US20060110252A1 - Impeller for axial-flow heat-dissipating fan - Google Patents
Impeller for axial-flow heat-dissipating fan Download PDFInfo
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- US20060110252A1 US20060110252A1 US11/030,176 US3017605A US2006110252A1 US 20060110252 A1 US20060110252 A1 US 20060110252A1 US 3017605 A US3017605 A US 3017605A US 2006110252 A1 US2006110252 A1 US 2006110252A1
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
Definitions
- the present invention relates to an impeller.
- the present invention relates to an impeller for an axial-flow heat-dissipating fan.
- FIG. 1 of the drawings illustrates an impeller 10 for an axial-flow heat-dissipating fan.
- the impeller 10 is mounted in a casing 20 and includes a hub 101 and a plurality of blades 102 .
- Each blade 102 is mounted on an outer periphery of the hub 101 in an inclined angle.
- the blades 102 drive air to flow in an axial direction. Due to limitation of release of the mold forming the impeller 10 , two blades 102 adjacent to each other cannot overlap with each other when viewed from the longitudinal direction parallel to the rotational axis of the impeller 10 .
- the total amount of air driven by the impeller 10 is in proportion to the number or total air-driving area of the blades 102 . In other words, the total amount of air driven by the impeller 10 can be increased only by overcoming the release limitation of the mold.
- a complex impeller consisting of two hub parts have been disclosed in, e.g., U.S. Pat. Nos. 6,318,964 and 6,572,336. As illustrated in FIGS. 2 and 3 , such a complex impeller 3 comprises a shaft 30 , a complex hub 31 , and a plurality of blades 32 .
- the complex hub 31 includes an upper hub 31 a and a lower hub 31 b .
- a plurality of upper blades 32 a are formed on an outer periphery of the upper hub 31 a
- a plurality of lower blades 32 b are formed on an outer periphery of the lower hub 31 b , with the upper blades 32 a and the lower blades 32 b together forming the blades 32 .
- Each blade 32 overlaps with an adjacent blade 32 when viewed from a longitudinal direction parallel to the shaft 30 .
- each blade 32 is coincident with the trailing edge 322 of an adjacent blade 32 .
- the number of the blades 32 and the total air-driving area of the blades 32 are increased.
- the blades 3 are not disposed properly such that the blowing noise is high.
- An object of the present invention is to provide an impeller for an axial-flow heat-dissipating fan for increasing the air inlet amount driven by the impeller.
- Another object of the present invention is to provide an impeller for an axial-flow heat-dissipating fan with lowered blowing noise.
- An impeller for an axial-flow heat-dissipating fan in accordance with the present invention comprises a hub including an outer periphery and a plurality of blades symmetrically formed on the outer periphery of the hub and extending in an inclined angle with respect to a longitudinal direction parallel to a rotational axis of the hub.
- Each blade includes a leading edge, a trailing edge, a radial inner edge, and a radial outer edge. Two of the blades adjacent to each other overlap with each other in the longitudinal direction such that each blade has a first overlapped area and a second overlapped area.
- the first overlapped area on each blade extends outward from the leading edge and the radial inner edge but spaced from the radial outer edge of the blade.
- the second overlapped area on each blade extend outward from the trailing edge and the radial inner edge but spaced from the radial outer edge of the blade. The air inlet amount is increased and blowing noise is lowered.
- each blade projects on an adjacent blade along a rear projection line.
- the first longitudinal overlapped area is defined by the rear projection line, the leading edge of the adjacent blade, and the radial inner edge of the adjacent blade.
- each blade intersects the radial inner edge of the blade at a front base point.
- the rear projection line intersects the leading edge of the adjacent blade at a first overlapped point.
- a distance between the front base point and the overlapped point is 1 ⁇ 5-4 ⁇ 5 of a length of the leading edge.
- the rear projection line intersects the radial inner edge of the adjacent blade at a second overlapped point.
- a distance between the front base point and the overlapped point is 1 ⁇ 6-5 ⁇ 6 of a length of the radial inner edge.
- each blade projects on an adjacent blade along a front projection line.
- the second longitudinal overlapped area is defined by the front projection line, the leading edge of the adjacent blade, and the radial inner edge of the adjacent blade.
- the trailing edge of each blade intersects the radial inner edge of the blade at a rear base point.
- the front projection line intersects the trailing edge of the adjacent blade at a third overlapped point.
- a distance between the rear base point and the overlapped point is 1 ⁇ 5-4 ⁇ 5 of a length of the trailing edge.
- the front projection line intersects the trailing edge of the adjacent blade at a fourth overlapped point.
- a distance between the rear base point and the overlapped point is 1 ⁇ 6-5 ⁇ 6 of a length of the trailing edge.
- each blade is at an angle between 10 degrees and 90 degrees with the trailing edge of an adjacent blade when viewed from the longitudinal direction parallel to the rotational axis of the hub.
- each blade intersects the radial outer edge of the blade at a front end point.
- the trailing edge of each blade intersects the radial outer edge of the blade at a rear end point.
- a line passing through the front end point of the leading edge and the rear end point of the trailing edge of each blade is at an angle between 10 degrees and 70 degrees with a plane orthogonal to the rotational axis of the hub.
- FIG. 1 is a sectional view of a conventional impeller for an axial-flow heat-dissipating fan
- FIG. 2 is a side view of another conventional impeller for an axial-flow heat-dissipating fan
- FIG. 3 is a top view of the impeller in FIG. 2 ;
- FIG. 4 is an exploded perspective view of an axial-flow heat-dissipating fan with an impeller in accordance with the present invention
- FIG. 5 is an enlarged view of a circled portion in FIG. 4 ;
- FIG. 6 is a top view of the impeller in accordance with the present invention.
- FIG. 7 is a side view of the impeller in accordance with the present invention.
- FIG. 8 is a perspective view of the impeller in FIG. 5 .
- FIG. 4 shows an axial-flow heat-dissipating fan with an impeller 4 in accordance with the present invention.
- the axial-flow heat-dissipating fan includes a casing 5 for accommodating the impeller 4 .
- a motor 6 is mounted in the casing 5 for driving the impeller 4 to turn.
- the impeller 4 comprises a shaft 40 (see FIG. 7 ), a hub 41 , and a plurality of blades 42 .
- the shaft 40 extends from a center of an inner face of the hub 41 for coupling with the motor 6 .
- the blades 42 are symmetrically formed on an outer periphery of the hub 41 and extend in an inclined angle with respect to a longitudinal direction parallel to an extending direction of the shaft 40 (i.e., the rotational axis of the hub 41 ).
- Each blade 42 includes a leading edge 421 on an air inlet side of the blade 42 , a trailing edge 422 on an air outlet side of the blade 42 , a radial inner edge 423 on the outer periphery of the hub 41 , and a radial outer edge 424 distal to the outer periphery of the hub 41 .
- the leading edge 421 , the trailing edge 422 , the radial inner edge 423 , and the radial outer edge 24 are rectilinear or curved with an appropriate radius of curvature according to product needs.
- the leading edge 421 intersects the radial inner edge 423 at a front base point 11
- the leading edge 421 intersects the radial outer edge 424 at a front end point 12
- the trailing edge 424 intersects the radial inner edge 423 at a rear base point O 1
- the trailing edge 424 intersects the radial outer edge 424 at a rear end point O 2 , best shown in FIG. 5 .
- each blade 42 projects on an adjacent blade 42 along a rear projection line L 1 that intersects the leading edge 421 of the adjacent blade 42 at a first overlapped point P 1 and that intersects the radial inner edge 423 of the adjacent blade 42 at a second overlapped point P 2 .
- a first longitudinal overlapped area A 1 is defined by the rear projection line L 1 , the leading edge 421 of the adjacent blade 42 , and the radial inner edge 423 of the adjacent blade 42 .
- the distance between the front base point I 1 and the first overlapped point P 1 is preferably 1 ⁇ 5-4 ⁇ 5 (most preferably 1 ⁇ 2) of a length of the leading edge 421 . Further, the distance between the front base point 11 and the second overlapped point P 2 is preferably 1 ⁇ 6-5 ⁇ 6 (most preferably 1 ⁇ 2) of a length of the radial inner edge 423 .
- each blade 42 projects on the other adjacent blade 42 along a front projection line L 2 that intersects the trailing edge 422 of the other adjacent blade 42 at a third overlapped point P 3 and that intersects the radial inner edge 423 of the other adjacent blade 42 at a fourth overlapped point P 4 .
- a second longitudinal overlapped area A 2 is defined by the front projection line L 2 , the trailing edge 422 of the other adjacent blade 42 , and the radial inner edge 423 of the other adjacent blade 42 .
- the distance between the rear base point O 1 and the third overlapped point P 3 is preferably 1 ⁇ 5-4 ⁇ 5 (most preferably 1 ⁇ 2) of a length of the trailing edge 422 . Further, the distance between the rear base point O 1 and the fourth overlapped point P 4 is preferably 1 ⁇ 6-5 ⁇ 6 (most preferably 1 ⁇ 2) of a length of the radial inner edge 423 .
- each blade 42 when viewed from the longitudinal direction parallel to the extending direction of the shaft 40 , the leading edge 421 of each blade 42 is at an angle ⁇ 1 with the trailing edge 422 of an adjacent blade 42 .
- the angle ⁇ 1 is preferably between 10 degrees and 90 degrees, and most preferably 45 degrees. Further, the rear projection line L 1 on each blade 42 is at the same angle ⁇ 1 with the front projection line L 2 on an adjacent blade 42 . Further, the first overlapped area A 1 and the second overlapped area A 2 are spaced from the radial outer edge 422 of each blade 42 .
- a line L passing through the front end point 12 of the leading edge 421 on each blade 42 and the rear end point O 2 of the trailing edge 422 of the blade 42 is at an angle ⁇ 2 with a plane P orthogonal to the extending direction of the shaft 40 .
- the angle ⁇ 2 is preferably between 10 degrees and 70 degrees, and most preferably 30 degrees.
- the casing 5 includes an airflow passage 50 , an air inlet 51 , an air outlet 52 , a base 53 , and a plurality of ribs 54 .
- the base 53 is located in the air outlet 52 side and supported by the ribs 54 that are connected to an inner periphery delimiting the airflow passage 50 .
- the motor 6 is mounted on the base 54 for coupling with and driving the impeller 4 .
- the ribs 54 may extend in an appropriate inclination angle in the air-driving direction to provide a guiding function as well as a pressure-boosting effect.
- the impeller 4 is mounted on the casing 5 to form an axial-flow heat-dissipating fan.
- the impeller 4 drives air into the airflow passage 50 via the air inlet 51 .
- the airflow is boosted by the ribs 54 and then exits the casing 5 via the air outlet 52 .
- each blade 42 has a first overlapped area A 1 with one of the two adjacent blades 42 and a second overlapped area A 2 with the other adjacent blade 42 . None of the first overlapped area A 1 and the second overlapped area A 2 extend to the radial outer edge 422 of the blade 42 .
- the number of the blades 42 and the total air-driving area of the blades 42 of the impeller 4 in accordance with the present invention are increased as compared to the conventional impeller 1 in FIG. 1 . Further, overlapping of the blades 42 in the area adjacent to the radial outer edge 424 is avoided in the impeller 4 in accordance with the present invention as compared to the conventional impeller 3 in FIGS. 2 and 3 . The blowing noise is lowered and the air amount driven by the impeller 4 is increased.
Abstract
An impeller for an axial-flow heat-dissipating fan includes a hub and a plurality of blades symmetrically formed on an outer periphery of the hub and extending in an inclined angle with respect to a longitudinal direction parallel to a rotational axis of the hub. Each blade includes a leading edge, a trailing edge, a radial inner edge, and a radial outer edge. Two adjacent blades overlap with each other in the longitudinal direction such that each blade has first and second overlapped areas. The first overlapped area on each blade extends outward from the leading edge and the radial inner edge but spaced from the radial outer edge of the blade. The second overlapped area on each blade extend outward from the trailing edge and the radial inner edge but spaced from the radial outer edge of the blade. The air inlet amount is increased and blowing noise is lowered.
Description
- 1. Field of the Invention
- The present invention relates to an impeller. In particular, the present invention relates to an impeller for an axial-flow heat-dissipating fan.
- 2. Description of Related Art
-
FIG. 1 of the drawings illustrates animpeller 10 for an axial-flow heat-dissipating fan. Theimpeller 10 is mounted in acasing 20 and includes ahub 101 and a plurality ofblades 102. Eachblade 102 is mounted on an outer periphery of thehub 101 in an inclined angle. Theblades 102 drive air to flow in an axial direction. Due to limitation of release of the mold forming theimpeller 10, twoblades 102 adjacent to each other cannot overlap with each other when viewed from the longitudinal direction parallel to the rotational axis of theimpeller 10. The total amount of air driven by theimpeller 10 is in proportion to the number or total air-driving area of theblades 102. In other words, the total amount of air driven by theimpeller 10 can be increased only by overcoming the release limitation of the mold. - A complex impeller consisting of two hub parts have been disclosed in, e.g., U.S. Pat. Nos. 6,318,964 and 6,572,336. As illustrated in
FIGS. 2 and 3 , such acomplex impeller 3 comprises ashaft 30, acomplex hub 31, and a plurality ofblades 32. Thecomplex hub 31 includes anupper hub 31 a and alower hub 31 b. A plurality ofupper blades 32 a are formed on an outer periphery of theupper hub 31 a, and a plurality oflower blades 32 b are formed on an outer periphery of thelower hub 31 b, with theupper blades 32 a and thelower blades 32 b together forming theblades 32. Eachblade 32 overlaps with anadjacent blade 32 when viewed from a longitudinal direction parallel to theshaft 30. - As illustrated in
FIG. 3 , after assembly, the leadingedge 321 of eachblade 32 is coincident with thetrailing edge 322 of anadjacent blade 32. By such an arrangement, the number of theblades 32 and the total air-driving area of theblades 32 are increased. However, theblades 3 are not disposed properly such that the blowing noise is high. - An object of the present invention is to provide an impeller for an axial-flow heat-dissipating fan for increasing the air inlet amount driven by the impeller.
- Another object of the present invention is to provide an impeller for an axial-flow heat-dissipating fan with lowered blowing noise. SUMMARY OF THE INVENTION
- An impeller for an axial-flow heat-dissipating fan in accordance with the present invention comprises a hub including an outer periphery and a plurality of blades symmetrically formed on the outer periphery of the hub and extending in an inclined angle with respect to a longitudinal direction parallel to a rotational axis of the hub. Each blade includes a leading edge, a trailing edge, a radial inner edge, and a radial outer edge. Two of the blades adjacent to each other overlap with each other in the longitudinal direction such that each blade has a first overlapped area and a second overlapped area.
- The first overlapped area on each blade extends outward from the leading edge and the radial inner edge but spaced from the radial outer edge of the blade. The second overlapped area on each blade extend outward from the trailing edge and the radial inner edge but spaced from the radial outer edge of the blade. The air inlet amount is increased and blowing noise is lowered.
- The trailing edge of each blade projects on an adjacent blade along a rear projection line. The first longitudinal overlapped area is defined by the rear projection line, the leading edge of the adjacent blade, and the radial inner edge of the adjacent blade.
- The leading edge of each blade intersects the radial inner edge of the blade at a front base point. The rear projection line intersects the leading edge of the adjacent blade at a first overlapped point. A distance between the front base point and the overlapped point is ⅕-⅘ of a length of the leading edge.
- The rear projection line intersects the radial inner edge of the adjacent blade at a second overlapped point. A distance between the front base point and the overlapped point is ⅙-⅚ of a length of the radial inner edge.
- The trailing edge of each blade projects on an adjacent blade along a front projection line. The second longitudinal overlapped area is defined by the front projection line, the leading edge of the adjacent blade, and the radial inner edge of the adjacent blade. The trailing edge of each blade intersects the radial inner edge of the blade at a rear base point. The front projection line intersects the trailing edge of the adjacent blade at a third overlapped point. A distance between the rear base point and the overlapped point is ⅕-⅘ of a length of the trailing edge. The front projection line intersects the trailing edge of the adjacent blade at a fourth overlapped point. A distance between the rear base point and the overlapped point is ⅙-⅚ of a length of the trailing edge.
- Preferably, the leading edge of each blade is at an angle between 10 degrees and 90 degrees with the trailing edge of an adjacent blade when viewed from the longitudinal direction parallel to the rotational axis of the hub.
- The leading edge of each blade intersects the radial outer edge of the blade at a front end point. The trailing edge of each blade intersects the radial outer edge of the blade at a rear end point. Preferably, a line passing through the front end point of the leading edge and the rear end point of the trailing edge of each blade is at an angle between 10 degrees and 70 degrees with a plane orthogonal to the rotational axis of the hub.
- Other objects, advantages and novel features of this invention will become more apparent from the following detailed description when taken in conjunction with the accompanying drawings.
-
FIG. 1 is a sectional view of a conventional impeller for an axial-flow heat-dissipating fan; -
FIG. 2 is a side view of another conventional impeller for an axial-flow heat-dissipating fan; -
FIG. 3 is a top view of the impeller inFIG. 2 ; -
FIG. 4 is an exploded perspective view of an axial-flow heat-dissipating fan with an impeller in accordance with the present invention; -
FIG. 5 is an enlarged view of a circled portion inFIG. 4 ; -
FIG. 6 is a top view of the impeller in accordance with the present invention; -
FIG. 7 is a side view of the impeller in accordance with the present invention; and -
FIG. 8 is a perspective view of the impeller inFIG. 5 . -
FIG. 4 shows an axial-flow heat-dissipating fan with animpeller 4 in accordance with the present invention. The axial-flow heat-dissipating fan includes acasing 5 for accommodating theimpeller 4. Amotor 6 is mounted in thecasing 5 for driving theimpeller 4 to turn. - Referring to
FIGS. 4 and 5 , theimpeller 4 comprises a shaft 40 (seeFIG. 7 ), ahub 41, and a plurality ofblades 42. Theshaft 40 extends from a center of an inner face of thehub 41 for coupling with themotor 6. - The
blades 42 are symmetrically formed on an outer periphery of thehub 41 and extend in an inclined angle with respect to a longitudinal direction parallel to an extending direction of the shaft 40 (i.e., the rotational axis of the hub 41). Eachblade 42 includes aleading edge 421 on an air inlet side of theblade 42, a trailingedge 422 on an air outlet side of theblade 42, a radialinner edge 423 on the outer periphery of thehub 41, and a radialouter edge 424 distal to the outer periphery of thehub 41. Theleading edge 421, the trailingedge 422, the radialinner edge 423, and the radial outer edge 24 are rectilinear or curved with an appropriate radius of curvature according to product needs. For eachblade 42, theleading edge 421 intersects the radialinner edge 423 at afront base point 11, theleading edge 421 intersects the radialouter edge 424 at afront end point 12, the trailingedge 424 intersects the radialinner edge 423 at a rear base point O1, and the trailingedge 424 intersects the radialouter edge 424 at a rear end point O2, best shown inFIG. 5 . - Still referring to
FIGS. 4 and 5 , in a longitudinal direction parallel to the extending direction of theshaft 40, the trailingedge 422 of eachblade 42 projects on anadjacent blade 42 along a rear projection line L1 that intersects theleading edge 421 of theadjacent blade 42 at a first overlapped point P1 and that intersects the radialinner edge 423 of theadjacent blade 42 at a second overlapped point P2. A first longitudinal overlapped area A1 is defined by the rear projection line L1, theleading edge 421 of theadjacent blade 42, and the radialinner edge 423 of theadjacent blade 42. - The distance between the front base point I1 and the first overlapped point P1 is preferably ⅕-⅘ (most preferably ½) of a length of the
leading edge 421. Further, the distance between thefront base point 11 and the second overlapped point P2 is preferably ⅙-⅚ (most preferably ½) of a length of the radialinner edge 423. - Still referring to
FIGS. 4 and 5 , in the longitudinal direction parallel to the extending direction of theshaft 40, theleading edge 421 of eachblade 42 projects on the otheradjacent blade 42 along a front projection line L2 that intersects the trailingedge 422 of the otheradjacent blade 42 at a third overlapped point P3 and that intersects the radialinner edge 423 of the otheradjacent blade 42 at a fourth overlapped point P4. A second longitudinal overlapped area A2 is defined by the front projection line L2, the trailingedge 422 of the otheradjacent blade 42, and the radialinner edge 423 of the otheradjacent blade 42. - The distance between the rear base point O1 and the third overlapped point P3 is preferably ⅕-⅘ (most preferably ½) of a length of the trailing
edge 422. Further, the distance between the rear base point O1 and the fourth overlapped point P4 is preferably ⅙-⅚ (most preferably ½) of a length of the radialinner edge 423. - Referring to
FIG. 6 , when viewed from the longitudinal direction parallel to the extending direction of theshaft 40, theleading edge 421 of eachblade 42 is at an angle θ1 with the trailingedge 422 of anadjacent blade 42. - The angle θ1 is preferably between 10 degrees and 90 degrees, and most preferably 45 degrees. Further, the rear projection line L1 on each
blade 42 is at the same angle θ1 with the front projection line L2 on anadjacent blade 42. Further, the first overlapped area A1 and the second overlapped area A2 are spaced from the radialouter edge 422 of eachblade 42. - Referring to
FIG. 7 , a line L passing through thefront end point 12 of theleading edge 421 on eachblade 42 and the rear end point O2 of the trailingedge 422 of theblade 42 is at an angle θ2 with a plane P orthogonal to the extending direction of theshaft 40. The angle θ2 is preferably between 10 degrees and 70 degrees, and most preferably 30 degrees. - Referring to
FIG. 4 , thecasing 5 includes anairflow passage 50, anair inlet 51, anair outlet 52, abase 53, and a plurality ofribs 54. Thebase 53 is located in theair outlet 52 side and supported by theribs 54 that are connected to an inner periphery delimiting theairflow passage 50. Themotor 6 is mounted on thebase 54 for coupling with and driving theimpeller 4. Theribs 54 may extend in an appropriate inclination angle in the air-driving direction to provide a guiding function as well as a pressure-boosting effect. - Referring to
FIGS. 5 and 8 , theimpeller 4 is mounted on thecasing 5 to form an axial-flow heat-dissipating fan. In operation, theimpeller 4 drives air into theairflow passage 50 via theair inlet 51. The airflow is boosted by theribs 54 and then exits thecasing 5 via theair outlet 52. For eachblade 42 and twoblades 42 adjacent to theblade 42, eachblade 42 has a first overlapped area A1 with one of the twoadjacent blades 42 and a second overlapped area A2 with the otheradjacent blade 42. None of the first overlapped area A1 and the second overlapped area A2 extend to the radialouter edge 422 of theblade 42. By such an arrangement, the number of theblades 42 and the total air-driving area of theblades 42 of theimpeller 4 in accordance with the present invention are increased as compared to theconventional impeller 1 inFIG. 1 . Further, overlapping of theblades 42 in the area adjacent to the radialouter edge 424 is avoided in theimpeller 4 in accordance with the present invention as compared to theconventional impeller 3 inFIGS. 2 and 3 . The blowing noise is lowered and the air amount driven by theimpeller 4 is increased. - While the principles of this invention have been disclosed in connection with a specific embodiment, it should be understood by those skilled in the art that these descriptions are not intended to limit the scope of the invention, and that any modification and variation without departing the spirit of the invention is intended to be covered by the scope of this invention defined only by the appended claims.
Claims (13)
1. An impeller for an axial-flow heat-dissipating fan, comprising:
a hub including an outer periphery; and
a plurality of blades symmetrically formed on the outer periphery of the hub and extending in an inclined angle with respect to a longitudinal direction parallel to a rotational axis of the hub;
each said blade including a leading edge, a trailing edge, a radial inner edge, and a radial outer edge;
two of the blades adjacent to each other overlapping with each other in the longitudinal direction such that each said blade having a first overlapped area and a second overlapped area;
the first overlapped area on each said blade extending outward from the leading edge and the radial inner edge but spaced from the radial outer edge of the blade, the second overlapped area on each said blade extending outward from the trailing edge and the radial inner edge but spaced from the radial outer edge of the blade, thereby increasing an air inlet amount and lowering blowing noise.
2. The impeller for an axial-flow heat-dissipating fan as claimed in claim 1 wherein the trailing edge of each said blade projects on an adjacent blade along a rear projection line, and wherein the first longitudinal overlapped area is defined by the rear projection line, the leading edge of the adjacent blade, and the radial inner edge of the adjacent blade.
3. The impeller for an axial-flow heat-dissipating fan as claimed in claim 2 wherein:
the leading edge of each said blade intersects the radial inner edge of the blade at a front base point;
the rear projection line intersects the leading edge of the adjacent blade at an overlapped point; and
a distance between the front base point and the overlapped point is ⅕-⅘ of a length of the leading edge.
4. The impeller for an axial-flow heat-dissipating fan as claimed in claim 2 wherein:
the leading edge of each said blade intersects the radial inner edge of the blade at a front base point;
the rear projection line intersects the radial inner edge of the adjacent blade at an overlapped point; and
a distance between the front base point and the overlapped point is ⅙-⅚ of a length of the radial inner edge.
5. The impeller for an axial-flow heat-dissipating fan as claimed in claim 1 wherein the trailing edge of each said blade projects on an adjacent blade along a front projection line, and wherein the second longitudinal overlapped area is defined by the front projection line, the trailing edge of the adjacent blade, and the radial inner edge of the adjacent blade.
6. The impeller for an axial-flow heat-dissipating fan as claimed in claim 5 wherein:
the trailing edge of each said blade intersects the radial inner edge of the blade at a rear base point;
the front projection line intersects the trailing edge of the adjacent blade at an overlapped point; and
a distance between the rear base point and the overlapped point is ⅕-⅘ of a length of the trailing edge.
7. The impeller for an axial-flow heat-dissipating fan as claimed in claim 5 wherein:
the trailing edge of each said blade intersects the radial inner edge of the blade at a rear base point;
the front projection line intersects the radial inner edge of the adjacent blade at an overlapped point; and
a distance between the rear base point and the overlapped point is ⅙-⅚ of a length of the radial inner edge.
8. The impeller for an axial-flow heat-dissipating fan as claimed in claim 1 wherein:
the leading edge of each said blade is at an angle between 10 degrees and 90 degrees with the trailing edge of an adjacent blade when viewed from the longitudinal direction parallel to the rotational axis of the hub.
9. The impeller for an axial-flow heat-dissipating fan as claimed in claim 1 wherein:
the leading edge of each said blade intersects the radial outer edge of the blade at a front end point;
the trailing edge of each said blade intersects the radial outer edge of the blade at a rear end point;
a line passing through the front end point of the leading edge and the rear end point of the trailing edge of each said blade is at an angle between 10 degrees and 70 degrees with a plane orthogonal to the rotational axis of the hub.
10. The impeller for an axial-flow heat-dissipating fan as claimed in claim 3 wherein:
the rear projection line intersects the radial inner edge of the adjacent blade at a second overlapped point; and
a distance between the front base point and the second overlapped point is ⅙-⅚ of a length of the radial inner edge.
11. The impeller for an axial-flow heat-dissipating fan as claimed in claim 10 wherein the trailing edge of each said blade projects on an adjacent blade along a front projection line, and wherein the second longitudinal overlapped area is defined by the front projection line, the trailing edge of the adjacent blade, and the radial inner edge of the adjacent blade.
12. The impeller for an axial-flow heat-dissipating fan as claimed in claim 11 wherein:
the trailing edge of each said blade intersects the radial inner edge of the blade at a rear base point;
the front projection line intersects the trailing edge of the adjacent blade at a third overlapped point; and
a distance between the rear base point and the third overlapped point is ⅕-⅘ of a length of the trailing edge.
13. The impeller for an axial-flow heat-dissipating fan as claimed in claim 12 wherein:
the front projection line intersects the trailing edge of the adjacent blade at a fourth overlapped point; and
a distance between the rear base point and the fourth overlapped point is ⅙-⅚ of a length of the trailing edge.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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TW093136119A TW200617286A (en) | 2004-11-24 | 2004-11-24 | Impeller structure for axial-flow heat-dissipating fan |
TW93136119 | 2004-11-24 |
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US20060110252A1 true US20060110252A1 (en) | 2006-05-25 |
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US11/030,176 Abandoned US20060110252A1 (en) | 2004-11-24 | 2005-01-07 | Impeller for axial-flow heat-dissipating fan |
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US (1) | US20060110252A1 (en) |
JP (1) | JP2006144764A (en) |
DE (1) | DE102005003357A1 (en) |
TW (1) | TW200617286A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070258812A1 (en) * | 2006-05-02 | 2007-11-08 | Delta Electronics, Inc. | Fan and impeller thereof |
CN103291656A (en) * | 2013-06-08 | 2013-09-11 | 维尔纳(福建)电机有限公司 | Motor axial fan |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6944194B2 (en) * | 2018-06-26 | 2021-10-06 | 株式会社昭和商会 | Blowers for air-conditioned garments and air-conditioned garments |
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US435602A (en) * | 1890-09-02 | Azadore m | ||
US4155602A (en) * | 1976-03-30 | 1979-05-22 | Massey-Ferguson Services N.V. | Trash removal apparatus for sugar cane harvesters |
US4896971A (en) * | 1987-03-26 | 1990-01-30 | General Signal Corporation | Mixing apparatus |
US6318964B1 (en) * | 2000-09-08 | 2001-11-20 | Sheng Shyan Yang | Complex cooling fan with increased cooling capacity |
US6572336B2 (en) * | 2001-09-28 | 2003-06-03 | Sunonwealth Electric Machine Industry Co., Ltd. | Impeller structure |
-
2004
- 2004-11-24 TW TW093136119A patent/TW200617286A/en unknown
- 2004-12-20 JP JP2004367260A patent/JP2006144764A/en active Pending
-
2005
- 2005-01-07 US US11/030,176 patent/US20060110252A1/en not_active Abandoned
- 2005-01-25 DE DE102005003357A patent/DE102005003357A1/en not_active Ceased
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US435602A (en) * | 1890-09-02 | Azadore m | ||
US4155602A (en) * | 1976-03-30 | 1979-05-22 | Massey-Ferguson Services N.V. | Trash removal apparatus for sugar cane harvesters |
US4896971A (en) * | 1987-03-26 | 1990-01-30 | General Signal Corporation | Mixing apparatus |
US6318964B1 (en) * | 2000-09-08 | 2001-11-20 | Sheng Shyan Yang | Complex cooling fan with increased cooling capacity |
US6572336B2 (en) * | 2001-09-28 | 2003-06-03 | Sunonwealth Electric Machine Industry Co., Ltd. | Impeller structure |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070258812A1 (en) * | 2006-05-02 | 2007-11-08 | Delta Electronics, Inc. | Fan and impeller thereof |
US7802969B2 (en) * | 2006-05-02 | 2010-09-28 | Delta Electronics, Inc. | Fan and impeller thereof |
CN103291656A (en) * | 2013-06-08 | 2013-09-11 | 维尔纳(福建)电机有限公司 | Motor axial fan |
Also Published As
Publication number | Publication date |
---|---|
DE102005003357A1 (en) | 2006-06-01 |
TW200617286A (en) | 2006-06-01 |
JP2006144764A (en) | 2006-06-08 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SUNONWEALTH ELECTRIC MACHINE INDUSTRY CO., LTD., T Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HORNG, ALEX;HONG, YIN-RONG;REEL/FRAME:016161/0677 Effective date: 20050103 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |