U.S. patent application number 11/332213 was filed with the patent office on 2006-08-17 for blowing device.
This patent application is currently assigned to LG Electronics Inc.. Invention is credited to Jun Ho Bae, Chang Joon Kim, Wook Kim.
Application Number | 20060182628 11/332213 |
Document ID | / |
Family ID | 36216960 |
Filed Date | 2006-08-17 |
United States Patent
Application |
20060182628 |
Kind Code |
A1 |
Kim; Wook ; et al. |
August 17, 2006 |
Blowing device
Abstract
Disclosed herein is a blowing device for small-sized electronic
appliances such as cleaning apparatuses. The blowing device
comprises a housing, a centrifugal impeller, a guide vane, and a
motor for rotating the centrifugal impeller. The centrifugal
impeller comprises a shroud, a hub, and a plurality of impeller
blades which have an average diameter 87.about.93% of a diameter of
the housing. The shroud and the hub of the centrifugal impeller,
and the guide vane are optimally designed with respect to a size of
the housing or an average diameter of the impeller blades,
maximizing fan efficiency and heat dissipation of the motor.
Inventors: |
Kim; Wook; (Seoul, KR)
; Bae; Jun Ho; (Seoul, KR) ; Kim; Chang Joon;
(Seoul, KR) |
Correspondence
Address: |
GREENBLUM & BERNSTEIN, P.L.C.
1950 ROLAND CLARKE PLACE
RESTON
VA
20191
US
|
Assignee: |
LG Electronics Inc.
Seoul
KR
|
Family ID: |
36216960 |
Appl. No.: |
11/332213 |
Filed: |
January 17, 2006 |
Current U.S.
Class: |
415/206 |
Current CPC
Class: |
F04D 17/165 20130101;
F04D 29/30 20130101; F04D 29/281 20130101; F04D 29/4253
20130101 |
Class at
Publication: |
415/206 |
International
Class: |
F04D 29/44 20060101
F04D029/44 |
Foreign Application Data
Date |
Code |
Application Number |
Jan 25, 2005 |
KR |
2005-6643 |
Claims
1. 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 a motor, and a plurality of impeller
blades radially disposed between the hub and the shroud, wherein,
when outer diameters of the impeller blades refer to diameters of
circles defined by connecting distal ends of the plurality of
impeller blades, and an average diameter of the impeller blades
refers to an average of the outer diameters of the impeller blades
in the axial direction, the impeller blades have the average
diameter in the range of 87.about.93% of a diameter of the
housing.
2. The blowing device as set forth in claim 1, wherein each
impeller blade has a distal end perpendicular to the axial
direction.
3. The blowing device as set forth in claim 1, wherein each
impeller blade has a distal end slanted such that the outer
diameter of the impeller blade is gradually decreased from the
shroud to the hub.
4. The blowing device as set forth in claim 1, wherein the shroud
has an outer diameter in the range of 103.about.106% of the average
diameter of the impeller blades.
5. The blowing device as set forth in claim 1, wherein the hub has
an outer diameter in the range of 95.about.98% of the average
diameter of the impeller blades.
6. The blowing device as set forth in claim 1, wherein an axial
distance between a distal end of the shroud and a distal end of the
hub is in the range of 25.about.50% of an axial height of the
housing.
7. The blowing device as set forth in claim 1, further comprising:
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, when an outer diameter of the guide vane
blades refers to a diameter of a circle defined by connecting
distal ends of the guide vane blades, the guide vane blades have
the outer diameter in the range of 103.about.108% of the average
diameter of the impeller blades.
8. The blowing device as set forth in claim 7, wherein the guide
vane plate has an outer diameter in the range of 100.about.102% of
the average diameter of the impeller blades.
9. The blowing device as set forth in claim 7, wherein the guide
vane has an axial height in the range of 100.about.110% of the
axial distance between the distal end of the shroud and the distal
end of the hub.
10. The blowing device as set forth in claim 1, further comprising:
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, when an outer diameter of the guide vane
blades refers to a diameter of a circle defined by connecting
distal ends of the guide vane blades, the guide vane plate has an
outer diameter in the range of 100.about.102% of the average
diameter of the impeller blades, the guide vane blades have the
outer diameter in the range of 103.about.108% of the average
diameter of the impeller blades, and the guide vane has an axial
height in the range of 100.about.110% of the axial distance between
the distal end of the shroud and the distal end of the hub.
11. The blowing device as set forth in claim 10, wherein each
impeller blade has a distal end perpendicular to the axial
direction.
12. The blowing device as set forth in claim 10, wherein each
impeller blade has a distal end slanted such that the outer
diameter of the impeller blade is gradually decreased from the
shroud to the hub.
13. 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 a motor, and a plurality of impeller
blades radially disposed between the hub and the shroud, wherein
when outer diameters of the impeller blades refer to diameters of
circles defined by connecting distal ends of the plurality of
impeller blades, and an average diameter of the impeller blades
refers to an average of the outer diameters of the impeller blades
in the axial direction, the impeller blades have the average
diameter in the range of 87.about.93% of a diameter of the housing,
the shroud has an outer diameter in the range of 103.about.106% of
the average diameter of the impeller blades, the hub has an outer
diameter in the range of 95.about.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.about.50% of an axial height of the housing.
14. The blowing device as set forth in claim 13, wherein each
impeller blade has a distal end perpendicular to the axial
direction.
15. The blowing device as set forth in claim 13, wherein each
impeller blade has a distal end slanted such that the outer
diameter of the impeller blade is gradually decreased from the
shroud to the hub.
16. The blowing device as set forth in claim 13, further
comprising: 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.about.102% of the average diameter of
the impeller blades.
17. The blowing device as set forth in claim 13, further
comprising: 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, when an outer diameter of the guide
vane blades refers to an outer diameter of a circle defined by
connecting distal ends of the plurality of guide vane blades, the
guide vane blades have the outer diameter in the range of
103.about.108% of the average diameter of the impeller blades.
18. The blowing device as set forth in claim 13, further
comprising: 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, when an outer diameter of the guide
vane blades refers to a diameter of a circle defined by connecting
distal ends of the guide vane blades, the guide vane plate has an
outer diameter in the range of 100.about.102% of the average
diameter of the impeller blades, the guide vane blades have the
outer diameter in the range of 103.about.108% of the average
diameter of the impeller blades, and the guide vane has an axial
height in the range of 100.about.110% of the axial distance between
the distal end of the shroud and the distal end of the hub.
19. The blowing device as set forth in claim 18, wherein each
impeller blade has a distal end perpendicular to the axial
direction.
20. The blowing device as set forth in claim 18, wherein each
impeller blade has a distal end slanted such that the outer
diameter of the impeller blade is gradually decreased from the
shroud to the hub.
21. 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.
22. The blowing device as set forth in claim 21, wherein the hub
has a diameter smaller than the average diameter of the impeller
blades.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] 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.
[0003] 2. Description of the Related Art
[0004] 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.
[0005] 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.
[0006] 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.
[0007] The centrifugal impeller 10 acts to blow air in a
centrifugal direction. The centrifugal impeller 10 comprises a
shroud 12 having an inlet 12' communicated with the intake port 1
of the housing 4, a hub 14 separated from the shroud 12 in an axial
direction while being coupled to the shaft 21 of the motor 20 to
integrally rotate with the shaft 21, and a plurality of blades 16
radially disposed between the shroud 12 and the hub 14.
[0008] As the floor area ratio of the centrifugal impeller 10 to
the housing 4 is increased, the centrifugal impeller 10 can have an
increased blowing capacity. However, if the floor area ratio of the
centrifugal impeller 10 to the housing 4 is excessive, the
centrifugal impeller 10 can interfere with the housing 4, and in
particular, there occurs an increase in flow resistance of air
blown from the centrifugal impeller 10 to the discharge port 2 of
the housing 4. Accordingly, the centrifugal impeller 10 is designed
to maintain a predetermined distance G from the housing 4.
[0009] Here, the shroud 12, the hub 14, and the blades 16 are
typically designed to have an identical outer diameter 10D. For
reference, 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.
[0010] In the mean time, the housing 4 is provided with a guide
vane 30 to guide the air from the centrifugal impeller 10 to the
discharge port 2 of the housing 4.
[0011] Operation of the conventional blowing device constructed as
described above will be described as follows.
[0012] When the motor 20 is driven, the centrifugal impeller 10 is
rotated by rotational force of the motor 20.
[0013] Then, air outside the housing 4 is sucked into the
centrifugal impeller 10 through the intake port 1 of the housing 4
and the inlet 12' of the shroud 12. The air sucked into the
centrifugal impeller 10 is blown in the centrifugal direction of
the centrifugal impeller 10 by the plurality of blades 16, and is
discharged from the centrifugal impeller 10. The air discharged
from the centrifugal impeller 10 is guided by the guide vane 30,
and is discharged from the housing 4 through the discharge port 2
of the housing 4.
[0014] As such, the centrifugal impeller 10 forcibly blows the air
to generate blowing force.
[0015] Meanwhile, the air discharged from the housing 4 can be
introduced into the motor 20 for heat dissipation of the motor
20.
[0016] 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 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. However, 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.
[0017] 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 the motor 20.
[0018] 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 the intake port 1 of the housing 4, causing severe
flow noise.
SUMMARY OF THE INVENTION
[0019] 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.
[0020] 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.about.93% of a
diameter of the housing.
[0021] 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.
[0022] The shroud may have an outer diameter in the range of
103.about.106% of the average diameter of the impeller blades.
[0023] The hub may have an outer diameter in the range of
95.about.98% of the average diameter of the impeller blades.
[0024] An axial distance between a distal end of the shroud and a
distal end of the hub may be in the range of 25.about.50% of an
axial height of the housing.
[0025] 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.about.108% of the average diameter of the impeller
blades.
[0026] The guide vane plate may have an outer diameter in the range
of 100.about.102% of the average diameter of the impeller
blades.
[0027] The guide vane may have an axial height in the range of
100.about.110% of the axial distance between the distal end of the
shroud and the distal end of the hub.
[0028] 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.about.93% of a diameter of the housing, the shroud has an
outer diameter in the range of 103.about.106% of the average
diameter of the impeller blades, the hub has an outer diameter in
the range of 95.about.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.about.50% of an
axial height of the housing.
[0029] 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.about.102% of the average diameter of the impeller blades, the
guide vane blades have an outer diameter in the range of
103.about.108% of the average diameter of the impeller blades, and
the guide vane has an axial height in the range of 100.about.110%
of the axial distance between the distal end of the shroud and the
distal end of the hub.
[0030] 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.
[0031] 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.
[0032] 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.
[0033] The hub may have a diameter smaller than the average
diameter of the impeller blades.
[0034] 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.
BRIEF DESCRIPTION OF THE DRAWINGS
[0035] 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:
[0036] FIG. 1 is a perspective view illustrating a conventional
blowing device;
[0037] FIG. 2 is a cross-sectional view illustrating a main
component of the conventional blowing device;
[0038] 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;
[0039] 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;
[0040] 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;
[0041] 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;
[0042] 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;
[0043] 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;
[0044] 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;
[0045] 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;
[0046] 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;
[0047] 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;
[0048] FIG. 13 is a graph depicting pressure coefficients of
inventive and conventional blowing devices;
[0049] FIG. 14 is a graph depicting the fan efficiency of the
inventive and conventional blowing devices; and
[0050] FIG. 15 is a cross-sectional view illustrating a blowing
device in accordance with a second embodiment of the present
invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0051] 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.
[0052] 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.
[0053] FIG. 3 is a cross-sectional view illustrating a main
component of a blowing device according to a first embodiment of
the invention.
[0054] The blowing device according to the first embodiment of the
invention 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.
[0055] 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. Here, the rear side of
the housing 50 can be entirely open.
[0056] The housing 50 may be designed to have an axial height 50H
in the range of 20.about.100% of a diameter 50D of the housing 50.
Here, 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.
[0057] 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.
[0058] 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.
[0059] The impeller blades 66 must be designed to maximize blowing
capacity of the centrifugal impeller 60 while minimizing flow loss
due to a narrow space between the housing 50 and the centrifugal
impeller 60 under a predetermined condition of dimensions of the
housing 50. With regard to this, FIG. 4 shows a graph depicting fan
efficiency according to variation in ratio of an average diameter
of the impeller blades 66 to the diameter 50D of the housing 50. As
can be appreciated from FIG. 4, it is desirable that the impeller
blades 66 have an average diameter in the range of 87.about.93% of
the diameter 50D of the housing 50 in order to ensure an
appropriate fan efficiency.
[0060] Here, outer diameters of the impeller blades 66 refer to
diameters of circles defined by connecting distal ends of the
plurality of impeller blades 66, and 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. Here, 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.
[0061] In addition, it is desirable that 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.
[0062] Next, it is desirable that 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.
[0063] With regard to this, 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. As can be
appreciated from FIG. 5, it is desirable that 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. Additionally, 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. As can be appreciated from FIG. 6, it is
desirable that 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.
[0064] Additionally, in order to ensure that 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. However, as
described with reference to FIG. 4, the impeller blades 66 have the
average diameter in the range of 87.about.93% of the diameter 50D
of the housing 50. Accordingly, it is desirable that the shroud 62
have the outer diameter 62D in the range of 90.about.95% of the
diameter 50D of the housing 50 while being in the range of
103.about.106% of the average diameter 66D of the impeller blades
66.
[0065] Next, it is desirable that the hub 64 be smaller than the
impeller blades 66 in order to allow the air blown by the
centrifugal impeller 60 to smoothly flow to the guide vane 70. With
regard to this, 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. As can be
appreciated from FIG. 7, it is desirable that the hub 64 have an
outer diameter 64D in the range of 95.about.98% of the average
diameter of the impeller blades 66.
[0066] With the structure as described above, the centrifugal
impeller 60 has an impeller height 60H in the range of 25.about.50%
of an axial height 50H of the housing 50. Here, 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.
[0067] 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.
[0068] 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.
[0069] 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. Additionally,
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.about.108% of the average diameter of the impeller blades
66.
[0070] Here, 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.
[0071] 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. Additionally, 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.about.102% of the average diameter
of the impeller blades 66.
[0072] As shown in FIG. 12, 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.about.110% of the impeller height 60H of the centrifugal
impeller 60.
[0073] Operation of the blowing device constructed as described
above will be described as follows.
[0074] When the motor is driven, 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.
[0075] 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 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.
[0076] 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.
[0077] 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.
[0078] 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.
[0079] FIG. 15 is a cross-sectional view illustrating a blowing
device according to a second embodiment of the invention.
[0080] As shown in FIG. 15, in the blowing device according to the
second embodiment, 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.
[0081] In particular, the impeller blades 66 are designed to have
an average diameter in the range of 87.about.93% of a diameter 50D
of the housing 50, and to have distal ends perpendicular to the
axial direction of the centrifugal impeller 60.
[0082] Here, since 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.
[0083] 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.
[0084] 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.
* * * * *