WO2023084652A1 - 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
WO2023084652A1
WO2023084652A1 PCT/JP2021/041402 JP2021041402W WO2023084652A1 WO 2023084652 A1 WO2023084652 A1 WO 2023084652A1 JP 2021041402 W JP2021041402 W JP 2021041402W WO 2023084652 A1 WO2023084652 A1 WO 2023084652A1
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WO
WIPO (PCT)
Prior art keywords
cross
support ring
flow fan
blade
notch
Prior art date
Application number
PCT/JP2021/041402
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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.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2021/041402 priority Critical patent/WO2023084652A1/fr
Priority to JP2023559269A priority patent/JPWO2023084652A1/ja
Priority to CN202180103855.5A priority patent/CN118176364A/zh
Publication of WO2023084652A1 publication Critical patent/WO2023084652A1/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 cross-flow fans, air blowers, and refrigeration cycle devices.
  • a known cross-flow fan is composed of a fixed plate and a blade integrally molded with resin with the fixed plate, and in which the outer peripheral edge of the blade is extended further to the outer periphery than the fixed plate (see, for example, Patent Document 1).
  • a cross-flow fan as shown in Patent Document 1 includes a support ring (fixed plate) and blades (blades) fixed to the support ring, and the outer ends of the blades are positioned closer to the outer periphery than the outer periphery of the support ring. protrudes to In other words, over the entire circumference of the support ring, the support ring lies only radially inward of the outer edge of the airfoil. In such prior art, part of the airflow passing between the blades flows around the ends of the blades where there is no support ring and leaks from the pressure surface to the suction surface, resulting in a decrease in air volume.
  • This disclosure has been made to solve such problems. It is an object of the present invention to provide a cross-flow fan, an air blower, and a refrigerating cycle device capable of achieving a high airflow without enlarging the size of the fan.
  • a cross-flow fan is provided between a plurality of support rings arranged at predetermined intervals in a rotation axis direction, and adjacent support rings, near the outer periphery of the support rings and on the periphery. a plurality of wings spaced apart in a direction, wherein the support ring is formed with cutouts cut from the outer peripheral end to the inner peripheral side between the adjacent wings, The outer diameter of the support ring at the notch is smaller than the distance from the axis of rotation to the outer ends of the blades.
  • the cross flow fan according to the present disclosure is provided between a plurality of support rings arranged at predetermined intervals in the direction of the rotation axis, and the adjacent support rings, near the outer periphery of the support rings, and and a plurality of circumferentially spaced wings, wherein the support ring is formed with a plurality of circumferentially alternating protrusions and recesses on the surface to which the wings are connected. , the wings are connected to the recesses of the support ring.
  • a blower device includes a cross-flow fan configured as described above.
  • a refrigeration cycle apparatus includes a cross-flow fan configured as described above, and a heat exchanger that exchanges heat between the airflow generated by the cross-flow fan and the refrigerant.
  • the cross-flow fan, the blower device, and the refrigeration cycle device according to the present disclosure, it is possible to increase the air volume without increasing the size of the fan.
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle apparatus 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. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle apparatus according to Embod
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 2 is a cross-sectional view showing an example of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 4 is a perspective view showing a modification of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 5 is a front view showing a modification of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 5 is an enlarged cross-sectional view of a main part showing a modification of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 4 is a perspective view showing a modification of the impeller of the cross-flow fan according to Embodiment 1;
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle apparatus.
  • FIG. 2 is a cross-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 cross-flow fan.
  • 4 to 10 are cross-sectional views showing examples of impellers of cross-flow fans.
  • FIG. 11 is a perspective view showing a modification of the impeller of the cross-flow fan.
  • FIG. 12 is a front view showing a modification of the impeller of the cross-flow fan.
  • FIG. 13 is an enlarged cross-sectional view of a main part showing a modification of the impeller of the cross-flow fan.
  • FIG. 14 is a perspective view showing a modification of the impeller of the cross-flow fan.
  • FIG. 1 shows the configuration of an air conditioner as an example of a refrigeration cycle device equipped with a cross-flow fan according to the present disclosure.
  • a refrigeration cycle apparatus provided with a cross-flow fan according to the present disclosure other than an air conditioner, for example, a showcase or the like can be cited.
  • the air conditioner has a function of blowing air. Therefore, the air conditioner described here is also an example of an air blower equipped with 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 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 circulatingly provided between the indoor unit heat exchanger 11 of the indoor unit 10 and the outdoor unit heat exchanger 21 of the outdoor unit 20 .
  • Refrigerant is sealed in the refrigerant pipe 30 .
  • the refrigerant enclosed 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 a ring. Therefore, a refrigerant circuit is formed in which the refrigerant circulates between the indoor unit heat exchanger 11 and the outdoor unit heat exchanger 21 .
  • the compressor 23 is a device that compresses the supplied refrigerant to increase the pressure and temperature of the refrigerant.
  • a rotary compressor, a scroll compressor, a reciprocating compressor, or the like can be used as the compressor 23, for example.
  • 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 around the indoor heat exchanger 11 .
  • the cross-flow fan 100 blows indoor air so as to pass around the indoor heat exchanger 11, promotes heat exchange between the refrigerant and the air in the indoor heat exchanger 11, and facilitates heat exchange. The air heated or cooled by 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 as to pass around the outdoor unit heat exchanger 21 to promote heat exchange between the refrigerant and the air in the outdoor unit heat exchanger 21 .
  • the refrigerant circuit configured in this way exchanges heat between the refrigerant and the air in each of the indoor unit heat exchanger 11 and the outdoor unit heat exchanger 21, thereby Acts as a heat pump to move heat in At this time, by switching the four-way valve 25, the circulation direction of the refrigerant in the refrigerant circuit can be reversed to switch between the cooling operation and the heating operation of the air conditioner.
  • the indoor unit 10 includes a housing 12.
  • the housing 12 is installed indoors.
  • the indoor unit heat exchanger 11 and the cross-flow fan 100 are housed inside the housing 12 .
  • 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.
  • a blowout port 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 passage leading from the suction port 13 to the air outlet 14 is formed inside the housing 12 .
  • a filter 15 is installed at the suction port 13 .
  • the filter 15 is for removing relatively large dirt, dust, dirt, etc. from the air entering the housing 12 from the suction port 13 .
  • the 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 passage in the housing 12 to heat or cool the air flowing through the air passage. Whether the air is heated or cooled depends on whether the air conditioner is in heating operation or cooling operation.
  • a cross-flow fan 100 is installed on the leeward side of the indoor unit heat exchanger 11 in the air passage described above.
  • the cross-flow fan 100 is for generating an air flow from the suction port 13 to the blow-out 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 inside the housing 12 .
  • 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 spirally arranged such that the distance from the impeller of the cross flow fan 100 increases from the indoor unit heat exchanger 11 side to the outlet 14 side.
  • the outlet 14 is provided with upper and lower vanes 16 .
  • the upper and lower vanes 16 are for adjusting the blowing angle of the air blown out from the blowing port 14 .
  • the indoor unit 10 can change the blowing direction up and down.
  • the outlet 14 is also provided with left and right vanes. The left and right vanes are for adjusting the blowing angle in the left and right direction of the air blown out from the blower port 14 .
  • an air flow from the suction port 13 to the blowout port 14 is generated in the air passage, sucking air from the suction port 13 and blowing the air out from the blowout port 14 .
  • the air sucked from the suction port 13 becomes an air flow that passes through the air passage inside the housing 12 in order of the filter 15 , the indoor unit heat exchanger 11 and the cross flow fan 100 and is blown out from the blowout port 14 .
  • the direction of the air blown out from the outlet 14, that is, the blowing direction 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 into the room.
  • the indoor unit 10 can change the temperature and direction of the blown airflow.
  • the cross-flow fan 100 includes an impeller 110 and a motor 150.
  • Impeller 110 includes support ring 120 , blades 130 and rotating shaft 140 .
  • Motor 150 rotates impeller 110 around rotating shaft 140 .
  • the impeller 110 includes a plurality of support rings 120.
  • the support ring 120 is a plate-like member having an annular shape.
  • the plurality of support rings 120 are arranged at predetermined intervals in a direction parallel to the rotation axis 140 (hereinafter also referred to as the direction of the rotation axis 140).
  • a rotating shaft 140 of the impeller 110 is provided through the center of the annular shape of the plurality of support rings 120 .
  • a plurality of wings 130 are provided between adjacent support rings 120 .
  • a plurality of wings 130 are provided near the outer circumference of the support ring 120 .
  • the plurality of wings 130 are aligned along the circumferential direction of the support ring 120 at intervals.
  • each of the plurality of airfoils 130 has a pressure side 131 and a suction side 132 and an outer end 133 and an inner end 134 .
  • the pressure side 131 is the side of the blade 130 facing in the direction of rotation.
  • the suction surface 132 is the surface of the blade 130 facing away from the direction of rotation.
  • Outer end 133 is the end of blade 130 furthest from axis of rotation 140 .
  • Inner end 134 is the end of wing 130 closest to axis of rotation 140 .
  • the blades 130 are connected to both flat plate-like surfaces of the support ring 120 in the middle.
  • one side of the support ring 120 is called a first side
  • the other side is called a second side. That is, the second surface is the back surface of the first surface.
  • wings 130 are connected to a first side of a support ring 120 and wings 130 are also connected to a second side of the same support ring 120 .
  • the positions of the wings 130 connected to the first surface of the support ring 120 and the positions of the wings 130 connected to the second surface of the same support ring 120 are arranged so as not to overlap. It is
  • a notch 121 is formed in the support ring 120 in the cross-flow fan 100 according to this embodiment.
  • the notch portion 121 is formed by notching the support ring 120 from the outer peripheral end toward the inner peripheral side.
  • the cutouts 121 are provided between adjacent wings 130 on one surface of the support ring 120 .
  • Outer end 133 of each wing 130 is located in support ring 120 where cutout 121 is not formed.
  • the number of notches 121 formed in one support ring 120 is the same as the number of blades 130 connected to the support ring 120 .
  • the outer diameter of the notch 121 of the support ring 120 is smaller than the distance from the rotating shaft 140 to the outer end of the blade 130 .
  • the outer diameter of the notch 121 of the support ring 120 is, for example, the distance from the rotating shaft 140 to the notch bottom (the deepest point of the notch) of the notch 121 .
  • the notch bottom of the notch portion 121 is a portion where the outer diameter of the support ring 120 is the smallest.
  • the cross-flow fan 100 configured as described above, by providing the cutout portion 121 in the support ring 120 on the side of the outer end 133 of the blade 130, the airflow from between the blades 130 flows into the space of the cutout portion 121. influx. Therefore, the airflow from between the blades 130 is likely to flow into the downstream side of the support ring 120 at the location where the notch 121 is provided.
  • the notch 121 in the support ring 120 by not providing the notch 121 in the support ring 120 on the side of the inner end 134 of the blade 130 , it is possible to suppress the generation of the flow around the inner end 134 of the blade 130 .
  • the low wind speed region downstream of the support ring 120 can be reduced, and the cross flow fan 100 can increase the air volume without enlarging the size of the fan.
  • an effect of reducing noise can also be obtained.
  • the notch 121 has a trapezoidal shape.
  • FIG. 4 shows a configuration example of the support rings 120 at both ends in the direction of the rotating shaft 140 .
  • the notch 121 is provided between adjacent wings 130 respectively.
  • the outer end 133 of each blade 130 is arranged at a location where the notch 121 is not formed in the support ring 120 .
  • Outer diameter A at notch 121 of support ring 120 is smaller than distance B from rotating shaft 140 to the outer end of blade 130 .
  • FIG. 5 shows a configuration example of the support ring 120 located in the middle other than at both ends.
  • the position of the wings 130 connected to the first surface which is one surface of the intermediate support ring 120
  • the position of the wings 130 connected to the second surface which is the other surface of the same support ring 120.
  • the positions are arranged so that they do not overlap. Therefore, as shown in the figure, two notches 121 are arranged between the wings 130 connected to the first surface of the support ring 120 .
  • two notches 121 are also arranged between the wings 130 connected to the second surface of the support ring 120 .
  • the shape of the notch 121 is V-shaped.
  • the notch 121 is arranged on the rotational direction side of the intermediate position between the adjacent blades 130 .
  • a portion of the notch 121 follows the shape of the suction surface 132 of the blade 130 .
  • FIG. 6 shows a configuration example of the support rings 120 at both ends in the direction of the rotating shaft 140 .
  • FIG. 7 shows a configuration example of the support ring 120 located in the middle other than at both ends.
  • cutouts 121 are provided between adjacent wings 130 respectively. Outer end 133 of each wing 130 is located in support ring 120 where cutout 121 is not formed. Outer diameter A at notch 121 of support ring 120 is smaller than distance B from rotating shaft 140 to the outer end of blade 130 .
  • the arrows shown in FIG. 6 indicate the rotation direction of the impeller 110 .
  • the notch 121 is arranged on the rotational direction side of the intermediate position between the adjacent blades 130 . That is, the distance from the notch 121 to the pressure surface 131 of the blade 130 on the counter-rotational direction side is longer than the distance from the notch 121 to the suction surface 132 of the blade 130 on the rotation direction side. Furthermore, the notch 121 extends along the suction surface 132 of the blade 130 at the portion indicated by C in the figure.
  • the notch 121 Since the pressure on the pressure surface 131 side of the blade 130 is high, if the notch 121 is provided in the vicinity of the pressure surface 131 side of the blade 130 , the air flow easily leaks from the notch 121 . Then, the flow around the outer end 133 of the blade 130 tends to cause turbulence in the airflow. Therefore, by arranging the notch 121 closer to the rotation direction side than the intermediate position of the adjacent blades 130, it is possible to suppress the occurrence of the flow around the outer end 133 of the blade 130 on the pressure surface 131 side of the blade 130. .
  • the shape of the notch 121 is V-shaped.
  • the width of the notch 121 on the rotation direction side from the point where the outer diameter of the support ring 120 is the smallest is smaller than the width on the counter-rotation direction side from the point where the outer diameter of the support ring 120 is the smallest.
  • FIG. 8 shows a configuration example of the support rings 120 at both ends in the direction of the rotating shaft 140 .
  • FIG. 9 shows a configuration example of the support ring 120 located in the middle other than at both ends.
  • cutouts 121 are provided between adjacent wings 130 respectively. Outer end 133 of each wing 130 is located in support ring 120 where cutout 121 is not formed. Outer diameter A at notch 121 of support ring 120 is smaller than distance B from rotating shaft 140 to the outer end of blade 130 .
  • the arrow shown in FIG. 8 indicates the rotation direction of the impeller 110 .
  • the portion where the outer diameter of the support ring 120 is the smallest, that is, the width of the notch 121 on the rotation direction side from the notch bottom is indicated by E in the drawing.
  • the width of the notch 121 on the side opposite to the rotation direction from the notch bottom is indicated by F in the drawing.
  • the width E on the side of the rotation direction from the bottom of the notch is smaller than the width F on the side opposite to the direction of rotation from the bottom of the notch. 8 and 9, a portion of the notch 121 follows the shape of the suction surface 132 of the blade 130, as in the configuration examples shown in FIGS.
  • the width of the notch 121 on the side of the rotation direction from the bottom of the notch is smaller than the width on the side opposite to the direction of rotation from the bottom of the notch.
  • the portion of the notch 121 that conforms to the shape of the suction surface 132 of the blade 130 , the end surface of the support ring 120 at may be integrated with the suction surface 132 of the blade 130 to form the blade surface.
  • the area of the suction surface 132 of the blade 130 can be increased by the thickness of the support ring 120 . Therefore, it is possible to expand the effective blade area for generating the airflow and increase the air volume.
  • the position of the blades 130 connected to the first surface which is one surface of the support ring 120 in the middle, and the position of the blades 130 connected to the other surface of the same support ring 120
  • the positions of the wings 130 connected to the second surface may be arranged so as to overlap each other.
  • the configuration of the support ring 120 is the same as the configuration of the support rings 120 at both ends in the direction of the rotating shaft 140 described above. That is, as shown in FIGS. 4, 6 and 8, one notch 121 is arranged between the wings 130 connected to the first surface of the support ring 120 . Similarly, one notch 121 is also arranged between the wings 130 connected to the second surface of the support ring 120 .
  • the number of notches 121 formed in one support ring 120 is the same as the number of blades 130 connected to one surface of the support ring 120 .
  • the inner diameter of the annular support ring 120 is assumed to be D1. Also, let D2 be the distance from the rotating shaft 140 to the inner end of the blade 130 .
  • the inner diameter D1 of the support ring 120 is half the distance D2 from the rotating shaft 140 to the inner end of the blade 130, that is, D2/2 or more, and The distance to the inner end of 130 should be less than or equal to D2.
  • the inner diameter D1 of the support ring 120 By setting the inner diameter D1 of the support ring 120 to be equal to or less than the distance D2 from the rotating shaft 140 to the inner end of the blade 130, it is possible to suppress the occurrence of airflow turbulence due to the airflow going around the inner end 134 of the blade 130.
  • the inner diameter D1 of the support ring 120 By setting the inner diameter D1 of the support ring 120 to be equal to or less than the distance D2 from the rotating shaft 140 to the inner end of the blade 130, the circulation vortex generated inside the impeller 110 is divided by the support ring 120, and the circulation vortex continues. It is possible to suppress the destabilization of the flow caused by the influence of each other.
  • the inner diameter D1 of the support ring 120 should be half the distance D2 from the rotating shaft 140 to the inner end of the blade 130, that is, D2/2 or more, and should be less than or equal to the distance D2 from the rotating shaft 140 to the inner end of the blade 130. Therefore, it is possible to both suppress the destabilization of the airflow in the impeller 110 and reduce the weight of the impeller 110 .
  • the support ring 120 is not flat but corrugated.
  • the support ring 120 is formed with a plurality of protrusions 122 and recesses 123 alternately arranged in the circumferential direction on the surface to which the blades 130 are connected.
  • the positions of the protrusions 122 on the first surface of the support ring 120 become recesses 123 on the second surface.
  • the positions of the concave portions 123 on the first surface of the support ring 120 become convex portions 122 on the second surface.
  • the back side of the protrusion 122 on one side of the support ring 120 is the recess 123 .
  • a protrusion 122 is provided on one side of the support ring 120 on the back side of the recess 123 .
  • These convex portions 122 and concave portions 123 are arranged in a curved radial shape in accordance with the cross-sectional shape of the blade 130 .
  • the wings 130 are then connected to the recesses 123 of the support ring 120 .
  • the ends of the wings 130 are for example welded to the recesses 123 to secure the wings 130 to the support ring 120 .
  • the concave portion 123 on the first surface of the support ring 120 and the concave portion 123 on the second surface are necessarily arranged so as not to overlap each other. Therefore, by connecting the wings 130 to the recesses 123 of the support ring 120, the positions of the wings 130 connected to the first surface of the support ring 120 and the positions of the wings 130 connected to the second surface do not overlap. will be placed.
  • the blades of the blades 130 arranged between the support rings 120 in the direction of the rotation axis 140 can be adjusted without greatly changing the overall width of the impeller 110 in the direction of the rotation axis 140 . Width can be increased. Therefore, it is possible to increase the effective blade area for generating airflow and increase the air volume.
  • the support ring 120 without the notch 121 may be provided with a projection 122 and a recess 123, and the blade 130 may be connected to the recess 123 of the support ring 120.
  • the width of each blade 130 arranged between the support rings 120 in the direction of the rotation axis 140 can be increased without significantly changing the overall width of the impeller 110 in the direction of the rotation axis 140 . Therefore, it is possible to increase the effective blade area for generating airflow and increase the air volume.
  • the present disclosure is provided between a plurality of support rings arranged at predetermined intervals in the direction of the rotation axis and adjacent support rings, arranged near the outer periphery of the support rings and spaced apart in the circumferential direction.
  • Available for cross-flow fans with multiple blades and The present disclosure can also be used for blowers and refrigerating cycle devices equipped with cross-flow fans.

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  • Engineering & Computer Science (AREA)
  • 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 permet de souffler une grande quantité d'air sans augmentation de la taille. Ce ventilateur à flux transversal (100) comprend : une pluralité de bagues de support (120) disposée à un intervalle prédéfini dans la direction d'un arbre rotatif (140) ; et une pluralité de pales (130) qui sont chacune disposées entre des bagues de support adjacentes parmi les bagues de support (120), et qui sont disposées plus près de la circonférence externe des bagues de support (120) et espacées les unes des autres dans une direction circonférentielle. Dans chacune des bagues de support (120), des découpes (121) découpées à partir de parties d'extrémité circonférentielles externes vers le côté circonférentiel interne sont formées entre des lames adjacentes parmi les pales (130). Le diamètre extérieur des bagues de support (120) au niveau des découpes (121) est inférieur à la distance de l'arbre rotatif (140) aux extrémités externes des pales (130).
PCT/JP2021/041402 2021-11-10 2021-11-10 Ventilateur à flux transversal, dispositif de soufflage et dispositif à cycle de réfrigération WO2023084652A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2021/041402 WO2023084652A1 (fr) 2021-11-10 2021-11-10 Ventilateur à flux transversal, dispositif de soufflage et dispositif à cycle de réfrigération
JP2023559269A JPWO2023084652A1 (fr) 2021-11-10 2021-11-10
CN202180103855.5A CN118176364A (zh) 2021-11-10 2021-11-10 横流风扇、送风装置以及制冷循环装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2021/041402 WO2023084652A1 (fr) 2021-11-10 2021-11-10 Ventilateur à flux transversal, dispositif de soufflage et dispositif à cycle de réfrigération

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WO2023084652A1 true WO2023084652A1 (fr) 2023-05-19

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PCT/JP2021/041402 WO2023084652A1 (fr) 2021-11-10 2021-11-10 Ventilateur à flux transversal, dispositif de soufflage et dispositif à cycle de réfrigération

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CN (1) CN118176364A (fr)
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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50147904U (fr) * 1974-05-23 1975-12-08
WO2017073593A1 (fr) * 2015-10-30 2017-05-04 ダイキン工業株式会社 Ventilateur tangentiel

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50147904U (fr) * 1974-05-23 1975-12-08
WO2017073593A1 (fr) * 2015-10-30 2017-05-04 ダイキン工業株式会社 Ventilateur tangentiel

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JPWO2023084652A1 (fr) 2023-05-19

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