EP1683972A2 - Blowing device - Google Patents
Blowing device Download PDFInfo
- Publication number
- EP1683972A2 EP1683972A2 EP05028212A EP05028212A EP1683972A2 EP 1683972 A2 EP1683972 A2 EP 1683972A2 EP 05028212 A EP05028212 A EP 05028212A EP 05028212 A EP05028212 A EP 05028212A EP 1683972 A2 EP1683972 A2 EP 1683972A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- impeller blades
- guide vane
- shroud
- blades
- 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.)
- Granted
Links
Images
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
- 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
- A63H33/046—Building blocks, strips, or similar building parts comprising magnetic interaction means, e.g. holding together by magnetic attraction
-
- 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
- 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, and the discharge port 2 of the housing 4 is located at a rear side of the housing 4.
- the shroud 12, the hub 14, and the blades 16 are typically designed to have an identical outer diameter 10D.
- 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 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.
- 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. 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 50H in the range of 20 - 100 % of a diameter 50D of the housing 50.
- the diameter 50D 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.
- 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 66D 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 66D 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 66d of the impeller blades 66 be smaller than a diameter 62D 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 62D larger than the average diameter 66D 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 62D of the shroud 62 to the diameter 50D of the housing 50.
- the shroud 62 be designed to have an outer diameter 62D greater than or equal to 90% of the diameter 50D of the housing 50.
- Fig. 6 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 62D of the shroud 62 to the average diameter of the impeller blades 66.
- the shroud 62 be designed to have the outer diameter 62D greater than or equal to 103 % of the average diameter of the impeller blades 66.
- the ratio of the outer diameter 62D 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 50D of the housing 50 must be decreased.
- the impeller blades 66 have the average diameter in the range of 87 - 93 % of the diameter 50D of the housing 50.
- the shroud 62 have the outer diameter 62D in the range of 90 - 95 % of the diameter 50D of the housing 50 while being in the range of 103 - 106 % of the average diameter 66D of the impeller blades 66.
- Fig. 7 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 64D of the hub 64 to the average diameter of the impeller blades 66.
- the hub 64 have an outer diameter 64D in the range of 95 - 98 % of the average diameter of the impeller blades 66.
- the centrifugal impeller 60 has an impeller height 60H in the range of 25 ⁇ 50 % of an axial height 50H of the housing 50.
- the impeller height 60H 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 72D of the guide vane blades 72 to the diameter 50D of the housing 50.
- the guide vane blades 72 are designed to have the outer diameter 72D about 90 % or 95 % or more of the diameter 50D of the housing 50.
- Fig. 9 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 72D 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 72D 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 72D in the range of 103 ⁇ 108 % of the average diameter of the impeller blades 66.
- the outer diameter 72D 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 74D of the guide vane plate 74 to the diameter 50D of the housing 50.
- the guide vane plate 74 is designed to have the outer diameter 74D about 90 % of the diameter 50D of the housing 50.
- Fig. 11 shows a graph depicting the fan efficiency according to variation in ratio of the outer diameter 74D 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 74D 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 74D in the range of 100 ⁇ 102 % of the average diameter of the impeller blades 66.
- an axial height 70H 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 70H of the guide vane 70 to the impeller height 60H of the centrifugal impeller 60.
- the guide vane 70 is designed to have the axial height 70H in the range of 100 - 110 % of the impeller height 60H 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.
- 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 50D 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 66D in the axial direction, and thus the average diameter of the impeller blades 66 is the outer diameter of the impeller blades 66.
- blowing device according to the first embodiment of the invention described with reference to Figs. 3 to 14 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
- 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, and 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 adischarge port 2, acentrifugal impeller 10 rotatably equipped within the housing 4, and amotor 20 connected to thecentrifugal impeller 10 via ashaft 21 to rotate thecentrifugal impeller 10. - The
intake port 1 of the housing 4 is located at the center of a front side of the housing 4, and thedischarge 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. Thecentrifugal impeller 10 comprises ashroud 12 having an inlet 12' communicated with theintake port 1 of the housing 4, ahub 14 separated from theshroud 12 in an axial direction while being coupled to theshaft 21 of themotor 20 to integrally rotate with theshaft 21, and a plurality ofblades 16 radially disposed between theshroud 12 and thehub 14. - As the floor area ratio of the
centrifugal impeller 10 to the housing 4 is increased, thecentrifugal impeller 10 can have an increased blowing capacity. However, if the floor area ratio of thecentrifugal impeller 10 to the housing 4 is excessive, thecentrifugal impeller 10 can interfere with the housing 4, and in particular, there occurs an increase in flow resistance of air blown from thecentrifugal impeller 10 to thedischarge port 2 of the housing 4. Accordingly, thecentrifugal impeller 10 is designed to maintain a predetermined distance G from the housing 4. - Here, the
shroud 12, thehub 14, and theblades 16 are typically designed to have an identicalouter diameter 10D. For reference, the outer diameter of theblades 16 refers to a diameter of a circle which is defined by connecting distal ends of the plurality ofblades 16. - In the mean time, the housing 4 is provided with a
guide vane 30 to guide the air from thecentrifugal impeller 10 to thedischarge port 2 of the housing 4. - Operation of the conventional blowing device constructed as described above will be described as follows.
- When the
motor 20 is driven, thecentrifugal impeller 10 is rotated by rotational force of themotor 20. - Then, air outside the housing 4 is sucked into the
centrifugal impeller 10 through theintake port 1 of the housing 4 and the inlet 12' of theshroud 12. The air sucked into thecentrifugal impeller 10 is blown in the centrifugal direction of thecentrifugal impeller 10 by the plurality ofblades 16, and is discharged from thecentrifugal impeller 10. The air discharged from thecentrifugal impeller 10 is guided by theguide vane 30, and is discharged from the housing 4 through thedischarge port 2 of the housing 4. - As such, the
centrifugal impeller 10 forcibly blows the air to generate blowing force. - Meanwhile, the air discharged from the housing 4 can be introduced into the
motor 20 for heat dissipation of themotor 20. - As such, since the conventional blowing device constructed as described above does not comprise a diffuser for distribution of air blown from the
centrifugal impeller 10 to theguide vane 30, and thus can be designed to have small dimensions, it is appropriate for small-sized electronic appliances such as cleaning apparatuses. However, the conventional blowing device has a problem in that absence of the diffuser causes the air discharged from thecentrifugal impeller 10 not to smoothly flow to theguide vane 30, and to leak to theintake port 1 of the housing 4 through a gap between the housing 4 and theshroud 12, lowering fan efficiency. - Additionally, 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 themotor 20. - Additionally, there is a problem in that air flow leaked from the
intake port 1 of the housing 4 collides with air flow sucked through theintake port 1 of the housing 4, causing severe flow noise. - 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.
- In accordance with one aspect of the present invention, the above and other objects can be accomplished by the provision of 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.
- In accordance with another aspect of the present invention, a blowing device is provided, 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.
- In accordance with yet another aspect of the present invention, 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.
- Here, when outer diameters of the impeller blades refer to diameters of circles defined by connecting distal ends of the plurality of impeller blades, the 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.
- One of the advantages of the 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.
- The foregoing and other objects and features of the present invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:
- 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; and
- Fig. 15 is a cross-sectional view illustrating a blowing device in accordance with a second embodiment of the present invention.
- Preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings, in which like reference numerals refer to like components throughout.
- It should be noted that although various embodiments can be realized within the scope of the invention, most preferred embodiments of the invention will be described hereinafter. Meanwhile, since the structure of a blowing device is the same as that of the conventional blowing device as described above, detailed description thereof will be omitted hereinafter.
- 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 according to the first embodiment of the invention comprises a
housing 50 having anintake port 51 and a discharge port 42, acentrifugal impeller 60 rotatably equipped within thehousing 50 while being connected to a motor via ashaft 54 to generate blowing force from theintake port 51 to thedischarge port 52 of thehousing 50, and aguide vane 70 equipped within thehousing 50 to guide air blown by thecentrifugal impeller 60 to thedischarge port 52 of thehousing 50. - The
intake port 51 of thehousing 50 is located at the center of a front side of thehousing 50 so as to allow air to be sucked into thehousing 50. Theoutlet 52 of thehousing 50 is located at a rear side of thehousing 50. Here, the rear side of thehousing 50 can be entirely open. - The
housing 50 may be designed to have anaxial height 50H in the range of 20 - 100 % of adiameter 50D of thehousing 50. Here, thediameter 50D of thehousing 50 refers to a diameter at a portion of thehousing 50 where thecentrifugal impeller 60 is located. - The
centrifugal impeller 60 comprises ashroud 62 having an inlet 62' communicated with theintake port 51 of thehousing 50, ahub 64 separated from a rear side of theshroud 12 while being integrally coupled to theshaft 54 of the motor to rotate with theshaft 54, and a plurality ofimpeller blades 66 radially disposed between thehub 64 and theshroud 62. - The
shroud 62, thehub 64, and theimpeller blades 66 are designed as follows in order to maximize fan efficiency and heat dissipation of the motor. For reference, since the size of thehousing 50, and an average diameter of theimpeller blades 66 are references for designing theshroud 62, thehub 64, and theimpeller blades 66, theimpeller blades 66 will be described first, and then theshroud 62 and thehub 64 will be described subsequently. - The
impeller blades 66 must be designed to maximize blowing capacity of thecentrifugal impeller 60 while minimizing flow loss due to a narrow space between thehousing 50 and thecentrifugal impeller 60 under a predetermined condition of dimensions of thehousing 50. With regard to this, Fig. 4 shows a graph depicting fan efficiency according to variation in ratio of an average diameter of theimpeller blades 66 to thediameter 50D of thehousing 50. As can be appreciated from Fig. 4, it is desirable that theimpeller blades 66 have an average diameter in the range of 87 - 93 % of thediameter 50D of thehousing 50 in order to ensure an appropriate fan efficiency. - Here, outer diameters of the
impeller blades 66 refer to diameters of circles defined by connecting distal ends of the plurality ofimpeller blades 66, and theaverage diameter 66D of theimpeller blades 66 refers to an average of the outer diameters of theimpeller blades 66 in the axial direction. Here, the reason for using theaverage diameter 66D of theimpeller blades 66 is that, as theimpeller blades 66 have the outer diameters gradually decreased from theshroud 62 to thehub 64, the distal ends of theimpeller blades 66 are slanted in the axial direction of thecentrifugal impeller 60. - In addition, it is desirable that the
average diameter 66d of theimpeller blades 66 be smaller than adiameter 62D of theshroud 62 in order to prevent air discharged from thecentrifugal impeller 60 from being leaked to theintake port 51 of thehousing 50 through a gap between theshroud 62 and thehousing 50 - Next, it is desirable that the
shroud 62 have not only thediameter 62D larger than theaverage diameter 66D of theimpeller blades 66, but also the following structure in consideration of interference with thehousing 50. - With regard to this, Fig. 5 shows a graph depicting the fan efficiency according to variation in ratio of an
outer diameter 62D of theshroud 62 to thediameter 50D of thehousing 50. As can be appreciated from Fig. 5, it is desirable that theshroud 62 be designed to have anouter diameter 62D greater than or equal to 90% of thediameter 50D of thehousing 50. Additionally, Fig. 6 shows a graph depicting the fan efficiency according to variation in ratio of theouter diameter 62D of theshroud 62 to the average diameter of theimpeller blades 66. As can be appreciated from Fig. 6, it is desirable that theshroud 62 be designed to have theouter diameter 62D greater than or equal to 103 % of the average diameter of theimpeller blades 66. - Additionally, in order to ensure that the ratio of the
outer diameter 62D of theshroud 62 to the average diameter of theimpeller blades 66 is greater than or equal to a predetermined value under the predetermined condition of the size of thehousing 50, the ratio of the average diameter of theimpeller blades 66 to thediameter 50D of thehousing 50 must be decreased. However, as described with reference to Fig. 4, theimpeller blades 66 have the average diameter in the range of 87 - 93 % of thediameter 50D of thehousing 50. Accordingly, it is desirable that theshroud 62 have theouter diameter 62D in the range of 90 - 95 % of thediameter 50D of thehousing 50 while being in the range of 103 - 106 % of theaverage diameter 66D of theimpeller blades 66. - Next, it is desirable that the
hub 64 be smaller than theimpeller blades 66 in order to allow the air blown by thecentrifugal impeller 60 to smoothly flow to theguide vane 70. With regard to this, Fig. 7 shows a graph depicting the fan efficiency according to variation in ratio of theouter diameter 64D of thehub 64 to the average diameter of theimpeller blades 66. As can be appreciated from Fig. 7, it is desirable that thehub 64 have anouter diameter 64D in the range of 95 - 98 % of the average diameter of theimpeller blades 66. - With the structure as described above, the
centrifugal impeller 60 has animpeller height 60H in the range of 25 ~ 50 % of anaxial height 50H of thehousing 50. Here, theimpeller height 60H of thecentrifugal impeller 60 refers to a distance defined by connecting a distal end of thehub 62 to a distal end of thehub 64 in the axial direction of theimpeller 60. - The
guide vane 70 comprises a plurality ofguide vane blades 72 radially disposed at a rear side of thecentrifugal impeller 60, and aguide vane plate 74 opposite to thehub 64 to connect the plurality ofguide vane blades 72. - The
guide vane blades 72 and theguide 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 72D of theguide vane blades 72 to thediameter 50D of thehousing 50. Theguide vane blades 72 are designed to have theouter diameter 72D about 90 % or 95 % or more of thediameter 50D of thehousing 50. Additionally, Fig. 9 shows a graph depicting the fan efficiency according to variation in ratio of theouter diameter 72D of theguide vane blades 72 to the average diameter of theimpeller blades 66. Theguide vane blades 72 are designed to have theouter diameter 72D less than 100 % or 103 % or more of the average diameter of theimpeller blades 66. Accordingly, in order to satisfy both conditions shown by the graphs of Figs. 8 and 9, theguide vane blades 72 are designed to have theouter diameter 72D in the range of 103 ~ 108 % of the average diameter of theimpeller blades 66. - Here, the
outer diameter 72D of theguide vane blades 72 refers to a diameter of a circle defined by connecting distal ends of theguide vane blades 72. - Fig. 10 shows a graph depicting the fan efficiency according to variation in ratio of an
outer diameter 74D of theguide vane plate 74 to thediameter 50D of thehousing 50. Theguide vane plate 74 is designed to have theouter diameter 74D about 90 % of thediameter 50D of thehousing 50. Additionally, Fig. 11 shows a graph depicting the fan efficiency according to variation in ratio of theouter diameter 74D of theguide vane plate 74 to the average diameter of theimpeller blades 66. Theguide vane plate 74 is designed to have theouter diameter 74D substantially the same as the average diameter of theimpeller blades 66. Accordingly, in order to satisfy both conditions shown by the graphs of Figs. 10 and 11, theguide vane plate 74 is also designed to have theouter diameter 74D in the range of 100 ~ 102 % of the average diameter of theimpeller blades 66. - As shown in Fig. 12, an
axial height 70H of theguide 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 theaxial height 70H of theguide vane 70 to theimpeller height 60H of thecentrifugal impeller 60. Theguide vane 70 is designed to have theaxial height 70H in the range of 100 - 110 % of theimpeller height 60H of thecentrifugal impeller 60. - Operation of the blowing device constructed as described above will be described as follows.
- When the motor is driven, the
shroud 62, thehub 64, and theimpeller blades 66 are integrally rotated to generate blowing force. Then, air outside thehousing 50 is sucked into thecentrifugal impeller 60 through theintake port 51 of thehousing 50, and the inlet 62' of theshroud 62. The air sucked into thecentrifugal impeller 60 is discharged from thecentrifugal impeller 60 in the centrifugal direction. The air discharged from thecentrifugal impeller 60 is guided by theguide vane 30, and is then discharged from thehousing 50 to the outside through thedischarge port 52 of thehousing 50. - As shown in Figs. 3 to 12, the blowing device of the invention constructed as described above has the optimally designed
centrifugal impeller 60 and guidevane 70, so that the fan efficiency of the invention is enhanced in comparison to the conventional blowing device shown in Figs. 1 and 2. - With regard to this, 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, and Fig. 14 shows a graph depicting relationship between the fan efficiency and the flow coefficient of the blowing devices A and B. As can be appreciated from Figs. 13 and 14, the inventive blowing device A is excellent in pressure efficiency and fan efficiency to the conventional blowing device B.
- Additionally, when air discharged from the
housing 50 flows into the motor in order to dissipate heat from the motor, 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. - 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.
- As shown in Fig. 15, in the blowing device according to the second embodiment, a
centrifugal impeller 60 comprises ashroud 62, ahub 64, and a plurality ofimpeller blades 66, which are optimally designed to ensure fan efficiency and heat dissipation of a motor. - In particular, the
impeller blades 66 are designed to have an average diameter in the range of 87 - 93 % of adiameter 50D of thehousing 50, and to have distal ends perpendicular to the axial direction of thecentrifugal impeller 60. - Here, since the
impeller blades 66 have the distal ends perpendicular to the axial direction of thecentrifugal impeller 60, theimpeller blades 66 have an identicalouter diameter 66D in the axial direction, and thus the average diameter of theimpeller blades 66 is the outer diameter of theimpeller blades 66. - As with the blowing device according to the first embodiment of the invention described with reference to Figs. 3 to 14, 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.
- It should be understood that the embodiments and the accompanying drawings have been described for illustrative purposes and the present invention is limited by the following claims. Further, those skilled in the art will appreciate that various modifications, additions and substitutions are allowed without departing from the scope and spirit of the invention as set forth in the accompanying claims.
Claims (13)
- A blowing device, comprising: a housing 50 having an intake port 51 and a discharge port 52, a shroud 62 rotatably equipped within the housing 50 and having an inlet 62' communicated with the intake port 51 of the housing 50, a hub 64 separated from the shroud 62 in an axial direction while being connected to a motor, and a plurality of impeller blades 66 radially disposed between the hub 64 and the shroud 62, wherein, when outer diameters 66D of the impeller blades 66 refer to diameters of circles defined by connecting distal ends of the plurality of impeller blades 66, and an average diameter of the impeller blades 66 refers to an average of the outer diameters 66D of the impeller blades 66 in the axial direction, the impeller blades 66 have the average diameter in the range of 87 - 93 % of a diameter 50D of the housing 50.
- The blowing device as set forth in claim 1, wherein each impeller blade 66 has a distal end perpendicular to the axial direction.
- The blowing device as set forth in claim 1, wherein each impeller blade 66 has a distal end slanted such that the outer diameter 66D of the impeller blade 66 is gradually decreased from the shroud 62 to the hub 64.
- The blowing device as set forth in any of claims 1 to 3, wherein the shroud 62 has an outer diameter 62D in the range of 103 ~ 106 % of the average diameter of the impeller blades 66.
- The blowing device as set forth in any of claims 1 to 4, wherein the hub 64 has an outer diameter 64D in the range of 95 - 98 % of the average diameter of the impeller blades 66.
- The blowing device as set forth in any of claims 1 to 5, wherein an axial distance 60H between a distal end of the shroud 62 and a distal end of the hub 64 is in the range of 25 - 50 % of an axial height 50H of the housing 50.
- The blowing device as set forth in any of claims 1 to 6, further comprising: a guide vane 70 including a guide vane plate 74 opposite to the hub 64, and a plurality of guide vane blades 72 radially disposed to the guide vane plate 74, wherein, when an outer diameter 72D of the guide vane blades 72 refers to a diameter of a circle defined by connecting distal ends of the guide vane blades 72, the guide vane blades 72 have the outer diameter 72D in the range of 103 - 108 % of the average diameter of the impeller blades 66.
- The blowing device as set forth in claim 7, wherein the guide vane plate 74 has an outer diameter 74D in the range of 100 - 102 % of the average diameter of the impeller blades 66.
- The blowing device as set forth in claim 7 or 8, wherein the guide vane 70 has an axial height 70H in the range of 100 - 110 % of the axial distance between the distal end of the shroud 62 and the distal end of the hub 64.
- A blowing device, comprising: a housing 50 having an intake port 51 and a discharge port 52, a shroud 62 rotatably equipped within the housing 50 and having an inlet 62' communicated with the intake port 51 of the housing 50, a hub 64 separated from the shroud 62 in an axial direction while being connected to a motor, and a plurality of impeller blades 66 radially disposed between the hub 64 and the shroud 62, wherein when outer diameters 66D of the impeller blades 66 refer to diameters of circles defined by connecting distal ends of the plurality of impeller blades 66, and an average diameter of the impeller blades 66 refers to an average of the outer diameters 66D of the impeller blades 66 in the axial direction, the impeller blades 66 have the average diameter in the range of 87 - 93 % of a diameter 50D of the housing 50, the shroud 62 has an outer diameter 62D in the range of 103 - 106 % of the average diameter of the impeller blades 66, the hub 64 has an outer diameter 64D in the range of 95 - 98 % of the average diameter of the impeller blades 66, and an axial distance 60H between a distal end of the shroud 62 and a distal end of the hub 64 is in the range of 25 - 50 % of an axial height 50H of the housing 50.
- The blowing device as set forth in claim 10, further comprising: a guide vane 70 including a guide vane plate 74 opposite to the hub 64, and a plurality of guide vane blades 72 radially disposed to the guide vane plate 74, wherein, when an outer diameter 72D of the guide vane blades 72 refers to a diameter of a circle defined by connecting distal ends of the guide vane blades 72, the guide vane plate 74 has an outer diameter 74D in the range of 100 - 102 % of the average diameter of the impeller blades 66, the guide vane blades 72 have the outer diameter 72D in the range of 103 - 108 % of the average diameter of the impeller blades 66, and the guide vane 70 has an axial height 70H in the range of 100 - 110 % of the axial distance 60H between the distal end of the shroud 62 and the distal end of the hub 64.
- 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, when outer diameters of the impeller blades refer to diameters of circles defined by connecting distal ends of the plurality of impeller blades, and the average diameter of the impeller blades refers to an average of the outer diameters of the impeller blades in an axial direction.
- The blowing device as set forth in claim 12, wherein the hub has a diameter smaller than the average diameter of the impeller blades.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020050006643A KR100748966B1 (en) | 2005-01-25 | 2005-01-25 | Fan |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1683972A2 true EP1683972A2 (en) | 2006-07-26 |
EP1683972A3 EP1683972A3 (en) | 2011-06-29 |
EP1683972B1 EP1683972B1 (en) | 2014-03-19 |
Family
ID=36216960
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05028212.8A Expired - Fee Related EP1683972B1 (en) | 2005-01-25 | 2005-12-22 | Blowing device |
Country Status (5)
Country | Link |
---|---|
US (1) | US20060182628A1 (en) |
EP (1) | EP1683972B1 (en) |
JP (1) | JP4995464B2 (en) |
KR (1) | KR100748966B1 (en) |
CN (1) | CN1811193B (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8142160B2 (en) * | 2006-10-24 | 2012-03-27 | Lg Electronics Inc. | High speed type impeller having a reinforcing ring |
KR100833379B1 (en) * | 2007-01-15 | 2008-05-28 | 엘지전자 주식회사 | Centrifugal blowing appratus |
JP5253215B2 (en) * | 2008-02-14 | 2013-07-31 | パナソニック株式会社 | Electric blower |
USD738481S1 (en) * | 2012-12-30 | 2015-09-08 | Nela D.O.O. | Electrical blower |
KR102061517B1 (en) | 2016-09-01 | 2020-02-11 | 삼성전자주식회사 | Cleaner |
EP3615807B1 (en) | 2017-04-28 | 2021-10-06 | Fluid Handling LLC | Technique to improve the performance of a pump with a trimmed impeller using additive manufacturing |
CN109372797A (en) * | 2018-11-30 | 2019-02-22 | 深圳市商田环保科技有限公司 | A kind of impeller and the Multi-stage centrifugal fan using the impeller |
KR102499311B1 (en) * | 2022-09-28 | 2023-02-13 | (주)동아풍력 | high efficiency blower |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR879346A (en) | 1941-02-17 | 1943-02-19 | Ventilator A G | Fan |
Family Cites Families (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR928200A (en) * | 1946-05-16 | 1947-11-20 | Centrifugal fan | |
US3584968A (en) * | 1969-10-06 | 1971-06-15 | Howard I Furst | Fan construction |
JPS5198808U (en) * | 1975-02-07 | 1976-08-07 | ||
JPS52112507U (en) * | 1976-02-24 | 1977-08-26 | ||
JPS60153498A (en) * | 1984-01-20 | 1985-08-12 | Sanyo Electric Co Ltd | Electric blower |
US4683370A (en) * | 1984-08-08 | 1987-07-28 | Wagner Spray Tech Corporation | Hot air gun with air directing housing |
JPS61237897A (en) * | 1985-04-11 | 1986-10-23 | Mitsubishi Electric Corp | Motor-driven blower |
JPH0211918A (en) * | 1988-06-29 | 1990-01-17 | Matsushita Electric Ind Co Ltd | Dynamic pressure type air bearing |
JPH0587094A (en) * | 1991-09-26 | 1993-04-06 | Matsushita Electric Ind Co Ltd | Electric motor driven blower |
DE4427115C1 (en) * | 1994-07-30 | 1995-04-06 | Braun Ag | Impeller for a radial-flow fan |
JPH08193595A (en) * | 1995-01-17 | 1996-07-30 | Hitachi Ltd | Motor-driven blower of electric vacuum cleaner |
JPH09158896A (en) * | 1995-12-13 | 1997-06-17 | Matsushita Electric Ind Co Ltd | Electric blower |
DE69724868T2 (en) * | 1996-05-17 | 2004-05-06 | Calsonic Kansei Corp. | Multi-blade rotor for centrifugal fans |
DE19629220B4 (en) * | 1996-07-19 | 2005-05-12 | Motoren Ventilatoren Landshut Gmbh | High Pressure Blower |
AUPO879497A0 (en) * | 1997-08-26 | 1997-09-18 | Warman International Limited | Pump impeller and method |
US6042335A (en) * | 1998-05-04 | 2000-03-28 | Carrier Corporation | Centrifugal flow fan and fan/orifice assembly |
JP2001241398A (en) * | 2000-02-29 | 2001-09-07 | Toshiba Tec Corp | Electric blower for circulation type vacuum cleaner |
JP2003074496A (en) * | 2001-08-31 | 2003-03-12 | Sumiyoshi Kinzoku Kk | Fan motor device |
JP2003090298A (en) * | 2001-09-17 | 2003-03-28 | Nippon Soken Inc | Centrifugal fan |
JP2003290087A (en) * | 2002-04-08 | 2003-10-14 | Matsushita Electric Ind Co Ltd | Vacuum cleaner |
KR100590333B1 (en) * | 2004-03-05 | 2006-06-19 | 엘지전자 주식회사 | The fan structure of air-conditioner inner door unit |
-
2005
- 2005-01-25 KR KR1020050006643A patent/KR100748966B1/en not_active IP Right Cessation
- 2005-12-22 EP EP05028212.8A patent/EP1683972B1/en not_active Expired - Fee Related
-
2006
- 2006-01-16 CN CN2006100054878A patent/CN1811193B/en not_active Expired - Fee Related
- 2006-01-17 US US11/332,213 patent/US20060182628A1/en not_active Abandoned
- 2006-01-25 JP JP2006016279A patent/JP4995464B2/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR879346A (en) | 1941-02-17 | 1943-02-19 | Ventilator A G | Fan |
Also Published As
Publication number | Publication date |
---|---|
KR100748966B1 (en) | 2007-08-13 |
JP4995464B2 (en) | 2012-08-08 |
US20060182628A1 (en) | 2006-08-17 |
CN1811193A (en) | 2006-08-02 |
EP1683972B1 (en) | 2014-03-19 |
CN1811193B (en) | 2011-06-01 |
KR20060085797A (en) | 2006-07-28 |
EP1683972A3 (en) | 2011-06-29 |
JP2006207587A (en) | 2006-08-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1683972B1 (en) | Blowing device | |
US7520314B2 (en) | Heat dissipation apparatus | |
EP2461042B1 (en) | Air blower for an air conditioner | |
KR101392784B1 (en) | centrifugal fan | |
KR101243935B1 (en) | High performance ventilator | |
US9964118B2 (en) | Sirocco fan and air conditioner having same | |
JP6242775B2 (en) | Centrifugal compressor | |
KR20100041278A (en) | Centrifugal fan and air conditioner having the same | |
EP1627590B1 (en) | Centrifugal fan for a vacuum cleaner | |
CN110291296B (en) | Cooling fan and seat cooling device with same | |
EP1618821A2 (en) | Centrifugal fan and vacuum cleaner having the centrifugal fan | |
JP4670285B2 (en) | Impeller and blower fan having the same | |
JP4703272B2 (en) | Electric blower and vacuum cleaner | |
KR100741787B1 (en) | Impeller of a suction-inforced type and fan-motor having the same | |
EP1847716B1 (en) | Axial flow blower | |
JPH05312189A (en) | Air conditioner | |
WO2010125735A1 (en) | Ceiling-embedded ventilation fan | |
WO1998053211A1 (en) | Multi-blade centrifugal fan | |
JP5246006B2 (en) | Electric blower and electric vacuum cleaner using the same | |
KR101139118B1 (en) | Dust collector | |
WO2024122026A1 (en) | Outdoor unit of refrigeration cycle device | |
WO2021049536A1 (en) | Ventilation fan | |
JPH0723778B2 (en) | Air conditioner | |
WO2023073768A1 (en) | Outdoor unit of refrigeration cycle device | |
CN210697310U (en) | Food processor base and food processor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20060120 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04D 29/30 20060101ALI20110523BHEP Ipc: F04D 29/28 20060101AFI20060509BHEP Ipc: F04D 29/42 20060101ALI20110523BHEP Ipc: F04D 17/16 20060101ALI20110523BHEP |
|
AKX | Designation fees paid |
Designated state(s): DE FR GB |
|
17Q | First examination report despatched |
Effective date: 20120322 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20130917 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: LG ELECTRONICS INC. |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: LG ELECTRONICS INC. |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: BAE, JUN HO Inventor name: KIM, CHANG JOON Inventor name: KIM, WOOK |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602005042995 Country of ref document: DE Effective date: 20140430 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602005042995 Country of ref document: DE |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20141222 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602005042995 Country of ref document: DE Effective date: 20141222 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 11 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 12 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20161107 Year of fee payment: 12 Ref country code: FR Payment date: 20161114 Year of fee payment: 12 Ref country code: GB Payment date: 20161110 Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602005042995 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20171222 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180703 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180102 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171222 |