EP3085966B1

EP3085966B1 - Axial flow fan

Info

Publication number: EP3085966B1
Application number: EP13899760.6A
Authority: EP
Inventors: Yasuaki Kato; Takahide Tadokoro; Atsushi Kono
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2013-12-20
Filing date: 2013-12-20
Publication date: 2020-05-20
Anticipated expiration: 2033-12-20
Also published as: JPWO2015092924A1; WO2015092924A1; EP3085966A4; EP3085966A1

Description

Technical Field

The present invention relates to an axial flow blower.

Background Art

As an axial flow blower achieving reduction in noise through improvement of a blade structure, an axial flow blower disclosed in Patent Literature 1 is exemplified. In the axial flow blower, a radial center portion of a trailing edge of each blade is formed into a protruding shape curved so as to swell to a suction side, thereby equalizing a blowing-out velocity of the air in a radial direction of the blade.

Citation List

Patent Literature

[PTL 1] JP 4501575 B2 (mainly FIG. 3 and FIG. 8) JP2006037800A provides a blower capable of reducing noise and improving efficiency by improving a blade structure. JP2002257088A provides an axial flow fan capable of reducing blade area without complicating a shape of a blade trailing edge part, improving a forming property and reducing cost, and saving energy by maintaining a load on a driving motor low when rotation speed is increased to increase the quantity of air flow. JP2011179330A discloses an impeller includes a hub provided in a rotation center and a plurality of blades provided around the hub. The radial cross-sectional shape of each blade is formed into a recessed curve on the peripheral side with respect to a suction side, and formed into a projecting curve on a hub side with respect to the suction side. The projecting curve on the hub side is formed into a substantially arcuate shape, and the value of the curvature radius of the projecting curve formed into the substantially arcuate shape is reduced from the leading edge side of each blade toward the trailing edge side thereof.

Summary of Invention

Technical Problem

However, in the above-mentioned related-art axial flow blower, when the air is abruptly moved in the radial direction, turbulence of an air stream is generated, which may lead to increase in noise.
The present invention has been made in view of the above, and has an obj ect to provide an axial flow blower capable of preventing increase in noise.

Solution to Problem

In order to achieve the above-mentioned object, an axial flow blower is provided according to the independent claim. Further advantages can be achieved by the features disclosed in the dependent claims. According to one embodiment of the present invention, there is provided an axial flow blower, including: a propeller fan; and a driving unit configured to rotate the propeller fan, the propeller fan including: the hub; and a plurality of blades supported by the hub, in which a pressure surface of each of the blades includes a protruding portion curved so as to swell to a suction side, in which a height of the protruding portion of the each of the blades on a trailing edge side is larger than a height of the protruding portion on a leading edge side, and in which a radial position of an apex of the protruding portion on the trailing edge side is located on a radially inner side with respect to a radial position of the apex of the protruding portion on the leading edge side.
Further, an outer peripheral edge of the each of the blades may be curved so as to bend to the suction side.
Further, a position of an inner end of the protruding portion on the trailing edge side is located on the radially inner side with respect to a position of the inner end of the protruding portion on the leading edge side.
Still further, a width dimension of the protruding portion on the trailing edge side may be larger than a width dimension of the protruding portion on the leading edge side.

Advantageous Effects of Invention

According to the one embodiment of the present invention, the increase in noise can be prevented.

Brief Description of Drawings

FIG. 1 is a sectional view of an axial flow blower according to a first embodiment of the present invention.
FIG. 2 is a perspective view of a propeller fan of the axial flow blower according to the first embodiment.
FIG. 3 is a plan view for illustrating one of blades according to the first embodiment as a representative example.
FIG. 4 is a view for illustrating the propeller fan according to the first embodiment when circumferential changes of a pressure surface are projected on a radial plane including a rotation axis.
FIG. 5 is a view for particularly illustrating only the pressure surface in one radial cross-section in the same manner as that of FIG. 4.

Description of Embodiment

Now, an axial flow blower according to an embodiment of the present invention is described with reference to the accompanying drawings. Note that, in the drawings, the same reference symbols represent the same or corresponding parts.

First Embodiment

FIG. 1 is a sectional view of an axial flow blower according to a first embodiment of the present invention, and FIG. 2 is a perspective view of a propeller fan of the axial flow blower according to the first embodiment. An axial flow blower 100 includes a propeller fan 1, a motor 4 being a driving unit, and a bellmouth 5.
The propeller fan 1 includes a hub 2 and a plurality of blades 3. The plurality of blades 3 are supported by the hub 2, and are arranged in a radiate manner on an outer peripheral surface of the hub 2 having substantially a columnar shape (including a truncated conical shape). Note that, in the illustrated example, the propeller fan including three blades is illustrated.
A center portion of the hub 2 is connected to the motor 4, and the propeller fan 1 is rotated by a driving force of the motor 4. The bellmouth 5 is arranged on a radially outer side of the propeller fan 1. That is, under a state in which a proper gap is defined between an outer peripheral portion of the propeller fan 1 and an inner peripheral portion of the bellmouth 5, the propeller fan 1 is surrounded by the bellmouth 5. Note that, an upper space on the drawing sheet of FIG. 1 corresponds to a suction side 6, and a lower space on the drawing sheet of FIG. 1 corresponds to a blowing-out side 7.
Each of the blades 3 is a forward blade having a leading edge extending to a forward side in a rotating direction RD. Among edges 8 of each of the blades 3, an edge facing the forward side in the rotating direction RD is referred to as a leading edge 8a, and an edge facing a backward side in the rotating direction RD is referred to as a trailing edge 8c. A portion connecting a radially outer portion of the leading edge 8a and a radially outer portion of the trailing edge 8c to each other is referred to as an outer peripheral edge 8b. Further, a portion connecting each of the blades 3 and the hub 2 to each other is referred to as a connection edge 8d.
One surface of each blade 3 surrounded by the leading edge 8a, the outer peripheral edge 8b, the trailing edge 8c, and the connection edge 8d as described above is referred to as a suction surface 9a, and the other surface thereof is referred to as a pressure surface 9b. The suction surface 9a is a surface on the suction side 6, and the pressure surface 9b is a surface on the blowing-out side 7. Further, a rotation center line of the propeller fan 1 is referred to as a rotation axis 10 . The rotating direction RD of the propeller fan is schematically indicated by the outline arrows of the drawings, and flows of the air are schematically indicated by the dashed arrows .
FIG. 3 is a plan view for illustrating one of the blades as an representative example, and FIG. 4 is a view for illustrating the propeller fan according to the first embodiment when circumferential changes of the pressure surface are projected on a radial plane including the rotation axis. In addition, FIG. 5 is a view for particularly illustrating only the pressure surface in one radial cross-section in the same manner as that of FIG. 4. The dot-and-dash lines A1 to A6 of FIG. 3 correspond to lines along which radial cross-sections of the hub and the blade are taken. The dot-and-dash lines A1 to A6 include the rotation axis, and extend continuously from the connection edge to the outer peripheral edge. Further, the lines B1 to B6 of FIG. 4 respectively correspond to the cross-sections of the pressure surface taken along the dot-and-dash lines A1 to A6. In addition, FIG. 5 is an illustration of only the pressure surface taken along the line B3 of FIG. 4.
A shape of the pressure surface of each of the blades 3 is described while one pressure surface illustrated in FIG. 5 is taken as an example . The pressure surface 9b includes a protruding portion 11 curved so as to swell to the suction side 6. Assuming that a straight line BL (chain double-dashed line of FIG. 5) is brought into abutment on the pressure surface 9b from the blowing-out side 7, a portion swelling from the straight line BL to the suction side 6 corresponds to the protruding portion 11.
An end portion of the protruding portion 11 on the outer peripheral edge side of each blade 3 is referred to as an outer end 11a of the protruding portion, and an end portion of the protruding portion 11 on the connection edge side thereof is referred to as an inner end 11b. A most distant point of the protruding portion 11 from the straight line BL (chain double-dashed line) is referred to as an apex 11c of the protruding portion. A distance between the apex 11c of the protruding portion 11 and the straight line BL (chain double-dashed line) is referred to as a height H of the protruding portion 11. A radial distance (denoted by W in FIG. 5) between the outer end 11a and the inner end 11b of the protruding portion 11 is referred to as a width dimension W of the protruding portion 11. Note that, in FIG. 3 and FIG. 4, a line connecting points of the outer end 11a of the protruding portion 11, a line connecting points of the inner end 11b thereof, and a line connecting points of the apex 11c thereof are indicated by the curved lines La, Lb, and Lc, respectively.
In radial cross-sections of each of the blades 3 according to the first embodiment, within an angle range where the radial cross-sections extend continuously from the connection edge 8d to the outer peripheral edge 8b (angle range defined between the dot-and-dash lines A1 and A6 of FIG. 3), the pressure surface 9b includes the protruding portion 11 curved so as to swell to the suction side 6. The outer end 11a of the protruding portion 11 is positioned on a radially inner side with respect to the outer peripheral edge 8b of each of the blades 3. Further, the height H of the protruding portion 11 on the trailing edge side is larger than the height H of the protruding portion 11 on the leading edge side. As an example, within the angle range defined between the dot-and-dash lines A1 and A6, the height H of the protruding portion 11 becomes larger as approaching to the trailing edge. Further, a radius position (radial position) of the apex 11c of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to a radius position (radial position) of the apex 11c of the protruding portion 11 on the leading edge side. As an example, within the angle range defined between the dot-and-dash lines A1 and A6, the radial position of the protruding portion 11 is shifted radially inward as approaching to the trailing edge.
Further, aposition of the inner end 11b of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to a position of the inner end 11b of the protruding portion 11 on the leading edge side. As an example, within the angle range defined between the dot-and-dash lines A1 and A6, the position of the inner end 11b of the protruding portion 11 is shifted radially inward as approaching to the trailing edge. In other words, within the angle range defined between the dot-and-dash lines A1 and A6, a point on the curved line Lb, which is obtained by connecting the points of the inner end 11b of the protruding portion 11, is shifted radially inward as approaching to the trailing edge.
Further, the width dimension W of the protruding portion 11 on the trailing edge side is larger than the width dimension W of the protruding portion 11 on the leading edge side. As an example, within the angle range defined between the dot-and-dash lines A1 and A6, the width dimension W of the protruding portion 11 becomes larger as approaching to the trailing edge.
In addition, the outer peripheral edge 8b of each of the blades 3 is curved so as to bend to the suction side 6.
Next, operation of the axial flow blower having the above-mentioned configuration is described. The hub 2 connected to the motor 4, and also the blades 3 are rotated by the driving force of the motor 4 as indicated by the reference symbol RD.
Owing to this rotation, the pressure surface 9b of each blade 3 pushes the air in the rotational region of the blade 3 to the blowing-out side 7, with the result that pressure is reduced on the suction surface 9a side of the blade 3 by movement of the suction surface 9a. Thus, the air is caused to flow from the suction side 6 into the rotational region of the blade 3. Owing to this action of the blade 3, as indicated by the dashed arrows, the air is caused to flow from the suction side 6 to the blowing-out side 7.
In a general radial distribution of an axial flow velocity at a vicinity of the trailing edge on the blowing-out side of the axial flowblower, the flow velocity increases from the radially inner side toward the radially outer side, and becomes maximum in a region positioned slightly radially outward of a radial center. The flow velocity decreases from the region toward the outer peripheral edge being a position of a maximum radius. Further, on the hub side of each blade, a flow is directed radially outward due to a centrifugal force, thereby reducing a flow rate on the hub side. Accordingly, insufficient flow rate causes the flow to be separated from a blade surface. Due to turbulence generated by the separation, noise may be increased, and efficiency may be reduced due to the separation. Further, on an outer peripheral side with respect to the radial center of the blade, the flow rate is concentrated, thereby increasing the flow velocity. Aerodynamic noise of the propeller fan increases mainly in proportion to the sixth power of the flow velocity. Accordingly, there is a problem in that noise is increased along with increase in flow velocity. As described above, on the blowing-out side, the distribution of the flow velocity appears in the radial direction of the blade. Further, the air flows slower on the hub side, whereas the air flows faster on the outer peripheral edge side. As a result, there arise a problem of increase in noise and a problem of reduction in efficiency, which are caused by the distribution of the flow velocity.
In contrast, in the first embodiment, the pressure surface 9b of each of the blades 3 includes the protruding portion 11, thereby suppressing appearance of the distribution of the flow rate in the radial direction, which causes the above-mentioned problems. The pressure surface 9b acts so as to push out the air in a direction of the blowing-out side 7. The protruding portion 11 functions as an escape route for the pushed air, and the flow directed toward the protruding portion 11 is generated on the pressure surface 9b. The radial position of the apex 11c of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to the radial position of the apex 11c of the protruding portion 11 on the leading edge side. Accordingly, it is possible to obtain such an effect that the air on the radially outer side of the pressure surface 9b is moved to the radially inner side. Thus, it is possible to reduce movement of the air to the radially outer side caused by the centrifugal force. Further, the height H of the protruding portion 11 on the trailing edge side is larger than the height H of the protruding portion 11 on the leading edge side. Accordingly, the effect of moving the air to the radially inner side can be further enhanced, and imbalanced concentration of the flow rate on the radially outer side can be further suppressed. Thus, the distribution of the flow rate in the radial direction can be almost equalized.
Further, in the radial cross-sections, the protruding portion 11 is formed over the entire angle range where the radial cross-sections extend continuously from the connection edge 8d to the outer peripheral edge 8b (entire angle range where the pressure surface extends continuously in the radial direction from the connection edge 8d to the outer peripheral edge 8b). Accordingly, without abruptly changing the flow of the air, the distribution of the flow rate in the radial direction can be controlled. Thus, turbulence of the air can be suppressed, and increase in noise and reduction in efficiency caused by the turbulence of the air can be prevented.
Further, in the propeller fan, at a vicinity of the outer peripheral edge, a swirling flow is generated from the pressure surface to the suction surface through the outer side of the outer peripheral edge due to a pressure difference between the pressure surface and the suction surface. Regarding this, in the first embodiment, it seems that the radially outer side of the protruding portion is inclined so as to push the air to the inner peripheral side, thereby increasing the pressure and intensifying the swirling flow from the pressure surface to the suction surface. However, the outer end of the protruding portion is arranged on the inner peripheral side with respect to the outer peripheral edge, thereby preventing intensification of the swirling flow generated on the outer side of the outer peripheral edge.
Further, in the first embodiment, the outer peripheral edge of each of the blades is curved so as to bend to the suction side. That is, the outer peripheral edge 8b is positioned on the suction side 6 with respect to the straight line BL (chain double-dashed line) of FIG. 5. Accordingly, even in the above-mentioned case where the swirling flow from the pressure surface to the suction surface may be generated, because the outer peripheral edge is curved to bend to the suction side, a pressure change is started before the air is caused to flow out from the pressure surface to the outer side of the outer peripheral edge. Consequently, the abrupt pressure change can be prevented from occurring afterward, and turbulence caused by the swirling can be reduced. Further, even if the swirling flow is generated, a position of the swirling flow can be shifted from the suction surface to the suction side. Thus, an influence of the swirling flow can be lessened.
Further, in the first embodiment, the position of the inner end 11b of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to the position of the inner end 11b of the protruding portion 11 on the leading edge side. Accordingly, as compared to a mode of merely forming the protruding portion, it is possible to intensify an effect of increasing the radially-inner-side flow rate of the air passing through the propeller fan.
Still further, in the first embodiment, the width dimension W of the protruding portion 11 on the trailing edge side is larger than the width dimension W of the protruding portion 11 on the leading edge side. Accordingly, with a view to equalizing the radial distribution of the flow velocity on the blowing-out side by forming the protruding portion, it is possible to enlarge a controllable range of the radial distribution of the flow velocity on the blowing-out side.
As described above, in the axial flow blower according to the first embodiment, the distribution of the axial flow velocity on the blowing-out side can be almost equalized. Accordingly, increase in noise and reduction in efficiency, which are caused by the extensive distribution of the flow velocity, can be prevented, thereby being capable of obtaining the propeller fan capable of achieving reduction in noise and high efficiency. In addition, it is possible to suppress turbulence of the flow, which may be generated in order to almost equalize the flow velocity. Thus, effects of reducing noise and increasing efficiency can be enhanced.
Although the details of the present invention are specifically described above with reference to the preferred embodiment, it is apparent that persons skilled in the art may adopt various modifications based on the basic technical concepts and teachings of the present invention.
As an application example of the present invention, an outdoor unit of an air-conditioning apparatus is given. When the axial flow blower according to the present invention is applied to a blower of the outdoor unit of the air-conditioning apparatus, it is possible to reduce aerodynamic noise caused when generating a desired quantity of air, and to reduce necessary power. In other words, it is possible to obtain the air-conditioning apparatus capable of reducing noise and excellent in energy saving performance .

Reference Signs List

1 propeller fan, 2 hub, 3 blade, 4 motor, 5 bellmouth, 6 suction side, 7 blowing-out side, 8a leading edge, 8b outer peripheral edge, 8c trailing edge, 8d connection edge, 9a suction surface, 9b pressure surface, 10 rotation axis, 11 protruding portion, 11a outer end of protruding portion, 11b inner end of protruding portion, 11c apex of protruding portion, 100 axial flow blower

Claims

An axial flow blower (100), comprising:
a propeller fan (1); and

a driving unit configured to rotate the propeller fan (1),

the propeller fan (1) comprising:
a hub (2) ; and

a plurality of blades (3) supported by the hub (2),

wherein a pressure surface (9b) of each of the blades (3) comprises a protruding portion (11) curved so as to swell to a suction side,

wherein a height (H) of the protruding portion of the each of the blades (3) on a trailing edge side is larger than a height of the protruding portion on a leading edge side, and

the axial flow blower being characterized in that:
a radial position of an apex (11c) of the protruding portion on the trailing edge side is located on a radially inner side with respect to a radial position of the apex of the protruding portion on the leading edge side, and

a position of an inner end (11b) of the protruding portion on the,trailing edge side is located on the radially inner side with respect to a position of the inner end of the protruding portion on the leading edge side.
An axial flow blower according to claim 1, wherein an outer peripheral edge (8b) of each of the blades (3) is curved so as to bend to the suction side.
An axial flow blower according to claim 1 or 2, wherein a width dimension (W) of the protruding portion on the trailing edge side is larger than a width dimension of the protruding portion on the leading edge side.
An outdoor unit of an air-conditioning apparatus, which uses the axial flow blower (100) of any one of claims 1 to 3.