WO2023223383A1 - Cross flow fan, blowing device, and refrigeration cycle device - Google Patents

Cross flow fan, blowing device, and refrigeration cycle device Download PDF

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Publication number
WO2023223383A1
WO2023223383A1 PCT/JP2022/020363 JP2022020363W WO2023223383A1 WO 2023223383 A1 WO2023223383 A1 WO 2023223383A1 JP 2022020363 W JP2022020363 W JP 2022020363W WO 2023223383 A1 WO2023223383 A1 WO 2023223383A1
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Prior art keywords
blade
cross
flow fan
blades
region
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PCT/JP2022/020363
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French (fr)
Japanese (ja)
Inventor
惇司 河野
拓矢 寺本
奈穂 安達
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三菱電機株式会社
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Priority to PCT/JP2022/020363 priority Critical patent/WO2023223383A1/en
Publication of WO2023223383A1 publication Critical patent/WO2023223383A1/en

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    • 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

Definitions

  • the present disclosure relates to a crossflow fan, a blower device, and a refrigeration cycle device.
  • a fan has an inner edge part disposed on the inner circumferential side and an outer edge part disposed on the outer circumferential side, and includes a plurality of blade parts arranged at intervals in the circumferential direction, and the blade part has an inner edge part and an outer edge part arranged on the outer peripheral side.
  • a blade surface is formed that extends between the outer edge part and consists of a positive pressure surface located on the side in the rotation direction of the fan and a negative pressure surface located on the back side of the positive pressure surface, and as the fan rotates, A fluid flow occurs between the inner edge and the outer edge on the blade surface, and when the blade is cut by a plane perpendicular to the rotation axis of the fan, recesses are formed on the pressure and suction surfaces.
  • An object of the present invention is to provide a cross flow fan, a blower device, and a refrigeration cycle device that can suppress separation.
  • a cross flow fan includes a plurality of support members arranged at preset intervals in a rotation axis direction and having a circular or annular flat plate shape, and provided between adjacent support members, and a plurality of blades disposed near the outer periphery of the member and spaced apart in the circumferential direction, each of the blades having a positive pressure surface on the rotation direction side and a negative pressure surface on the counter rotation direction side.
  • the plurality of blades have at least one first blade
  • the pressure surface of the first blade includes a first blade including an outer peripheral end of the first blade in a cross section perpendicular to the rotation axis.
  • One region has a convex shape in the opposite rotational direction, and a second region including the inner circumferential end of the first blade has a convex shape in the rotational direction.
  • a blower device includes a crossflow fan configured as described above.
  • a refrigeration cycle device includes a cross-flow fan configured as described above, and a heat exchanger that performs heat exchange between a refrigerant and an air flow generated by the cross-flow fan.
  • the cross-flow fan, blower device, and refrigeration cycle device it is possible to suppress sudden turning of airflow after passing between the blades from the outer circumferential side of the impeller to the inner circumferential side, and to reduce ventilation resistance between the blades.
  • the effect is that it is possible to suppress the increase in airflow, and in turn, it is possible to suppress airflow separation from the blade surface.
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle device according to Embodiment 1.
  • FIG. 1 is a cross-sectional view showing the configuration of an indoor unit of an air conditioner that is an example of a refrigeration cycle device and a blower device according to Embodiment 1.
  • FIG. 1 is a front view of a cross flow fan according to Embodiment 1.
  • FIG. 3 is a cross-sectional view showing an example of an impeller of the cross flow fan according to the first embodiment.
  • FIG. 2 is an enlarged cross-sectional view of a main part of an example of an impeller of the cross flow fan according to the first embodiment.
  • FIG. 3 is a diagram showing airflow in an example of an impeller of the crossflow fan according to the first embodiment.
  • FIG. 3 is a sectional view showing another example of the impeller of the cross flow fan according to the first embodiment.
  • FIG. 3 is a sectional view showing another example of the impeller of the cross flow fan according to the first embodiment.
  • FIG. 7 is an enlarged sectional view of a main part showing another example of the impeller of the cross flow fan according to the first embodiment.
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle device.
  • FIG. 2 is a sectional view showing the configuration of an indoor unit of an air conditioner, which is an example of a refrigeration cycle device and a blower device.
  • FIG. 3 is a front view of the crossflow fan.
  • FIG. 4 is a sectional view showing an example of an impeller of a cross flow fan.
  • FIG. 5 is an enlarged sectional view of a main part of an example of an impeller of a cross flow fan.
  • FIG. 6 is a diagram showing airflow in an example of an impeller of a crossflow fan.
  • 7 and 8 are cross-sectional views showing other examples of the impeller of the cross flow fan.
  • FIG. 9 is an enlarged sectional view of a main part showing another example of an impeller of a cross flow fan.
  • FIG. 1 shows the configuration of an air conditioner as an example of a refrigeration cycle device equipped with a crossflow fan according to the present disclosure.
  • examples of the refrigeration cycle device including the crossflow fan according to the present disclosure include a showcase and the like.
  • the air conditioner has a function of blowing air. Therefore, the air conditioner described here is also an example of a blower device including a cross-flow fan according to the present disclosure.
  • examples of the blower device including the cross-flow fan according to the present disclosure include a circulator, a tower-type electric fan, and the like.
  • the air conditioner which is a refrigeration cycle device according to this embodiment, includes an indoor unit 10 and an outdoor unit 20.
  • the indoor unit 10 is installed inside a room to be air-conditioned, that is, indoors.
  • the outdoor unit 20 is installed outside the room, that is, outdoors.
  • the indoor unit 10 includes an indoor unit heat exchanger 11 and a cross flow fan 100.
  • the outdoor unit 20 includes an outdoor unit heat exchanger 21, an outdoor unit fan 22, a compressor 23, an expansion valve 24, and a four-way valve 25.
  • the indoor unit 10 and the outdoor unit 20 are connected by a refrigerant pipe 30.
  • the refrigerant pipe 30 is provided cyclically between the indoor unit heat exchanger 11 of the indoor unit 10 and the outdoor unit heat exchanger 21 of the outdoor unit 20.
  • a refrigerant is sealed inside the refrigerant pipe 30.
  • the refrigerant sealed in the refrigerant pipe 30 is, for example, difluoromethane (CH2F2:R32).
  • the refrigerant pipe 30 connects the indoor unit heat exchanger 11, the four-way valve 25, the compressor 23, the outdoor unit heat exchanger 21, and the expansion valve 24 in an annular manner. Therefore, a refrigerant circuit in which refrigerant circulates between the indoor heat exchanger 11 and the outdoor heat exchanger 21 is formed.
  • the compressor 23 is a device that compresses the supplied refrigerant to increase the pressure and temperature of the refrigerant.
  • the compressor 23 for example, a rotary compressor, a scroll compressor, a reciprocating compressor, etc. can be used.
  • the expansion valve 24 expands the refrigerant condensed in the outdoor unit heat exchanger 21 and reduces the pressure of the refrigerant.
  • the indoor heat exchanger 11 exchanges heat between the refrigerant that has flowed into the indoor heat exchanger 11 and the air surrounding the indoor heat exchanger 11.
  • the cross flow fan 100 blows indoor air so that it passes around the indoor unit heat exchanger 11, promotes heat exchange between the refrigerant and air in the indoor unit heat exchanger 11, and also promotes heat exchange. The heated or cooled air is sent back into the room.
  • the outdoor heat exchanger 21 exchanges heat between the refrigerant that has flowed into the outdoor heat exchanger 21 and the air around the outdoor heat exchanger 21 .
  • the outdoor unit fan 22 blows outdoor air so that it passes around the outdoor unit heat exchanger 21, and promotes heat exchange between the refrigerant and the air in the outdoor unit heat exchanger 21.
  • the refrigerant circuit configured in this manner exchanges heat between the refrigerant and air in each of the indoor unit heat exchanger 11 and the outdoor unit heat exchanger 21, thereby providing a connection between the indoor unit 10 and the outdoor unit 20. It works as a heat pump to move heat.
  • the circulation direction of the refrigerant in the refrigerant circuit can be reversed, and the air conditioner can be switched between cooling operation and heating operation.
  • the indoor unit 10 includes a housing 12.
  • the housing 12 is installed indoors. Inside the housing 12, an indoor unit heat exchanger 11 and a cross flow fan 100 are housed.
  • a suction port 13 is formed in the upper surface of the housing 12 .
  • the suction port 13 is an opening for taking air into the housing 12 from the outside.
  • An air outlet 14 is formed on the lower surface of the housing 12 .
  • the air outlet 14 is an opening for discharging air from the inside of the housing 12 to the outside.
  • An air path leading from the suction port 13 to the blowout port 14 is formed inside the housing 12 .
  • a filter 15 is installed in the suction port 13. The filter 15 is for removing relatively large particles, dirt, dust, etc. from the air entering the interior of the housing 12 from the suction port 13.
  • An indoor unit heat exchanger 11 is installed on the leeward side of the filter 15 in the air passage inside the housing 12.
  • the indoor unit heat exchanger 11 exchanges heat with the air flowing through the air path inside the housing 12 to heat or cool the air flowing through the air path. Whether the air is heated or cooled depends on whether the air conditioner is in heating mode or cooling mode.
  • a cross flow fan 100 is installed on the leeward side of the indoor unit heat exchanger 11 in the aforementioned air path.
  • the crossflow fan 100 is for generating an airflow from the suction port 13 toward the blowout port 14 in the air path inside the housing 12 .
  • a rear guide 17 is provided on the rear side of the impeller of the cross flow fan 100 in the housing 12. Further, a stabilizer 18 is provided on the front side of the impeller of the cross flow fan 100 inside the housing 12.
  • the rear guide 17 is arranged in a spiral shape such that the distance from the impeller of the cross flow fan 100 increases from the indoor unit heat exchanger 11 side to the air outlet 14 side.
  • Upper and lower vanes 16 are provided at the air outlet 14.
  • the upper and lower vanes 16 are for adjusting the blowing angle of air blown out from the blowing outlet 14.
  • the indoor unit 10 can change the air blowing direction up and down.
  • the air outlet 14 is also provided with left and right vanes. The left and right vanes are for adjusting the blowing angle of the air blown out from the air outlet 14 in the left and right direction.
  • the crossflow fan 100 When the crossflow fan 100 operates, an air flow from the suction port 13 to the blowout port 14 is generated in the air path, air is sucked in from the suction port 13, and air is blown out from the blowout port 14.
  • the air sucked in from the suction port 13 becomes an airflow that passes through the air path inside the housing 12 in this order through the filter 15, the indoor unit heat exchanger 11, and the crossflow fan 100, and is blown out from the blowout port 14.
  • the direction of the wind blown out from the outlet 14, that is, the direction of the air blowing is adjusted by the upper and lower vanes 16 and the left and right vanes arranged on the leeward side of the cross flow fan 100.
  • the indoor unit 10 of the air conditioner configured as described above blows air indoors.
  • the indoor unit 10 can change the temperature and direction of the airflow.
  • the crossflow fan 100 includes an impeller 110 and a motor 150.
  • the impeller 110 includes a support member 120, blades 130, and a rotating shaft 140.
  • the motor 150 rotates the impeller 110 around the rotating shaft 140.
  • the impeller 110 includes a plurality of support members 120.
  • the support member 120 is a flat member having a circular or annular shape.
  • the plurality of support members 120 are arranged at preset intervals in a direction parallel to the rotation axis 140 (hereinafter also referred to as the rotation axis 140 direction).
  • the rotation shaft 140 of the impeller 110 is provided to pass through the center of the circular or annular shape of the plurality of support members 120.
  • a plurality of wings 130 are provided between adjacent support members 120.
  • the plurality of wings 130 are provided near the outer periphery of the support member 120.
  • the plurality of wings 130 are arranged at intervals along the circumferential direction of the support member 120.
  • a plurality of wings 130 supported between a pair of support members 120 constitute a series.
  • the impeller 110 of the cross-flow fan 100 is configured such that about 7 to 14 impellers are connected in the direction of the rotating shaft 140.
  • FIG. 4 shows a cross section of the blades 130 of the impeller 110 perpendicular to the rotation axis 140.
  • FIG. 5 shows an enlarged view of the main part of FIG.
  • a cross section perpendicular to the rotating shaft 140 is also referred to as a cross section C.
  • each of the plurality of blades 130 has a pressure surface 131 and a suction surface 132, as well as an outer peripheral end 133 and an inner peripheral end 134.
  • the positive pressure surface 131 is the surface of the blade 130 facing toward the direction of rotation.
  • the suction surface 132 is a surface of the blade 130 facing toward the side opposite to the rotation direction (hereinafter also referred to as the counter-rotation direction side).
  • the outer peripheral end 133 is the end of the blade 130 furthest from the rotating shaft 140.
  • Inner peripheral end 134 is the end of blade 130 closest to rotation axis 140.
  • the shapes of the outer circumferential end 133 and the inner circumferential end 134 in cross section C are both arcuate. In particular, as will be described later, when the shapes of the positive pressure surface 131 and the negative pressure surface 132 in the cross section C are the same, the shapes of the outer peripheral end 133 and the inner peripheral end 134 in the cross section C are both semicircular.
  • Each of the positive pressure surface 131 and the negative pressure surface 132 and the outer peripheral end portion 133 are smoothly connected. Further, each of the positive pressure surface 131 and the negative pressure surface 132 and the inner peripheral end portion 134 are smoothly connected.
  • the plurality of wings 130 have at least one first wing 201.
  • all of the plurality of wings 130 are the first wings 201.
  • not all of the plurality of wings 130 need to be the first wings 201, and at least some of the plurality of wings 130 may be the first wings 201. That is, in other words, some or all of the plurality of wings 130 are the first wings 201.
  • the pressure surface 131 of the first blade 201 has a convex shape in the first region 301 in the counter-rotational direction. In other words, the pressure surface 131 of the first blade 201 is concave in the rotation direction in the first region 301 .
  • the first region 301 is a region that includes the outer peripheral end portion 133 of the first blade 201 and is continuous in the radial direction of the impeller 110.
  • the pressure surface 131 of the first blade 201 has a convex shape in the second region 302 in the rotation direction side. In other words, the pressure surface 131 of the first blade 201 has a concave shape in the second region 302 in the counter-rotational direction.
  • the second region 302 is a region that includes the inner peripheral end portion 134 of the first blade 201 and is continuous in the radial direction of the impeller 110.
  • the suction surface 132 of the first blade 201 has the same shape as the pressure surface 131 of the first blade 201 in the cross section C. That is, in cross section C, the suction surface 132 of the first blade 201 has a convex shape in the first region 301 in the counter-rotational direction. In other words, the suction surface 132 of the first blade 201 is concave in the rotation direction in the first region 301 . Further, in cross section C, the suction surface 132 of the first blade 201 has a convex shape in the rotation direction side in the second region 302. In other words, the suction surface 132 of the first blade 201 has a concave shape in the second region 302 in the counter-rotational direction.
  • the impeller 110 switches between suction and blowout of the airflow.
  • the airflow flowing from the outer peripheral side of the impeller 110 between the blades 130 is abruptly turned in the direction of rotation after passing between the blades 130.
  • the crossflow fan 100 configured as described above at least some of the plurality of blades 130 are the first blades 201.
  • the first blade 201 at least the convex shape of the pressure surface 131 is oriented in opposite directions in the first region 301 and the second region 302.
  • the pressure surface 131 has a convex shape in the rotation direction side. Therefore, as shown in FIG. 6, the airflow passing between the blades 130 on the suction side of the cross-flow fan 100 tends to be directed toward the counter-rotation direction along the positive pressure surface 131 on the inner peripheral side. Therefore, the airflow after passing between the blades 130 on the suction side of the crossflow fan 100 can be suppressed from abruptly turning in the rotation direction. Accordingly, it is possible to suppress an increase in resistance due to a sudden turn of the airflow after passing between the blades.
  • the pressure surface 131 has a convex shape in the counter-rotation direction. Therefore, on the outer circumferential side of the suction side of the crossflow fan 100, separation of airflow from the negative pressure surface 132 can be suppressed, and inflow resistance between the blades can be reduced. In this way, ventilation resistance can be reduced on both the outer circumferential side and the inner circumferential side on the suction side of the crossflow fan 100, thereby making it easier for airflow to flow between the blades and preventing airflow separation from the negative pressure surface 132. It is possible to suppress the
  • first region 301 in which the positive pressure surface 131 and the negative pressure surface 132 have a convex shape in the counter-rotational direction
  • first region 301 in which the positive pressure surface 131 and the negative pressure surface 132 have a convex shape in the rotational direction.
  • the two areas 302 are directly connected.
  • an inflection point 303 exists in the shape of the pressure surface 131 and the suction surface 132 in the cross section C.
  • the first region 301 and the second region 302 may not be directly connected, and a third region may exist between the first region 301 and the second region 302. In the third region, for example, the shapes of the positive pressure surface 131 and the negative pressure surface 132 in cross section C are linear.
  • the curvature of the convex shape of the first region 301 is larger than the curvature of the convex shape of the second region 302.
  • the radial length of the convex shape of the first region 301 is longer than the radial length of the convex shape of the second region 302.
  • the first region 301 and the second region 302 are directly connected, and there is an inflection point 303 in the shape of the positive pressure surface 131 and the negative pressure surface 132 in cross section C.
  • the inflection point 303 is located closer to the inner circumferential end portion 134 than the midpoint in the radial direction of the first blade 201 .
  • the curvature of the blade cross-sectional shape on the outer peripheral side can be made small.
  • the curvature of the cross-sectional shape of the blades on the outer circumferential side becomes large, the airflow cannot follow the blade surfaces on both the suction side and the blowout side of the cross flow fan 100, and separation tends to occur.
  • FIG. 7 shows another example of the impeller 110 of the cross flow fan according to this embodiment.
  • the plurality of wings 130 need to be the first wings 201, and at least some of the plurality of wings 130 may be the first wings 201.
  • the plurality of blades 130 further include a second blade 202 in addition to the first blade 201. That is, some of the plurality of blades 130 that the impeller 110 has are the first blades 201 and the rest are the second blades 202.
  • the pressure surface 131 of the second blade 202 is a region from the outer peripheral end 133 of the second blade 202 to the inner peripheral end 134 of the second blade 202 in cross section C, that is, the area between the second blade 202 and the inner peripheral end 134 of the second blade 202.
  • the entire shape is convex in the counter-rotational direction.
  • the pressure surface 131 of the second blade 202 has a concave shape in the rotation direction side in the cross section C as a whole of the second blade 202 .
  • the suction surface 132 of the second blade 202 has the same shape as the pressure surface 131 of the second blade 202 in the cross section C.
  • the suction surface 132 of the second blade 202 has a convex shape in the counter-rotation direction as a whole.
  • the suction surface 132 of the second blade 202 has a concave shape in the rotation direction in the entire second blade 202 in the cross section C.
  • the length from the outer peripheral end 133 to the inner peripheral end 134 of the second blade 202 is the length from the outer peripheral end 133 to the inner peripheral end 134 of the first blade 201. length, i.e. shorter than the radial length.
  • the distance from the rotating shaft 140 to the outer peripheral end 133 of the first blade 201 is equal to the distance from the rotating shaft 140 to the outer peripheral end 133 of the second blade 202.
  • the distance from the rotating shaft 140 to the inner peripheral end 134 of the first blade 201 is shorter than the distance from the rotating shaft 140 to the inner peripheral end 134 of the second blade 202.
  • At least one second wing 202 is arranged between the first wings 201.
  • the second blade 202 is shorter than the first blade 201, and the inner peripheral end 134 of the second blade 202 is arranged on the outer peripheral side than the inner peripheral end 134 of the first blade 201. Therefore, the second blades 202 do not exist between the first blades 201 on the inner peripheral side. Since the first blades 201 have a long radial length, when the first blades 201 are arranged next to each other, the distance between the blades becomes small, especially on the inner peripheral side.
  • the second blade 202 which has a shorter radial length than the first blade 201, between the first blades 201, the distance between the blades on the inner circumferential side is suppressed from becoming smaller. However, it is possible to suppress an increase in ventilation resistance due to narrowing of the space between the blades.
  • the first blade 201 and the second blade 202 have the same outer peripheral cross-sectional shape. That is, in cross section C, the shape of the first region 301 of the first blade 201 is preferably the same as the shape of the second blade 202 in the same radial range as the first region 301. By doing so, on the blowout side of the crossflow fan 100, the directions of the airflow flowing out from between the blades 130 can be aligned, and destabilization of the blowing airflow can be suppressed.
  • the number of second wings 202 is greater than the number of first wings 201.
  • separation of airflow tends to occur at the inner peripheral end portion 134 of the first blade 201.
  • the number of second wings 202 arranged between the first wings 201 may be one or more, but in particular, two or more second wings 202 may be arranged between the first wings 201. It is preferable to arrange three.
  • a line T extending from a line tangent to the positive pressure surface 131 at the connection point between the positive pressure surface 131 and the inner peripheral end 134 of the first blade 201 toward the inner peripheral end 134 side is , it is preferable to pass through the opposite rotation direction side of the rotating shaft 140. That is, the inner circumferential end 134 side of the positive pressure surface 131 of the first blade 201 is inclined toward the opposite rotation direction than the surface from the inner circumferential end 134 toward the rotating shaft 140 . By doing so, the airflow passing between the blades 130 on the suction side of the crossflow fan 100 and flowing out to the inner peripheral side of the impeller 110 can be made more likely to be oriented in the counter-rotation direction.
  • the airflow that has passed between the blades 130 on the suction side of the crossflow fan 100 can be further suppressed from abruptly turning in the rotation direction, and the increase in resistance due to the sudden turning of the airflow after passing between the blades can be further suppressed.
  • a line extending from a line that is in contact with the positive pressure surface 131 at the connection point between the positive pressure surface 131 and the inner peripheral end 134 of the second blade 202 toward the inner peripheral end 134 side is a line that extends toward the inner peripheral end 134 side. It may be made to pass on the rotation direction side. In this case, it is preferable that the inner peripheral end 134 side of the pressure surface 131 of the first blade 201 is tilted more toward the counter-rotational direction than the second blade 202.
  • the inner circumference of the pressure surface 131 of the first blade 201 can be tilted more toward the counter-rotation direction. , it is possible to make the airflow passing between the blades 130 from the outer circumferential side to the inner circumferential side of the impeller 110 even more likely to be oriented in the counter-rotational direction.
  • the present disclosure includes a plurality of support members arranged at preset intervals in the direction of a rotation axis, and provided between adjacent support members, and arranged near the outer periphery of the support members and spaced apart in the circumferential direction. Available for cross flow fans with multiple blades. Further, the present disclosure can also be used in a blower device and a refrigeration cycle device equipped with a cross-flow fan.

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  • General Engineering & Computer Science (AREA)
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Abstract

Provided is a cross flow fan that can suppress an increase in ventilation resistance between blades of an impeller. For this purpose, a cross flow fan (100) comprises: a plurality of support members (120) that are disposed at a preset interval in a rotational axis direction, and that have a circular or annular plate shape; and a plurality of blades (130) that are provided between the support members (120) adjacent to each other, and that are disposed closer to the outer circumference of the support members (120) and spaced apart from each other in a circumferential direction. Each of the blades (130) has a positive pressure surface (131) on a rotational direction side and a negative pressure surface (132) on an anti-rotational direction side. The plurality of blades (130) include at least one first blade (201). The positive pressure surface (131) of the first blade (201) has, in a cross section thereof perpendicular to a rotational axis (140), a protruding shape on the anti-rotational direction side in a first area (301) including an outer circumferential end (133) of the first blade (201), and has a protruding shape on the rotational direction side in a second area (302) including an inner circumferential end (134) of the first blade (201).

Description

クロスフローファン、送風装置及び冷凍サイクル装置Cross flow fans, blowers and refrigeration cycle equipment
　本開示は、クロスフローファン、送風装置及び冷凍サイクル装置に関するものである。 The present disclosure relates to a crossflow fan, a blower device, and a refrigeration cycle device.
　内周側に配置される内縁部と、外周側に配置される外縁部とを有し、周方向に互いに間隔を隔てて配列される複数の羽根部を備え、羽根部には、内縁部と外縁部との間で延在し、ファンの回転方向の側に配置される正圧面と、正圧面の裏側に配置される負圧面とからなる翼面が形成され、ファンの回転に伴って、翼面上には内縁部と外縁部との間を流れる流体流れが発生し、羽根部は、ファンの回転軸に直交する平面により切断された場合に、正圧面および負圧面に凹部が形成される翼断面を有し、複数の羽根部は、互いに異なる形状の翼断面を有する第１羽根部および第２羽根部を含むファンが知られている（例えば、特許文献１参照）。 It has an inner edge part disposed on the inner circumferential side and an outer edge part disposed on the outer circumferential side, and includes a plurality of blade parts arranged at intervals in the circumferential direction, and the blade part has an inner edge part and an outer edge part arranged on the outer peripheral side. A blade surface is formed that extends between the outer edge part and consists of a positive pressure surface located on the side in the rotation direction of the fan and a negative pressure surface located on the back side of the positive pressure surface, and as the fan rotates, A fluid flow occurs between the inner edge and the outer edge on the blade surface, and when the blade is cut by a plane perpendicular to the rotation axis of the fan, recesses are formed on the pressure and suction surfaces. 2. Description of the Related Art A fan is known in which a plurality of blade parts include a first blade part and a second blade part each having a blade cross section of a different shape (see, for example, Patent Document 1).
日本特開２０１１－１９０７４７号公報Japanese Patent Application Publication No. 2011-190747
　しかしながら、特許文献１に示されるようなクロスフローファンでは、特に、羽根車への気流の吸込みが吹出しに切り替わる直前の領域において、翼間を通過した後に気流が羽根車の回転方向に急転向する。このような気流の急転向に起因して翼間の通風抵抗が増大する。そして、翼間の通風抵抗の増大により、風量が低下し、翼の負圧面からの気流剥離を生じやすい。 However, in a cross-flow fan as shown in Patent Document 1, the airflow suddenly turns in the direction of rotation of the impeller after passing between the blades, especially in the region immediately before the airflow changes from suction to the impeller to blowout. . Due to such a sudden turn of the airflow, the ventilation resistance between the blades increases. Further, due to the increase in ventilation resistance between the blades, the air volume decreases, and air flow tends to separate from the suction surface of the blade.
　本開示は、このような課題を解決するためになされたものである。その目的は、特に羽根車の外周側から内周側に翼間を通過した後における気流の急転向を抑制し、翼間の通風抵抗の増大を抑制することができ、ひいては翼面からの気流剥離を抑制することが可能であるクロスフローファン、送風装置及び冷凍サイクル装置を提供することにある。 The present disclosure has been made to solve such problems. The purpose of this is to suppress the sharp turn of the airflow after passing between the blades, especially from the outer circumferential side to the inner circumferential side of the impeller, and to suppress the increase in ventilation resistance between the blades, which in turn suppresses the airflow from the blade surface. An object of the present invention is to provide a cross flow fan, a blower device, and a refrigeration cycle device that can suppress separation.
　本開示に係るクロスフローファンは、回転軸方向に予め設定された間隔で配置され、円形又は円環形の平板状を呈する複数の支持部材と、隣り合う前記支持部材の間に設けられ、前記支持部材の外周寄りで、かつ、周方向に間隔をあけて配置された複数の翼と、を備え、それぞれの前記翼は、回転方向側の正圧面と反回転方向側の負圧面とを有し、複数の前記翼は、少なくとも１つの第１の翼を有し、前記第１の翼の前記正圧面は、前記回転軸に垂直な断面において、前記第１の翼の外周端部を含む第１領域で前記反回転方向側に凸形状であり、かつ、前記第１の翼の内周端部を含む第２領域で前記回転方向側に凸形状である。 A cross flow fan according to the present disclosure includes a plurality of support members arranged at preset intervals in a rotation axis direction and having a circular or annular flat plate shape, and provided between adjacent support members, and a plurality of blades disposed near the outer periphery of the member and spaced apart in the circumferential direction, each of the blades having a positive pressure surface on the rotation direction side and a negative pressure surface on the counter rotation direction side. , the plurality of blades have at least one first blade, and the pressure surface of the first blade includes a first blade including an outer peripheral end of the first blade in a cross section perpendicular to the rotation axis. One region has a convex shape in the opposite rotational direction, and a second region including the inner circumferential end of the first blade has a convex shape in the rotational direction.
　本開示に係る送風装置は、上記のように構成されたクロスフローファンを備える。 A blower device according to the present disclosure includes a crossflow fan configured as described above.
　本開示に係る冷凍サイクル装置は、上記のように構成されたクロスフローファンと、前記クロスフローファンにより生成された空気流と冷媒との間で熱交換を行わせる熱交換器と、を備える。 A refrigeration cycle device according to the present disclosure includes a cross-flow fan configured as described above, and a heat exchanger that performs heat exchange between a refrigerant and an air flow generated by the cross-flow fan.
　本開示に係るクロスフローファン、送風装置及び冷凍サイクル装置によれば、特に羽根車の外周側から内周側に翼間を通過した後における気流の急転向を抑制し、翼間の通風抵抗の増大を抑制することができ、ひいては翼面からの気流剥離を抑制することが可能であるという効果を奏する。 According to the cross-flow fan, blower device, and refrigeration cycle device according to the present disclosure, it is possible to suppress sudden turning of airflow after passing between the blades from the outer circumferential side of the impeller to the inner circumferential side, and to reduce ventilation resistance between the blades. The effect is that it is possible to suppress the increase in airflow, and in turn, it is possible to suppress airflow separation from the blade surface.
実施の形態１に係る冷凍サイクル装置の構成を示す図である。1 is a diagram showing the configuration of a refrigeration cycle device according to Embodiment 1. FIG. 実施の形態１に係る冷凍サイクル装置及び送風装置の一例である空気調和機の室内機の構成を示す断面図である。1 is a cross-sectional view showing the configuration of an indoor unit of an air conditioner that is an example of a refrigeration cycle device and a blower device according to Embodiment 1. FIG. 実施の形態１に係るクロスフローファンの正面図である。1 is a front view of a cross flow fan according to Embodiment 1. FIG. 実施の形態１に係るクロスフローファンの羽根車の一例を示す断面図である。FIG. 3 is a cross-sectional view showing an example of an impeller of the cross flow fan according to the first embodiment. 実施の形態１に係るクロスフローファンの羽根車の一例を示す要部拡大断面図である。FIG. 2 is an enlarged cross-sectional view of a main part of an example of an impeller of the cross flow fan according to the first embodiment. 実施の形態１に係るクロスフローファンの羽根車の一例における気流を示す図である。FIG. 3 is a diagram showing airflow in an example of an impeller of the crossflow fan according to the first embodiment. 実施の形態１に係るクロスフローファンの羽根車の別例を示す断面図である。FIG. 3 is a sectional view showing another example of the impeller of the cross flow fan according to the first embodiment. 実施の形態１に係るクロスフローファンの羽根車の別例を示す断面図である。FIG. 3 is a sectional view showing another example of the impeller of the cross flow fan according to the first embodiment. 実施の形態１に係るクロスフローファンの羽根車の別例を示す要部拡大断面図である。FIG. 7 is an enlarged sectional view of a main part showing another example of the impeller of the cross flow fan according to the first embodiment.
　本開示に係るクロスフローファン、送風装置及び冷凍サイクル装置を実施するための形態について添付の図面を参照しながら説明する。各図において、同一又は相当する部分には同一の符号を付して、重複する説明は適宜に簡略化又は省略する。以下の説明においては便宜上、図示の状態を基準に各構造の位置関係を表現することがある。なお、本開示は以下の実施の形態に限定されることなく、本開示の趣旨を逸脱しない範囲において、各実施の形態の自由な組み合わせ、各実施の形態の任意の構成要素の変形、又は各実施の形態の任意の構成要素の省略が可能である。 Embodiments for implementing the crossflow fan, blower device, and refrigeration cycle device according to the present disclosure will be described with reference to the accompanying drawings. In each figure, the same or corresponding parts are given the same reference numerals, and overlapping explanations will be simplified or omitted as appropriate. In the following description, for convenience, the positional relationship of each structure may be expressed based on the illustrated state. Note that the present disclosure is not limited to the following embodiments, and any combination of embodiments, modification of any component of each embodiment, or modification of each embodiment may be made without departing from the spirit of the present disclosure. Any component of the embodiment can be omitted.
実施の形態１．
　図１から図９を参照しながら、本開示の実施の形態１について説明する。図１は冷凍サイクル装置の構成を示す図である。図２は冷凍サイクル装置及び送風装置の一例である空気調和機の室内機の構成を示す断面図である。図３はクロスフローファンの正面図である。図４はクロスフローファンの羽根車の一例を示す断面図である。図５はクロスフローファンの羽根車の一例を示す要部拡大断面図である。図６はクロスフローファンの羽根車の一例における気流を示す図である。図７及び図８はクロスフローファンの羽根車の別例を示す断面図である。図９はクロスフローファンの羽根車の別例を示す要部拡大断面図である。 Embodiment 1.
Embodiment 1 of the present disclosure will be described with reference to FIGS. 1 to 9. FIG. 1 is a diagram showing the configuration of a refrigeration cycle device. FIG. 2 is a sectional view showing the configuration of an indoor unit of an air conditioner, which is an example of a refrigeration cycle device and a blower device. FIG. 3 is a front view of the crossflow fan. FIG. 4 is a sectional view showing an example of an impeller of a cross flow fan. FIG. 5 is an enlarged sectional view of a main part of an example of an impeller of a cross flow fan. FIG. 6 is a diagram showing airflow in an example of an impeller of a crossflow fan. 7 and 8 are cross-sectional views showing other examples of the impeller of the cross flow fan. FIG. 9 is an enlarged sectional view of a main part showing another example of an impeller of a cross flow fan.
　本開示に係るクロスフローファンを備えた冷凍サイクル装置の一例として、空気調和機の構成を図１に示す。なお、本開示に係るクロスフローファンを備えた冷凍サイクル装置としては、空気調和機の他に、例えばショーケース等を挙げることができる。また、後述するように、空気調和機は送風する機能を有している。したがって、ここで説明する空気調和機は、本開示に係るクロスフローファンを備えた送風装置の一例でもある。なお、本開示に係るクロスフローファンを備えた送風装置としては、空気調和機の他に、例えばサーキュレータ、タワー型扇風機等を挙げることができる。 FIG. 1 shows the configuration of an air conditioner as an example of a refrigeration cycle device equipped with a crossflow fan according to the present disclosure. Note that, in addition to an air conditioner, examples of the refrigeration cycle device including the crossflow fan according to the present disclosure include a showcase and the like. Furthermore, as described later, the air conditioner has a function of blowing air. Therefore, the air conditioner described here is also an example of a blower device including a cross-flow fan according to the present disclosure. Note that, in addition to an air conditioner, examples of the blower device including the cross-flow fan according to the present disclosure include a circulator, a tower-type electric fan, and the like.
　図１に示すように、この実施の形態に係る冷凍サイクル装置である空気調和機は、室内機１０と室外機２０とを備えている。室内機１０は、空気調和の対象となる室の内部すなわち室内に設置される。室外機２０は、当該室の外部すなわち室外に設置される。室内機１０は、室内機熱交換器１１とクロスフローファン１００とを備えている。室外機２０は、室外機熱交換器２１、室外機ファン２２、圧縮機２３、膨張弁２４及び四方弁２５を備えている。 As shown in FIG. 1, the air conditioner, which is a refrigeration cycle device according to this embodiment, includes an indoor unit 10 and an outdoor unit 20. The indoor unit 10 is installed inside a room to be air-conditioned, that is, indoors. The outdoor unit 20 is installed outside the room, that is, outdoors. The indoor unit 10 includes an indoor unit heat exchanger 11 and a cross flow fan 100. The outdoor unit 20 includes an outdoor unit heat exchanger 21, an outdoor unit fan 22, a compressor 23, an expansion valve 24, and a four-way valve 25.
　室内機１０と室外機２０とは冷媒配管３０で接続されている。冷媒配管３０は、室内機１０の室内機熱交換器１１と室外機２０の室外機熱交換器２１との間で循環的に設けられている。冷媒配管３０内には冷媒が封入されている。冷媒配管３０内に封入される冷媒は、例えば、ジフルオロメタン（ＣＨ２Ｆ２：Ｒ３２）等である。 The indoor unit 10 and the outdoor unit 20 are connected by a refrigerant pipe 30. The refrigerant pipe 30 is provided cyclically between the indoor unit heat exchanger 11 of the indoor unit 10 and the outdoor unit heat exchanger 21 of the outdoor unit 20. A refrigerant is sealed inside the refrigerant pipe 30. The refrigerant sealed in the refrigerant pipe 30 is, for example, difluoromethane (CH2F2:R32).
　冷媒配管３０は、室内機熱交換器１１、四方弁２５、圧縮機２３、室外機熱交換器２１及び膨張弁２４を環状に接続している。したがって、室内機熱交換器１１と室外機熱交換器２１との間で冷媒が循環する冷媒回路が形成されている。 The refrigerant pipe 30 connects the indoor unit heat exchanger 11, the four-way valve 25, the compressor 23, the outdoor unit heat exchanger 21, and the expansion valve 24 in an annular manner. Therefore, a refrigerant circuit in which refrigerant circulates between the indoor heat exchanger 11 and the outdoor heat exchanger 21 is formed.
　圧縮機２３は、供給された冷媒を圧縮して当該冷媒の圧力及び温度を高める機器である。圧縮機２３は、例えば、ロータリ圧縮機、スクロール圧縮機、レシプロ圧縮機等を用いることができる。膨張弁２４は、室外機熱交換器２１で凝縮された冷媒を膨張させ、当該冷媒を減圧する。 The compressor 23 is a device that compresses the supplied refrigerant to increase the pressure and temperature of the refrigerant. As the compressor 23, for example, a rotary compressor, a scroll compressor, a reciprocating compressor, etc. can be used. The expansion valve 24 expands the refrigerant condensed in the outdoor unit heat exchanger 21 and reduces the pressure of the refrigerant.
　室内機熱交換器１１は、室内機熱交換器１１に流入した冷媒と室内機熱交換器１１の周囲の空気との間で熱を交換させる。クロスフローファン１００は、室内の空気が室内機熱交換器１１の周囲を通過するように送風し、室内機熱交換器１１における冷媒と空気との間での熱交換を促進するとともに、熱交換により加熱又は冷却された空気を再び室内に送り出す。室外機熱交換器２１は、室外機熱交換器２１に流入した冷媒と室外機熱交換器２１の周囲の空気との間で熱を交換させる。室外機ファン２２は、室外の空気が室外機熱交換器２１の周囲を通過するように送風し、室外機熱交換器２１における冷媒と空気との間での熱交換を促進する。 The indoor heat exchanger 11 exchanges heat between the refrigerant that has flowed into the indoor heat exchanger 11 and the air surrounding the indoor heat exchanger 11. The cross flow fan 100 blows indoor air so that it passes around the indoor unit heat exchanger 11, promotes heat exchange between the refrigerant and air in the indoor unit heat exchanger 11, and also promotes heat exchange. The heated or cooled air is sent back into the room. The outdoor heat exchanger 21 exchanges heat between the refrigerant that has flowed into the outdoor heat exchanger 21 and the air around the outdoor heat exchanger 21 . The outdoor unit fan 22 blows outdoor air so that it passes around the outdoor unit heat exchanger 21, and promotes heat exchange between the refrigerant and the air in the outdoor unit heat exchanger 21.
　このようにして構成された冷媒回路は、室内機熱交換器１１及び室外機熱交換器２１のそれぞれにおいて冷媒と空気の間で熱交換を行うことにより、室内機１０と室外機２０との間で熱を移動させるヒートポンプとして働く。この際、四方弁２５を切り換えることにより、冷媒回路における冷媒の循環方向を反転させて空気調和機の冷房運転と暖房運転とを切り換えることができる。 The refrigerant circuit configured in this manner exchanges heat between the refrigerant and air in each of the indoor unit heat exchanger 11 and the outdoor unit heat exchanger 21, thereby providing a connection between the indoor unit 10 and the outdoor unit 20. It works as a heat pump to move heat. At this time, by switching the four-way valve 25, the circulation direction of the refrigerant in the refrigerant circuit can be reversed, and the air conditioner can be switched between cooling operation and heating operation.
　図２に示すように、室内機１０は筐体１２を備えている。筐体１２は室内に設置される。筐体１２の内部には、室内機熱交換器１１及びクロスフローファン１００が収容されている。筐体１２の上面部には、吸込口１３が形成されている。吸込口１３は、外部から筐体１２の内部に空気を取り込むための開口である。筐体１２の下面には、吹出口１４が形成されている。吹出口１４は、筐体１２の内部から外部へと空気を排出するための開口である。 As shown in FIG. 2, the indoor unit 10 includes a housing 12. The housing 12 is installed indoors. Inside the housing 12, an indoor unit heat exchanger 11 and a cross flow fan 100 are housed. A suction port 13 is formed in the upper surface of the housing 12 . The suction port 13 is an opening for taking air into the housing 12 from the outside. An air outlet 14 is formed on the lower surface of the housing 12 . The air outlet 14 is an opening for discharging air from the inside of the housing 12 to the outside.
　筐体１２の内部には、吸込口１３から吹出口１４へと通じる風路が形成されている。吸込口１３には、フィルター１５が設置されている。フィルター１５は、吸込口１３から筐体１２の内部へと入る空気から、比較的大きなごみ、塵、埃等を取り除くためのものである。 An air path leading from the suction port 13 to the blowout port 14 is formed inside the housing 12 . A filter 15 is installed in the suction port 13. The filter 15 is for removing relatively large particles, dirt, dust, etc. from the air entering the interior of the housing 12 from the suction port 13.
　筐体１２内の風路におけるフィルター１５の風下側には、室内機熱交換器１１が設置されている。室内機熱交換器１１は、筐体１２内の風路を流れる空気と熱交換を行って、風路を流れる空気を加熱又は冷却する。空気を加熱するか冷却するかは、空気調和機が暖房運転であるか冷房運転であるかによる。 An indoor unit heat exchanger 11 is installed on the leeward side of the filter 15 in the air passage inside the housing 12. The indoor unit heat exchanger 11 exchanges heat with the air flowing through the air path inside the housing 12 to heat or cool the air flowing through the air path. Whether the air is heated or cooled depends on whether the air conditioner is in heating mode or cooling mode.
　前述した風路における室内機熱交換器１１の風下側には、クロスフローファン１００が設置されている。クロスフローファン１００は、吸込口１３から吹出口１４へと向かう空気流を、筐体１２内の風路中に生成するためのものである。筐体１２内におけるクロスフローファン１００の羽根車の後面側には、リアガイド１７が設けられている。また、筐体１２内におけるクロスフローファン１００の羽根車の前面側には、スタビライザー１８が設けられている。リアガイド１７は、室内機熱交換器１１側から吹出口１４側にいくに従って、クロスフローファン１００の羽根車からの距離が拡大する螺旋状に配置されている。これらのリアガイド１７及びスタビライザー１８により、クロスフローファン１００の羽根車の回転時に、流路抵抗が最も小さい室内機熱交換器１１側から吸い込み、流路抵抗が次に小さい吹出口１４側に吹き出す空気の流れが実現される。 A cross flow fan 100 is installed on the leeward side of the indoor unit heat exchanger 11 in the aforementioned air path. The crossflow fan 100 is for generating an airflow from the suction port 13 toward the blowout port 14 in the air path inside the housing 12 . A rear guide 17 is provided on the rear side of the impeller of the cross flow fan 100 in the housing 12. Further, a stabilizer 18 is provided on the front side of the impeller of the cross flow fan 100 inside the housing 12. The rear guide 17 is arranged in a spiral shape such that the distance from the impeller of the cross flow fan 100 increases from the indoor unit heat exchanger 11 side to the air outlet 14 side. With these rear guides 17 and stabilizers 18, when the impeller of the cross flow fan 100 rotates, air is sucked in from the indoor unit heat exchanger 11 side where the flow path resistance is lowest, and is blown out to the outlet 14 side where the flow path resistance is the next lowest. Air flow is achieved.
　吹出口１４には、上下ベーン１６が設けられている。上下ベーン１６は、吹出口１４から吹き出す空気の吹き出し角度を調整するためのものである。上下ベーン１６の向きを変えることで、室内機１０は、送風方向を上下に変更可能である。また、ここでは図示が省略されているが、吹出口１４には、左右ベーンも備えている。左右ベーンは、吹出口１４から吹き出す空気の左右方向の吹き出し角度を調整するためのものである。 Upper and lower vanes 16 are provided at the air outlet 14. The upper and lower vanes 16 are for adjusting the blowing angle of air blown out from the blowing outlet 14. By changing the orientation of the upper and lower vanes 16, the indoor unit 10 can change the air blowing direction up and down. Although not shown here, the air outlet 14 is also provided with left and right vanes. The left and right vanes are for adjusting the blowing angle of the air blown out from the air outlet 14 in the left and right direction.
　クロスフローファン１００が動作すると、吸込口１３から吹出口１４へと向かう空気流が風路中に生成されて、吸込口１３から空気が吸い込まれ、吹出口１４から空気が吹き出される。吸込口１３から吸い込まれた空気は、筐体１２内部の風路を、フィルター１５、室内機熱交換器１１、クロスフローファン１００の順に通過する空気流となり、吹出口１４から吹き出す。この際、クロスフローファン１００の風下側に配置された上下ベーン１６及び左右ベーンにより、吹出口１４から吹き出される風の方向すなわち送風方向が調整される。以上のように構成された空気調和機の室内機１０は、室内に送風する。そして、室内機１０は、送風する気流の温度及び風向を変更可能である。 When the crossflow fan 100 operates, an air flow from the suction port 13 to the blowout port 14 is generated in the air path, air is sucked in from the suction port 13, and air is blown out from the blowout port 14. The air sucked in from the suction port 13 becomes an airflow that passes through the air path inside the housing 12 in this order through the filter 15, the indoor unit heat exchanger 11, and the crossflow fan 100, and is blown out from the blowout port 14. At this time, the direction of the wind blown out from the outlet 14, that is, the direction of the air blowing, is adjusted by the upper and lower vanes 16 and the left and right vanes arranged on the leeward side of the cross flow fan 100. The indoor unit 10 of the air conditioner configured as described above blows air indoors. The indoor unit 10 can change the temperature and direction of the airflow.
　図３に示すように、クロスフローファン１００は、羽根車１１０及びモータ１５０を備えている。羽根車１１０は、支持部材１２０、翼１３０及び回転軸１４０を備えている。モータ１５０は、回転軸１４０を中心に羽根車１１０を回転させる。 As shown in FIG. 3, the crossflow fan 100 includes an impeller 110 and a motor 150. The impeller 110 includes a support member 120, blades 130, and a rotating shaft 140. The motor 150 rotates the impeller 110 around the rotating shaft 140.
　羽根車１１０は、複数の支持部材１２０を備えている。支持部材１２０は、円形又は円環形を呈する平板状の部材である。複数の支持部材１２０は、回転軸１４０に平行な方向（以下、回転軸１４０方向ともいう）に予め設定された間隔で配置されている。羽根車１１０の回転軸１４０は、複数の支持部材１２０の円形又は円環形の中心を貫通して設けられている。隣り合う支持部材１２０の間には、複数の翼１３０が設けられている。複数の翼１３０は、支持部材１２０の外周寄りに設けられている。複数の翼１３０は、支持部材１２０の周方向に沿って間隔をあけて整列されている。一対の支持部材１２０の間に支持される複数の翼１３０により１連が構成される。クロスフローファン１００の羽根車１１０は、回転軸１４０方向に７連から１４連程度が連なって構成されている。 The impeller 110 includes a plurality of support members 120. The support member 120 is a flat member having a circular or annular shape. The plurality of support members 120 are arranged at preset intervals in a direction parallel to the rotation axis 140 (hereinafter also referred to as the rotation axis 140 direction). The rotation shaft 140 of the impeller 110 is provided to pass through the center of the circular or annular shape of the plurality of support members 120. A plurality of wings 130 are provided between adjacent support members 120. The plurality of wings 130 are provided near the outer periphery of the support member 120. The plurality of wings 130 are arranged at intervals along the circumferential direction of the support member 120. A plurality of wings 130 supported between a pair of support members 120 constitute a series. The impeller 110 of the cross-flow fan 100 is configured such that about 7 to 14 impellers are connected in the direction of the rotating shaft 140.
　図４は、羽根車１１０の翼１３０の回転軸１４０に垂直な断面を示している。図５は、図４の要部を拡大して示したものである。本開示においては、回転軸１４０に垂直な断面を断面Ｃともいう。これらの図に示すように、複数の翼１３０のそれぞれは、正圧面１３１及び負圧面１３２、並びに、外周端部１３３及び内周端部１３４を有している。正圧面１３１は、回転方向側に向いた翼１３０の面である。負圧面１３２は、回転方向とは反対側（以下、反回転方向側ともいう）に向いた翼１３０の面である。 FIG. 4 shows a cross section of the blades 130 of the impeller 110 perpendicular to the rotation axis 140. FIG. 5 shows an enlarged view of the main part of FIG. In the present disclosure, a cross section perpendicular to the rotating shaft 140 is also referred to as a cross section C. As shown in these figures, each of the plurality of blades 130 has a pressure surface 131 and a suction surface 132, as well as an outer peripheral end 133 and an inner peripheral end 134. The positive pressure surface 131 is the surface of the blade 130 facing toward the direction of rotation. The suction surface 132 is a surface of the blade 130 facing toward the side opposite to the rotation direction (hereinafter also referred to as the counter-rotation direction side).
　外周端部１３３は、回転軸１４０から最も遠い翼１３０の端部である。内周端部１３４は、回転軸１４０に最も近い翼１３０の端部である。断面Ｃにおける外周端部１３３及び内周端部１３４の形状は、いずれも円弧状である。特に、後述するように、断面Ｃにおける正圧面１３１及び負圧面１３２の形状が同一である場合、断面Ｃにおける外周端部１３３及び内周端部１３４の形状は、いずれも半円状である。正圧面１３１及び負圧面１３２のそれぞれと外周端部１３３とは、滑らかに接続されている。また、正圧面１３１及び負圧面１３２のそれぞれと内周端部１３４とは、滑らかに接続されている。 The outer peripheral end 133 is the end of the blade 130 furthest from the rotating shaft 140. Inner peripheral end 134 is the end of blade 130 closest to rotation axis 140. The shapes of the outer circumferential end 133 and the inner circumferential end 134 in cross section C are both arcuate. In particular, as will be described later, when the shapes of the positive pressure surface 131 and the negative pressure surface 132 in the cross section C are the same, the shapes of the outer peripheral end 133 and the inner peripheral end 134 in the cross section C are both semicircular. Each of the positive pressure surface 131 and the negative pressure surface 132 and the outer peripheral end portion 133 are smoothly connected. Further, each of the positive pressure surface 131 and the negative pressure surface 132 and the inner peripheral end portion 134 are smoothly connected.
　複数の翼１３０は、少なくとも１つの第１の翼２０１を有している。図４に示す構成例では、複数の翼１３０の全てが第１の翼２０１である。ただし、複数の翼１３０の全てが第１の翼２０１である必要はなく、複数の翼１３０の少なくとも一部が第１の翼２０１であればよい。すなわち、換言すれば、複数の翼１３０の一部又は全部が第１の翼２０１である。 The plurality of wings 130 have at least one first wing 201. In the configuration example shown in FIG. 4, all of the plurality of wings 130 are the first wings 201. However, not all of the plurality of wings 130 need to be the first wings 201, and at least some of the plurality of wings 130 may be the first wings 201. That is, in other words, some or all of the plurality of wings 130 are the first wings 201.
　図５に示すように、断面Ｃにおいて、第１の翼２０１の正圧面１３１は、第１領域３０１で反回転方向側に凸形状である。換言すれば、第１の翼２０１の正圧面１３１は、第１領域３０１で回転方向側に凹形状である。第１領域３０１とは、当該第１の翼２０１の外周端部１３３を含み、かつ、羽根車１１０の径方向に連続した領域である。また、断面Ｃにおいて、第１の翼２０１の正圧面１３１は、第２領域３０２で回転方向側に凸形状である。換言すれば、第１の翼２０１の正圧面１３１は、第２領域３０２で反回転方向側に凹形状である。第２領域３０２とは、当該第１の翼２０１の内周端部１３４を含み、かつ、羽根車１１０の径方向に連続した領域である。 As shown in FIG. 5, in cross section C, the pressure surface 131 of the first blade 201 has a convex shape in the first region 301 in the counter-rotational direction. In other words, the pressure surface 131 of the first blade 201 is concave in the rotation direction in the first region 301 . The first region 301 is a region that includes the outer peripheral end portion 133 of the first blade 201 and is continuous in the radial direction of the impeller 110. Further, in cross section C, the pressure surface 131 of the first blade 201 has a convex shape in the second region 302 in the rotation direction side. In other words, the pressure surface 131 of the first blade 201 has a concave shape in the second region 302 in the counter-rotational direction. The second region 302 is a region that includes the inner peripheral end portion 134 of the first blade 201 and is continuous in the radial direction of the impeller 110.
　さらに、図５に示す構成例では、断面Ｃにおいて、第１の翼２０１の負圧面１３２は、第１の翼２０１の正圧面１３１と同形状である。すなわち、断面Ｃにおいて、第１の翼２０１の負圧面１３２は、第１領域３０１で反回転方向側に凸形状である。換言すれば、第１の翼２０１の負圧面１３２は、第１領域３０１で回転方向側に凹形状である。また、断面Ｃにおいて、第１の翼２０１の負圧面１３２は、第２領域３０２で回転方向側に凸形状である。換言すれば、第１の翼２０１の負圧面１３２は、第２領域３０２で反回転方向側に凹形状である。 Further, in the configuration example shown in FIG. 5, the suction surface 132 of the first blade 201 has the same shape as the pressure surface 131 of the first blade 201 in the cross section C. That is, in cross section C, the suction surface 132 of the first blade 201 has a convex shape in the first region 301 in the counter-rotational direction. In other words, the suction surface 132 of the first blade 201 is concave in the rotation direction in the first region 301 . Further, in cross section C, the suction surface 132 of the first blade 201 has a convex shape in the rotation direction side in the second region 302. In other words, the suction surface 132 of the first blade 201 has a concave shape in the second region 302 in the counter-rotational direction.
　クロスフローファン１００のリアガイド１７の近傍では、羽根車１１０の気流の吸込みと吹出しとが切り替わる。クロスフローファン１００の吸込側におけるリアガイド１７の近傍では、羽根車１１０の外周側から翼１３０の間に流入した気流は、翼１３０の間を通過した後に回転方向に急転向する。以上のように構成されたクロスフローファン１００においては、複数の翼１３０の少なくとも一部が第１の翼２０１である。そして、この第１の翼２０１では、少なくとも正圧面１３１の凸形状の向きが、第１領域３０１と第２領域３０２とで反対向きになっている。すなわち、第１の翼２０１では、当該第１の翼２０１の内周端部１３４を含む第２領域３０２において、少なくとも正圧面１３１が回転方向側に凸形状である。このため、図６に示すように、クロスフローファン１００の吸込側で翼１３０の間を通過する気流は、内周側で正圧面１３１に沿って反回転方向側に向きやすくなる。したがって、クロスフローファン１００の吸込側で翼１３０の間を通過した後の気流が、回転方向へと急転向することを抑制できる。そして、これにより、翼間通過後の気流の急転向による抵抗増大を抑制できる。 In the vicinity of the rear guide 17 of the crossflow fan 100, the impeller 110 switches between suction and blowout of the airflow. In the vicinity of the rear guide 17 on the suction side of the cross-flow fan 100, the airflow flowing from the outer peripheral side of the impeller 110 between the blades 130 is abruptly turned in the direction of rotation after passing between the blades 130. In the crossflow fan 100 configured as described above, at least some of the plurality of blades 130 are the first blades 201. In the first blade 201, at least the convex shape of the pressure surface 131 is oriented in opposite directions in the first region 301 and the second region 302. That is, in the first blade 201, in the second region 302 including the inner peripheral end portion 134 of the first blade 201, at least the pressure surface 131 has a convex shape in the rotation direction side. Therefore, as shown in FIG. 6, the airflow passing between the blades 130 on the suction side of the cross-flow fan 100 tends to be directed toward the counter-rotation direction along the positive pressure surface 131 on the inner peripheral side. Therefore, the airflow after passing between the blades 130 on the suction side of the crossflow fan 100 can be suppressed from abruptly turning in the rotation direction. Accordingly, it is possible to suppress an increase in resistance due to a sudden turn of the airflow after passing between the blades.
　また、第１の翼２０１では、当該第１の翼２０１の外周端部１３３を含む第１領域３０１において、少なくとも正圧面１３１が反回転方向側に凸形状である。このため、クロスフローファン１００の吸込側の外周側において、負圧面１３２からの気流剥離を抑制して、翼間への流入抵抗を低減できる。このようにして、クロスフローファン１００の吸込側における外周側及び内周側の両方で通風抵抗を低減させることができ、これにより、翼間に気流が流入しやすくなり負圧面１３２からの気流剥離を抑制することが可能である。 Further, in the first blade 201, in the first region 301 including the outer peripheral end portion 133 of the first blade 201, at least the pressure surface 131 has a convex shape in the counter-rotation direction. Therefore, on the outer circumferential side of the suction side of the crossflow fan 100, separation of airflow from the negative pressure surface 132 can be suppressed, and inflow resistance between the blades can be reduced. In this way, ventilation resistance can be reduced on both the outer circumferential side and the inner circumferential side on the suction side of the crossflow fan 100, thereby making it easier for airflow to flow between the blades and preventing airflow separation from the negative pressure surface 132. It is possible to suppress the
　図５に示す構成例では、断面Ｃにおいて、正圧面１３１及び負圧面１３２が反回転方向に凸形状を呈する第１領域３０１と、正圧面１３１及び負圧面１３２が回転方向に凸形状を呈する第２領域３０２とが直接的に接続されている。換言すれば、断面Ｃにおける正圧面１３１及び負圧面１３２の形状について変曲点３０３が存在する。なお、第１領域３０１と第２領域３０２とが直接的に接続されておらず、第１領域３０１と第２領域３０２との間に第３領域が存在してもよい。第３領域においては、例えば、断面Ｃにおける正圧面１３１及び負圧面１３２の形状が直線状である。 In the configuration example shown in FIG. 5, in the cross section C, there is a first region 301 in which the positive pressure surface 131 and the negative pressure surface 132 have a convex shape in the counter-rotational direction, and a first region 301 in which the positive pressure surface 131 and the negative pressure surface 132 have a convex shape in the rotational direction. The two areas 302 are directly connected. In other words, an inflection point 303 exists in the shape of the pressure surface 131 and the suction surface 132 in the cross section C. Note that the first region 301 and the second region 302 may not be directly connected, and a third region may exist between the first region 301 and the second region 302. In the third region, for example, the shapes of the positive pressure surface 131 and the negative pressure surface 132 in cross section C are linear.
　クロスフローファン１００の吹出側においては、内周側における翼断面形状の曲率が大きいほど、内周端部１３４から気流が剥離しやすくなる。図５に示す構成例では、断面Ｃにおいて、第１領域３０１の凸形状の曲率は、第２領域３０２の凸形状の曲率よりも大きい。このようにすることで、内周側における翼断面形状の曲率を小さくすることができるため、内周端部１３４からの気流剥離を抑制することが可能である。 On the blowout side of the cross-flow fan 100, the larger the curvature of the blade cross-sectional shape on the inner circumferential side, the more easily the airflow separates from the inner circumferential end 134. In the configuration example shown in FIG. 5, in cross section C, the curvature of the convex shape of the first region 301 is larger than the curvature of the convex shape of the second region 302. By doing so, it is possible to reduce the curvature of the blade cross-sectional shape on the inner circumferential side, so it is possible to suppress separation of airflow from the inner circumferential end 134.
　図５に示す構成例では、第１領域３０１の凸形状の径方向の長さは、第２領域３０２の凸形状の径方向の長さより長い。同図の例では、前述したように、第１領域３０１と第２領域３０２とが直接的に接続されており、断面Ｃにおける正圧面１３１及び負圧面１３２の形状について変曲点３０３が存在する。この場合、変曲点３０３は、第１の翼２０１の径方向における中間点よりも、内周端部１３４側に配置されている。 In the configuration example shown in FIG. 5, the radial length of the convex shape of the first region 301 is longer than the radial length of the convex shape of the second region 302. In the example shown in the figure, as described above, the first region 301 and the second region 302 are directly connected, and there is an inflection point 303 in the shape of the positive pressure surface 131 and the negative pressure surface 132 in cross section C. . In this case, the inflection point 303 is located closer to the inner circumferential end portion 134 than the midpoint in the radial direction of the first blade 201 .
　このような構成によれば、第１領域３０１の凸形状の径方向の長さを相対的に長くできるため、外周側における翼断面形状の曲率を小さくできる。外周側における翼断面形状の曲率が大きくなると、クロスフローファン１００の吸込側及び吹出側の両側で翼面に気流が沿いきれずに剥離を生じやすくなる。図５に示す本開示の構成例によれば、外周側における翼断面形状の曲率を小さくできるため、このような羽根車１１０の外周側における気流剥離を抑制することが可能である。 According to such a configuration, since the length in the radial direction of the convex shape of the first region 301 can be made relatively long, the curvature of the blade cross-sectional shape on the outer peripheral side can be made small. When the curvature of the cross-sectional shape of the blades on the outer circumferential side becomes large, the airflow cannot follow the blade surfaces on both the suction side and the blowout side of the cross flow fan 100, and separation tends to occur. According to the configuration example of the present disclosure shown in FIG. 5, it is possible to reduce the curvature of the blade cross-sectional shape on the outer circumferential side, so it is possible to suppress such airflow separation on the outer circumferential side of the impeller 110.
　図７に示すのは、この実施の形態に係るクロスフローファンの羽根車１１０の別例である。前述したように、複数の翼１３０の全てが第１の翼２０１である必要はなく、複数の翼１３０の少なくとも一部が第１の翼２０１であればよい。同図に示す構成例は、複数の翼１３０は、第１の翼２０１に加えて、第２の翼２０２をさらに有している。すなわち、羽根車１１０が有する複数の翼１３０のうちの一部が第１の翼２０１であり、残りが第２の翼２０２である。 FIG. 7 shows another example of the impeller 110 of the cross flow fan according to this embodiment. As described above, not all of the plurality of wings 130 need to be the first wings 201, and at least some of the plurality of wings 130 may be the first wings 201. In the configuration example shown in the figure, the plurality of blades 130 further include a second blade 202 in addition to the first blade 201. That is, some of the plurality of blades 130 that the impeller 110 has are the first blades 201 and the rest are the second blades 202.
　第２の翼２０２の正圧面１３１は、断面Ｃにおいて、当該第２の翼２０２の外周端部１３３から第２の翼２０２の内周端部１３４までの領域、つまり、当該第２の翼２０２の全体で反回転方向側に凸形状である。換言すれば、第２の翼２０２の正圧面１３１は、断面Ｃにおいて、当該第２の翼２０２の全体で回転方向側に凹形状である。さらに、図７に示す構成例では、断面Ｃにおいて、第２の翼２０２の負圧面１３２は、第２の翼２０２の正圧面１３１と同形状である。すなわち、断面Ｃにおいて、第２の翼２０２の負圧面１３２は、当該第２の翼２０２の全体で反回転方向側に凸形状である。換言すれば、第２の翼２０２の負圧面１３２は、断面Ｃにおいて、当該第２の翼２０２の全体で回転方向側に凹形状である。 The pressure surface 131 of the second blade 202 is a region from the outer peripheral end 133 of the second blade 202 to the inner peripheral end 134 of the second blade 202 in cross section C, that is, the area between the second blade 202 and the inner peripheral end 134 of the second blade 202. The entire shape is convex in the counter-rotational direction. In other words, the pressure surface 131 of the second blade 202 has a concave shape in the rotation direction side in the cross section C as a whole of the second blade 202 . Further, in the configuration example shown in FIG. 7, the suction surface 132 of the second blade 202 has the same shape as the pressure surface 131 of the second blade 202 in the cross section C. That is, in cross section C, the suction surface 132 of the second blade 202 has a convex shape in the counter-rotation direction as a whole. In other words, the suction surface 132 of the second blade 202 has a concave shape in the rotation direction in the entire second blade 202 in the cross section C.
　また、第２の翼２０２の外周端部１３３から内周端部１３４までの長さ、すなわち径方向の長さは、第１の翼２０１の外周端部１３３から内周端部１３４までの長さ、すなわち径方向の長さよりも短い。そして、回転軸１４０から第１の翼２０１の外周端部１３３までの距離と、回転軸１４０から第２の翼２０２の外周端部１３３までの距離とは等しい。一方、回転軸１４０から第１の翼２０１の内周端部１３４までの距離は、回転軸１４０から第２の翼２０２の内周端部１３４までの距離よりも短い。 Further, the length from the outer peripheral end 133 to the inner peripheral end 134 of the second blade 202, that is, the length in the radial direction, is the length from the outer peripheral end 133 to the inner peripheral end 134 of the first blade 201. length, i.e. shorter than the radial length. The distance from the rotating shaft 140 to the outer peripheral end 133 of the first blade 201 is equal to the distance from the rotating shaft 140 to the outer peripheral end 133 of the second blade 202. On the other hand, the distance from the rotating shaft 140 to the inner peripheral end 134 of the first blade 201 is shorter than the distance from the rotating shaft 140 to the inner peripheral end 134 of the second blade 202.
　図７に示す構成例では、第１の翼２０１同士の間に、少なくとも１つの第２の翼２０２が配置されている。第２の翼２０２は第１の翼２０１よりも短く、かつ、第２の翼２０２の内周端部１３４は、第１の翼２０１の内周端部１３４よりも外周側に配置されているため、内周側において第１の翼２０１同士の間に第２の翼２０２が存在しない。第１の翼２０１は径方向の長さが長いため、第１の翼２０１同士を隣に配列すると、特に内周側における翼間距離が小さくなってしまう。そこで、第１の翼２０１同士の間に、第１の翼２０１よりも径方向の長さが短い第２の翼２０２を配置することで、内周側における翼間距離が小さくなることを抑制し、翼間が狭まることによる通風抵抗の増加を抑制することが可能である。 In the configuration example shown in FIG. 7, at least one second wing 202 is arranged between the first wings 201. The second blade 202 is shorter than the first blade 201, and the inner peripheral end 134 of the second blade 202 is arranged on the outer peripheral side than the inner peripheral end 134 of the first blade 201. Therefore, the second blades 202 do not exist between the first blades 201 on the inner peripheral side. Since the first blades 201 have a long radial length, when the first blades 201 are arranged next to each other, the distance between the blades becomes small, especially on the inner peripheral side. Therefore, by arranging the second blade 202, which has a shorter radial length than the first blade 201, between the first blades 201, the distance between the blades on the inner circumferential side is suppressed from becoming smaller. However, it is possible to suppress an increase in ventilation resistance due to narrowing of the space between the blades.
　第１の翼２０１と第２の翼２０２の外周側の断面形状は同じものにするとよい。すなわち、断面Ｃにおいて、第１の翼２０１の第１領域３０１の形状は、第１領域３０１と同じ径方向の範囲の第２の翼２０２の形状と同一にするとよい。このようにすることで、クロスフローファン１００の吹出側において、翼１３０の間から流出する気流の風向を揃えることができ、吹き出す気流の不安定化を抑制できる。 It is preferable that the first blade 201 and the second blade 202 have the same outer peripheral cross-sectional shape. That is, in cross section C, the shape of the first region 301 of the first blade 201 is preferably the same as the shape of the second blade 202 in the same radial range as the first region 301. By doing so, on the blowout side of the crossflow fan 100, the directions of the airflow flowing out from between the blades 130 can be aligned, and destabilization of the blowing airflow can be suppressed.
　図８に示す構成例では、第２の翼２０２の数は、第１の翼２０１の数よりも多い。クロスフローファン１００の吹出側において、第１の翼２０１の内周端部１３４で気流の剥離が生じやすくなる。第２の翼２０２の数を第１の翼２０１の数よりも多くして、羽根車１１０が有する第１の翼２０１の数を少なくすることで、翼１３０の内周端部１３４における気流剥離を低減できる。なお、第１の翼２０１同士の間に配置される第２の翼２０２の数は１つ以上であればよいが、特に第１の翼２０１同士の間に第２の翼２０２を２つ又は３つ配置するのが好ましい。 In the configuration example shown in FIG. 8, the number of second wings 202 is greater than the number of first wings 201. On the blowout side of the cross-flow fan 100, separation of airflow tends to occur at the inner peripheral end portion 134 of the first blade 201. By increasing the number of second blades 202 than the number of first blades 201 and reducing the number of first blades 201 that the impeller 110 has, air flow separation at the inner peripheral end portion 134 of the blade 130 is reduced. can be reduced. Note that the number of second wings 202 arranged between the first wings 201 may be one or more, but in particular, two or more second wings 202 may be arranged between the first wings 201. It is preferable to arrange three.
　図９に示すように、断面Ｃにおいて、第１の翼２０１の正圧面１３１と内周端部１３４との接続部で正圧面１３１に接する線を内周端部１３４側に延長した線Ｔが、回転軸１４０の反回転方向側を通るようにするとよい。すなわち、第１の翼２０１の正圧面１３１の内周端部１３４側は、内周端部１３４から回転軸１４０に向かう面よりも反回転方向側に傾いている。このようにすることで、クロスフローファン１００の吸込側で翼１３０の間を通過して羽根車１１０の内周側に流出する気流が、反回転方向側にさらに向きやすくできる。したがって、クロスフローファン１００の吸込側で翼１３０の間を通過した気流が回転方向へと急転向することをさらに抑制し、翼間通過後の気流の急転向による抵抗増大をより一層抑制できる。 As shown in FIG. 9, in the cross section C, a line T extending from a line tangent to the positive pressure surface 131 at the connection point between the positive pressure surface 131 and the inner peripheral end 134 of the first blade 201 toward the inner peripheral end 134 side is , it is preferable to pass through the opposite rotation direction side of the rotating shaft 140. That is, the inner circumferential end 134 side of the positive pressure surface 131 of the first blade 201 is inclined toward the opposite rotation direction than the surface from the inner circumferential end 134 toward the rotating shaft 140 . By doing so, the airflow passing between the blades 130 on the suction side of the crossflow fan 100 and flowing out to the inner peripheral side of the impeller 110 can be made more likely to be oriented in the counter-rotation direction. Therefore, the airflow that has passed between the blades 130 on the suction side of the crossflow fan 100 can be further suppressed from abruptly turning in the rotation direction, and the increase in resistance due to the sudden turning of the airflow after passing between the blades can be further suppressed.
　なお、羽根車１１０が第２の翼２０２を有する場合、第２の翼２０２についても同様にしてもよい。すなわち、断面Ｃにおいて、第２の翼２０２の正圧面１３１と内周端部１３４との接続部で正圧面１３１に接する線を内周端部１３４側に延長した線が、回転軸１４０の反回転方向側を通るようにしてもよい。この場合、第１の翼２０１の方が第２の翼２０２よりも、正圧面１３１の内周端部１３４側が反回転方向側に、より大きく傾くようにするとよい。第１の翼２０１の方が第２の翼２０２よりも内周側に配置されているため、第１の翼２０１の正圧面１３１の内周側を、より大きく反回転方向側に傾けることで、羽根車１１０の外周側から内周側に向かって翼１３０の間を通過する気流を、より一層、反回転方向側に向きやすくすることが可能である。 Note that when the impeller 110 has the second blades 202, the same may be applied to the second blades 202. That is, in the cross section C, a line extending from a line that is in contact with the positive pressure surface 131 at the connection point between the positive pressure surface 131 and the inner peripheral end 134 of the second blade 202 toward the inner peripheral end 134 side is a line that extends toward the inner peripheral end 134 side. It may be made to pass on the rotation direction side. In this case, it is preferable that the inner peripheral end 134 side of the pressure surface 131 of the first blade 201 is tilted more toward the counter-rotational direction than the second blade 202. Since the first blade 201 is arranged closer to the inner circumference than the second blade 202, the inner circumference of the pressure surface 131 of the first blade 201 can be tilted more toward the counter-rotation direction. , it is possible to make the airflow passing between the blades 130 from the outer circumferential side to the inner circumferential side of the impeller 110 even more likely to be oriented in the counter-rotational direction.
　本開示は、回転軸方向に予め設定された間隔で配置された複数の支持部材と、隣り合う支持部材の間に設けられ、支持部材の外周寄りで、かつ、周方向に間隔をあけて配置された複数の翼とを備えたクロスフローファンに利用できる。また、本開示は、クロスフローファンを備えた送風装置及び冷凍サイクル装置にも利用できる。 The present disclosure includes a plurality of support members arranged at preset intervals in the direction of a rotation axis, and provided between adjacent support members, and arranged near the outer periphery of the support members and spaced apart in the circumferential direction. Available for cross flow fans with multiple blades. Further, the present disclosure can also be used in a blower device and a refrigeration cycle device equipped with a cross-flow fan.
　１０　　室内機
　１１　　室内機熱交換器
　１２　　筐体
　１３　　吸込口
　１４　　吹出口
　１５　　フィルター
　１６　　上下ベーン
　１７　　リアガイド
　１８　　スタビライザー
　２０　　室外機
　２１　　室外機熱交換器
　２２　　室外機ファン
　２３　　圧縮機
　２４　　膨張弁
　２５　　四方弁
　３０　　冷媒配管
１００　　クロスフローファン
１１０　　羽根車
１２０　　支持部材
１３０　　翼
１３１　　正圧面
１３２　　負圧面
１３３　　外周端部
１３４　　内周端部
１４０　　回転軸
１５０　　モータ
２０１　　第１の翼
２０２　　第２の翼
３０１　　第１領域
３０２　　第２領域
３０３　　変曲点 10 Indoor unit 11 Indoor unit heat exchanger 12 Housing 13 Suction port 14 Air outlet 15 Filter 16 Upper and lower vanes 17 Rear guide 18 Stabilizer 20 Outdoor unit 21 Outdoor unit heat exchanger 22 Outdoor unit fan 23 Compressor 24 Expansion valve 25 Four-way valve 30 Refrigerant piping 100 Crossflow fan 110 Impeller 120 Support member 130 Wings 131 Positive pressure surface 132 Negative pressure surface 133 Outer peripheral end 134 Inner peripheral end 140 Rotating shaft 150 Motor 201 First blade 202 Second blade 301 First region 302 Second area 303 Inflection point

Claims (9)

  1. 　回転軸方向に予め設定された間隔で配置され、円形又は円環形の平板状を呈する複数の支持部材と、
    　隣り合う前記支持部材の間に設けられ、前記支持部材の外周寄りで、かつ、周方向に間隔をあけて配置された複数の翼と、を備え、
    　それぞれの前記翼は、回転方向側の正圧面と反回転方向側の負圧面とを有し、
    　複数の前記翼は、少なくとも１つの第１の翼を有し、
    　前記第１の翼の前記正圧面は、前記回転軸に垂直な断面において、前記第１の翼の外周端部を含む第１領域で前記反回転方向側に凸形状であり、かつ、前記第１の翼の内周端部を含む第２領域で前記回転方向側に凸形状であるクロスフローファン。     A plurality of support members arranged at preset intervals in the direction of the rotation axis and having a circular or annular flat plate shape;
    a plurality of wings provided between adjacent support members and arranged near the outer periphery of the support member and spaced apart in the circumferential direction;
    Each of the blades has a pressure surface on the rotation direction side and a suction surface on the counter rotation direction side,
    the plurality of wings have at least one first wing;
    The positive pressure surface of the first blade has a convex shape toward the counter-rotation direction in a first region including an outer peripheral end of the first blade in a cross section perpendicular to the rotation axis, and A cross flow fan having a second region including an inner circumferential end of one blade having a convex shape in the rotation direction side.
  2. 　前記第１の翼の前記負圧面は、前記回転軸に垂直な断面において、前記第１領域で前記反回転方向側に凸形状であり、かつ、前記第２領域で前記回転方向側に凸形状である請求項１に記載のクロスフローファン。 The suction surface of the first blade has a convex shape in the first region in the opposite rotation direction, and a convex shape in the second region in the rotation direction in a cross section perpendicular to the rotation axis. The cross flow fan according to claim 1.
  3. 　前記回転軸に垂直な断面において、前記第１領域の凸形状の曲率は、前記第２領域の凸形状の曲率よりも大きい請求項１又は請求項２に記載のクロスフローファン。 3. The cross-flow fan according to claim 1, wherein the curvature of the convex shape of the first region is larger than the curvature of the convex shape of the second region in a cross section perpendicular to the rotation axis.
  4. 　前記第１領域の凸形状の径方向の長さは、前記第２領域の凸形状の径方向の長さより長い請求項１から請求項３のいずれか一項に記載のクロスフローファン。 The cross flow fan according to any one of claims 1 to 3, wherein the radial length of the convex shape of the first region is longer than the radial length of the convex shape of the second region.
  5. 　複数の前記翼は、第２の翼をさらに有し、
    　前記第２の翼の前記正圧面は、前記回転軸に垂直な断面において、前記第２の翼の外周端部から前記第２の翼の内周端部までの領域で前記反回転方向側に凸形状であり、
    　前記第１の翼同士の間に、少なくとも１つの前記第２の翼が配置される請求項１から請求項４のいずれか一項に記載のクロスフローファン。     The plurality of wings further includes a second wing,
    The positive pressure surface of the second blade is located on the counter-rotation direction side in a region from the outer peripheral end of the second blade to the inner peripheral end of the second blade in a cross section perpendicular to the rotation axis. It has a convex shape,
    The cross-flow fan according to any one of claims 1 to 4, wherein at least one of the second blades is arranged between the first blades.
  6. 　前記第２の翼の数は、前記第１の翼の数よりも多い請求項５に記載のクロスフローファン。 The cross flow fan according to claim 5, wherein the number of the second blades is greater than the number of the first blades.
  7. 　前記回転軸に垂直な断面において、前記第１の翼の前記正圧面と前記内周端部との接続部で前記正圧面に接する線を前記内周端部側に延長した線は、前記回転軸の前記反回転方向側を通る請求項１から請求項６のいずれか一項に記載のクロスフローファン。 In a cross section perpendicular to the rotational axis, a line extending toward the inner peripheral end side a line that is in contact with the positive pressure surface at the connection point between the positive pressure surface and the inner peripheral end of the first blade is a line that extends toward the inner peripheral end side. The cross flow fan according to any one of claims 1 to 6, which passes through the opposite rotation direction side of the shaft.
  8. 　請求項１から請求項７のいずれか一項に記載のクロスフローファンを備えた送風装置。 A blower device comprising the cross flow fan according to any one of claims 1 to 7.
  9. 　請求項１から請求項７のいずれか一項に記載のクロスフローファンと、
    　前記クロスフローファンにより生成された空気流と冷媒との間で熱交換を行わせる熱交換器と、を備えた冷凍サイクル装置。     The cross flow fan according to any one of claims 1 to 7,
    A refrigeration cycle device comprising: a heat exchanger that performs heat exchange between an air flow generated by the cross-flow fan and a refrigerant.
PCT/JP2022/020363 2022-05-16 2022-05-16 Cross flow fan, blowing device, and refrigeration cycle device WO2023223383A1 (en)

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0479991U (en) * 1990-11-26 1992-07-13
CN112160937A (en) * 2020-09-21 2021-01-01 华中科技大学 Cross-flow fan blade

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0479991U (en) * 1990-11-26 1992-07-13
CN112160937A (en) * 2020-09-21 2021-01-01 华中科技大学 Cross-flow fan blade

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