WO2022201218A1 - Roue à aubes et soufflante à aubes multiples - Google Patents

Roue à aubes et soufflante à aubes multiples Download PDF

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Publication number
WO2022201218A1
WO2022201218A1 PCT/JP2021/011587 JP2021011587W WO2022201218A1 WO 2022201218 A1 WO2022201218 A1 WO 2022201218A1 JP 2021011587 W JP2021011587 W JP 2021011587W WO 2022201218 A1 WO2022201218 A1 WO 2022201218A1
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WO
WIPO (PCT)
Prior art keywords
impeller
side wall
main plate
opening
air
Prior art date
Application number
PCT/JP2021/011587
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English (en)
Japanese (ja)
Inventor
健一 迫田
一輝 岡本
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/JP2021/011587 priority Critical patent/WO2022201218A1/fr
Priority to JP2023508143A priority patent/JP7292549B2/ja
Publication of WO2022201218A1 publication Critical patent/WO2022201218A1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer

Definitions

  • the present disclosure relates to impellers and multi-blade fans.
  • a multi-blade blower also known as a sirocco fan
  • a sirocco fan is a device that uses the centrifugal force acting on the air by an impeller that rotates inside the fan casing to pressurize the air sucked in through the air inlet and discharge it through the air outlet.
  • Such fans are used in ventilation ducts in factories or buildings, devices for forcibly circulating air in places where static pressure is relatively high, such as under the floors of houses, or in rooms such as kitchens and cooking areas. Used as a device for ventilation.
  • An impeller of a multi-blade blower generally includes a rotating main plate and a plurality of blades provided along the outer edge of the main plate. Air sucked from the intake port flows into a space surrounded by a plurality of blades and the main plate, and is sent out while being pressurized radially outward of the main plate from between the blades by centrifugal force. After the air pressurized by the impeller flows between the impeller and the fan casing, it is exhausted from the exhaust port through the inlet port of the duct.
  • the duct guides air toward the exhaust port and is connected to the fan casing via tongues extending in the direction of the rotation axis of the impeller outside the radius of rotation of the impeller.
  • the impeller of the multi-blade blower has a cup-shaped cup portion provided in the center of the rotating main plate.
  • a motor for rotating the impeller is installed inside the cup portion.
  • the amount of heat generated by the motor increases. If the temperature due to the heat generated by the motor exceeds the allowable temperature range set for the motor, it may lead to failure of the multi-blade blower. Therefore, for example, in Patent Document 1, in a blower, a through hole is formed in the cup portion to communicate the outside and the inside of the cup portion, and an air flow for cooling the motor is introduced into the inside of the cup portion. It has been proposed to provide two wings.
  • the present disclosure is intended to solve the above-described problems, and aims to obtain an impeller and a multi-blade fan that can cool the inside of the cup portion and suppress a decrease in air blowing performance.
  • An impeller includes a main plate that rotates about a rotation axis, and a plurality of blades that are fixed to the main plate at intervals along a circumference about the rotation axis, the main plate comprising: A plurality of blades are fixed, and has a flat portion having an opening in the center, and a cup portion provided on the flat portion, the cup portion having a lid facing the opening and a circumference of the opening. and a side wall connecting the lid portion and the flat portion, the side wall being inclined with respect to the rotation direction of the main plate.
  • the multi-blade blower includes the impeller, a fan casing housing the impeller and having an air inlet, a duct connected to the fan casing and having an air outlet, and a cup portion of the impeller. and a driving device for driving the impeller.
  • the impeller and the multi-blade blower of the present disclosure by arranging the side wall of the cup portion at an angle with respect to the rotation direction of the main plate, the inside of the cup portion is efficiently cooled, and the decrease in air blowing performance is prevented. can be suppressed.
  • FIG. 1 is a perspective view of a multi-blade fan according to Embodiment 1.
  • FIG. 1 is a perspective view of an impeller of a multi-blade fan according to Embodiment 1.
  • FIG. 2 is a schematic cross-sectional view of the impeller of the multi-blade fan according to Embodiment 1 cut along a plane perpendicular to the rotation axis;
  • FIG. 2 is a schematic cross-sectional view of the multi-blade fan according to Embodiment 1 cut along a plane parallel to the rotation axis;
  • FIG. 4 is a diagram illustrating a side wall of the impeller according to Embodiment 1;
  • FIG. 4 is a diagram for explaining the flow of air during operation of the multi-blade fan according to Embodiment 1;
  • FIG. 1 is a perspective view of an impeller of a multi-blade fan according to Embodiment 1.
  • FIG. 2 is a schematic cross-sectional view of the impeller of the multi-blade fan
  • FIG. 8 is a schematic cross-sectional view of the impeller of the multi-blade blower according to Embodiment 2 taken along a plane perpendicular to the rotation axis;
  • FIG. 10 is a schematic cross-sectional view of the multi-blade fan according to Embodiment 3 taken along a plane parallel to the rotation axis;
  • FIG. 11 is a schematic cross-sectional view of a multi-blade fan according to a modification of Embodiment 3 cut along a plane parallel to the rotation axis;
  • FIG. 11 is a schematic cross-sectional view of the multi-blade fan according to Embodiment 4 taken along a plane parallel to the rotation axis;
  • FIG. 11 is a schematic cross-sectional view of a multi-blade fan according to a modification of Embodiment 4 cut along a plane parallel to the rotation axis;
  • FIG. 1 is a perspective view of a multi-blade fan 1 according to Embodiment 1.
  • FIG. 2 is a perspective view of the impeller 4 of the multi-blade fan 1 according to Embodiment 1.
  • FIG. 3 is a schematic cross-sectional view of the impeller 4 of the multi-blade fan 1 according to Embodiment 1 taken along a plane perpendicular to the rotating shaft 7.
  • FIG. 4 is a schematic cross-sectional view of the multi-blade fan 1 according to Embodiment 1 taken along a plane parallel to the rotating shaft 7 .
  • the multi-blade fan 1 of the present embodiment is a device for forcibly flowing the air by pressurizing the air sucked from the air inlet 2 and discharging it from the air outlet 3 .
  • a multi-blade fan 1 includes an impeller 4 , a fan casing 13 , a duct 18 and a drive device 20 .
  • the fan casing 13 is composed of, for example, a hollow cylinder that forms a generally columnar space inside.
  • the fan casing 13 is a scroll-type fan casing that can be arranged so as to surround the entire impeller 4 in an internal space.
  • the shape of the space formed inside the fan casing 13 is not limited to a cylindrical shape, and may be, for example, a columnar shape with a polygonal cross section.
  • the fan casing 13 is arranged perpendicular to the rotating shaft 7 , and connects a lower end surface 14 and an upper end surface 15 facing each other to the outer edge of the lower end surface 14 and the outer edge of the upper end surface 15 . and a peripheral wall 16 extending to the
  • the upper end face 15 has an air intake port 2 so that air can flow between the impeller 4 and the outside of the fan casing 13 .
  • the intake port 2 is an opening formed in a region surrounded by tips of the plurality of blades 6 of the impeller 4 . It should be noted that, of the ends of the blades 6, the one away from the main plate 5 is called the "tip”, and the one connected to the main plate 5 is called the "base end”.
  • the upper end surface 15 is provided on the side of the intake port 2 (the tip side of the blade 6), and the lower end surface 14 is provided on the side of the main plate 5 of the impeller 4, respectively.
  • the intake port 2 of this embodiment is formed by a bell mouth 19 provided on the upper end surface 15 .
  • the bell mouth 19 is formed as an opening whose diameter gradually decreases from the outside to the inside of the fan casing 13 in order to allow air to flow smoothly through the air intake 2 and its vicinity. Further, the air intake port 2 is provided at a position where the center of the air intake port 2 and the rotating shaft 7 of the impeller 4 are substantially aligned.
  • the gap between the peripheral wall 16 of the fan casing 13 and the outer peripheral edge of the impeller 4 expands at a predetermined rate from the tongue 17 connected to the peripheral wall 16 to the duct 18 .
  • the air sent out from the impeller 4 can smoothly flow through the gap.
  • the flow path area of the air gradually expands from the tongue portion 17 to the duct 18, the static pressure of the air efficiently rises as the air flows through the gap.
  • the duct 18 is a hollow tube having a substantially rectangular cross section perpendicular to the air flow direction, and forms a flow path for guiding the air sent radially outward from the impeller 4 to the outside air. do.
  • One end of the duct 18 is fixed to the fan casing 13 and forms an inlet through which air flows into the duct 18 .
  • the other end of the duct 18 forms an exhaust port 3 for discharging the air that has flowed through the flow path inside the duct 18 to the outside air.
  • the duct 18 is formed from an extension plate 21 , a diffuser plate 22 , a duct bottom plate 23 and a duct top plate 24 .
  • the extension plate 21 is smoothly connected to the downstream end of the peripheral wall 16 of the fan casing 13 in the air flow direction, and is formed integrally with the fan casing 13 .
  • the diffuser plate 22 is connected to the upstream end of the peripheral wall 16 of the fan casing 13 in the direction of air flow, and is arranged so that the cross-sectional area of the flow path gradually expands in the direction of air flow in the duct 18 . It is arranged at a predetermined angle with the extension plate 21 .
  • the duct bottom plate 23 and the duct top plate 24 are plate members connected to the lower end surface 14 and the upper end surface 15 of the fan casing 13, respectively, and are connected to the outer edge portions of the extension plate 21 and the diffuser plate 22, and have a rectangular cross section. form a channel of shape.
  • the diffuser plate 22 and the peripheral wall 16 of the fan casing 13 are smoothly connected with a predetermined curvature radius from the lower end surface 14 to the upper end surface 15 of the fan casing 13 by the tongue portion 17 .
  • the tongue portion 17 serves as a branching point for the flow of air that has flowed into the fan casing 13 from the intake port 2 through the impeller 4 and is collected by the fan casing 13 and flows into the duct 18 . That is, the static pressure of the air flowing into the duct 18 rises while passing through the fan casing 13 and becomes higher than inside the fan casing 13 . Due to this pressure difference, the tongue portion 17 functions to block the flow of air that flows into the fan casing 13 again from the duct 18 .
  • the tongue portion 17 is formed with a predetermined radius of curvature. Therefore, even if the air collides with the tongue portion 17 when the air flows into the duct 18 from the fan casing 13, the turbulence generated at the tongue portion 17 can be reduced. As a result, it is possible to prevent the deterioration of air blowing performance and the increase of noise.
  • the radius of curvature of tongue 17 is constant in the direction of the rotation axis, but the radius of curvature of tongue 17 need not be constant in the direction of the rotation axis.
  • the curvature radius of the tongue portion 17 may be larger on the air inlet 2 side than on the lower end surface 14 side of the fan casing 13 .
  • the driving device 20 is a motor, and the rotating shaft of the motor is connected to the impeller 4.
  • the axis of rotation of the motor coincides with the axis of rotation 7 of the impeller 4 .
  • a side wall or bottom surface of the drive device 20 is fixed to the bottom surface 14 of the fan casing 13 .
  • the impeller 4 is a member that rotates in the rotational direction D shown in FIG. .
  • the impeller 4 has a main plate 5 and a plurality of blades 6 .
  • the main plate 5 is a circular plate that is rotatable around the rotation shaft 7 .
  • the main plate 5 rotates in the same rotational direction D as the impeller 4 .
  • the main plate 5 has a substantially cylindrical cup portion 9 with a lid provided in the center, and a flat portion 50 provided on the outer periphery of the cup portion 9 and to which the plurality of blades 6 are fixed.
  • a plurality of blades 6 are fixed near the outer peripheral edge of the flat portion 50 of the main plate 5 along the circumference around the rotating shaft 7 at regular intervals. Each blade 6 extends substantially perpendicularly from the plane portion 50 of the main plate 5 toward the intake port 2 . Each blade 6 is arranged such that the pressure surface and the suction surface are inclined at a predetermined angle with respect to the radial direction of the main plate 5 . In another embodiment, each blade 6 may be arranged such that the pressure surface and the suction surface are parallel to the radial direction of the main plate 5 .
  • the tip of each blade 6 is connected by a connecting portion 8 .
  • the connecting portion 8 is a series of annular members having an inner diameter or an outer diameter that can connect the tips of the plurality of blades 6 .
  • the connecting portion 8 may be an annular plate material having a width capable of covering the tips of the blades 6, or may be an annular member that connects the outer circumferences of the tip portions of the blades 6.
  • the flat portion 50 of the main plate 5 is an annular disc having an opening 11 in the center.
  • the flat portion 50 is arranged parallel to the lower end surface 14 of the fan casing 13 .
  • the cup portion 9 of the main plate 5 is provided on the flat portion 50 and comprises a circular lid portion 10 centered on the rotating shaft 7 and a plurality of side walls 12 connecting the lid portion 10 and the flat portion 50 .
  • the lid portion 10 of the cup portion 9 is arranged to face the opening portion 11 so that the center of the lid portion 10 coincides with the center of the opening portion 11 . That is, the opening 11 of the flat portion 50 serves as the opening of the cup portion 9 .
  • a rotating shaft of a driving device 20 is fixed to the center of the lid portion 10 . That is, the center of the lid portion 10 and the opening portion 11 becomes the rotation axis 7 .
  • the diameter of lid portion 10 is larger than the diameter of opening portion 11 .
  • a plurality of side walls 12 are arranged on a circumference around the rotating shaft 7 with a certain gap 120 between them.
  • a plurality of side walls 12 extend vertically from the flat portion 50 toward the lid portion 10 .
  • One ends of the plurality of side walls 12 are fixed around the opening 11 of the flat portion 50 .
  • the other ends of the plurality of side walls 12 are fixed near the outer peripheral edge of the lid portion 10 .
  • FIG. 5 is a diagram illustrating the side wall 12 of the impeller 4 according to Embodiment 1.
  • FIG. FIG. 5 schematically shows a cross section obtained by cutting the main plate 5 along a plane perpendicular to the rotating shaft 7 .
  • the lid portion 10 is indicated by a dashed line for reference.
  • the cross-sectional shape of each side wall 12 perpendicular to the rotation axis 7 is substantially arc-shaped.
  • each side wall 12 is arranged to be inclined at a predetermined inclination angle ⁇ other than 0 degree with respect to the rotation direction D of the main plate 5 .
  • the side wall in the case where the inclination angle with respect to the rotation direction D of the main plate 5 is 0 degrees is indicated by a dotted line.
  • the side wall 12 forms part of a cylindrical surface centered on the rotation axis 7 .
  • each side wall 12 of the present embodiment is arranged such that the front end portion 121 and the rear end portion 122 in the rotation direction D are not positioned on the same circumference around the rotation shaft 7 .
  • a front end portion 121 and a rear end portion 122 of each side wall 12 are arc-shaped.
  • the radius of the front end 121 and the rear end 122 of each side wall 12 may be the same or different.
  • the radius of the rear end 122 of each side wall 12 is larger than the radius of the front end 121 .
  • each side wall 12 is inclined such that the front end portion 121 of each side wall 12 is positioned on the inner peripheral side and the rear end portion 122 is positioned on the outer peripheral side.
  • the cup portion 9 has six side walls 12, but the number of side walls 12 is not limited to this.
  • the number of side walls 12 may be less than or greater than the number of blades 6 .
  • the dimension of each side wall 12 in the direction of the axis of rotation is smaller than the dimension of the blades 6 in the direction of the axis of rotation.
  • the dimension of each side wall 12 in the rotational direction D may be the same as the dimension of the blade 6 in the rotational direction D, or may be smaller or larger than the dimension in the rotational direction D of the blade 6 .
  • the cross-sectional shape of each side wall 12 perpendicular to the rotation axis 7 may be a streamline shape such as an airfoil instead of a substantially circular arc shape.
  • FIG. 6 is a diagram for explaining the flow of air during operation of the multi-blade fan 1 according to Embodiment 1.
  • FIG. 6 omits the illustration of the driving device 20, it is assumed that the driving device 20 is arranged inside the cup portion 9.
  • the air inside the impeller 4 is sent radially outward due to the centrifugal force generated by the rotation of the impeller 4 , and is discharged from the air inlet 2 to the impeller 4 .
  • Air flows into the interior of the The air sent out of the impeller 4 flows along the peripheral wall 16 of the fan casing 13 in the rotational direction of the impeller 4 .
  • the cross-sectional area between the impeller 4 and the peripheral wall 16 of the fan casing 13 increases in the direction of rotation of the impeller 4 , the dynamic pressure of the air flowing inside the fan casing 13 is converted into static pressure, and the fan casing 13 Gradually increase the static pressure inside.
  • the air with increased static pressure is discharged from the exhaust port 3 via the duct 18 .
  • each side wall 12 of the cup portion 9 Since the side walls 12 of the cup portion 9 are inclined with respect to the rotation direction D, the centrifugal force caused by the rotation of the impeller 4 causes the air inside the cup portion 9 to pass through the gaps 120 between the side walls 12. and radially outward. That is, each side wall 12 produces the same blowing effect as the blades 6 of the impeller 4 . Part of the air that has passed through the blades 6 and is sent into the fan casing 13 passes through the gap between the flat portion 50 of the main plate 5 and the lower end surface 14 due to the centrifugal force caused by the rotation of the side wall 12, and passes through the opening 11. Then, it is delivered to the inside of the impeller 4 again.
  • the drive device 20 is cooled as the air passing through the opening 11 flows over the surface of the drive device 20 located inside the cup portion 9 . Therefore, damage to the driving device 20 due to temperature rise of the driving device 20 can be suppressed.
  • part of the air sent from the impeller 4 to the inside of the fan casing 13 passes through the gap 120 between the side walls 12 again. That is, the air passes through the blades (side wall 12) having a pressurizing effect a plurality of times, improving the blowing performance.
  • the side wall 12 of the cup portion 9 can generate an air flow passing through the gap between the impeller 4 and the lower end surface 14 of the fan casing 13. can.
  • This air flow can efficiently cool the driving device 20, and can suppress a decrease in air blowing performance while maintaining the dimension of the multi-blade fan 1 in the rotation axis direction.
  • FIG. 7 is a schematic cross-sectional view of the impeller 4A of the multi-blade fan 1 according to Embodiment 2 taken along a plane perpendicular to the rotating shaft 7.
  • items that are not described below are the same as those in the first embodiment, and the same functions or configurations are described using the same reference numerals.
  • the inclination angle with respect to the rotation direction D of the main plate 5 continuously changes from the connection portion with the flat portion 50 to the connection portion with the lid portion 10.
  • the inclination angle of the side wall 12 may change linearly from the flat portion 50 to the lid portion 10, or may change quadratically.
  • the inclination angle of the side wall 12A connected to the plane portion 50 at an inclination angle other than 0 degree is continuously changed to 0 degree at a predetermined height in the rotation axis direction, and the lid portion is rotated from that height.
  • the angle of inclination may be maintained at 0 degrees up to the connecting portion with 10 .
  • the inclination angle of the side wall 12A is set to 0 up to a predetermined height in the rotation axis direction from the connection portion with the plane portion 50, and the side wall 12A is rotated from this height so that the lid portion 10 is connected at an inclination angle other than 0 degrees. may be changed.
  • the axial direction of the air passing through the gap 120 between the side walls 12A changes from the radial direction to the axial direction depending on the inclination angle of each side wall 12A. Due to the inertia of the air flow, the flow that has passed through the opening 11 is distributed in the rotation axis direction.
  • the inclination angle of the side wall 12A is formed so as to continuously change from the flat portion 50 to the lid portion 10 according to the velocity distribution of the air, the blowing effect due to the centrifugal force of the side wall 12A is improved, and the multi-blade blower is provided.
  • the air blowing performance of 1 is improved.
  • the inclination angle of the side wall 12A is such that, for example, when the main heat generating portion of the drive device 20 exists on the lower end surface 14 side of the fan casing 13, the amount of air passing through the side wall 12A on the side of the flat portion 50 increases. It is preferable to increase the inclination angle on the 50 side.
  • the main heat generating portion of the driving device 20 exists on the lid portion 10 side, it is preferable to increase the inclination angle of the lid portion 10 side so that more air passes through the side wall 12A on the lid portion 10 side. As a result, the drive device 20 can be efficiently cooled, and the blowing performance of the multi-blade fan 1 can be further improved.
  • FIG. 8 is a schematic cross-sectional view of the multi-blade fan 1 according to Embodiment 3 taken along a plane parallel to the rotating shaft 7. As shown in FIG. Although the drive device 20 is not shown in FIG. 8, it is assumed that the drive device 20 is arranged inside the cup portion 9B. Also, in Embodiment 3, items not described below are the same as those in Embodiment 1, and the same functions or configurations are described using the same reference numerals.
  • the radius of the opening 11 of the main plate 5 of the impeller 4B according to Embodiment 3 is formed larger than the radius of the lid portion 10 .
  • Each side wall 12B of the cup portion 9B extends from the flat portion 50 toward the lid portion 10 while being inclined with respect to the direction of gravity. Specifically, the end of each side wall 12 ⁇ /b>B connected to the flat portion 50 is arranged radially outside the main plate 5 relative to the end connected to the lid portion 10 .
  • the impeller 4B configured in this way, when the main plate 5 is viewed from the intake port 2 in the rotation axis direction, the side wall 12B can be seen to protrude to the outside of the lid portion 10. Therefore, the direction of flow of the air that has flowed into the interior of the impeller 4B from the intake port 2 due to the rotation of the impeller 4B is changed from the rotation axis direction to the radial direction by the side wall 12B before passing through the blades 6. . As a result, the blowing effect of the blades 6 is improved, and the cooling effect of the drive device 20 by the flow passing through the gap between the fan casing 13 and the main plate 5 can be obtained.
  • the radius of the opening 11 of the main plate 5 of the impeller 4B is larger than the radius of the lid 10
  • the upper and lower dies for injection molding can be The impeller 4B can be manufactured by moving in the rotation axis direction. Therefore, manufacturing of the impeller 4B is facilitated.
  • FIG. 9 is a schematic cross-sectional view of the multi-blade fan 1 according to the modification of Embodiment 3 taken along a plane parallel to the rotation shaft 7.
  • the radius of the lid portion 10 of the cup portion 9C of the impeller 4C is configured to be smaller than the distance from the rotating shaft 7 to the outer peripheral edge of the end portion of the side wall 12C connected to the lid portion 10.
  • FIG. 10 is a schematic cross-sectional view of the multi-blade fan 1 according to Embodiment 4 taken along a plane parallel to the rotating shaft 7. As shown in FIG. 10 omits illustration of the drive device 20, it is assumed that the drive device 20 is arranged inside the cup portion 9. As shown in FIG. Also, in Embodiment 4, items that are not described below are the same as those in Embodiment 1, and the same functions or configurations are described using the same reference numerals.
  • the radius of the opening 11 of the main plate 5 of the impeller 4D of the present embodiment is greater than the distance from the rotation shaft 7 to the inner peripheral end of the end of the side wall 12 connected to the plane portion 50. is large and smaller than the distance from the rotating shaft 7 to the outer peripheral edge of the side wall 12. As shown in FIG. 10, the radius of the opening 11 of the main plate 5 of the impeller 4D of the present embodiment is greater than the distance from the rotation shaft 7 to the inner peripheral end of the end of the side wall 12 connected to the plane portion 50. is large and smaller than the distance from the rotating shaft 7 to the outer peripheral edge of the side wall 12. As shown in FIG.
  • the impeller 4D configured in this way, the flow passing through the gap between the fan casing 13 and the plane portion 50 of the main plate 5 smoothly flows into the opening 11. Therefore, the flow passing through the opening 11 pressure drop is reduced and the flow rate through sidewall 12 is increased. As a result, the cooling effect of the driving device 20 is improved, and the blowing performance of the multi-blade fan 1 is further improved.
  • FIG. 11 is a schematic cross-sectional view of the multi-blade fan 1 according to the modification of the fourth embodiment taken along a plane parallel to the rotation shaft 7.
  • a bell mouth 25 whose diameter gradually decreases from the flat portion 50A toward the lid portion 10 may be provided around the opening 11 of the flat portion 50A of the main plate 5 of the impeller 4E.
  • an inclined surface 26 that smoothly guides air toward the opening 11 may be provided at the connecting portion between the driving device 20 and the lower end surface 14 of the fan casing 13 .
  • the impeller 4E configured in this way, the flow passing through the gap between the fan casing 13 and the main plate 5 smoothly flows into the opening 11, so the pressure loss of the flow passing through the opening 11 is is reduced and the flow rate through sidewall 12 is increased. As a result, the same effects as in the fourth embodiment can be obtained.
  • the lid portion 10 of the cup portion 9 of the above-described embodiment may be provided with one or a plurality of through holes that allow the inside and outside of the cup portion 9 to communicate with each other.
  • the side wall 12 in the above embodiment may be parallel to the radial direction of the main plate 5 or inclined at a predetermined angle with respect to the radial direction.
  • 1 multi-blade blower 2 intake port, 3 exhaust port, 4, 4A, 4B, 4C, 4D, 4E impeller, 5 main plate, 6 blades, 7 rotating shaft, 8 connecting portion, 9, 9B, 9C cup portion, 10 Cover, 11 opening, 12, 12A, 12B, 12C side wall, 13 fan casing, 14 lower end surface, 15 upper end surface, 16 peripheral wall, 17 tongue, 18 duct, 19 bell mouth, 20 driving device, 21 extension plate , 22 diffuser plate, 23 duct bottom plate, 24 duct upper plate, 25 bell mouth, 26 inclined surface, 50, 50A plane portion, 120 gap, 121 front end portion, 122 rear end portion.

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

Abstract

Roue à aubes (4) comprenant une plaque principale (5) qui tourne autour d'un axe de rotation (7), et une pluralité d'aubes (6) qui sont espacées et fixées à la plaque principale le long d'une circonférence centrée sur l'axe de rotation. La plaque principale a une partie plane (50) ayant la pluralité d'aubes fixées à celle-ci et ayant une partie d'ouverture (11) en son centre, et une partie de coupelle (9) disposée sur la partie plane. La partie de coupelle a une partie de couvercle (10) opposée à la partie d'ouverture et une paroi latérale (12) qui est disposée autour de la partie d'ouverture et relie la partie de couvercle et la partie plane l'une à l'autre. La paroi latérale est disposée selon un angle par rapport à une direction de rotation (D) de la plaque principale.
PCT/JP2021/011587 2021-03-22 2021-03-22 Roue à aubes et soufflante à aubes multiples WO2022201218A1 (fr)

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PCT/JP2021/011587 WO2022201218A1 (fr) 2021-03-22 2021-03-22 Roue à aubes et soufflante à aubes multiples
JP2023508143A JP7292549B2 (ja) 2021-03-22 2021-03-22 羽根車及び多翼送風機

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PCT/JP2021/011587 WO2022201218A1 (fr) 2021-03-22 2021-03-22 Roue à aubes et soufflante à aubes multiples

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JPS6453496U (fr) * 1987-09-30 1989-04-03
US20110116928A1 (en) * 2009-11-16 2011-05-19 Robert Bosch Gmbh Open-hub centrifugal blower assembly
CN109322852A (zh) * 2017-07-31 2019-02-12 芜湖美的厨卫电器制造有限公司 叶轮、复合型风机和具有其的燃气热水器
CN210013837U (zh) * 2019-01-17 2020-02-04 青岛海尔空调器有限总公司 层流风扇

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