WO2023223383A1 - Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération - Google Patents

Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération 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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WO
WIPO (PCT)
Prior art keywords
blade
cross
flow fan
blades
region
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Application number
PCT/JP2022/020363
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English (en)
Japanese (ja)
Inventor
惇司 河野
拓矢 寺本
奈穂 安達
Original Assignee
三菱電機株式会社
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.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/020363 priority Critical patent/WO2023223383A1/fr
Publication of WO2023223383A1 publication Critical patent/WO2023223383A1/fr

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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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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un ventilateur à flux transversal qui peut supprimer une augmentation de résistance à la ventilation entre des pales d'une turbine. À cet effet, un ventilateur à flux transversal (100) comprend : une pluralité d'éléments de support (120) qui sont disposés à un intervalle prédéfini dans une direction d'axe de rotation, et qui ont une forme de plaque circulaire ou annulaire ; et une pluralité de pales (130) qui sont disposées entre les éléments de support (120) adjacentes les unes aux autres, et qui sont disposées plus près de la circonférence externe des éléments de support (120) et espacées les unes des autres dans une direction circonférentielle. Chacune des pales (130) a une surface de pression positive (131) sur un côté de direction de rotation et une surface de pression négative (132) sur un côté de direction anti-rotation. La pluralité de pales (130) comprend au moins une première pale (201). La surface de pression positive (131) de la première pale (201) a, dans une section transversale de celle-ci perpendiculaire à un axe de rotation (140), une forme en saillie sur le côté de direction anti-rotation dans une première zone (301) comprenant une extrémité circonférentielle externe (133) de la première pale (201), et a une forme en saillie sur le côté de direction de rotation dans une seconde zone (302) comprenant une extrémité circonférentielle interne (134) de la première pale (201).
PCT/JP2022/020363 2022-05-16 2022-05-16 Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération WO2023223383A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/020363 WO2023223383A1 (fr) 2022-05-16 2022-05-16 Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération

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Application Number Priority Date Filing Date Title
PCT/JP2022/020363 WO2023223383A1 (fr) 2022-05-16 2022-05-16 Ventilateur à flux transversal, dispositif de soufflage, et dispositif à cycle de réfrigération

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WO2023223383A1 true WO2023223383A1 (fr) 2023-11-23

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0479991U (fr) * 1990-11-26 1992-07-13
CN112160937A (zh) * 2020-09-21 2021-01-01 华中科技大学 一种贯流风叶

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0479991U (fr) * 1990-11-26 1992-07-13
CN112160937A (zh) * 2020-09-21 2021-01-01 华中科技大学 一种贯流风叶

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