JP2011174403A - Blower fan - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a blower fan suppressing the degradation of impeller characteristics due to the interference of an air flow generated by the rotation of blades with the connection part, exerting cooling effects in the peripheral direction while maintaining cooling effects in the axial direction. <P>SOLUTION: The blower fan 2 includes an approximately cylindrical cup part 10, the plurality of blades 11 to be rotated together with the cup part 10, a motor for rotating the plurality of blades 11, and a housing 30 storing the plurality of blades 11 and others. The plurality of blades 11 are connected to one another via the approximately annular connection part 12, and partitioned into radially inside portions 11A and radially outside portions 11B with the connection part 12. The connection part 12 is formed 70-90% of the blade length along the radial direction of each blade 11, distant from the root of the blade 11 on the outer peripheral face of the cup part 10. On the side of the housing 30, an opening portion 30a is formed in communication with the inside of the housing 30. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a blower fan provided with an impeller that generates an air flow along a central axis.

  An impeller used in a conventional so-called axial fan (air blower fan) is configured such that a plurality of blades fixed to the outer peripheral surface of a cylindrical impeller cup rotate around the central axis, thereby causing air along the direction of the central axis. Generate a flow.

  Here, when the impeller rotates, a radial centrifugal force acts on the blade. The effect of this centrifugal force becomes more pronounced as the impeller rotates at a higher speed. In the case of a wing with a high degree of advancement, the radial outer end of the wing is positioned forward in the rotational direction of the wing root, so a large moment is generated at the wing root due to the centrifugal force generated at each part of the wing. To do. Therefore, the impeller is required to have a strength design that considers the influence of such centrifugal force.

  In order to reduce the influence of this centrifugal force, a technique for increasing the strength of a blade against centrifugal force by connecting a plurality of blades to each other with an annular connecting portion is disclosed in US Patent Application Publication No. 2008/0056899, US It is described in Japanese Patent No. 6554574, US Pat. No. 6,241,474, and the like.

  On the other hand, when the blower fan is used to cool the heating element in the electronic device, in addition to improving the air flow characteristic in order to enhance the cooling effect of the blower fan, it is possible to reduce the noise accompanying the operation of the blower fan. Required.

In order to reduce the noise caused by the operation of the blower fan, an opening is provided on the side of the housing that houses the impeller, and air is taken into the housing from the outside of the housing through this opening. Japanese Patent Application Laid-Open No. 2008-267176, Japanese Patent Application Laid-Open No. 4-183998, and the like describe techniques for rectifying the turbulent flow to reduce noise. In addition, US Patent Application Publication No. 2005/0180849 describes an axial fan in which an impeller in which a plurality of blades are connected by an annular connecting portion is housed in a housing having an opening at a side portion. ing.
US Patent Application Publication No. 2008/0056899 US Pat. No. 6,554,574 US Pat. No. 6,241,474 JP 2008-267176 A JP-A-4-183998 US Patent Application Publication No. 2005/0180849

  However, the above Patent Documents 1 to 3 do not consider the influence of the impeller characteristics due to the interference between the air flow generated by the rotation of the blades and the connecting portion.

  In addition, Patent Documents 4 to 6 reduce noise by taking air into the housing from the outside of the housing through an opening provided on the side of the housing, and cooling the axial fan in the circumferential direction. The effect is not considered at all.

  The present invention includes an impeller that suppresses a decrease in impeller characteristics due to interference between an air flow generated by rotation of a blade and a coupling portion, and exhibits a circumferential cooling effect while maintaining an axial cooling effect. It is to provide a blower fan.

  In order to solve the above-described problems, the present invention provides an impeller having an annular coupling portion that couples a plurality of blades to each other, and the plurality of blades are connected to a radially inner portion and a radially outer portion by the coupling portion. A configuration is adopted in which an opening communicating with the inside of the housing is formed in a side portion of the housing which is partitioned into two and accommodates a plurality of blades.

  That is, the blower fan according to one aspect of the present invention is fixed to the substantially cylindrical cup portion that rotates about the central axis and the outer peripheral surface of the cup portion, and rotates together with the cup portion, thereby sucking air from one side in the axial direction. And a plurality of blades for exhausting in the other axial direction, a motor for rotating the blades together with the cup portion, and a housing for housing the cup portion, the plurality of blades, and the motor. Are connected to each other by a connecting portion, and are divided into a radially inner portion and a radially outer portion by the connecting portion, and the connecting portion is relative to the blade length along the radial direction of the blade, It is formed in a substantially cylindrical shape at a position of 70% to 90% of the blade length from the base of the outer peripheral surface of the cup portion of the blade, and an opening communicating with the inside of the housing is formed on the side portion of the housing. It is characterized by.

  By configuring the blower fan in this way, the air sucked from one of the axial directions is exhausted to the other axial direction by the rotation of the blades at the radially inner portion partitioned by the connecting portion, and the connecting portion A part of the air sucked from one of the axial directions is exhausted radially outward at the housing side portion through the opening due to the rotation of the blades at the partitioned radially outer portion.

  According to the present invention, in the impeller having an annular coupling portion that couples a plurality of blades to each other, the coupling portion is 70% to the blade length from the root of the blade to the blade length along the radial direction of the blade. By forming it at the 90% position, an increase in noise due to interference between the air flow and the connecting portion can be suppressed, and by forming an opening in the side portion of the housing that accommodates the plurality of blades, axial cooling is achieved. A blower fan that exhibits a cooling effect in the circumferential direction while maintaining the effect can be realized.

It is the top view seen from the central-axis direction intake side of the impeller in one Embodiment of this invention. It is a side view of the impeller of FIG. It is the graph which showed the static pressure characteristic and noise characteristic of each impeller about the some sample of the impeller in which the connection part was formed in a different position. It is sectional drawing which showed the structure of the ventilation fan in one Embodiment of this invention. It is sectional drawing which showed typically the airflow of the ventilation fan in one Embodiment of this invention. It is the graph which showed an example of the static pressure-air volume characteristic of the ventilation fan in one Embodiment of this invention. It is the perspective view which showed the structure of the housing integrally molded in one Embodiment of this invention, a base part, a bearing holding | maintenance part, and a stationary blade.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the description of the present embodiment, a direction parallel to the central axis is referred to as “axial direction”, and a radial direction centered on the central axis is referred to as “radial direction”. In addition, this invention is not limited to the following embodiment. Moreover, it can change suitably in the range which does not deviate from the range which has the effect of this invention.

  FIG. 1 is a plan view of an impeller 1 according to an embodiment of the present invention as viewed from the intake side in the central axis direction, and FIG. 2 is a side view of the impeller 1 of FIG.

  As shown in FIGS. 1 and 2, the impeller 1 in the present embodiment is fixed to a substantially cylindrical cup portion 10 that rotates about a central axis J and an outer peripheral surface 10 a of the cup portion 10. By rotating, a plurality of blades 11 that intake air from one side in the axial direction and exhaust air to the other side in the axial direction, and a substantially annular connecting portion 12 that connects the plurality of blades 11 to each other are provided. Here, the connection part 12 is formed in the substantially cylindrical shape in the circumferential direction along the arbitrary circle centering on the central axis J. As shown in FIG.

  The inventors of the present application have studied the influence of the impeller characteristics due to the interference between the air flow generated by the rotation of the blade 11 and the connecting portion 12, and as a result, obtained important knowledge regarding the formation position of the connecting portion 12 in the radial direction of the blade 11. It was.

  FIG. 3 is a graph showing the static pressure characteristics and noise characteristics of the impeller 1 for a plurality of samples A to E of the impeller 1 in which the connecting portions 12 are formed at different positions with respect to the radial direction of the blade 11. Here, in the samples A to E, as shown in FIG. 1, the connecting portion 12 is connected to the blade length La along the radial direction of the blade 11 from the root of the cup outer peripheral surface 10 a of the blade 11. Are formed at positions where the distance Lb is 50%, 70%, 80%, 90%, and 100% of the blade length La. Curves G1b to G5b in the figure show the results of measuring the relationship between the air volume and static pressure of samples A to E, and curves G1a to G5a show the results of measuring the relationship between the air volume and noise of samples A to E, respectively. It is a thing.

  As shown in FIG. 3, in the samples A and E (curves G1a and G5a) where the position of the connecting portion 12 corresponds to 50% and 100%, the positions of the connecting portion 12 correspond to 70%, 80% and 90%. It can be seen that the noise increases compared to samples B, C, and D (curves G2a, G3a, and G4a). The reason for the increase in noise in sample A is considered to be that interference between the air flow and the connecting portion 12 becomes large in the central portion in the radial direction of the blade 11 because the contribution of air flow generation is large. Further, the noise increases in the sample E because the air flow in the reverse direction is generated in the gap between the connecting portion 12 and the side wall of the housing when the connecting portion 12 is provided at the radially outer end 11b of the blade 11. Conceivable.

  Therefore, the connecting portion 12 is formed at a position 70% to 90% of the blade length La from the root of the blade 11 with respect to the blade length La along the radial direction of the blade 11. The increase in noise due to the noise can be suppressed.

  In addition, since the connecting portion 12 is disposed on the radially inner side with respect to the radially outer end 11b of the blade 11, the connecting portion 12A is located at the portion 11A of the blade 11 positioned radially inward of the connecting portion 12. The inner surface of 12 serves as the inner surface of the housing. That is, there is no gap between the inner surface of the virtual housing (the inner surface of the connecting portion 12) and the portion 11 </ b> A of the wing 11 positioned radially inward of the connecting portion 12. Therefore, in the portion 11A of the blade 11 that is located radially inward of the connecting portion 12, it is difficult for the backflow of airflow to occur, and most of the backflowing airflow is located radially outward of the connecting portion 12. It will pass through the part 11B of the wing 11 to be performed. As a result, the portion 11B of the blade 11 positioned radially outward from the connecting portion 12 can function exclusively for preventing the backflow of airflow. Accordingly, it is possible to improve the static pressure characteristics on the low air volume side while securing the air volume characteristics of the impeller 1 at the portion 11A of the blade 11 positioned radially inward from the connecting portion 12.

  In addition, although the intensity | strength of the wing | blade 11 with respect to a centrifugal force is improved by mutually connecting the several wing | blade 11 with the connection part 12, when the wing | blade 11 is comprised as a forward wing | blade, the effect is exhibited. Here, as shown in FIG. 1, the forward wing is an intersection P1 between a leading edge 11a located at the forefront in the rotational direction R of the wing 11 and a wing tip 11b located at the radially outer end of the wing 11. In this case, the front edge 11a and the outer peripheral surface 10a of the cup portion 10 are located on the front side in the rotational direction R with respect to the intersection P2. Further, when the degree of advancement is extremely large, that is, as shown in FIG. 1, the trailing edge 11 c located rearward in the rotational direction R of the blade 11 and the blade tip 11 b located at the radially outer end of the blade 11. The effect is further obtained when the intersection point P3 is located on the front side in the rotation direction R from the intersection point P2 between the front edge 11a located in front of the blade 11 in the rotation direction R and the outer peripheral surface 10a of the cup portion 10. Can be demonstrated.

  By the way, a so-called axial fan (blower fan) generates an air flow along the direction of the central axis J by rotating a plurality of blades 11 fixed to the outer peripheral surface of the cup portion 10 about the central axis J. Then, a heating element such as an electronic component on the exhaust side is cooled.

  However, as the amount of heat generated in the electronic device increases as the density of electronic components and the like mounted in the electronic device increases, it is required to improve the cooling efficiency of the blower fan. Under such circumstances, if a blower fan capable of cooling not only the heating element on the axial exhaust side but also the heating element on the side of the housing can be realized, an improvement in cooling efficiency can be expected.

  Conventionally, a blower fan in which an opening is provided in a side portion of a housing that accommodates an impeller has been proposed (see Patent Documents 4 to 6), and all of these air flows into the housing from the outside of the housing through the opening. This is intended to rectify turbulent flow that causes noise or to improve intake efficiency to reduce noise and suppress surging.

  That is, the inside of the housing that houses the impeller has a negative pressure due to the axial airflow generated by the rotation of the impeller. Therefore, when an opening is provided on the side of the housing, air is inevitably taken into the housing from outside the housing through the opening.

  On the other hand, as described above, the impeller in which the plurality of blades 11 are connected to each other by the annular connecting portion 12 has a diameter defined by the connecting portion 12 because the connecting portion 12 serves as an inner side surface of the virtual housing. In the region 11A on the inner side in the direction, an air flow is generated exclusively along the axial direction, and in the region 11B on the outer side in the radial direction, an air flow that flows backward is generated exclusively. Therefore, in the housing, it is conceivable that the negative pressure is large in the region 11A on the radially inner side, and the negative pressure is small in the region 11B on the radially outer side.

  Therefore, the inventors of the present application accommodate an impeller in which a plurality of blades 11 are connected to each other by an annular connecting portion 12 in a housing provided with an opening over substantially the entire circumference of the side portion, and thereby the airflow characteristics of the impeller. As a result of the measurement, in the axial direction, the same airflow characteristics as the impeller accommodated in the housing without the opening were obtained, and the air flow toward the radially outward direction was also observed at the side of the housing. It was.

  This is because even in the housing, since the negative pressure is small in the region of the radially outer portion 11B, the air flow of the centrifugal component spreading radially outward overcomes the negative pressure, and the opening on the side portion of the housing It is considered that an air flow directed outward in the radial direction was generated through the.

  The present invention has been made on the basis of such knowledge, and in the impeller 1 including the annular coupling portion 12 that couples the plurality of blades 11 to each other, the plurality of blades 11 are connected to the radially inner portion 11A by the coupling portion 12. And a radially outer portion 11 </ b> B, and an opening that communicates with the inside of the housing is formed on the side of the housing that houses the plurality of blades 11.

  FIG. 4 is a cross-sectional view schematically showing the configuration of the blower fan 2 in the present embodiment. As shown in FIG. 4, the blower fan 2 is fixed to the substantially cylindrical cup portion 10 that rotates about the central axis J, and the outer peripheral surface of the cup portion 10. A plurality of blades 11 that take in air from one of them and exhaust it in the other axial direction, a motor that rotates the plurality of blades 11 together with the cup portion 10, and a housing 30 that houses the cup portion 10, the plurality of blades 11, and the motor, The housing 30 and the base portion 24 are connected by a stationary blade 31.

  The motor includes a rotor holder 22 and a rotor magnet 23 attached to the inner peripheral surface of the cup portion 10, a stator 26 in which a coil is wound around a stator core, and a sleeve bearing 21 fixed inside the bearing holding portion 25. I have. The shaft 20 fixed to the center portion of the cup portion 10 is inserted into a sleeve bearing 21 and is rotatably supported.

  The blower fan 2 configured in this manner generates a rotational torque between the stator 26 and the rotor magnet 23 by supplying a drive current to the coil of the stator 26, and thereby the outer peripheral surface 10 a of the cup portion 10. The plurality of wings 11 fixed to the center of the wing 11 rotate about the central axis J.

  In the present invention, in the blower fan 2, the connecting portion 12 is positioned 70% to 90% of the blade length from the root of the outer peripheral surface of the cup portion 10 of the blade 11 with respect to the blade length along the radial direction of the blade 11. In addition, an opening 30 a communicating with the inside of the housing 30 is formed on the side of the housing 30.

  As shown in FIG. 5, the blower fan 2 configured as described above was sucked from one side (the intake side) in the axial direction by the rotation of the blade 11 in the radially inner portion 11 </ b> A defined by the connecting portion 12. The air is exhausted to the other side (exhaust side) in the axial direction, and part of the air sucked from one side in the axial direction is caused by the rotation of the blades 11 in the radially outer portion 11B defined by the connecting portion 12. The air is exhausted radially outward at the side of the housing 30 through the opening 30a.

  In this way, the air sucked from the axial intake side is classified into an air flow exhausted to the axial exhaust side and an air flow exhausted radially outward at the side of the housing 30. In addition to cooling the heating element on the axial exhaust side, the heating element on the side of the housing 30 can be cooled. Thereby, the ventilation fan with high cooling efficiency is realizable.

  In the present invention, the air flow discharged to the exhaust side in the axial direction by the rotation of the blades 11 in the radially inner portion 11A and the radially outer portion 11B, and radially outward in the housing 30 side portion. The exhausted air flow need not be completely sorted. For example, the air flow discharged to the exhaust side in the axial direction may be generated by the rotation of the blades 11 in the radially outer portion 11B.

  FIG. 6 is a graph showing an example of the static pressure-air volume characteristic of the blower fan 2 in the present embodiment. The air flow shown in this graph is the air flow of the air flow exhausted to the axial exhaust side, but is not so different from the air flow in the blower fan in which the opening 30a is not provided on the side of the housing 30. This is because, in the portion 11B on the radially outer side defined by the connecting portion 12, a backflowing air flow is generated and does not contribute much to the axial air flow, and the axial air flow is exclusively used by the connecting portion. This is because it is generated by the radially inner portion 11 </ b> A partitioned by 12.

  FIG. 7 is a perspective view showing a structure in which the housing 30, the base portion 24, the bearing holding portion 25, and the stationary blade 31 are integrally formed by injection molding. As shown in FIG. 7, the opening 30 a is preferably formed over almost the entire side of the housing 30. Thereby, the air volume of the air flow exhausted radially outward at the side portion of the housing 30 through the opening 30a can be increased. The size, shape, and the like of the opening 30a are not particularly limited, and may be appropriately determined in consideration of the strength of the housing 30 and the usage status of the blower fan.

1 impeller
2 Blower fans
10 Cup part
10a Cup outer peripheral surface
11 Wings
11A Radial inner part of the wing
11B Radial outer part of the wing
11a Leading edge of the wing
11b Radial outer end of wing 11c Trailing edge of wing
12 Connecting part
20 shaft
21 Sleeve bearing
22 Rotor holder
23 Rotor magnet
24 Base part
25 Bearing holding part
26 Stator
30 Housing
30a opening
31

Claims (5)

A substantially cylindrical cup portion that rotates about a central axis;
A plurality of blades that are fixed to the outer peripheral surface of the cup portion and rotate together with the cup portion, thereby sucking air from one axial direction and exhausting the other axial direction;
A motor for rotating the plurality of blades together with the cup portion;
A housing that houses the cup portion, the plurality of blades, and the motor;
With
The plurality of wings are connected to each other by a substantially annular connecting portion, and are divided into a radially inner portion and a radially outer portion by the connecting portion,
The connecting portion is formed in a substantially cylindrical shape at a position of 70% to 90% of the blade length from the root on the outer peripheral surface of the cup portion of the blade with respect to the blade length along the radial direction of the blade. And
A blower fan in which an opening communicating with the inside of the housing is formed in a side portion of the housing. The blower fan according to claim 1,
The plurality of blades is a blower fan configured as a forward blade. The blower fan according to claim 1,
By the rotation of the blades at the radially inner portion defined by the connecting portion, the air sucked from one of the axial directions is exhausted to the other of the axial directions,
A part of the air sucked from one of the axial directions by the rotation of the blades at the radially outer portion defined by the connecting portion is exhausted radially outward at the housing side portion through the opening. Be blown fan. The blower fan according to claim 1,
The said opening part is a ventilation fan currently formed over the perimeter of the side part of the said housing. The blower fan according to claim 1,
The intersection of the trailing edge located at the rear of the blade in the rotational direction and the blade tip located at the radially outer end of the blade is defined by the front edge located at the forward direction of the blade and the outer peripheral surface of the cup part. A blower fan located on the front side in the rotational direction from the intersection.

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