US20060182628A1 - Blowing device - Google Patents

Blowing device Download PDF

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Publication number
US20060182628A1
US20060182628A1 US11/332,213 US33221306A US2006182628A1 US 20060182628 A1 US20060182628 A1 US 20060182628A1 US 33221306 A US33221306 A US 33221306A US 2006182628 A1 US2006182628 A1 US 2006182628A1
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US
United States
Prior art keywords
guide vane
blades
impeller
shroud
hub
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
US11/332,213
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English (en)
Inventor
Wook Kim
Jun Bae
Chang Kim
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BAE, JUN HO, KIM, WOOK, KIM, CHANG JOON
Publication of US20060182628A1 publication Critical patent/US20060182628A1/en
Abandoned legal-status Critical Current

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    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63H—TOYS, e.g. TOPS, DOLLS, HOOPS OR BUILDING BLOCKS
    • A63H33/00—Other toys
    • A63H33/04—Building blocks, strips, or similar building parts
    • A63H33/046—Building blocks, strips, or similar building parts comprising magnetic interaction means, e.g. holding together by magnetic attraction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/165—Axial entry and discharge
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63H—TOYS, e.g. TOPS, DOLLS, HOOPS OR BUILDING BLOCKS
    • A63H33/00—Other toys
    • A63H33/04—Building blocks, strips, or similar building parts
    • A63H33/10—Building blocks, strips, or similar building parts to be assembled by means of additional non-adhesive elements
    • 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4253—Fan casings with axial entry and discharge

Definitions

  • the present invention relates to a blowing device for small-sized electronic appliances such as cleaning apparatus, and, in particular, to a blowing device which comprises a centrifugal impeller and a guide vane optimally designed to maximize fan efficiency and heat dissipation of a motor without a diffuser.
  • FIG. 1 is a perspective view illustrating a conventional blowing device
  • FIG. 2 is a cross-sectional view illustrating a main component of the conventional blowing device.
  • the conventional blowing device comprises a housing 4 having an intake port 1 and a discharge port 2 , a centrifugal impeller 10 rotatably equipped within the housing 4 , and a motor 20 connected to the centrifugal impeller 10 via a shaft 21 to rotate the centrifugal impeller 10 .
  • the intake port 1 of the housing 4 is located at the center of a front side of the housing 4
  • the discharge port 2 of the housing 4 is located at a rear side of the housing 4 .
  • the centrifugal impeller 10 acts to blow air in a centrifugal direction.
  • the centrifugal impeller 10 comprises a shroud 12 having an inlet 12 ′ communicated with the intake port 1 of the housing 4 , a hub 14 separated from the shroud 12 in an axial direction while being coupled to the shaft 21 of the motor 20 to integrally rotate with the shaft 21 , and a plurality of blades 16 radially disposed between the shroud 12 and the hub 14 .
  • the centrifugal impeller 10 can have an increased blowing capacity. However, if the floor area ratio of the centrifugal impeller 10 to the housing 4 is excessive, the centrifugal impeller 10 can interfere with the housing 4 , and in particular, there occurs an increase in flow resistance of air blown from the centrifugal impeller 10 to the discharge port 2 of the housing 4 . Accordingly, the centrifugal impeller 10 is designed to maintain a predetermined distance G from the housing 4 .
  • the shroud 12 , the hub 14 , and the blades 16 are typically designed to have an identical outer diameter 10 D.
  • the outer diameter of the blades 16 refers to a diameter of a circle which is defined by connecting distal ends of the plurality of blades 16 .
  • the housing 4 is provided with a guide vane 30 to guide the air from the centrifugal impeller 10 to the discharge port 2 of the housing 4 .
  • the centrifugal impeller 10 forcibly blows the air to generate blowing force.
  • the air discharged from the housing 4 can be introduced into the motor 20 for heat dissipation of the motor 20 .
  • the conventional blowing device constructed as described above does not comprise a diffuser for distribution of air blown from the centrifugal impeller 10 to the guide vane 30 , and thus can be designed to have small dimensions, it is appropriate for small-sized electronic appliances such as cleaning apparatuses.
  • the conventional blowing device has a problem in that absence of the diffuser causes the air discharged from the centrifugal impeller 10 not to smoothly flow to the guide vane 30 , and to leak to the intake port 1 of the housing 4 through a gap between the housing 4 and the shroud 12 , lowering fan efficiency.
  • the conventional blowing device has a problem in that, if the motor 20 is designed to dissipate heat using the air discharged from the housing 4 , the fan efficiency is lowered, causing insufficient heat dissipation of the motor 20 .
  • the present invention has been made to solve the above problems, and it is an object of the present invention to provide a blowing device which comprises a centrifugal impeller and a guide vane optimally designed to smoothly guide air from the centrifugal impeller to the guide vane, so that the blowing device can be reduced in dimensions and noise, while maximizing fan efficiency and heat dissipation of a motor.
  • a blowing device comprising: a housing having an intake port and a discharge port, a shroud rotatably equipped within the housing and having an inlet communicated with the intake port of the housing, a hub separated from the shroud in an axial direction while being connected to the motor, and a plurality of impeller blades radially disposed between the hub and the shroud, wherein the impeller blades have an average diameter in the range of 87 ⁇ 93% of a diameter of the housing.
  • Each impeller blade may have a distal end perpendicular to the axial direction or slanted such that an outer diameter of the impeller blade is gradually decreased from the shroud to the hub.
  • the shroud may have an outer diameter in the range of 103 ⁇ 106% of the average diameter of the impeller blades.
  • the hub may have an outer diameter in the range of 95 ⁇ 98% of the average diameter of the impeller blades.
  • An axial distance between a distal end of the shroud and a distal end of the hub may be in the range of 25 ⁇ 50% of an axial height of the housing.
  • the blowing device may further comprise: a guide vane including a guide vane plate opposite to the hub, and a plurality of guide vane blades radially disposed to the guide vane plate, wherein the guide vane blades have an outer diameter in the range of 103 ⁇ 108% of the average diameter of the impeller blades.
  • the guide vane plate may have an outer diameter in the range of 100 ⁇ 102% of the average diameter of the impeller blades.
  • the guide vane may have an axial height in the range of 100 ⁇ 110% of the axial distance between the distal end of the shroud and the distal end of the hub.
  • a blowing device comprising: a housing having an intake port and a discharge port, a shroud rotatably equipped within the housing and having an inlet communicated with the intake port of the housing, a hub separated from the shroud in an axial direction while being connected to the motor, and a plurality of impeller blades radially disposed between the hub and the shroud, wherein the impeller blades have an average diameter in the range of 87 ⁇ 93% of a diameter of the housing, the shroud has an outer diameter in the range of 103 ⁇ 106% of the average diameter of the impeller blades, the hub has an outer diameter in the range of 95 ⁇ 98% of the average diameter of the impeller blades, and an axial distance between a distal end of the shroud and a distal end of the hub is in the range of 25 ⁇ 50% of an axial height of the housing.
  • the blowing device may further comprise: a guide vane including a guide vane plate opposite to the hub, and a plurality of guide vane blades radially disposed to the guide vane plate, wherein the guide vane plate has an outer diameter in the range of 100 ⁇ 102% of the average diameter of the impeller blades, the guide vane blades have an outer diameter in the range of 103 ⁇ 108% of the average diameter of the impeller blades, and the guide vane has an axial height in the range of 100 ⁇ 110% of the axial distance between the distal end of the shroud and the distal end of the hub.
  • Each impeller blade may have a distal end perpendicular to the axial direction or slanted such that an outer diameter of the impeller blade is gradually decreased from the shroud to the hub.
  • a blowing device comprises: a housing having an intake port and a discharge port, a shroud rotatably equipped within the housing and having an inlet communicated with the intake port of the housing, a hub separated from the shroud in an axial direction while being connected to the motor, and a plurality of impeller blades radially disposed between the hub and the shroud, wherein the impeller blades have an average diameter smaller than a diameter of the shroud.
  • outer diameters of the impeller blades refer to diameters of circles defined by connecting distal ends of the plurality of impeller blades
  • average diameter of the impeller blades refers to an average of the outer diameters of the impeller blades in an axial direction.
  • the hub may have a diameter smaller than the average diameter of the impeller blades.
  • blowing apparatus constructed as described above is that the centrifugal impeller and the guide vane are optimally designed to allow air to smoothly flow from the centrifugal impeller to the guide vane without a diffuser, so that the blowing device can be reduced in dimensions and noise, while ensuring good fan efficiency and heat dissipation of a motor.
  • FIG. 1 is a perspective view illustrating a conventional blowing device
  • FIG. 2 is a cross-sectional view illustrating a main component of the conventional blowing device
  • FIG. 3 is a cross-sectional view illustrating a main component of a blowing device in accordance with a first embodiment of the present invention
  • FIG. 4 is a graph depicting fan efficiency according to variation in ratio of an average diameter of impeller blades to a diameter of a housing of the blowing device in accordance with the present invention
  • FIG. 5 is a graph depicting the fan efficiency according to variation in ratio of an outer diameter of a shroud to the diameter of the housing of the blowing device in accordance with the present invention
  • FIG. 6 is a graph depicting the fan efficiency according to variation in ratio of the outer diameter of the shroud to the average diameter of the impeller blades of the blowing device in accordance with the present invention
  • FIG. 7 is a graph depicting the fan efficiency according to variation in ratio of the outer diameter of the hub to the average diameter of the impeller blades of the blowing device in accordance with the present invention.
  • FIG. 8 is a graph depicting the fan efficiency according to variation in ratio of an outer diameter of guide vane blades to the diameter of the housing of the blowing device in accordance with the present invention
  • FIG. 9 is a graph depicting the fan efficiency according to variation in ratio of the outer diameter of the guide vane blades to the average diameter of the impeller blades of the blowing device in accordance with the present invention.
  • FIG. 10 is a graph depicting the fan efficiency according to variation in ratio of an outer diameter of a guide vane plate to the diameter of the housing of the blowing device in accordance with the present invention.
  • FIG. 11 is a graph depicting the fan efficiency according to variation in ratio of the outer diameter of the guide vane plate to the average diameter of the impeller blades of the blowing device in accordance with the present invention
  • FIG. 12 is a graph depicting the fan efficiency according to variation in ratio of an axial height of the guide vane to an impeller height of a centrifugal impeller of the blowing device in accordance with the present invention
  • FIG. 13 is a graph depicting pressure coefficients of inventive and conventional blowing devices
  • FIG. 14 is a graph depicting the fan efficiency of the inventive and conventional blowing devices.
  • FIG. 15 is a cross-sectional view illustrating a blowing device in accordance with a second embodiment of the present invention.
  • FIG. 3 is a cross-sectional view illustrating a main component of a blowing device according to a first embodiment of the invention.
  • the blowing device comprises a housing 50 having an intake port 51 and a discharge port 42 , a centrifugal impeller 60 rotatably equipped within the housing 50 while being connected to a motor via a shaft 54 to generate blowing force from the intake port 51 to the discharge port 52 of the housing 50 , and a guide vane 70 equipped within the housing 50 to guide air blown by the centrifugal impeller 60 to the discharge port 52 of the housing 50 .
  • the intake port 51 of the housing 50 is located at the center of a front side of the housing 50 so as to allow air to be sucked into the housing 50 .
  • the outlet 52 of the housing 50 is located at a rear side of the housing 50 .
  • the rear side of the housing 50 can be entirely open.
  • the housing 50 may be designed to have an axial height 50 H in the range of 20 ⁇ 100% of a diameter 50 D of the housing 50 .
  • the diameter 50 D of the housing 50 refers to a diameter at a portion of the housing 50 where the centrifugal impeller 60 is located.
  • the centrifugal impeller 60 comprises a shroud 62 having an inlet 62 ′ communicated with the intake port 51 of the housing 50 , a hub 64 separated from a rear side of the shroud 12 while being integrally coupled to the shaft 54 of the motor to rotate with the shaft 54 , and a plurality of impeller blades 66 radially disposed between the hub 64 and the shroud 62 .
  • the shroud 62 , the hub 64 , and the impeller blades 66 are designed as follows in order to maximize fan efficiency and heat dissipation of the motor. For reference, since the size of the housing 50 , and an average diameter of the impeller blades 66 are references for designing the shroud 62 , the hub 64 , and the impeller blades 66 , the impeller blades 66 will be described first, and then the shroud 62 and the hub 64 will be described subsequently.
  • the impeller blades 66 must be designed to maximize blowing capacity of the centrifugal impeller 60 while minimizing flow loss due to a narrow space between the housing 50 and the centrifugal impeller 60 under a predetermined condition of dimensions of the housing 50 .
  • FIG. 4 shows a graph depicting fan efficiency according to variation in ratio of an average diameter of the impeller blades 66 to the diameter 50 D of the housing 50 .
  • the impeller blades 66 have an average diameter in the range of 87 ⁇ 93% of the diameter 50 D of the housing 50 in order to ensure an appropriate fan efficiency.
  • outer diameters of the impeller blades 66 refer to diameters of circles defined by connecting distal ends of the plurality of impeller blades 66
  • the average diameter 66 D of the impeller blades 66 refers to an average of the outer diameters of the impeller blades 66 in the axial direction.
  • the reason for using the average diameter 66 D of the impeller blades 66 is that, as the impeller blades 66 have the outer diameters gradually decreased from the shroud 62 to the hub 64 , the distal ends of the impeller blades 66 are slanted in the axial direction of the centrifugal impeller 60 .
  • the average diameter 66 d of the impeller blades 66 be smaller than a diameter 62 D of the shroud 62 in order to prevent air discharged from the centrifugal impeller 60 from being leaked to the intake port 51 of the housing 50 through a gap between the shroud 62 and the housing 50 .
  • the shroud 62 have not only the diameter 62 D larger than the average diameter 66 D of the impeller blades 66 , but also the following structure in consideration of interference with the housing 50 .
  • FIG. 5 shows a graph depicting the fan efficiency according to variation in ratio of an outer diameter 62 D of the shroud 62 to the diameter 50 D of the housing 50 .
  • the shroud 62 be designed to have an outer diameter 62 D greater than or equal to 90% of the diameter 50 D of the housing 50 .
  • FIG. 6 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 62 D of the shroud 62 to the average diameter of the impeller blades 66 .
  • the shroud 62 be designed to have the outer diameter 62 D greater than or equal to 103% of the average diameter of the impeller blades 66 .
  • the ratio of the outer diameter 62 D of the shroud 62 to the average diameter of the impeller blades 66 is greater than or equal to a predetermined value under the predetermined condition of the size of the housing 50 .
  • the ratio of the average diameter of the impeller blades 66 to the diameter 50 D of the housing 50 must be decreased.
  • the impeller blades 66 have the average diameter in the range of 87 ⁇ 93% of the diameter 50 D of the housing 50 .
  • the shroud 62 have the outer diameter 62 D in the range of 90 ⁇ 95% of the diameter 50 D of the housing 50 while being in the range of 103 ⁇ 106% of the average diameter 66 D of the impeller blades 66 .
  • FIG. 7 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 64 D of the hub 64 to the average diameter of the impeller blades 66 .
  • the hub 64 have an outer diameter 64 D in the range of 95 ⁇ 98% of the average diameter of the impeller blades 66 .
  • the centrifugal impeller 60 has an impeller height 60 H in the range of 25 ⁇ 50% of an axial height 50 H of the housing 50 .
  • the impeller height 60 H of the centrifugal impeller 60 refers to a distance defined by connecting a distal end of the hub 62 to a distal end of the hub 64 in the axial direction of the impeller 60 .
  • the guide vane 70 comprises a plurality of guide vane blades 72 radially disposed at a rear side of the centrifugal impeller 60 , and a guide vane plate 74 opposite to the hub 64 to connect the plurality of guide vane blades 72 .
  • the guide vane blades 72 and the guide vane plates 74 are also designed to optimize the fan efficiency and the heat dissipation of the motor, as described below.
  • FIG. 8 shows a graph depicting the fan efficiency according to variation in ratio of an outer diameter 72 D of the guide vane blades 72 to the diameter 50 D of the housing 50 .
  • the guide vane blades 72 are designed to have the outer diameter 72 D about 90% or 95% or more of the diameter 50 D of the housing 50 .
  • FIG. 9 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 72 D of the guide vane blades 72 to the average diameter of the impeller blades 66 .
  • the guide vane blades 72 are designed to have the outer diameter 72 D less than 100% or 103% or more of the average diameter of the impeller blades 66 . Accordingly, in order to satisfy both conditions shown by the graphs of FIGS. 8 and 9 , the guide vane blades 72 are designed to have the outer diameter 72 D in the range of 103 ⁇ 108% of the average diameter of the impeller blades 66 .
  • the outer diameter 72 D of the guide vane blades 72 refers to a diameter of a circle defined by connecting distal ends of the guide vane blades 72 .
  • FIG. 10 shows a graph depicting the fan efficiency according to variation in ratio of an outer diameter 74 D of the guide vane plate 74 to the diameter 50 D of the housing 50 .
  • the guide vane plate 74 is designed to have the outer diameter 74 D about 90% of the diameter 50 D of the housing 50 .
  • FIG. 11 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 74 D of the guide vane plate 74 to the average diameter of the impeller blades 66 .
  • the guide vane plate 74 is designed to have the outer diameter 74 D substantially the same as the average diameter of the impeller blades 66 . Accordingly, in order to satisfy both conditions shown by the graphs of FIGS. 10 and 11 , the guide vane plate 74 is also designed to have the outer diameter 74 D in the range of 100 ⁇ 102% of the average diameter of the impeller blades 66 .
  • an axial height 70 H of the guide vane 70 also influences the fan efficiency of the blowing device.
  • FIG. 12 shows a graph depicting the fan efficiency according to variation in ratio of the axial height 70 H of the guide vane 70 to the impeller height 60 H of the centrifugal impeller 60 .
  • the guide vane 70 is designed to have the axial height 70 H in the range of 100 ⁇ 110% of the impeller height 60 H of the centrifugal impeller 60 .
  • the shroud 62 , the hub 64 , and the impeller blades 66 are integrally rotated to generate blowing force. Then, air outside the housing 50 is sucked into the centrifugal impeller 60 through the intake port 51 of the housing 50 , and the inlet 62 ′ of the shroud 62 . The air sucked into the centrifugal impeller 60 is discharged from the centrifugal impeller 60 in the centrifugal direction. The air discharged from the centrifugal impeller 60 is guided by the guide vane 30 , and is then discharged from the housing 50 to the outside through the discharge port 52 of the housing 50 .
  • the blowing device of the invention constructed as described above has the optimally designed centrifugal impeller 60 and guide vane 70 , so that the fan efficiency of the invention is enhanced in comparison to the conventional blowing device shown in FIGS. 1 and 2 .
  • FIG. 13 shows a graph depicting relationship between pressure coefficient and flow coefficient of an inventive blowing device A and a conventional blowing device B
  • FIG. 14 shows a graph depicting relationship between the fan efficiency and the flow coefficient of the blowing devices A and B.
  • the inventive blowing device A is excellent in pressure efficiency and fan efficiency to the conventional blowing device B.
  • the blowing device of the invention having the enhanced blowing force in comparison to the conventional blowing device can enhance the heat dissipation of the motor.
  • FIGS. 13 and 14 Another embodiment of the invention will be described with reference to FIGS. 13 and 14 , in which like elements will be denoted by like reference numerals, and detailed description thereof will be omitted.
  • FIG. 15 is a cross-sectional view illustrating a blowing device according to a second embodiment of the invention.
  • a centrifugal impeller 60 comprises a shroud 62 , a hub 64 , and a plurality of impeller blades 66 , which are optimally designed to ensure fan efficiency and heat dissipation of a motor.
  • the impeller blades 66 are designed to have an average diameter in the range of 87 ⁇ 93% of a diameter 50 D of the housing 50 , and to have distal ends perpendicular to the axial direction of the centrifugal impeller 60 .
  • the impeller blades 66 have the distal ends perpendicular to the axial direction of the centrifugal impeller 60 , the impeller blades 66 have an identical outer diameter 66 D in the axial direction, and thus the average diameter of the impeller blades 66 is the outer diameter of the impeller blades 66 .
  • the blowing device according to the second embodiment of the invention constructed as described above can maximize the fan efficiency and heat dissipation of the motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US11/332,213 2005-01-25 2006-01-17 Blowing device Abandoned US20060182628A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR2005-6643 2005-01-25
KR1020050006643A KR100748966B1 (ko) 2005-01-25 2005-01-25 송풍장치

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US20060182628A1 true US20060182628A1 (en) 2006-08-17

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US11/332,213 Abandoned US20060182628A1 (en) 2005-01-25 2006-01-17 Blowing device

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US (1) US20060182628A1 (ja)
EP (1) EP1683972B1 (ja)
JP (1) JP4995464B2 (ja)
KR (1) KR100748966B1 (ja)
CN (1) CN1811193B (ja)

Cited By (3)

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US20080286113A1 (en) * 2006-10-24 2008-11-20 Lg Electronics Inc. High Speed Type Impeller
USD738481S1 (en) * 2012-12-30 2015-09-08 Nela D.O.O. Electrical blower
US11511372B2 (en) 2017-04-28 2022-11-29 Fluid Handling Llc Technique to improve the performance of a pump with a trimmed impeller using additive manufacturing

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KR100833379B1 (ko) * 2007-01-15 2008-05-28 엘지전자 주식회사 원심 송풍기
US8141201B2 (en) * 2008-02-14 2012-03-27 Panasonic Corporation Electric fan
KR102061517B1 (ko) 2016-09-01 2020-02-11 삼성전자주식회사 청소기
CN109372797A (zh) * 2018-11-30 2019-02-22 深圳市商田环保科技有限公司 一种叶轮及使用该叶轮的多级离心风机
KR102499311B1 (ko) * 2022-09-28 2023-02-13 (주)동아풍력 고효율 송풍기

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US20080286113A1 (en) * 2006-10-24 2008-11-20 Lg Electronics Inc. High Speed Type Impeller
US8142160B2 (en) 2006-10-24 2012-03-27 Lg Electronics Inc. High speed type impeller having a reinforcing ring
USD738481S1 (en) * 2012-12-30 2015-09-08 Nela D.O.O. Electrical blower
US11511372B2 (en) 2017-04-28 2022-11-29 Fluid Handling Llc Technique to improve the performance of a pump with a trimmed impeller using additive manufacturing

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KR20060085797A (ko) 2006-07-28
JP2006207587A (ja) 2006-08-10
JP4995464B2 (ja) 2012-08-08
EP1683972A2 (en) 2006-07-26
EP1683972A3 (en) 2011-06-29
CN1811193B (zh) 2011-06-01
KR100748966B1 (ko) 2007-08-13
EP1683972B1 (en) 2014-03-19
CN1811193A (zh) 2006-08-02

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