US20200370562A1 - Impeller having primary blades and secondary blades - Google Patents

Impeller having primary blades and secondary blades Download PDF

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Publication number
US20200370562A1
US20200370562A1 US16/761,530 US201716761530A US2020370562A1 US 20200370562 A1 US20200370562 A1 US 20200370562A1 US 201716761530 A US201716761530 A US 201716761530A US 2020370562 A1 US2020370562 A1 US 2020370562A1
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United States
Prior art keywords
blade
impeller
blades
primary
hub
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Abandoned
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US16/761,530
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English (en)
Inventor
Seungbae Lee
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Aeronet Inc
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Aeronet Inc
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Assigned to AERONET INC. reassignment AERONET INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LEE, SEUNGBAE
Publication of US20200370562A1 publication Critical patent/US20200370562A1/en
Abandoned legal-status Critical Current

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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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • 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
    • 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
    • F04D29/30—Vanes
    • 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
    • F04D29/26—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
    • F04D29/386—Skewed blades
    • 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
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes

Definitions

  • the present disclosure herein relates to an impeller, and more particularly, to an impeller performing blade flow control by disposing a plurality of secondary blades between a plurality of primary blades.
  • a typical axial impeller applied to the fluid machinery exhibits performance thereof by using a pressure and a flow rate.
  • a pressure difference ( ⁇ p) between an inlet and an outlet is formed such that while a fluid passes between blades 1 , a streamline is bent along a curvature of the blade, and a pressure increases by a lift force.
  • ⁇ p a pressure difference between an inlet and an outlet
  • ⁇ 0 is an air foil shape
  • mo is the soildity
  • b is a constant determined according to an inlet flow angle ( ⁇ 1 ).
  • the related art has been focused to lengthen the chord while generating great pressure increase through lift force increase by magnifying the camber angle as large as possible while preventing flow separation or reducing an outlet deviation angle through soildity increase by increasing the number of blades and reducing the pitch between the blades.
  • the impeller increases in a rotation shaft direction, and the camber angle for increasing a pressure is restricted due to flow separation at a negative-pressure surface.
  • U.S. Publication Patent No. US 2014/0233178 A1 discloses an example of improving performance by reducing a deviation angle of a blade outlet and increasing soildity by using an effect of lengthened blade as a secondary blade initiates around a trailing edge (T.E.) of a primary blade.
  • T.E. trailing edge
  • the above-described invention has a limitation in that a height of the impeller increases, a length of the primary blade increases as much as a length in which the primary blade and the secondary blade overlap, and a difference in performance is insignificant.
  • Korean Registered Patent No. 10-1342746 discloses a typical impeller having increasing soildity by installing a plurality of secondary blades between a plurality of primary blades to reduce a blade pitch.
  • the above-described impeller has a disadvantage in that a portion in which primary blades overlap is removed due to difficulty of injection molding to cause reduction in lift force and noise increase.
  • FIG. 2 illustrates a flow angle and a blade of a backward centrifugal impeller 20 .
  • Mathematical equation 2 shows a relationship between pressure increase of the impeller and a work given by Euler equation.
  • ⁇ R is an efficiency of the impeller, i.e., a percentage (%) of substantial transfer energy except for a flow loss from theoretical voltage increase caused by internal flow with respect to theoretical transfer energy.
  • a flow discharged from the impeller in FIG. 2 does not flow along an outlet blade and generates slip.
  • a slip coefficient is ⁇ when a blade angle is ⁇ 2b
  • N B is the number of blades
  • ⁇ 2 is an outlet flow angle
  • U 2 and C m2 are rotation velocity of an edge of the blade and a radial component of an absolute velocity of outlet flow, respectively.
  • a rotation component C ⁇ 2 of an absolute velocity of an outlet necessarily increases in order to improve pressure transfer, and, to this end, a slip coefficient necessarily increases by increasing the number of blades as many as possible.
  • U.S. Publication Patent No. US 2009/0155048 A1 discloses an example of an effect of increasing the number of blades by installing split vanes, which are secondary blades rotating by using the same shaft as primary blades, between the primary blades in a centrifugal pump impeller.
  • split vanes which are secondary blades rotating by using the same shaft as primary blades
  • a centrifugal pump impeller In a fan or a blower that requires flow rate increase instead of pressure increase unlike the centrifugal pump producing a great static pressure, since a ratio of a height to a diameter of the impeller is extremely greater than that of a pump, an upper portion of an impeller blade is necessarily covered by a typical shroud plate, or an outlet above the blade is necessarily covered by a circular plate having a narrow band shape to reinforce rigidity. However, this case has a difficulty in injection molding.
  • the present invention provides an impeller in which a plurality of secondary blades are installed between primary blades without increasing a height of the impeller for performance improvement and noise reduction in the axial and centrifugal impeller.
  • a blade deviation angle is reduced to improve performance, and a size of a blade wake flow is reduced, to reduce noises.
  • the centrifugal impeller as flow separation at a negative-pressure surface is reduced, performance improvement and reduction in flow separation noise are obtained through improvement of a slip constant.
  • An embodiment of the present invention provides an impeller including: a first portion including a first hub and a plurality of primary blades each extending while being spaced an equal distance from each other along an outer circumference of the first hub; and a second portion including a second hub coupled to a lower side of the first hub by using a projection-groove coupling manner and a plurality of secondary blades each extending while being spaced apart from each other along an outer circumference of the second hub.
  • the projection angle ⁇ 1 and ⁇ 1 includes an upstream angle ⁇ 1u and ⁇ 1u and a downstream angle ⁇ 1d and ⁇ 1d , at which the primary blade and the secondary blade overlap each other, and an angle ⁇ 1m and ⁇ 1m at which the primary blade and the secondary blade do not overlap each other, and the projection angle ⁇ 1 is less than the projection angle ⁇ 1 to satisfy an equation 0 ⁇ 1 ⁇ 1 as a radius of each of the primary blade and the secondary blade goes from the hub to the edge.
  • angles Om and Old of the secondary blade may have magnitudes overlapping the primary blade so that a channel around a downstream of a negative-pressure surface of the primary blade is guided.
  • the first hub may include a plurality of first coupling projections, which are spaced apart from each other on a bottom surface thereof, and a plurality of first coupling grooves that are provided by the plurality of first coupling projections
  • the second hub may include a plurality of second coupling projections, which are spaced apart from each other on a top surface thereof, and a plurality of second coupling grooves that are provided by the plurality of second coupling projections
  • the plurality of first coupling projections may be coupled to the plurality of second coupling grooves
  • the plurality of second coupling projections may be coupled to the plurality of first coupling grooves.
  • the plurality of first coupling projections may be coupled to the plurality of second coupling grooves in a pressing manner
  • the plurality of second coupling projections may be coupled to the plurality of first coupling grooves in a pressing manner
  • the plurality of first coupling projections may be coupled to the plurality of second coupling grooves by using an adhesive
  • the plurality of second coupling projections may be coupled to the plurality of first coupling grooves by using an adhesive
  • each of the first hub and the second hub may have a band shape.
  • first and second hubs may form a single cone shape when coupled to each other.
  • an impeller includes: a first portion including a circular bottom plate, a hub protruding from a central portion of a top surface of the circular bottom plate, and a plurality of primary blades formed in a circumferential direction with respect to the hub while being spaced an equal distance from each other on the top surface of the circular bottom plate; and a second portion including a shroud having a band shape and a plurality of secondary blades spaced a distance from each other along a bottom surface of the shroud in an integrated manner
  • an inlet area between a negative-pressure surface of the primary blade and a pressure surface of the secondary blade is Ssu
  • an inlet area between the pressure surface of the primary blade and a negative-pressure surface of the secondary blade is Spu
  • a downstream area of a channel of the negative-pressure surface of the primary blade which is an area at a downstream of each channel, is Ssd
  • a downstream area of a channel of the pressure surface of the primary blade is Spd
  • a leading edge (L.E.) of the secondary blade may be disposed between channels having the same radial inlet so hat the areas Ssu and Spu are equal to each other.
  • an outlet angle and an outlet position between channels may be set by rotating a trailing edge (T.E.) of the secondary blade to be disposed between channels having the same radial outlet by using a leading edge (L.E.) of the secondary blade as a pivot point, thereby maintaining the areas Ssu and Ssd are similar to each other.
  • T.E. trailing edge
  • L.E. leading edge
  • the shroud may have a band shape.
  • a plurality of first coupling groove, to which lower edges of the plurality of secondary blades are inserted, may be defined in the top surface of the bottom plate
  • a plurality of second coupling groove, to which upper edges of the plurality of primary blades are inserted may be defined in the bottom surface of the shroud
  • the lower edges of the plurality of secondary blades may be coupled to the plurality of first coupling grooves in a pressing manner, and the lower edges of the plurality of primary blades may be coupled to the plurality of second coupling grooves in a pressing manner.
  • the lower edges of the plurality of secondary blades may be coupled to the plurality of first coupling grooves by using an adhesive
  • the lower edges of the plurality of primary blades may be coupled to the plurality of second coupling grooves by using an adhesive
  • the plurality of secondary blades each disposed between each of the primary blades may be spaced different distances from each other along a rotation direction of the impeller.
  • the circular bottom plate and the shroud may be inclined in a flow downstream direction or formed in a horizontal direction.
  • the circular bottom plate may have an outer diameter less than an inner diameter of the shroud.
  • the plurality of primary blades and the plurality of secondary blades may be coupled to the circular plate and the shroud in an integrated manner
  • FIG. 1 is a view for explaining design variables related to a flow between blades of a general axial impeller and design variables related to the blades;
  • FIG. 2 is a view for explaining design variables related to a blade of a typical backward centrifugal impeller and a flow angle;
  • FIG. 3 is an assembly perspective view illustrating an axial impeller according to an embodiment of the present invention
  • FIG. 4 is an exploded perspective view simultaneously illustrating a bottom surface of a first portion and a top surface of a second portion of the axial impeller in FIG. 3 ;
  • FIG. 5 is a schematic view illustrating a flow around a blade of each of the axial impeller according to an embodiment of the present invention and a typical impeller in conjunction with a streamline;
  • FIG. 6 is a view illustrating a structure between a primary blade and a secondary blade of the axial impeller according to an embodiment of the present invention
  • FIG. 7 is an assembly perspective view illustrating a centrifugal impeller according to another embodiment of the present invention.
  • FIG. 8 is an exploded perspective view simultaneously illustrating a bottom surface of a first portion and a top surface of a second portion of the centrifugal impeller in FIG. 7 ;
  • FIG. 9 is a view illustrating an example of a centrifugal impeller including a primary blade having a backward wake flow shape (expressed by a solid line) and a secondary blade having a split vane shape according to another embodiment of the present invention in conjunction with an example of a centrifugal impeller including a primary blade having a forward wake flow shape (expressed by a dotted line);
  • FIG. 10 is a cross-sectional view illustrating the primary blade and the secondary blade of the centrifugal impeller according to another embodiment of the present invention.
  • FIG. 11 is a view illustrating an example of randomly determining a position of the secondary blade of the centrifugal impeller between channels instead of determining the position as same as a rotation direction according to another embodiment of the present invention
  • FIG. 12 is a perspective view illustrating an impeller including a mixed flow type primary blade and a secondary blade according to another embodiment of the present invention.
  • FIG. 13 is a plan view illustrating an impeller according to another embodiment of the present invention.
  • FIG. 14 is a cross-sectional view taken along line A-A of FIG. 13 .
  • FIG. 3 is an assembly perspective view illustrating an axial impeller according to an embodiment of the present invention
  • FIG. 4 is an exploded perspective view simultaneously illustrating a bottom surface of a first portion and a top surface of a second portion of the axial impeller in FIG. 3 .
  • an axial impeller 100 includes a first portion 110 and a second portion 130 , which are manufactured by separate components.
  • the first portion 110 and the second portion 130 which are separately manufactured, are coupled to each other to be used as an impeller.
  • the first portion 110 includes a first hub 111 having an approximately ring shape and a plurality of primary blades 120 spaced an equal distance from each other on an outer circumferential surface of the first hub 111 .
  • the first hub 111 may have a hole 113 defined at a central portion thereof so as to be connected with a predetermined driving member such as a rotation shaft (not shown), thereby rotating the axial impeller 100 .
  • the first hub 111 includes a plurality of first coupling projections 115 protruding from a bottom surface thereof and spaced an equal distance from each other along the bottom surface.
  • a plurality of coupling grooves 117 to which a plurality of second coupling projections 135 are inserted are provided between the first coupling projections 115 .
  • Each of a plurality of primary blades 120 has one edge connected to the outer circumferential surface of the first hub 111 in an integrated manner and is gradually bent at a predetermined curvature in a direction toward the other edge thereof.
  • each of the primary blades 120 includes a negative-pressure surface 121 , a pressure surface 123 disposed opposite to the negative-pressure surface 121 , a blade hub surface 125 disposed adjacent to the first hub 111 , and a blade tip surface 127 disposed at an edge of the primary blade 120 .
  • each of the primary blades 120 has an upper edge that is defined as a leading edge (L.E.) and a lower edge that is defined as a trailing edge (T.E.).
  • the second portion 130 includes a second hub 131 having an approximately ring shape and a plurality of primary blades 140 spaced an equal distance from each other on an outer circumferential surface of the second hub 131 .
  • the second hub 131 may have a hole 133 defined at a central portion thereof like the first hub 111 .
  • the second hub 131 may have an outer diameter equal to that of the first hub 111 and an inner diameter equal to or less than that of the first hub 111 .
  • This structure may fix the impeller 100 to a rotation shaft or a rotating driving member corresponding to the rotation shaft.
  • a plurality of second coupling projections 135 protrude from a top surface of the second hub 131 and are spaced an equal distance from each other along the top surface.
  • a plurality of second coupling grooves 137 to which a plurality of first coupling projections 115 are inserted are provided between the second coupling projections 135 .
  • the first and second hubs 111 and 131 are coupled to each other as the plurality of first coupling projections 115 are inserted to the plurality of second coupling grooves 137 , and the plurality of second coupling projections 135 are inserted to the plurality of first coupling grooves 117 .
  • the first and second hubs 111 and 131 are coupled in a mutually pressing state or attached to each other by using a separate adhesive.
  • Each of the plurality of secondary blades 140 has one edge connected to an outer circumferential surface of the second hub 131 in an integrated manner and is gradually bent at a predetermined curvature in a direction toward the other edge thereof. Also, when the first and second hubs 111 and 131 are coupled to each other, the plurality of secondary blades 140 are disposed below the plurality of primary blades 120 , respectively.
  • each of the secondary blades 140 includes a negative-pressure surface 141 , a pressure surface 143 disposed opposite to the negative-pressure surface 140 , a blade hub surface 145 disposed adjacent to the second hub 131 , and a blade tip surface 147 disposed at an edge of the secondary blade 140 .
  • each of the secondary blades 140 has an upper edge that is defined as a leading edge (L.E.) and a lower edge that is defined as a trailing edge (T.E.).
  • FIG. 5 is a schematic view illustrating a flow around a blade of each of the axial impeller according to an embodiment of the present invention and a typical impeller in conjunction with a streamline
  • an incidence angle of an inlet is positive (+) (i.e., an inlet flow is incident toward a pressure surface more than a camber tangential direction of an inlet blade)
  • a streamline may not flow along the blade and be deviated toward the negative-pressure surface more than a camber tangential direction of a trailing edge of the blade.
  • a reference symbol P represents the pressure surface of the blade.
  • the secondary blade 140 is disposed between two primary blades 120 as in FIG. 5B .
  • a flow separation is not generated at a downstream of the pressure surface 121 of the primary blade 120 , unlike a case in FIG. 5A , in which a flow is decelerated from an inlet area A 1 between primary blades to generate flow separation.
  • a narrow wake thickness ⁇ ′ is generated at the negative-pressure surface due to small-sized flow separation, and pressure increase is generated due to a blade camber as a deviation angle ⁇ between channels is reduced, a camber angle greater than a case without the secondary blade may be applied.
  • FIG. 6 is a view illustrating a relationship between the primary blade and the secondary blade of the axial impeller according to an embodiment of the present invention.
  • a first cylinder projection angle between the leading edge (L.E.) and the trailing edge (T.E.) of the primary blade 120 is ⁇ 1
  • a second cylinder projection angle between leading edge (L.E.) and the trailing edge (T.E.) of the secondary blade 140 is ⁇ 1 .
  • the first cylinder projection angle ⁇ 1 includes an upstream angle ⁇ 1 u and a downstream angle ⁇ 1 d, which overlap the secondary blade 140 , and an angle ⁇ 1 m not overlapping the secondary blade 140 .
  • ⁇ 1 u ⁇ 1 d
  • ⁇ 1 d ⁇ 1 u
  • an equation 0 ⁇ 1 ⁇ 1 is satisfied, i.e., an angle gap of the secondary blade 140 is less than that of the primary blade 120 , the trailing edge of the secondary blade 140 coincides with the trailing edge of the primary blade 120 so that a height of the impeller 100 (refer to FIG. 3 ) does not increase, and ⁇ 1 u of the secondary blade is greater than ⁇ 1 d so that a channel around a downstream of the negative-pressure surface 121 (refer to FIG. 4 ) of the primary blade 120 is sufficiently guided.
  • first hub 111 and the second hub 131 are coupled to each other by the first and second coupling projections 115 and 135 and the first and second coupling grooves 117 and 137 as in FIG. 3 .
  • the trailing edge of the primary blade 120 corresponding to the downstream angle ⁇ 1 d of the primary blade 120 is not attached to the first hub 111 , but coupled with the second hub 132 .
  • each of the first and second hubs 111 and 131 may have a cone shape instead of the cylinder shape.
  • an overall integrated cone shape may be formed.
  • the first and second hubs forming the cone shape may be used for a mixed flow impeller.
  • FIG. 7 is an assembly perspective view illustrating a centrifugal impeller according to another embodiment of the present invention
  • FIG. 8 is an exploded perspective view simultaneously illustrating a bottom surface of a first portion and a top surface of a second portion of the centrifugal impeller in FIG. 7 .
  • a centrifugal impeller 200 impeller according to another embodiment of the present invention includes a first portion 210 and a second portion 230 , which are components separately manufactured through injection molding, like the above-described axial impeller 100 according to an embodiment of the present invention
  • the first portion 210 and the second portion 230 are coupled to each other to be used as an impeller.
  • the first portion 210 includes a hub 211 , a bottom plate 225 formed by a circular plate, and a plurality of primary blades 220 spaced an equal distance from each other.
  • the hub 211 may have a hole 213 defined at a central portion thereof so as to be connected with a predetermined driving member such as a rotation shaft (not shown), thereby rotating the centrifugal impeller 200 .
  • the hub 211 may have an approximately cone shape.
  • the hub 211 has a lower edge connected to a central portion of a top surface of the bottom plate 215 in an integrated manner.
  • the plurality of primary blades 220 are spaced an equal distance from each other along a circumferential direction on the bottom plate 215 , and lower edges of the plurality of primary blades 220 are connected to the top surface of the bottom plate 215 in an integrated manner.
  • a plurality of first coupling grooves 217 to which lower edges of a plurality of secondary blades 240 that will be described later are inserted between neighboring primary blades 220 , are defined in the top surface of the bottom plate 215 .
  • Each of the plurality of primary blades 220 has a leading edge (L.E.) disposed adjacent to an outer circumferential surface of the first hub 211 and is gradually bent at a predetermined curvature in a direction from the leading edge (L.E.) to a trailing edge (T.E.).
  • Each of the primary blades 220 includes a negative-pressure surface 221 , a pressure surface disposed opposite to the negative-pressure surface, a blade bottom surface 225 adjacent to the bottom plate 215 , and a blade top surface 227 adjacent to a shroud 231 of the second portion 230 , which will be described later.
  • each of the primary blades 220 has an inside edge that is defined as a leading edge (L.E.) and an outside edge that is defined as a trailing edge (T.E.).
  • the second portion 230 includes a shroud 231 having an approximately ring shape and a plurality of secondary blades 240 spaced an equal distance from each other along a bottom surface of the shroud 231 .
  • each of the plurality of secondary blades 240 may have an arc shape or an S-shape.
  • the shroud 231 may have an outer diameter that is approximately equal to that of the bottom plate 215 . Also, a plurality of second coupling grooves 233 , to which the plurality of primary blades 220 are inserted, are defined between the plurality of secondary blades 240 in a bottom surface of the shroud 231 . A portion of an upper edge of each of the plurality of primary blades 220 may be inserted to each of the plurality of second coupling grooves 233 .
  • the first and second portions 210 and 230 are coupled to each other.
  • each of coupled portions are coupled in a mutually pressing manner or attached to each other by using a separate adhesive.
  • Each of the plurality of secondary blades 240 includes a negative-pressure surface 241 , a pressure surface 243 disposed opposite to the negative-pressure surface, a blade bottom surface 245 , and a blade top surface 247 adjacent to the shroud 231 .
  • each of the secondary blades 240 has an inside edge that is defined as a leading edge (L.E.) and an outside edge that is defined as a trailing edge (T.E.).
  • the wake flow is expressed by a solid line when the primary blade of the centrifugal impeller has the backward wake flow shape, and the wake flow is expressed by a dotted line when the primary blade of the centrifugal impeller has the forward wake flow shape.
  • S-shaped hybrid blades are illustrated in FIG. 10 in order to use advantages of a high efficiency of the backward blade and a high pressure energy of the forward blade at the same time, as a channel is divided into two portions as in the axial impeller by installing the secondary blade called a split vane between the primary blades to overcome the great flow separation of the negative-pressure surface of the forward blade, slip and wake flow at the negative-pressure surface of the primary blade are reduced as expressed by a green solid line, and wake flow exists only at the negative-pressure surface of the secondary blade in conjunction with small flow separation.
  • this flow type is the most preferable among three flow types.
  • reference symbols U 2 and Cm 2 are a rotation velocity of a blade edge and a radial component of an absolute velocity of an outlet flow, respectively, a reference symbol C ⁇ 2 is a rotation component of an outlet absolute velocity, and reference symbols C 2 and W 2 are a magnitude of an outlet absolute velocity vector and a magnitude of an outlet relative velocity vector, respectively.
  • the channel of the hybrid blade installing the secondary blade includes: an inlet area Ssu (here, the suffix u represents the upstream) between the negative-pressure surface of the primary blade and the pressure surface of the secondary blade; an inlet area Spu between the pressure surface of the primary blade and the negative-pressure surface of the secondary blade; and an areas Ssd and Spd at each channel downstream. Since an inlet height and an outlet height of the blade are generally similar to each other, a flow separation is generated by pressure increase and velocity decrease as an outlet area increases more than an inlet area because a radius increases in a direction toward the blade downstream.
  • the present invention maintains an outlet angle of the secondary blade to be similar to an outlet angle ⁇ 2b (refer to FIG. 2 ) of the primary blade and initiates an inlet of the secondary blade around a position at which the S-shape is varied, so that an inlet angle of the secondary blade allows a flow angle tangent line to coincide with a primary streamline between the channels in order to prevent the inlet area Ssu and the outlet area Ssd of the channel of the negative-pressure surface of the primary blade from being greatly varied.
  • the leading edge (L.E.) of the secondary blade may move between channels having the same radial inlet so that the two areas are equal to each other, and as the leading edge (L.E.) of the secondary blade at the previously obtained position moves to a pivot point, and the trailing edge (T.E.) of the secondary blade moves between channels having the same radial outlet so that the area Ssu is similar to the area Ssd, an outlet angle and an outlet position between the channels may be determined.
  • FIG. 11 is a view illustrating an example of randomly determining a position of the secondary blade of the centrifugal impeller between channels instead of determining the position as same as a rotation direction according to another embodiment of the present invention.
  • the present invention randomly determines a position between the channels of the secondary blade of the centrifugal impeller as in FIG. 11 instead of determining the position as same as the rotation direction in order to cancel phases of a flow separation vortex above the negative-pressure surface of the secondary blade and a vortex passing through the channel
  • the position may be determined so that a thrust and a torque balance of a shaft vertical surface are obtained by lift force distribution.
  • the centrifugal impeller 200 in FIG. 7 is obtained by coupling the first portion 210 and the second portion 230 to each other, and the first and second portions 210 and 230 are separately manufactured.
  • the embodiment of the present invention is not limited thereto.
  • an impeller having an integrated body may be provided.
  • FIGS. 12 to 14 detailed description will be described with reference to FIGS. 12 to 14 .
  • FIG. 12 is a perspective view illustrating an impeller including a mixed flow type primary blade and a secondary blade according to another embodiment of the present invention
  • FIG. 13 is a plan view illustrating an impeller according to another embodiment of the present invention
  • FIG. 14 is a cross-sectional view taken along line A-A of FIG. 13 .
  • all of the circular bottom plate 315 and the shroud 331 are formed inclined to a flow downstream direction as in FIG. 14 , the embodiment of the present invention is not limited thereto.
  • all of the circular bottom plate 315 and the shroud 331 may be formed in a horizontal direction to be perpendicular to a rotation shaft direction.
  • a plurality of primary blades 320 and a plurality of secondary blades 330 of the impeller 300 may be integrated with the shroud 331 and the circular bottom plate 315 or a hub 317 so as to be manufactured by using a single mold. That is, each of the plurality of primary blades 320 may have an upper edge connected to the shroud 331 and a lower edge connected to the circular bottom plate 315 or the hub 317 . Also, each of the plurality of secondary blades 330 may have an upper edge connected to the shroud 331 and a lower edge connected to the circular bottom plate 315 or the hub 317 .
  • the plurality of primary blades 320 and the plurality of secondary blades 330 may be alternately formed along a circumferential direction.
  • the impeller according to the present invention in which the secondary blades are disposed between the primary blades, has an advantage with respect to each of the axial type and the centrifugal type as stated below.
  • the first portion including the upper hub to which the plurality of primary blades are connected and the second portion including the lower hub to which the plurality of secondary blades are connected may be separately injection-molded, and the upper hub and the lower hub may each have a band shape having a circumferential radial thickness and be coupled to each other in the projection-groove coupling manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US16/761,530 2017-11-07 2017-12-15 Impeller having primary blades and secondary blades Abandoned US20200370562A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
KR10-2017-0147057 2017-11-07
KR20170147057 2017-11-07
KR1020170171944A KR102083168B1 (ko) 2017-11-07 2017-12-14 주 날개 및 보조 날개를 구비한 임펠러
KR10-2017-0171944 2017-12-14
PCT/KR2017/014809 WO2019093576A1 (ko) 2017-11-07 2017-12-15 주 날개 및 보조 날개를 구비한 임펠러

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US (1) US20200370562A1 (ko)
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US20240026898A1 (en) * 2022-07-25 2024-01-25 Sanyo Denki Co., Ltd. Axial fan

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RU2019106653A (ru) * 2018-03-14 2020-09-11 Кэрриер Корпорейшн Открытое рабочее колесо центробежного компрессора
CN111946664B (zh) * 2020-09-16 2022-03-15 台州学院 一种带开缝结构的离心通风机叶片

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US11518443B1 (en) * 2021-06-16 2022-12-06 Quinn Aerospace Inc. Control system for rotating thrust-producing apparatus
US20240026898A1 (en) * 2022-07-25 2024-01-25 Sanyo Denki Co., Ltd. Axial fan
US11988225B2 (en) * 2022-07-25 2024-05-21 Sanyo Denki Co., Ltd. Axial fan

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KR20180020117A (ko) 2018-02-27
KR102083168B1 (ko) 2020-03-02

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