has passed through the device 9 and flows into the crossflow fan 5. A counterflow vortex that rotates in a direction opposite to the rotational direction of the crossflow fan 5 is generated in a space between the crossflow fan 5 and the surface 6e of the upper end protrusion 6b that faces the crossflow fan 5. In the air conditioner 1, this backflow vortex is attached to the surface 6e of the upper end protrusion 6b facing the crossflow fan 5, and the vortex center of the backflow vortex is located upstream of the adjacent portion 6a, thereby preventing contact with the blades 5a. The aim is to reduce interference and suppress noise.
　次に、図８を用いて特許文献１に開示されている空気調和機１の上端突起部６ｂ近傍の空気の流れを説明する。図８において、実線は気流の流線を示し、コンター（ｃｏｎｔｏｕｒ）は気流の渦粘性係数を示している。上端突起部６ｂはクロスフローファン５の回転軸に平行な長手方向に一様な形状をしている。クロスフローファン５の回転軸に垂直な断面における、上端突起部６ｂの上端の断面形状は、上端突起部６ｂの背面熱交換器９に対向する面と上端突起部６ｂのクロスフローファン５に対向する面とに正接する円弧で形成されている。クロスフローファン５と上端突起部６ｂのクロスフローファン５に対向する面との間の空間に生じ、クロスフローファン５の回転方向と逆方向に回転する逆流渦が、上端突起部６ｂの円弧に沿って上端突起部６ｂの背面熱交換器９に対向する面に向かい流動する。また、上端突起部６ｂの上端より下方に位置する背面熱交換器９を通過した吸込気流は、上端突起部６ｂの背面熱交換器９に対向する面に沿って上方へ流動し、上端突起部６ｂの円弧に沿って上端突起部６ｂのクロスフローファン５に対向する面に向かい流動する。そして、逆流渦と吸込気流とが、上端突起部６ｂの上端近傍で衝突し、乱れた気流となりクロスフローファン５に流入する。気流のクロスフローファン５への流入の際に、ブレード５ａが乱れた気流を横切るため、ブレード５ａとブレード５ａの表面における吸込気流との間で摩擦損失が生じる、または干渉による騒音が生じる場合がある。このような場合には、空気調和機の送風性能が低下すること、具体的には吹出風量が低下する、ファンの入力電力が増加する、または騒音を抑制できないといった問題があることを発明者らは見出した。発明者らは当該問題を解決するために、本開示の主題を構成するに至った。 Next, the flow of air near the upper end protrusion 6b of the air conditioner 1 disclosed in Patent Document 1 will be described using FIG. 8. In FIG. 8, solid lines indicate streamlines of the airflow, and contours indicate the eddy viscosity coefficient of the airflow. The upper end protrusion 6b has a uniform shape in the longitudinal direction parallel to the rotation axis of the cross flow fan 5. The cross-sectional shape of the upper end of the upper end protrusion 6b in a cross section perpendicular to the rotation axis of the cross flow fan 5 is such that the surface of the upper end protrusion 6b facing the back heat exchanger 9 and the surface of the upper end protrusion 6b facing the cross flow fan 5 It is formed by an arc tangent to the surface. A countercurrent vortex, which is generated in the space between the crossflow fan 5 and the surface of the upper end protrusion 6b facing the crossflow fan 5 and rotates in a direction opposite to the rotational direction of the crossflow fan 5, flows into the arc of the upper end protrusion 6b. The liquid flows along the upper end protrusion 6b toward the surface facing the back heat exchanger 9. In addition, the suction airflow that has passed through the back heat exchanger 9 located below the upper end of the upper end protrusion 6b flows upward along the surface of the upper end protrusion 6b that faces the back heat exchanger 9, and The liquid flows along the circular arc 6b toward the surface of the upper end protrusion 6b that faces the crossflow fan 5. Then, the backflow vortex and the suction airflow collide near the upper end of the upper end protrusion 6b, resulting in a turbulent airflow that flows into the crossflow fan 5. When the airflow flows into the cross-flow fan 5, the blades 5a cross the turbulent airflow, so friction loss may occur between the blades 5a and the suction airflow on the surface of the blades 5a, or noise may occur due to interference. be. The inventors have found that in such cases, there are problems such as a decrease in the air blowing performance of the air conditioner, specifically a decrease in the blowout air volume, an increase in the input power of the fan, or an inability to suppress noise. found out. In order to solve the problem, the inventors came up with the subject matter of the present disclosure.
　本開示は、背面熱交換器を通過した吸込気流とクロスフローファンと上端突起部のクロスフローファンに対向する面との間の空間に生じる逆流渦との衝突を抑制し、クロスフローファンに流入する気流の乱れを改善することで送風性能の向上を可能とする空気調和機を提供する。 The present disclosure suppresses the collision between the suction airflow that has passed through the back heat exchanger and the backflow vortex generated in the space between the crossflow fan and the surface facing the crossflow fan of the upper end protrusion, and flows into the crossflow fan. To provide an air conditioner that can improve air blowing performance by improving airflow turbulence.
　以下、図面を参照しながら、実施の形態を詳細に説明する。但し、必要以上に詳細な説明は省略する場合がある。例えば、既によく知られた事項の詳細説明、または、実質的に同一の構成に対する重複説明を省略する場合がある。これは、以下の説明が必要以上に冗長になるのを避け、当業者の理解を容易にするためである。 Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed explanation than necessary may be omitted. For example, detailed explanations of well-known matters or redundant explanations of substantially the same configurations may be omitted. This is to avoid making the following description unnecessarily redundant and to facilitate understanding by those skilled in the art.
　なお、添付図面および以下の説明は、当業者が本開示を十分に理解するために提供されるのであって、これらにより請求の範囲に記載の主題を限定することを意図していない。 The accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter recited in the claims.
　（実施の形態１）
　以下、図１～図３を用いて、実施の形態１の空気調和機１００について説明する。図１は、本開示の実施の形態１における空気調和機１００の縦断面図である。図２は、空気調和機１００の上端突起部１０５ｂ近傍の縦断面構成を示す図である。図３は、空気調和機１００の上端突起部１０５ｂ近傍の空気の流れを示す流線図である。なお、本実施の形態においては、図１における左側を前面側、右側を背面側として説明する。 (Embodiment 1)
The air conditioner 100 of the first embodiment will be described below with reference to FIGS. 1 to 3. FIG. 1 is a longitudinal cross-sectional view of an air conditioner 100 in Embodiment 1 of the present disclosure. FIG. 2 is a diagram showing a vertical cross-sectional configuration of the vicinity of the upper end protrusion 105b of the air conditioner 100. FIG. 3 is a streamline diagram showing the flow of air near the upper end protrusion 105b of the air conditioner 100. In this embodiment, the left side in FIG. 1 will be described as the front side and the right side as the back side.
　［１－１．構成］
　図１において、空気調和機１００は、吸込口１０１と、吹出口１０２を有する本体ケーシング１０３と、スタビライザ１０４と、リアガイダ１０５と、クロスフローファン１０６と、熱交換器１０７とを備えている。 [1-1. composition]
In FIG. 1, an air conditioner 100 includes a main body casing 103 having an inlet 101 and an outlet 102, a stabilizer 104, a rear guider 105, a cross flow fan 106, and a heat exchanger 107.
　リアガイダ１０５は、近接部１０５ａと、上端突起部１０５ｂとを有する。近接部１０５ａは、クロスフローファン１０６に対向してクロスフローファン１０６と所定の距離で近接する部分である。上端突起部１０５ｂは、近接部１０５ａから上方へ向かって延設された部分である。リアガイダ１０５はクロスフローファン１０６と、後述する背面熱交換器１０７ｂとの間に配置されている。 The rear guider 105 has a proximal portion 105a and an upper end protrusion 105b. The proximal portion 105a is a portion that faces the cross-flow fan 106 and is close to the cross-flow fan 106 at a predetermined distance. The upper end protrusion 105b is a portion extending upward from the proximal portion 105a. The rear guider 105 is arranged between the crossflow fan 106 and a backside heat exchanger 107b, which will be described later.
　クロスフローファン１０６は、回転軸と、円筒状に配置された複数のブレード１０６ａを有する。 The cross flow fan 106 has a rotating shaft and a plurality of blades 106a arranged in a cylindrical shape.
　熱交換器１０７は、前面熱交換器１０７ａと、背面熱交換器１０７ｂとで構成される。熱交換器１０７は、補助熱交換器を含んでもよい。前面熱交換器１０７ａは、クロスフローファン１０６の前面側に配置される。背面熱交換器１０７ｂは、クロスフローファン１０６の背面側に配置される。補助熱交換器を有する場合、補助熱交換器は、例えば、背面熱交換器１０７ｂにおける、クロスフローファン１０６と背面熱交換器１０７ｂの対面する面とは反対側の面に配置される。言い換えると、補助熱交換器は背面熱交換器１０７ｂにおける、クロスフローファン回転時に吸込口１０１から流入する空気の上流側の面に配置される。 The heat exchanger 107 is composed of a front heat exchanger 107a and a back heat exchanger 107b. Heat exchanger 107 may include an auxiliary heat exchanger. The front heat exchanger 107a is arranged on the front side of the cross flow fan 106. The back heat exchanger 107b is arranged on the back side of the cross flow fan 106. When an auxiliary heat exchanger is provided, the auxiliary heat exchanger is arranged, for example, on the surface of the rear heat exchanger 107b opposite to the surface where the cross flow fan 106 and the rear heat exchanger 107b face each other. In other words, the auxiliary heat exchanger is arranged on the surface of the back heat exchanger 107b on the upstream side of the air flowing in from the suction port 101 when the crossflow fan rotates.
　また、熱交換器１０７は、複数のフィン１０７ｃと、それら複数のフィン１０７ｃを貫通する複数の伝熱管１０７ｄとを備える。各伝熱管１０７ｄの外径Ｄｔは５ｍｍ以下であり、例えば本実施の形態ではＤｔ＝５ｍｍである。 Furthermore, the heat exchanger 107 includes a plurality of fins 107c and a plurality of heat transfer tubes 107d passing through the plurality of fins 107c. The outer diameter Dt of each heat exchanger tube 107d is 5 mm or less, and for example, in this embodiment, Dt=5 mm.
　次に、図２において、リアガイダ１０５の近接部１０５ａおよび上端突起部１０５ｂの詳細形状について説明する。近接部１０５ａ上のクロスフローファン１０６と最短距離となる点を近接点Ａとする。背面熱交換器１０７ｂの下流面に垂直な直線を直線Ｘとする。上端突起部１０５ｂは直線Ｘと外接する円弧部１０５ｃを有し、直線Ｘと円弧部１０５ｃの接点を先端点Ｂとする。先端点Ｂは上端突起部の中心線Ｗよりもクロスフローファン１０６側に位置する。上端突起部１０５ｂは、円弧部１０５ｃの直径をＤとし、上端突起部１０５ｂの厚さをＴとした時にＤ／Ｔ＜０．６となるように構成されている。 Next, referring to FIG. 2, detailed shapes of the proximal portion 105a and the upper end protrusion 105b of the rear guider 105 will be described. A point on the proximal portion 105a that is the shortest distance from the cross flow fan 106 is defined as a proximate point A. A straight line X is a straight line perpendicular to the downstream surface of the back heat exchanger 107b. The upper end protrusion 105b has a circular arc portion 105c that circumscribes the straight line X, and the point of contact between the straight line X and the circular arc portion 105c is a tip point B. The tip point B is located closer to the cross flow fan 106 than the center line W of the upper end protrusion. The upper end protrusion 105b is configured such that D/T<0.6, where D is the diameter of the arcuate portion 105c and T is the thickness of the upper end protrusion 105b.
　ここで、本実施の形態において上端突起部の中心線Ｗと上端突起部１０５ｂの厚さＴを以下のように定める。近接点Ａと先端点Ｂとを結ぶ直線を直線Ｙとし、直線Ｙの長さをＬとする。直線Ｙ上にあって先端点Ｂからの距離をＫとした時にＫ＝０．２５×Ｌとなる点を点Ｐとする。上端突起部１０５ｂのクロスフローファン１０６に対向する面１０５ｆ上にあって点Ｐから上端突起部１０５ｂのクロスフローファン１０６に対向する面１０５ｆに最短距離となる点を点Ｑとする。上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅ上にあって点Ｑから上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅに最短距離となる点を点Ｒとする。点Ｑと点Ｒとを結ぶ直線を直線Ｚとする。直線Ｚの中点を通り直線Ｚに直交する直線を、上端突起部の中心線Ｗとする。直線Ｚ上の線分ＱＲの長さを上端突起部１０５ｂの厚さＴとする。 Here, in this embodiment, the center line W of the upper end protrusion and the thickness T of the upper end protrusion 105b are determined as follows. Let the straight line connecting the proximal point A and the tip point B be a straight line Y, and let the length of the straight line Y be L. A point on the straight line Y where K=0.25×L is defined as a point P when the distance from the tip point B is K. Point Q is a point on the surface 105f of the upper end protrusion 105b facing the cross flow fan 106, which is the shortest distance from point P to the surface 105f of the upper end projection 105b facing the cross flow fan 106. Point R is a point on the surface 105e of the upper end protrusion 105b facing the rear heat exchanger 107b, which is the shortest distance from point Q to the surface 105e of the upper end projection 105b facing the rear heat exchanger 107b. Let the straight line connecting point Q and point R be straight line Z. A straight line passing through the midpoint of the straight line Z and perpendicular to the straight line Z is defined as the center line W of the upper end protrusion. Let the length of the line segment QR on the straight line Z be the thickness T of the upper end protrusion 105b.
　また、上端突起部１０５ｂは、円弧部１０５ｃと正接して背面熱交換器１０７ｂに対向する平面部１０５ｄを有する。上端突起部１０５ｂは、平面部１０５ｄの長さをＵとした時にＵ／Ｔ＜１．０となるように構成されている。 Furthermore, the upper end protrusion 105b has a flat portion 105d that is tangential to the arcuate portion 105c and faces the back heat exchanger 107b. The upper end protrusion 105b is configured such that U/T<1.0, where U is the length of the flat portion 105d.
　［１－２．動作］
　以上のように構成された空気調和機１００について、図３を用いてその動作を以下説明する。 [1-2. motion]
The operation of the air conditioner 100 configured as described above will be described below using FIG. 3.
　空気調和機１００において、クロスフローファン１０６が回転することにより、室内空気は吸込口１０１から本体ケーシング１０３内へ吸い込まれる。本体ケーシング１０３内へ吸い込まれた室内空気は、前面熱交換器１０７ａおよび背面熱交換器１０７ｂを通過してクロスフローファン１０６に流入し、吹出口１０２から室内空間へ吹き出される。なお、図１～図３において、クロスフローファン１０６は右回りに回転する。 In the air conditioner 100, when the cross flow fan 106 rotates, indoor air is sucked into the main body casing 103 from the suction port 101. The indoor air sucked into the main body casing 103 passes through the front heat exchanger 107a and the back heat exchanger 107b, flows into the cross flow fan 106, and is blown out from the outlet 102 into the indoor space. Note that in FIGS. 1 to 3, the cross flow fan 106 rotates clockwise.
　クロスフローファン１０６の回転により背面熱交換器１０７ｂにおける上端突起部１０５ｂの上端より下方に位置する部分を通過した吸込気流は、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅに沿って上方へ流動し、上端突起部１０５ｂの上端近傍で、クロスフローファン１０６へ向けて旋回し、クロスフローファン１０６へ流入する。また、背面熱交換器１０７ｂにおける上端突起部１０５ｂの上端より上方に位置する部分を通過する吸込気流は、上端突起部１０５ｂの上端近傍で、背面熱交換器１０７ｂにおける上端突起部１０５ｂの上端より下方に位置する部分を通過した吸込気流と合流して、クロスフローファン１０６へ流入する。クロスフローファン１０６と上端突起部１０５ｂとの間の空間に、クロスフローファン１０６の回転方向と逆方向に回転する逆流渦が生じる。逆流渦は上端突起部１０５ｂのクロスフローファン１０６に対向する面１０５ｆに付着し、逆流渦の渦中心が近接部１０５ａよりも上方に位置する。 Due to the rotation of the crossflow fan 106, the suction airflow that has passed through the portion of the rear heat exchanger 107b located below the upper end of the upper end protrusion 105b is caused to flow along the surface 105e of the upper end protrusion 105b facing the rear heat exchanger 107b. It flows upward, turns toward the cross-flow fan 106 near the upper end of the upper end protrusion 105b, and flows into the cross-flow fan 106. In addition, the suction airflow passing through the portion located above the upper end of the upper end protrusion 105b in the back heat exchanger 107b is near the upper end of the upper end protrusion 105b, and is lower than the upper end of the upper end protrusion 105b in the back heat exchanger 107b. It merges with the suction airflow that has passed through the portion located at , and flows into the crossflow fan 106 . A countercurrent vortex that rotates in a direction opposite to the rotational direction of the crossflow fan 106 is generated in the space between the crossflow fan 106 and the upper end protrusion 105b. The backflow vortex adheres to the surface 105f of the upper end protrusion 105b facing the crossflow fan 106, and the vortex center of the backflow vortex is located above the proximal portion 105a.
　背面熱交換器１０７ｂにおける上端突起部１０５ｂの上端より下方に位置する部分を通過する吸込気流は、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅに沿って上方へ流動し、平面部１０５ｄに到達する。背面熱交換器１０７ｂにおける上端突起部１０５ｂの上端より下方に位置する部分を通過する吸込気流は、吸込気流が持つ慣性力により、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅと平面部１０５ｄとの連接点Ｓで上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅから剥離する。 The suction airflow passing through the portion of the back heat exchanger 107b that is located below the upper end of the upper end protrusion 105b flows upward along the surface 105e of the upper end protrusion 105b that faces the back heat exchanger 107b, and flows upward through the plane portion. Reach 105d. Due to the inertial force of the suction airflow, the suction airflow passing through the portion of the back heat exchanger 107b located below the upper end of the upper end protrusion 105b is flat with the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b. The upper end protrusion 105b is separated from the surface 105e facing the back heat exchanger 107b at the connection point S with the portion 105d.
　本実施の形態では、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅと平面部１０５ｄは連続しておらず、また、平面部１０５ｄの長さＵは上端突起部１０５ｂの厚さＴに対して、Ｕ／Ｔ＜１．０となる。このことから、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅから剥離した吸込気流は、平面部１０５ｄに再付着せず、クロスフローファン１０６へ流入する流れに合流する。 In this embodiment, the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b and the flat part 105d are not continuous, and the length U of the flat part 105d is equal to the thickness T of the upper end protrusion 105b. , U/T<1.0. For this reason, the suction airflow separated from the surface 105e of the upper end protrusion 105b facing the back surface heat exchanger 107b does not re-adhere to the flat portion 105d, but joins the flow flowing into the cross-flow fan 106.
　逆流渦は、上端突起部１０５ｂのクロスフローファン１０６に対向する面１０５ｆに沿って上方へ流動し、円弧部１０５ｃに達する。本実施の形態では、円弧部１０５ｃは、先端点Ｂが上端突起部１０５ｂの中心線Ｗよりもクロスフローファン１０６側に位置し、また、円弧部１０５ｃの直径Ｄは上端突起部１０５ｂの厚さＴに対してＤ／Ｔ＜０.６となる。このことから、逆流渦は円弧部１０５ｃに沿って流れようとする際に偏向半径が小さく急偏向することになるが、逆流渦が持つ慣性力により、円弧部１０５ｃから剥離してクロスフローファン１０６へ流入する流れに合流する。また、先端点Ｂは上端突起部１０５ｂの中心線Ｗよりもクロスフローファン１０６側に位置することから、逆流渦は、クロスフローファン１０６に近い位置で円弧部１０５ｃから剥離してクロスフローファン１０６へ流入する流れに合流する。 The backflow vortex flows upward along the surface 105f of the upper end protrusion 105b facing the crossflow fan 106, and reaches the arcuate portion 105c. In this embodiment, the tip point B of the arcuate portion 105c is located closer to the crossflow fan 106 than the centerline W of the upper end protrusion 105b, and the diameter D of the arcuate portion 105c is equal to the thickness of the upper end protrusion 105b. D/T<0.6 for T. Therefore, when the backflow vortex tries to flow along the circular arc portion 105c, the deflection radius is small and it is deflected sharply, but due to the inertia of the backflow vortex, it separates from the circular arc portion 105c and the cross flow fan 105 joins the flow flowing into the Furthermore, since the tip point B is located closer to the cross-flow fan 106 than the center line W of the upper end protrusion 105b, the backflow vortex separates from the arcuate portion 105c at a position close to the cross-flow fan 106, and the cross-flow fan 106 joins the flow flowing into the
　図４Ａ～図５Ｂを用いて、Ｄ／Ｔの数値に対する送風性能の向上を詳細に説明する。図４Ａは、空気調和機１００のＤ／Ｔに対する吹出風量比の変化および上端突起部１０５ｂの形状を示す図である。図４Ｂは、空気調和機１００のＤ／Ｔに対する吹出風量比の変化を示すグラフである。図５Ａは、空気調和機１００のＤ／Ｔに対するクロスフローファン１０６の入力変化（入力電力の変化）および上端突起部１０５ｂの形状を示す図である。図５Ｂは、空気調和機１００のＤ／Ｔに対するクロスフローファン１０６の入力変化（入力電力の変化）を示すグラフである。 The improvement in air blowing performance with respect to the value of D/T will be explained in detail using FIGS. 4A to 5B. FIG. 4A is a diagram showing changes in the blowout air volume ratio with respect to D/T of the air conditioner 100 and the shape of the upper end protrusion 105b. FIG. 4B is a graph showing changes in the blowout air volume ratio with respect to D/T of the air conditioner 100. FIG. 5A is a diagram showing the input change (change in input power) of the crossflow fan 106 with respect to the D/T of the air conditioner 100 and the shape of the upper end protrusion 105b. FIG. 5B is a graph showing a change in input to the crossflow fan 106 (change in input power) with respect to D/T of the air conditioner 100.
　まず、図４Ａおよび図４Ｂにおいて、Ｄ／Ｔに対する風量変化について説明する。図４Ａおよび図４Ｂは、数値解析によるＤ／Ｔをパラメータとして、空気調和機１００のクロスフローファン１０６の単位時間当たりの回転数を同一回転数とした時の風量比を示す。なお、図４Ａおよび図４Ｂの風量比は、Ｄ／Ｔ＝１.０の時の風量比を１００として示している。図４Ａでは、上段にＤ／Ｔの値、中段に風量比、下段に上端突起部１０５ｂの形状を示している。図４Ｂでは、横軸をＤ／Ｔ、縦軸をＤ／Ｔに対する風量比としている。Ｄ／Ｔを１から０.２７まで低下させたとすると、図４Ｂに示すように、Ｄ／Ｔが１.０から０.６までの間は急激に風量比が増加し、一方Ｄ／Ｔが０.６未満になると、風量比はほぼ一定の値を保つ。つまり、Ｄ／Ｔが１.０から０.６の間で急激に風量比は向上し、Ｄ／Ｔが０.６に達した時点で風量比が上限に達する。従ってＤ／Ｔが０.６未満であると、風量比が改善されて、送風性能が向上するといえる。 First, in FIGS. 4A and 4B, changes in air volume with respect to D/T will be described. 4A and 4B show the air volume ratio when the number of rotations per unit time of the cross flow fan 106 of the air conditioner 100 is set to the same number of rotations using D/T determined by numerical analysis as a parameter. Note that the air volume ratios in FIGS. 4A and 4B are shown assuming that the air volume ratio when D/T=1.0 is 100. In FIG. 4A, the value of D/T is shown in the upper row, the air volume ratio is shown in the middle row, and the shape of the upper end protrusion 105b is shown in the lower row. In FIG. 4B, the horizontal axis represents D/T, and the vertical axis represents the air volume ratio to D/T. Assuming that D/T is decreased from 1 to 0.27, as shown in Figure 4B, the air volume ratio increases rapidly between D/T 1.0 and 0.6, while D/T When it becomes less than 0.6, the air volume ratio maintains a substantially constant value. That is, the air volume ratio increases rapidly when D/T is between 1.0 and 0.6, and reaches the upper limit when D/T reaches 0.6. Therefore, it can be said that when D/T is less than 0.6, the air volume ratio is improved and the air blowing performance is improved.
　図５Ａおよび図５Ｂにおいて、Ｄ／Ｔに対する入力変化について説明する。図５Ａおよび図５Ｂは、数値解析によるＤ／Ｔをパラメータとして、空気調和機１００から吹き出される風量を同一吹出風量とした時の入力比を示す。なお、図５Ａおよび図５Ｂの入力比は、Ｄ／Ｔ＝１.０の時の入力比を１００として示している。図５Ａでは、上段にＤ／Ｔの値、中段に入力比、下段に上端突起部１０５ｂの形状を示している。図５Ｂでは、横軸をＤ／Ｔ、縦軸を入力比としている。Ｄ／Ｔを１.０から０.２７まで低下させたとすると、図５Ｂに示すように、Ｄ／Ｔが１.０から０.６までの間では入力比はほぼ一定の値を保ち、Ｄ／Ｔが０.６未満になると急激に入力比が低下する。つまり、Ｄ／Ｔが１.０から０.６までは入力比の向上の効果は少なく、Ｄ／Ｔの値が０.６を境にして０．６未満になると入力比の改善の効果があるといえる。つまり、Ｄ／Ｔが０.６未満になると、入力比が急激に低下して、送風性能が向上するといえる。さらに、図５Ｂに示すように、Ｄ／Ｔ＝０.５では、Ｄ／Ｔ＝１.０と比較して入力比を０.５％低減できることがわかる。従って、Ｄ／Ｔが０.５以下であると入力比はより改善されて、さらに送風性能が向上するといえる。 Input changes to the D/T will be explained with reference to FIGS. 5A and 5B. 5A and 5B show input ratios when the air volume blown out from the air conditioner 100 is set to the same air volume using D/T determined by numerical analysis as a parameter. Note that the input ratios in FIGS. 5A and 5B are shown assuming that the input ratio when D/T=1.0 is 100. In FIG. 5A, the value of D/T is shown in the upper row, the input ratio is shown in the middle row, and the shape of the upper end protrusion 105b is shown in the lower row. In FIG. 5B, the horizontal axis represents D/T, and the vertical axis represents input ratio. Assuming that D/T is decreased from 1.0 to 0.27, as shown in Figure 5B, when D/T is between 1.0 and 0.6, the input ratio remains almost constant, and D When /T becomes less than 0.6, the input ratio rapidly decreases. In other words, the effect of improving the input ratio is small when D/T is from 1.0 to 0.6, and when the value of D/T becomes less than 0.6 after reaching 0.6, the effect of improving the input ratio becomes less effective. It can be said that there is. In other words, it can be said that when D/T becomes less than 0.6, the input ratio decreases rapidly and the air blowing performance improves. Further, as shown in FIG. 5B, it can be seen that when D/T=0.5, the input ratio can be reduced by 0.5% compared to D/T=1.0. Therefore, it can be said that when D/T is 0.5 or less, the input ratio is further improved and the air blowing performance is further improved.
　［１－３．効果等］
　以上のように、本実施の形態において、空気調和機１００は、吸込口１０１と、吹出口１０２を有する本体ケーシング１０３と、スタビライザ１０４と、リアガイダ１０５と、クロスフローファン１０６と、前面熱交換器１０７ａと、背面熱交換器１０７ｂとを備えている。リアガイダ１０５は、クロスフローファン１０６に対向し、かつ所定の寸法（距離）でクロスフローファン１０６と近接する近接部１０５ａと、近接部１０５ａから上方へ向かって延設された上端突起部１０５ｂとを有する。上端突起部１０５ｂは、円弧部１０５ｃを有し、円弧部１０５ｃの先端点Ｂが上端突起部１０５ｂの中心線Ｗよりもクロスフローファン１０６側に位置する。上端突起部１０５ｂは、円弧部１０５ｃの直径をＤとし、上端突起部１０５ｂの厚さをＴとした時に、Ｄ／Ｔ＜０．６となるように構成されている。 [1-3. Effects, etc.]
As described above, in this embodiment, the air conditioner 100 includes a main body casing 103 having an inlet 101 and an outlet 102, a stabilizer 104, a rear guider 105, a cross flow fan 106, and a front heat exchanger. 107a, and a back heat exchanger 107b. The rear guider 105 includes a proximal portion 105a that faces the cross-flow fan 106 and is close to the cross-flow fan 106 by a predetermined dimension (distance), and an upper end protrusion 105b that extends upward from the proximal portion 105a. have The upper end protrusion 105b has an arcuate portion 105c, and the tip point B of the arcuate portion 105c is located closer to the cross flow fan 106 than the centerline W of the upper end protrusion 105b. The upper end protrusion 105b is configured so that D/T<0.6, where D is the diameter of the arcuate portion 105c and T is the thickness of the upper end protrusion 105b.
　円弧部１０５ｃは、先端点Ｂが上端突起部１０５ｂの中心線Ｗよりもクロスフローファン１０６側に位置し、Ｄ／Ｔ＜０.６となることから、発生した逆流渦は円弧部１０５ｃに沿って流れようとする際に偏向半径が小さく急偏向することになるが、逆流渦は逆流渦が持つ慣性力により円弧部１０５ｃから剥離して、クロスフローファン１０６へ流入する流れに合流する。また、先端点Ｂは上端突起部１０５ｂの中心線Ｗよりもクロスフローファン１０６側に位置することから、逆流渦は、クロスフローファン１０６に近い位置で円弧部１０５ｃから剥離してクロスフローファン１０６へ流入する流れに合流する。 The tip point B of the arcuate portion 105c is located closer to the crossflow fan 106 than the centerline W of the upper end protrusion 105b, and D/T<0.6, so the generated backflow vortex flows along the arcuate portion 105c. When attempting to flow, the deflection radius is small and the flow is abruptly deflected, but the reverse flow vortex separates from the circular arc portion 105c due to the inertial force of the reverse flow vortex and joins the flow flowing into the cross flow fan 106. Furthermore, since the tip point B is located closer to the cross-flow fan 106 than the center line W of the upper end protrusion 105b, the backflow vortex separates from the arcuate portion 105c at a position close to the cross-flow fan 106, and the cross-flow fan 106 joins the flow flowing into the
　これにより、本実施の形態の空気調和機１００では、上端突起部１０５ｂの上端において、逆流渦が上端突起部１０５ｂの円弧部１０５ｃに沿って上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅに向かって流動することが抑制される。従って、逆流渦と吸込気流との衝突の発生を抑制又は緩和することができる。そのため、クロスフローファン１０６に流入する気流の乱れが改善されることにより、クロスフローファン１０６の吹出風量を増加させ、クロスフローファン１０６への入力電力を低減することができる。また、クロスフローファン１０６に流入する気流の乱れが改善されることにより、騒音を抑制することができる。 As a result, in the air conditioner 100 of the present embodiment, at the upper end of the upper end protrusion 105b, the backflow vortex flows along the arcuate portion 105c of the upper end protrusion 105b to the surface of the upper end protrusion 105b facing the back heat exchanger 107b. Flowing toward 105e is suppressed. Therefore, the occurrence of collision between the backflow vortex and the suction airflow can be suppressed or alleviated. Therefore, by improving the turbulence of the airflow flowing into the cross-flow fan 106, the amount of air blown from the cross-flow fan 106 can be increased, and the power input to the cross-flow fan 106 can be reduced. Moreover, noise can be suppressed by improving the turbulence of the airflow flowing into the cross-flow fan 106.
　上端突起部１０５ｂは、平面部１０５ｄを有し、平面部１０５ｄの長さをＵとした時にＵ／Ｔ＜１.０となるように構成されると好ましい。このように構成すれば、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅと平面部１０５ｄとは連続しないように接続される。これにより、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅと平面部１０５ｄ平面部との連接点Ｓにおいて、上端突起部１０５ｂの上端より下方に位置する背面熱交換器１０７ｂを通過する吸込気流は、吸込気流が持つ慣性力により、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅから剥離する。平面部１０５ｄがＵ／Ｔ＜１.０となるように構成されることから、上端突起部１０５ｂの背面熱交換器１０７ｂに対向する面１０５ｅから剥離した吸込気流は、平面部１０５ｄに再付着せず、クロスフローファン１０６へ流入する流れに合流する。 It is preferable that the upper end protrusion 105b has a flat portion 105d, and is configured such that U/T<1.0, where U is the length of the flat portion 105d. With this configuration, the surface 105e of the upper end protrusion 105b facing the back surface heat exchanger 107b and the plane portion 105d are connected so as not to be continuous. As a result, at the connection point S between the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b and the plane part 105d, the heat passes through the back heat exchanger 107b located below the upper end of the upper end protrusion 105b. The suction airflow separates from the surface 105e of the upper end protrusion 105b facing the back surface heat exchanger 107b due to the inertial force of the suction airflow. Since the flat portion 105d is configured such that U/T<1.0, the suction airflow separated from the surface 105e of the upper end protrusion 105b facing the back heat exchanger 107b is not reattached to the flat portion 105d. First, it joins the flow flowing into the crossflow fan 106.
　これにより、空気調和機１００は、上端突起部１０５ｂの上端において、吸込気流が上端突起部１０５ｂの円弧部１０５ｃに沿って上端突起部１０５ｂのクロスフローファン１０６に対向する面１０５ｆに向かって流動することを抑制し、逆流渦との衝突の発生を抑制又は緩和することができる。そのため、クロスフローファン１０６に流入する気流の乱れが改善されることにより、クロスフローファン１０６における入力電力を低減し、騒音を抑制することができる。 Thereby, in the air conditioner 100, at the upper end of the upper end protrusion 105b, the suction airflow flows toward the surface 105f of the upper end protrusion 105b facing the cross flow fan 106 along the arcuate part 105c of the upper end protrusion 105b. It is possible to suppress or alleviate the occurrence of collision with a backflow vortex. Therefore, by improving the turbulence of the airflow flowing into the cross-flow fan 106, the input power to the cross-flow fan 106 can be reduced and noise can be suppressed.
　本実施の形態のように、伝熱管１０７ｄの外径ＤｔはＤｔ＝５ｍｍであってもよい。但し、本実施の形態で示す伝熱管１０７ｄの外径Ｄｔは一例に過ぎない。Ｄｔ≦５ｍｍを満たす伝熱管１０７ｄであればよい。 As in this embodiment, the outer diameter Dt of the heat exchanger tube 107d may be Dt=5 mm. However, the outer diameter Dt of the heat exchanger tube 107d shown in this embodiment is only an example. It is sufficient if the heat exchanger tube 107d satisfies Dt≦5mm.
　このように、空気調和機１００が、伝熱管１０７ｄの外径ＤｔをＤｔ＝５ｍｍとすることで圧力損失の軽減を図った背面熱交換器１０７ｂを備える場合にも、クロスフローファン１０６に流入する気流の乱れが改善されることにより、クロスフローファン１０６における吹出風量を増大させ、クロスフローファン１０６の入力電力を低減することができる。また、クロスフローファン１０６に流入する気流の乱れが改善されることにより、騒音を抑制することができる。 In this way, even when the air conditioner 100 includes the back heat exchanger 107b in which pressure loss is reduced by setting the outer diameter Dt of the heat transfer tube 107d to Dt = 5 mm, the amount of water flowing into the crossflow fan 106 By improving the turbulence of the airflow, the amount of air blown from the crossflow fan 106 can be increased, and the input power to the crossflow fan 106 can be reduced. Moreover, noise can be suppressed by improving the turbulence of the airflow flowing into the cross-flow fan 106.
　なお、上述の実施の形態は、本開示における技術を例示するためのものであるから、請求の範囲またはその均等の範囲において種々の変更、置き換え、付加、省略などを行うことができる。 Note that the above-described embodiments are for illustrating the technology of the present disclosure, and therefore various changes, substitutions, additions, omissions, etc. can be made within the scope of the claims or their equivalents.
　本開示は、吸込気流とリアガイダの近接部上流で形成される逆流渦との衝突の発生を抑制又は緩和し、クロスフローファンに流入する気流の乱れを改善することで送風性能を向上できる。従って、家庭用空調や業務用空調に好適に用いることができる。 The present disclosure can improve air blowing performance by suppressing or mitigating the collision between the intake airflow and the backflow vortex formed upstream of the vicinity of the rear guider, and improving the turbulence of the airflow flowing into the crossflow fan. Therefore, it can be suitably used for home air conditioning and commercial air conditioning.
　１００　　空気調和機
　１０１　　吸込口
　１０２　　吹出口
　１０３　　本体ケーシング
　１０４　　スタビライザ
　１０５　　リアガイダ
　１０５ａ　近接部
　１０５ｂ　上端突起部
　１０５ｃ　円弧部
　１０５ｄ　平面部
　１０６　　クロスフローファン
　１０６ａ　ブレード
　１０７　　熱交換器
　１０７ａ　前面熱交換器
　１０７ｂ　背面熱交換器
　１０７ｃ　フィン
　１０７ｄ　伝熱管 100 Air conditioner 101 Suction port 102 Air outlet 103 Main body casing 104 Stabilizer 105 Rear guider 105a Proximity portion 105b Upper end protrusion 105c Arc portion 105d Plane portion 106 Cross flow fan 106a Blade 107 Heat exchanger 107a Front heat exchanger 107b Rear heat exchanger 107c Fin 107d Heat exchanger tube

Claims (4)

  1. 　クロスフローファンと、
    　スタビライザと、
    　リアガイダと、
    　前記クロスフローファンの前面側に配置される前面熱交換器と、
    　前記クロスフローファンの背面側に配置される背面熱交換器と、を備え、
    　前記リアガイダは、
    　　前記クロスフローファンに対向し、かつ所定の距離で前記クロスフローファンと近接して配置される近接部と、
    　　前記近接部から上方へ向かって延出した上端突起部と、を備え、
    　前記クロスフローファンの回転軸と直交する前記リアガイダの断面視において、
    　　前記リアガイダの前記上端突起部は、前記背面熱交換器の下流面に垂直な直線Ｘと外接する円弧部を有し、
    　　前記円弧部が前記直線Ｘと外接する接点を先端点Ｂとしたときに、前記先端点Ｂは前記上端突起部の中心線よりも前記クロスフローファン側に位置し、前記円弧部の直径をＤとし前記上端突起部の厚さをＴとしたときにＤ／Ｔ＜０.６となる、
    空気調和機。     cross flow fan,
    stabilizer and
    rear guider and
    a front heat exchanger disposed on the front side of the cross flow fan;
    a rear heat exchanger disposed on the rear side of the cross flow fan,
    The rear guider is
    a proximal part facing the cross-flow fan and disposed close to the cross-flow fan at a predetermined distance;
    an upper end protrusion extending upward from the proximal portion;
    In a cross-sectional view of the rear guider perpendicular to the rotation axis of the cross flow fan,
    The upper end protrusion of the rear guider has a circular arc portion that circumscribes a straight line X perpendicular to the downstream surface of the rear heat exchanger,
    When the point of contact of the circular arc section with the straight line When the thickness of the upper end protrusion is T, D/T<0.6.
    Air conditioner.
  2. 　Ｄ／Ｔ≦０.５となる、
    請求項１に記載の空気調和機。     D/T≦0.5,
    The air conditioner according to claim 1.
  3. 　前記リアガイダの前記断面視において、前記上端突起部は、前記円弧部と正接して前記背面熱交換器に対向する平面部を有し、
    　前記平面部の長さをＵとしたときにＵ／Ｔ＜１.０となる、
    請求項１または２に記載の空気調和機。     In the cross-sectional view of the rear guider, the upper end protrusion has a flat part that is tangential to the arcuate part and faces the back heat exchanger,
    When the length of the flat part is U, U/T<1.0,
    The air conditioner according to claim 1 or 2.
  4. 　前記背面熱交換器は、フィンと、前記フィンを貫通する伝熱管と、を備え、
    　前記伝熱管の外径ＤｔがＤｔ≦５ｍｍとなる、
    請求項１～３のいずれか一項に記載の空気調和機。     The back heat exchanger includes fins and heat transfer tubes passing through the fins,
    The outer diameter Dt of the heat exchanger tube is Dt≦5 mm,
    The air conditioner according to any one of claims 1 to 3.
PCT/JP2023/009491 2022-03-22 2023-03-13 Air conditioner WO2023182025A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0861685A (en) * 1994-08-25 1996-03-08 Matsushita Electric Ind Co Ltd Indoor unit for air conditioner
JP2000291594A (en) * 1999-04-05 2000-10-17 Sharp Corp Cross flow fan
JP2001090689A (en) * 1999-09-24 2001-04-03 Daikin Ind Ltd Fan mechanism and air conditioner with the same
JP2014020243A (en) * 2012-07-17 2014-02-03 Panasonic Corp Cross flow air blowing device
WO2014050365A1 (en) * 2012-09-28 2014-04-03 ダイキン工業株式会社 Air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0861685A (en) * 1994-08-25 1996-03-08 Matsushita Electric Ind Co Ltd Indoor unit for air conditioner
JP2000291594A (en) * 1999-04-05 2000-10-17 Sharp Corp Cross flow fan
JP2001090689A (en) * 1999-09-24 2001-04-03 Daikin Ind Ltd Fan mechanism and air conditioner with the same
JP2014020243A (en) * 2012-07-17 2014-02-03 Panasonic Corp Cross flow air blowing device
WO2014050365A1 (en) * 2012-09-28 2014-04-03 ダイキン工業株式会社 Air conditioner

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