Patent Application
20120027597
The present application claims the benefits of priority to Korean Patent Application No. 10-2010-0072163 (filed on Jul. 27, 2010), which is herein incorporated by reference in its entirety.
1. The Field
The present invention relates to a centrifugal fan.
2. Description of the Related Art
A centrifugal fan suctions air in an axial direction and discharges the air in a radial direction. The centrifugal fan may be mounted on an evaporation chamber or a machine chamber of an air conditioner and a refrigerator. In particular, in the case of the refrigerator, an area of a cooled air passage is decreased in order to increase a volume in the refrigerator, such that a passage resistance is increased. In order to solve the problem, a centrifugal fan having a high constant pressure property is generally used.
However, a general centrifugal fan in the related art has disadvantages to be described below.
Specifically, while the axial-direction flow is switched to the radial-direction flow, air is discharged from a trailing edge of a fan blade at an angle between the axial direction and the radial direction. Therefore, a larger flow rate is generated from a lower side than an upper side of the trailing edge of the fan blade.
Accordingly, a large pressure difference between the upper side and the lower side of the trailing edge is caused, and as a result, some of the air discharged through the trailing edge flows backward through a bell mouth mounted on the top of the blade. Therefore, the flow is lost and noise increases and an eddy phenomenon occurs at the upper side of the trailing edge, such that fan efficiency deteriorates.
The present invention has been made in an effort to solve the problems.
An exemplary embodiment of the present invention provides a centrifugal fan including: a hub penetrated by a rotational axis; a plurality of main blades extended in a radial direction from a predetermined point of the top of the hub; a bell mouth formed on a top of the exteriors of the plurality of main blades; and a plurality of auxiliary blades extended in the radial direction between the plurality of main blades, wherein a ratio (D1/D2) of an inner diameter D1 to an outer diameter D1 of each of the auxiliary blades is in the range of 07 to 0.9.
The following effects can be achieved by the centrifugal fan according to the exemplary embodiment of the present invention configured as above.
First, a constant pressure and a flow rate of a fan are increased by installing an auxiliary blade between main blades.
Second, since the flow rate increases at the same rpm, rpm can decrease while the same flow rate is maintained, and as a result, noise is reduced.
Third, a velocity distribution of a flow discharged through a trailing edge of the auxiliary blade is substantially uniform, such that a pressure difference between an upper side and a lower side of the trailing edge is minimized, and as a result, a flow property in which the discharged air flows backward is improved.
In the following detailed description of the preferred embodiments, reference is made to the accompanying drawings that form a part hereof, and in which is shown by way of illustration specific preferred embodiments in which the invention may be practiced. These embodiments are described in sufficient detail to enable those skilled in the art to practice the invention, and it is understood that other embodiments may be utilized and that logical structural, mechanical, electrical, and chemical changes may be made without departing from the spirit or scope of the invention. To avoid detail not necessary to enable those skilled in the art to practice the invention, the description may omit certain information known to those skilled in the art. The following detailed description is, therefore, not to be taken in a limiting sense, and the scope of the present invention is defined only by the appended claims.
Hereinafter, a centrifugal fan according to an exemplary embodiment of the present invention will be described in detail with reference to the accompanying drawings.
Referring to
Specifically, the blade includes main blades 12 extended from the edge of the bottom of the hub and auxiliary blades 13 each of which the top is connected to the bottom of the bell mouth 14. The auxiliary blade 13 is provided between the main blade 12 to improve flow loss caused by a difference in velocity and pressure between an upper side and a lower side of a trailing edge of the blade.
The hub 11 has the circular cone shape in which the diameter increases toward the bottom to serve to diffuse air suctioned in a rotational axial direction to a radial direction. In addition, the main blade 12 extends in the radial direction starting from a point spaced apart toward the center from the edge of the bottom of the hub 11 by a predetermined distance. In addition, the main blade 12 is extended with being rounded at a predetermined curvature. Further, the auxiliary blade 13 is shorter than the main blade 12 and does not contact the hub 11. That is, the auxiliary blade 13 is connected to only the bell mouth 14.
Moreover, an outer diameter of the bell mouth 14 is larger than that of the bottom of the hub 11. In addition, the inner edge of the bell mouth 14 is rounded in an extending direction of the rotational axis of the hub 11. In other words, the inner edge of the bell mouth 14 is extended by a predetermined length with being rounded toward the top of the hub 11.
Meanwhile, in the structure of the main blade 12, an end of the main blade at the side of the hub 11 may be defined as a leading edge 121 and an opposite end to the leading edge 121 may be defined as a trailing edge 122. Of course, similarly, both ends of the auxiliary blade 13 may also be defined as a leading edge 131 and a trailing edge 132.
Specifically, when the centrifugal fan 10 is viewed from the top (
Further, the diameter D1 of the circumference passing the leading edges 131 of the auxiliary blades 13 may be equal to or larger than an inner diameter of the bell mouth 14. In addition, the auxiliary blade 13 may be interposed between one or two or more main blades 12. Moreover, hereinafter, the diameter D1 of the circumference passing the leading edges 131 of the auxiliary blade 13 is defined as an inner diameter of the auxiliary blade 13 and the diameter D2 of the circumference passing the trailing edges 132 is defined as an outer diameter of the auxiliary blade 13.
Meanwhile, the inner diameter D1 of the auxiliary blade 13 may be larger than the diameter of the circumference linking the leading edges 121 of the main blade 12, i.e., an inner diameter of the main blade 12.
Further, a ratio (D1/D2) of the inner diameter to the outer diameter of the auxiliary blade 13 is preferably in the range of 0.7 to 0.9 and this is a result extracted through tests performed at several times.
Referring to
In addition, the main blade 12 is extended from a predetermined point of the top of the hub 11. Further, a length from an upper end to a lower end of the trailing edge 122 of the main blade 12 is defined as a width W2 of the trailing edge 122 of the auxiliary blade 12. In another aspect, the width W2 may be the height of the trailing edge 122 from the bottom of the bell mouth 14.
Further, a ratio (W1/W2) of the trailing edge 132 of the auxiliary blade 13 to the width of the trailing edge 122 of the main blade 12 is preferably in the range of 0.45 to 0.65 and this is also a result extracted through tests performed at several times.
Referring to
Referring to
This means that the magnitude of noise generated in the centrifugal fan 10 is smaller than that of the general centrifugal fan at the same rpm or frequency. Accordingly, fan noise can be reduced by using the centrifugal fan 10 according to the exemplary embodiment of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2010-0072163 | Jul 2010 | KR | national |
