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US20200408225A1 - Axial blower - Google Patents

Axial blower Download PDF

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Publication number
US20200408225A1
US20200408225A1 US16/962,594 US201816962594A US2020408225A1 US 20200408225 A1 US20200408225 A1 US 20200408225A1 US 201816962594 A US201816962594 A US 201816962594A US 2020408225 A1 US2020408225 A1 US 2020408225A1
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US
United States
Prior art keywords
blade
inflection point
airflow
curved surface
axial blower
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US16/962,594
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English (en)
Inventor
Toshikatsu Arai
Hitoshi Kikuchi
Chikage Kadoi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ARAI, TOSHIKATSU, KADOI, Chikage, KIKUCHI, HITOSHI
Publication of US20200408225A1 publication Critical patent/US20200408225A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to an axial blower that generates an airflow that flows in the axial direction of a rotation axis.
  • Axial blowers are often installed at places close to living spaces, and there have thus been demands for lowering noise thereof.
  • For achieving lower noise of an axial blower inclining blades of a rotating blade assembly toward the upstream side of an airflow, and bending outer peripheries of blades of a rotating blade assembly toward the upstream side of an airflow have been proposed.
  • Bell mouths are formed around rotating blade assemblies of axial blowers, so that air is smoothly sucked into the rotating blade assemblies.
  • the shape of the bell mouths affects the air blowing performance and the noise characteristics of the axial blowers.
  • Patent Literature 1 there have been attempts to enhance the air blowing performance and the quietness of axial blowers by devising the shapes of bell mouths.
  • Patent Literature 1 Japanese Patent Application Laid-open No. 2002-257096
  • the air blowing performance and the noise characteristics of an axial blower are significantly affected not only by the shape of a rotating blade assembly but also the shape of a bell mouth, and the shape of the rotating blade assembly and the shape of the bell mouth are therefore designed to satisfy a required air blowing performance and required noise characteristics.
  • the rotating blade assembly and the bell mouth are individually designed, however, the shapes thereof may not be necessarily ideal for the air blowing performance and the noise characteristics owing to dimensional constraints.
  • the present invention has been made in view of the above, and an object thereof is to provide an axial blower with improved air blowing performance and noise characteristics based on the shape of a bell mouth and the shape of a rotating blade assembly.
  • an axial blower includes: a rotating blade assembly including a plurality of blades; a motor to rotate the rotating blade assembly to generate an airflow; and a bell mouth being a frame surrounding the rotating blade assembly from a direction perpendicular to a rotation axis of the rotating blade assembly.
  • the bell mouth has an inlet curved surface on an upstream side of the airflow, the inlet curved surface becoming narrower toward a downstream side of the airflow in an axial direction of the rotation axis, and R 1 /D ⁇ 0.05 is satisfied where D represents an outer diameter of the rotating blade assembly, and R 1 represents a radius of curvature of the inlet curved surface.
  • An axial blower according to the present invention produces effects of improving air blowing performance and noise characteristics based on the shape of a bell mouth and the shape of a rotating blade assembly.
  • FIG. 1 is a perspective view of a rotating blade assembly of an axial blower according to an embodiment of the present invention.
  • FIG. 2 is a drawing illustrating positional relation between a rotating blade assembly and a bell mouth of the axial blower according to the embodiment.
  • FIG. 3 is a front view of the axial blower according to the embodiment.
  • FIG. 4 is a cross-sectional view of the axial blower according to the embodiment.
  • FIG. 5 is a plan view illustrating the shape of a blade of the axial blower according to the embodiment.
  • FIG. 6 is a cross-sectional view of a blade of the axial blower according to the embodiment.
  • FIG. 7 is a diagram illustrating the shape of a blade cross section of a blade of the axial blower according to the embodiment and the airflow condition.
  • FIG. 8 is a diagram illustrating the shape of a blade cross section of a blade of the axial blower according to the embodiment and the airflow condition.
  • FIG. 9 is a diagram illustrating the shape of a blade cross section of a blade of the axial blower according to the embodiment and the airflow condition.
  • FIG. 10 is a diagram illustrating the shape of a blade cross section of a blade of the axial blower according to the embodiment and the airflow condition.
  • FIG. 11 is a graph illustrating the relation between a blade cross-sectional position and radius of curvature of a blade of the axial blower according to the embodiment.
  • FIG. 12 is a graph illustrating the relation between the ratio of the radius of an inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly and the air volume at a release point at which the static pressure becomes 0 in the axial blower according to the embodiment.
  • FIG. 13 is a graph illustrating the relation between the ratio of the radius of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly and the noise level of front noise at the release point in the axial blower according to the embodiment.
  • FIG. 14 is a graph illustrating the relation between the ratio of the radius of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly and the noise level in the direction inclined 45° at the release point in the axial blower according to the embodiment.
  • FIG. 15 is a graph illustrating the relation between the ratio of a cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth and the air volume at the release point in the axial blower according to the embodiment.
  • FIG. 16 is a graph illustrating the relation between the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth and the noise level of front noise at the release point in the axial blower according to the embodiment.
  • FIG. 17 is a graph illustrating the relation between the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth and the noise level in the direction inclined 45° at the release point in the axial blower according to the embodiment.
  • FIG. 18 is a graph illustrating the relation between air volume and static pressure in the axial blower according to the embodiment depending on the ratio of the radius of curvature of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly.
  • FIG. 19 is a graph illustrating the relation between air volume and the noise level of front noise in the axial blower according to the embodiment depending on the ratio of the radius of curvature of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly.
  • FIG. 20 is a graph illustrating the relation between air volume and the noise level of diagonal noise in the axial blower according to the embodiment depending on the ratio of the radius of curvature of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly.
  • FIG. 21 is a graph illustrating the relation between air volume and static pressure in the axial blower according to the embodiment depending on the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth.
  • FIG. 22 is a graph illustrating the relation between air volume and the noise level of front noise in the axial blower according to the embodiment depending on the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth.
  • FIG. 23 is a graph illustrating the relation between air volume and the noise level of diagonal noise in the axial blower according to the embodiment depending on the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth.
  • FIG. 24 is a graph illustrating a difference in the relation between air volume and static pressure depending on the difference in the radius of curvature of the inlet curved surface of the bell mouth in the axial blower according to the embodiment.
  • FIG. 25 is a graph illustrating a difference in the relation between air volume and the noise level of front noise depending on the difference in the radius of curvature of the inlet curved surface of the bell mouth in the axial blower according to the embodiment.
  • FIG. 26 is a graph illustrating a difference in the relation between air volume and the noise level of diagonal noise depending on the difference in the radius of curvature of the inlet curved surface of the bell mouth in the axial blower according to the embodiment.
  • FIG. 1 is a perspective view of a rotating blade assembly of an axial blower according to an embodiment of the present invention.
  • FIG. 2 is a drawing illustrating a positional relation between a rotating blade assembly and a bell mouth of the axial blower according to the embodiment.
  • the rotating blade assembly 1 according to the embodiment includes a columnar boss 2 , and three blades 1 a attached to the boss 2 . Although the shape of one of the three blades 1 a will be mainly described in the description below, the three blades 1 a have the same shape.
  • a blade 1 a has a three-dimensional shape.
  • the blade 1 a is radially attached to the outer circumference of the boss 2 .
  • the boss 2 is driven to rotate about a rotation axis AX by a motor 3 .
  • the blade 1 a rotates with the boss 2 in the direction of an arrow S, to generate an airflow flowing in the direction of an arrow A.
  • the rotating blade assembly 1 is positioned at the center of a blower main unit 6 that includes the bell mouth 5 .
  • the blower main unit 6 is a frame having a square outer shape in front view.
  • the motor 3 is positioned downstream of the bell mouth 5 in the airflow direction. Alternatively, the motor 3 may be positioned upstream of the bell mouth 5 in the airflow direction.
  • FIG. 3 is a front view of the axial blower according to the embodiment.
  • FIG. 4 is a cross-sectional view of the axial blower according to the embodiment.
  • the bell mouth 5 includes an inlet curved surface 51 , a straight portion 53 , and an outlet curved surface 52 .
  • the inlet curved surface 51 is located upstream of the airflow, and the flow passage becomes narrower toward the downstream side of the airflow in the axial direction of the rotation axis AX.
  • the outlet curved surface 52 is located downstream of the airflow, and the flow passage becomes wider toward the downstream side of the airflow in the axial direction of the rotation axis AX.
  • the inlet curved surface 51 of the bell mouth 5 has a radius of curvature R 1 larger than the radius of curvature R 2 of the outlet curved surface 52 thereof.
  • the axial blower 10 is designed to satisfy DR 1 ⁇ L in view of easiness of installation and manufacturing cost.
  • the inlet curved surface 51 is formed to be as large as possible within the length L of one side of the outer shape of the blower main unit 6 in front view, so that the airflow is smoothly guided into the rotating blade assembly 1 .
  • the rotating blade assembly 1 of the axial blower 10 has an outer diameter D of 260 mm.
  • An outer trailing edge I of the rotating blade assembly 1 is located near the boundary between the straight portion 53 and the outlet curved surface 52 of the bell mouth 5 .
  • a blade leading edge 1 b and a blade outer edge 1 d of the rotating blade assembly 1 project toward the upstream side of the airflow relative to the inlet curved surface 51 of the bell mouth 5 .
  • the straight portion 53 prevents air from flowing backward when static pressure is applied.
  • the outlet curved surface 52 allows a flow in the centrifugal direction included in the airflow flowing out from the rotating blade assembly 1 to smoothly flow out of the rotating blade assembly 1 .
  • the outlet curved surface 52 also serves as a diffuser that increases the static pressure.
  • the outer diameter D of the rotating blade assembly 1 and the radius of curvature R 1 of the inlet curved surface 51 of the bell mouth 5 satisfy the following relation: R 1 /D ⁇ 0.05.
  • R 1 ′ the outer diameter DR 1 ′ of the inlet curved surface 51 of the bell mouth 5 when the inlet curved surface 51 is extended so that a tangential line TL at an upstream end 51 a of the inlet curved surface 51 of the bell mouth 5 is perpendicular to the rotation axis AX and the outer diameter DR 1 of the inlet curved surface 51 of the bell mouth 5 is represented by R 1 ′
  • the following relation is satisfied: 0 ⁇ R 1 ′/R 1 ⁇ 0.505.
  • the inlet curved surface 51 of the bell mouth 5 of the axial blower 10 according to the embodiment can be assumed to have such a shape that a part corresponding to a length R 1 ′ is removed from the outer circumference of the inlet curved surface 51 ′ having the outer diameter DR 1 ′, and to have the outer diameter DR 1 .
  • the part assumed to be removed from the inlet curved surface 51 ′ having the outer diameter DR 1 ′ will be referred to as a cut part.
  • the length of the cut part will be referred to as a cut length.
  • the cut length is R 1 ′.
  • the outer diameter DR 1 of the inlet curved surface 51 of the bell mouth 5 is smaller than the length L of one side of the blower main unit 6 .
  • the radius of curvature R 1 of the inlet curved surface 51 of the bell mouth 5 is increased, and the bell mouth 5 can be made smaller than the outer shape of the blower main unit 6 in front view.
  • FIG. 5 is a plan view illustrating the shape of a blade of the axial blower according to the embodiment.
  • FIG. 6 is a cross-sectional view of a blade of the axial blower according to the embodiment.
  • FIG. 6 illustrates a blade cross section of a blade 1 a at a plane along a plane including the rotation axis AX and a blade inner edge 1 e .
  • the blade 1 a has an inflection point IP between the outer side and the inner side at the blade cross section including the rotation axis AX and the blade inner edge 1 e .
  • the blade 1 a has a blade cross section convex to the upstream side of the airflow on the inner side closer to the boss 2 with respect to the inflection point IP, and has a blade cross section convex to the downstream side of the airflow on the outer side farther from the boss 2 with respect to the inflection point IP.
  • the blade 1 a has a curvature R 1 b at the blade cross section on the inner side with respect to the inflection point IP.
  • the blade 1 a has a curvature R 2 b at the blade cross section on the outer side with respect to the inflection point IP.
  • the radii of curvature R 1 b and R 2 b of the blade 1 a change continuously from the blade leading edge 1 b to a blade tailing edge 1 c.
  • FIGS. 7, 8, 9, and 10 are diagrams illustrating the shapes of blade cross sections of a blade of the axial blower according to the embodiment and the airflow condition.
  • FIG. 7 illustrates the shape of a blade cross section at a plane along the radial direction including the rotation axis AX at a blade cross-sectional position O-D 1 in FIG. 5 .
  • FIG. 8 illustrates the shape of a blade cross section at a plane along the radial direction including the rotation axis AX at a blade cross-sectional position O-D 2 in FIG. 5 .
  • FIG. 9 illustrates the shape of a blade cross section at a plane along the radial direction including the rotation axis AX at a blade cross-sectional position O-D 3 in FIG. 5 .
  • FIG. 7 illustrates the shape of a blade cross section at a plane along the radial direction including the rotation axis AX at a blade cross-sectional position O-D 1 in FIG. 5 .
  • FIG. 8 illustrates
  • FIG. 10 illustrates the shape of a blade cross section at a plane along the radial direction including the rotation axis AX at a blade cross-sectional position O-D 4 in FIG. 5 .
  • the blade 1 a is inclined at ⁇ (O-D 1 ) toward the upstream side of the airflow at the blade cross-sectional position O-D 1 , but the inclination angle ⁇ (O-D 2 ) at the blade cross-sectional position O-D 2 , the inclination angle ⁇ (O-D 3 ) at the blade cross-sectional position O-D 3 , and the inclination angle ⁇ (O-D 4 ) at the blade cross-sectional position O-D 4 change in such a manner that the blade 1 a is more inclined toward the downstream side of the airflow as the position is closer to the blade tailing edge 1 c .
  • a lateral flow 9 parallel to the blade cross section is present near the blade leading edge 1 b of the rotating blade assembly 1 , a side face of the rotating blade assembly 1 projects toward the upstream side of the airflow relative to the bell mouth 5 , which enables the lateral flow 9 to be drawn into the rotating blade assembly 1 .
  • the inclination of the blade cross section changes in such a manner that the entire blade cross section is more inclined toward the downstream side of the airflow as the position is closer to the blade tailing edge 1 c of the rotating blade assembly 1 .
  • the pressure of the airflow is increased by controlling a radial flow 11 , which tends to flow in the centrifugal direction as the pressure increases, so as not to leak out of the rotating blade assembly 1 .
  • the blade 1 a has a blade cross section in which the inner side thereof is away from the boss 2 at a position near the front in the rotating direction.
  • a blade tip vortex 7 is generated by a pressure difference between the pressure surface and the negative pressure surface of the blade 1 a .
  • the blade tip vortex 7 interferes with: the negative pressure surface of the blade 1 a ; another adjacent blade 1 a ; or the bell mouth 5 , the noise characteristics of the axial blower 10 lower.
  • the blade 1 a has an S-shaped blade cross section convex to the upstream side of the airflow on the inner side and convex to the downstream side of the airflow on the outer side, generation of the blade tip vortex 7 is reduced, and the flow with an increased pressure is prevented from leaking out of the rotating blade assembly 1 .
  • FIG. 11 is a graph illustrating the relation between a blade cross-sectional position and radius of curvature of a blade of the axial blower according to the embodiment.
  • the radius of curvature R 1 b on the inner side of the blade 1 a gradually decreases from the blade leading edge 1 b toward the blade tailing edge 1 c .
  • the radius of curvature R 2 b on the outer side of the blade 1 a gradually decreases from the blade leading edge 1 b to the blade cross-sectional position O-D 3 , and gradually increases from the blade cross-sectional position O-D 3 to the blade tailing edge 1 c.
  • FIG. 12 is a graph illustrating the relation between the ratio of the radius of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly and the air volume at a release point at which the static pressure 0 in the axial blower according to the embodiment. Note that, in FIG. 12 , the air volume is normalized so that the air volume at the release point is 100%. As illustrated in FIG. 12 , the air volume tends to increase as the ratio R 1 /D of the radius of curvature R 1 of the inlet curved surface 51 of the bell mouth 5 to the outer diameter D of the rotating blade assembly 1 is larger.
  • FIG. 13 is a graph illustrating the relation between the ratio of the radius of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly and the noise level of front noise at the release point in the axial blower according to the embodiment.
  • the noise level is normalized so that the noise level at the release point is 0 dB.
  • the noise level of the front noise is smaller as the ratio R 1 /D of the radius of curvature R 1 of the inlet curved surface 51 of the bell mouth 5 to the outer diameter D of the rotating blade assembly 1 , but unlike the air volume, the noise level of the front noise hardly changes with the increase in R 1 /D after the noise level reaches a certain small level.
  • FIG. 14 is a graph illustrating the relation between the ratio of the radius of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly and the noise level in the direction inclined 45° at the release point in the axial blower according to the embodiment.
  • the noise level is normalized so that the noise level at the release point is 0 dB.
  • the noise level becomes smaller as R 1 /D becomes larger.
  • the noise level in the direction inclined 45° is, however, different from the noise level of front noise in that the noise level in the direction inclined 45° at the release point does not stop decreasing from a certain level.
  • FIG. 15 is a graph illustrating the relation between the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth and the air volume at the release point in the axial blower according to the embodiment.
  • the air volume is normalized so that the air volume at the release point is 100%.
  • the ratio R 1 ′/R 1 of the cut length R 1 ′ of the inlet curved surface 51 of the bell mouth 5 to the radius of curvature R 1 of the inlet curved surface 51 of the bell mouth 5 is equal to or smaller than 0.45, the air volume is not dependent on R 1 ′/R 1 .
  • R 1 ′/R 1 exceeds 0.45, the air volume decreases sharply.
  • FIG. 16 is a graph illustrating the relation between the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth and the noise level of front noise at the release point in the axial blower according to the embodiment.
  • the noise level is normalized so that the noise level at the release point is 0 dB.
  • R 1 ′/R 1 is equal to or smaller than 0.45
  • the noise level of the front noise lowers.
  • FIG. 17 is a graph illustrating the relation between the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth and the noise level in the direction inclined 45° at the release point in the axial blower according to the embodiment.
  • the noise level is normalized so that the noise level at the release point is 0 dB.
  • R 1 ′/R 1 is equal to or smaller than 0.45
  • the noise level of the noise lowers.
  • FIG. 18 is a graph illustrating the relation between air volume and static pressure in the axial blower according to the embodiment depending on the ratio of the radius of curvature of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly.
  • FIG. 19 is a graph illustrating the relation between air volume and the noise level of front noise in the axial blower according to the embodiment depending on the ratio of the radius of curvature of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly.
  • FIG. 20 is a graph illustrating the relation between air volume and the noise level of diagonal noise in the axial blower according to the embodiment depending on the ratio of the radius of curvature of the inlet curved surface of the bell mouth to the outer diameter of the rotating blade assembly. As illustrated in FIGS.
  • FIG. 21 is a graph illustrating the relation between air volume and static pressure in the axial blower according to the embodiment depending on the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth.
  • FIG. 22 is a graph illustrating the relation between air volume and the noise level of front noise in the axial blower according to the embodiment depending on the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth.
  • FIGS. 21, 22, and 23 is a graph illustrating the relation between air volume and the noise level of diagonal noise in the axial blower according to the embodiment depending on the ratio of the cut length of the inlet curved surface of the bell mouth to the radius of curvature of the inlet curved surface of the bell mouth.
  • R 1 ′/R 1 0.447, which is in a suitable range of R 1 ′/R 1
  • FIG. 24 is a graph illustrating a difference in the relation between air volume and static pressure depending on the difference in the radius of curvature of the inlet curved surface of the bell mouth in the axial blower according to the embodiment.
  • FIG. 25 is a graph illustrating a difference in the relation between air volume and the noise level of front noise depending on the difference in the radius of curvature of the inlet curved surface of the bell mouth in the axial blower according to the embodiment.
  • FIG. 26 is a graph illustrating a difference in the relation between air volume and the noise level of diagonal noise depending on the difference in the radius of curvature of the inlet curved surface of the bell mouth in the axial blower according to the embodiment.
  • R 1 1 >R 1 2 is satisfied.
  • the ratio of the radius of curvature R 1 of the inlet curved surface 51 of the bell mouth 5 to the outer diameter D of the rotating blade assembly 1 satisfies R 1 /D ⁇ 0.05, which controls increase of noise by turbulence of the airflow generated by the inlet curved surface 51 of the bell mouth 5 and sucked into rotating blade assembly 1 .
  • the outer diameter of the inlet curved surface 51 of the bell mouth 5 is equal to or smaller than the length of a side of the blower main unit 6 , which prevents the equipment size from increasing.
  • the outer diameter of the inlet curved surface 51 of the bell mouth 5 is equal to or smaller than the length of a side of the blower main unit 6 , the need for mounting a bell mouth 5 that is a component separate from a blower main unit 6 onto the blower main unit 6 is eliminated, and an increase in man-hours is thus prevented.
  • 1 rotating blade assembly 1 a blade; 1 b blade leading edge; 1 c blade tailing edge; 1 d blade outer edge; 1 e blade inner edge; 2 boss; 3 motor; 5 bell mouth; 6 blower main unit; 7 blade tip vortex; 9 lateral flow; 10 axial blower; 51 , 51 ′ inlet curved surface; 51 a upstream end; 52 outlet curved surface.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US16/962,594 2018-02-02 2018-02-02 Axial blower Abandoned US20200408225A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/003704 WO2019150567A1 (ja) 2018-02-02 2018-02-02 軸流送風機

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US (1) US20200408225A1 (zh)
JP (1) JP6914371B2 (zh)
CN (1) CN111656019B (zh)
TW (1) TW201934888A (zh)
WO (1) WO2019150567A1 (zh)

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US20220178382A1 (en) * 2019-08-26 2022-06-09 Daikin Industries, Ltd. Blower and heat pump unit
US11519422B2 (en) * 2018-05-09 2022-12-06 York Guangzhou Air Conditioning And Refrigeration Co., Ltd. Blade and axial flow impeller using same
US11933315B2 (en) 2021-07-20 2024-03-19 Sanyo Denki Co., Ltd. Axial fan
US20240209864A1 (en) * 2022-03-31 2024-06-27 Nanjing Chervon Industry Co., Ltd. Fan

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BR112023017994A2 (pt) * 2021-03-12 2023-10-03 Daikin Ind Ltd Ventilador de hélice e aparelho de refrigeração
CN113847275B (zh) * 2021-08-30 2023-06-16 珠海格力电器股份有限公司 翼型轴流风叶及空调外机
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CN111656019A (zh) 2020-09-11
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