JP2013053618A - Blade for centrifugal fan device, centrifugal fan device, and electronic device including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a blade for a centrifugal fan device capable of cooling a wide range by dividing distal ends of blades of the centrifugal fan to divide the airflow directions, and to provide the centrifugal fan device and the electronic device including the same.SOLUTION: A blade part 15 has a first region integrated in a thickness direction of the blade part 15 in a radial direction inner side and a plurality of divided second regions divided in the thickness direction of the blade part 15 in a radial direction outer side. The diameter of a first blade 25 is larger than that of a second blade 26.

Description

  The present invention relates to a centrifugal fan device used for cooling a heating element such as an ultra-compact processing unit (hereinafter referred to as MPU) mounted inside a housing of an electronic device, from a heat receiving member thermally connected to the heating element. A blade for a centrifugal fan device, a centrifugal fan device that forcibly blows and cools the heat dissipator after efficiently transporting heat to the heat dissipator by a system such as a heat pipe or liquid refrigerant circulation, and an electronic device including the same It relates to equipment.

  Recently, the speed of data processing in computers has been very rapid, and the clock frequency of MPU has become much higher than before.

  As a result, the amount of heat generated by the MPU increases, and not only the conventional method of dissipating heat by bringing a heat sink having a heat radiation fin into contact with the heat generator, but also a method of directly cooling the heat sink with a fan, or the heat generator and heat A heat sink module that transports heat from a connected heat receiving body to a heat sink using a heat pipe is configured, and the heat sink is forcibly cooled by blowing air from a fan, and a liquid refrigerant with high thermal conductivity is pumped. For example, a method for forcibly blowing and radiating heat from a heat radiating body that is forcibly circulated by the centrifugal fan device and is thermally transported between the heat receiving body and the heat radiating body is indispensable.

  On the other hand, the improvement of the cooling performance of the centrifugal fan device described above largely depends on the improvement of the air blowing performance such as high air volume and high static pressure, and the air blowing performance of the centrifugal fan device usually increases the rotation speed of the centrifugal fan. However, since the wind noise (hereinafter referred to as fan noise) of the blade portion of the centrifugal fan also tends to increase, the fan faces the fan in order to reduce the fan noise. There is a type in which two blades have a step at the outer peripheral edge, and a circular plate centered on the rotation axis of the blade is provided at the step (for example, see Patent Document 1).

JP 2009-257113 A

  However, in the case where there is a step at the outer peripheral edge of the blade as described above and a circular plate centered on the rotation axis of the blade is provided at the step, the direction of the wind from the rotating blade becomes one direction, and the fan device The wind blown out from the air is also biased in one direction, which is suitable for spot cooling aiming at the cooling point, but there is a problem in effectively cooling a wide range.

  Further, although the vortex that causes noise generated at the tip of the fan can be diverted and reduced, the vortices move in the same direction, so that the vortices can easily rejoin and return to the vortex before the diversion. As a result, it has been difficult to reduce noise.

  Therefore, in view of the above problems, the present invention can increase the cooling performance without effectively increasing the rotational speed of the centrifugal fan by effectively sucking the outside air into the centrifugal fan, and branch the tip of the centrifugal fan blade. It is another object of the present invention to provide a centrifugal fan device blade, a centrifugal fan device, and an electronic device including the same, which can cool a wide range by dividing the air flow direction.

  In order to achieve the above object, the present invention provides a hub portion, a blade portion having a plurality of blades extending in the radial direction around the hub portion, and a wind generated by the blade portion extending in the radial direction around the hub portion. The blade portion includes a first region that is integral in the thickness direction of the blade portion on the radially inner side and a second region that is divided into a plurality of portions in the thickness direction of the blade portion on the radially outer side. The diameter of one blade divided into a plurality of areas in the second area and the diameter of the other blade are larger than the diameter of the current plate, and the diameter of one blade divided into a plurality of areas in the second area is A centrifugal fan device blade having a diameter larger than the diameter of the other blade divided into a plurality in the second region, a centrifugal fan device including the centrifugal fan device blade, and the centrifugal fan device The It is a child equipment.

  According to the present invention, by changing the length from the outer periphery of the rectifying plate of each blade branched into two from the middle of the blade, generation of air vortices causing noise generated at the tip of the blade portion The position to be moved can be shifted three-dimensionally, and recombination of air vortices can be prevented, so that the centrifugal fan can be silenced.

Overview of centrifugal fan device in an embodiment of the present invention The perspective view of the blade of the centrifugal fan apparatus in the Example of this invention The enlarged view of the blade of the centrifugal fan apparatus in the Example of this invention The enlarged view of the blade of the centrifugal fan apparatus in the Example of this invention The characteristic view which shows the cooling performance of the centrifugal fan apparatus in the Example of this invention The figure which shows the shape of the braid | blade of the centrifugal fan apparatus in the Example of this invention. The perspective view of the other form of the baffle plate of the blade of the centrifugal fan apparatus in the Example of this invention The figure which shows operation | movement of the blade of the centrifugal fan apparatus in the Example of this invention. The figure which shows the shape of the other blade of the centrifugal fan apparatus in the Example of this invention.

  According to the first aspect of the present invention, there is provided a hub portion, a blade portion having a plurality of blades extending radially about the hub portion, and a wind generated by the blade portion extending radially about the hub portion. The blade portion is divided into a plurality of first regions integrated in the thickness direction of the blade portion on the radially inner side and a thickness direction of the blade portion on the radially outer side. A diameter of one blade divided into a plurality of portions in the second region and a diameter of the other blade is larger than a diameter of the current plate, and a plurality of the second regions are divided in the second region. A blade for a centrifugal fan device characterized in that the diameter of one of the blades divided into two is larger than the diameter of the other blade divided into a plurality in the second region, and the blade is branched into two from the middle of the blade Let each brace By changing the length from the outer periphery of the current plate, the location of the air vortex that causes noise at the tip of the blade can be shifted three-dimensionally to recombine the air vortex. Therefore, it is possible to achieve the noise reduction of the centrifugal fan.

  According to a second aspect of the present invention, there is provided a drive unit, a hub unit that houses the drive unit, a blade unit that has a plurality of blades extending in a radial direction around the hub unit, and a radial direction around the hub unit. A rectifying plate that rectifies the wind generated by the blade portion, and the blade portion is integral with the first region in the thickness direction of the blade portion on the radially inner side, and on the radially outer side. A second region divided into a plurality of portions in the thickness direction of the blade portion, and the diameter of one blade divided into a plurality of portions in the second region and the diameter of the other blade are the diameter of the current plate A centrifugal fan device, wherein the diameter of one blade divided into a plurality in the second region is larger than the diameter of the other blade divided into a plurality in the second region, Two minutes from the middle of the blade By changing the length of each of the blades from the outer periphery of the current plate, the location of the air vortex that causes noise generated at the tip of the blade can be shifted three-dimensionally. Since recombination of the vortex can be prevented, it is possible to achieve the silence of the centrifugal fan.

  The invention according to claim 3 is provided with a casing that houses the hub portion and the blade portion, and has an intake port on each of the surfaces opposed to each other in the rotation axis direction of the blade portion, and the two intake ports have an opening area. The centrifugal fan device according to claim 2, wherein the one blade is opposed to a surface having an intake port having a large intake area among the two intake ports. By providing a blade with a long blade length on the side where there is a large air intake, it is possible to easily carry out a large amount of outside air to the outside of the blade by the large centrifugal force of the blade, and the amount of air blown for cooling Can be secured sufficiently.

  According to a fourth aspect of the present invention, there is provided an electronic apparatus comprising the centrifugal fan device according to the second or third aspect, wherein each of the blades branched into two from the middle of the blade is provided. By changing the length from the outer periphery of the current plate, the location of the air vortex that causes noise at the tip of the blade can be shifted three-dimensionally, preventing recombination of the air vortex. As a result, the centrifugal fan can be silenced.

  In addition, by providing a blade with a long blade length on the side of the frame surface where there is a large air intake, it is possible to easily carry out a large amount of outside air to the outside of the blade part due to the large centrifugal force of the blade. Therefore, it is possible to ensure a sufficient amount of air to be blown.

  That is, it is possible to achieve both the quietness of the centrifugal fan provided in the electronic device and the cooling performance.

(Example)
Embodiments of the present invention will be described below with reference to the drawings. In each drawing, the cover side is described as the upper side and the frame side is described as the lower side.

  1A and 1B are schematic views of a centrifugal fan device according to an embodiment of the present invention. FIG. 1A is a perspective view from above, and FIG. 1B is a perspective view from below.

  First, as shown in FIG. 1A, the fan casing 12 of the centrifugal fan device 11 is composed of a frame 12a located at the lower part and a cover 12b located at the upper part.

  However, the cover 12b is not necessarily essential, and for example, a wall of another member may be substituted.

  Here, in the frame 12a, the side wall 12aa and the bottom wall 12ab are integrally formed by resin molding, die casting of aluminum alloy, press molding, or the like, and the air sucked into the fan casing 12 in the two directions to the outside. An exhaust port 13 for exhausting air is disposed, and a substantially circular air intake port 14a through which air sucked from the surroundings passes is disposed on the bottom wall 12ab (see FIG. 1B).

  On the other hand, the cover 12b is formed into a plate shape by stamping or resin molding of a metal material such as steel, aluminum, or copper, and a substantially circular intake port 14b through which air sucked in from the periphery is passed in the center. It is arranged.

  Since the fan casing 12 rotatably accommodates the blade portion 15 that is rotationally driven, the pair of intake ports 14a and 14b are disposed to face each other with the blade portion 15 in between.

  Further, a motor (not shown) which is a drive unit housed and attached in the hub portion 21 rotates the blade 22 of the blade portion 15. For example, a motor is configured by including a stator around which a coil is wound, and a rotor provided around the stator and provided with an annular magnet inside thereof, and a current is passed through the coil of the stator.

  Here, the material of the blade portion 15 is formed by integral molding using a resin material such as polyphenylene sulfide (PPS), polybutylene terephthalate (PBT), or polyethylene terephthalate (PET).

  With the configuration as described above, the air sucked from both the air inlet 14a and the air inlet 14b is in mutually opposite directions in the direction of the rotary shaft 18 fixed at the inner center of the hub portion 21 of the blade portion 15 ( In the direction of collision).

  FIG. 2 is a perspective view of a blade of a centrifugal fan device according to an embodiment of the present invention, (a) is a perspective view from above, and (b) is a perspective view from below.

  As shown in FIG. 2, the blade portion 15 includes a hub portion 21 and a plurality of blades 22 extending from the hub portion 21. The outer periphery of the hub portion 21 is configured by a ring-shaped rectifying plate 30 that has a rectifying effect for smoothly flowing air sucked from the air inlet 14a and the air inlet 14b, and reinforces the strength of the blade 22. 15 is configured to rotate in the clockwise R direction. That is, the rectifying plate 30 can smoothly turn the wind sucked in the vertical direction in the centrifugal direction. Therefore, the outer diameter of the intake port 14a or the intake port 14b and the outer diameter of the rectifying plate 30 are substantially the same. The rectifying plate 30 does not have to be in an annular shape, and may be anything such as a polygon, but is preferably in an annular shape as in the present embodiment.

  Here, the blade 22 extended from the hub portion 21 is divided into a first region integrated in the thickness direction of the blade portion 15 on the radially inner side and a plurality of portions divided in the thickness direction of the blade portion on the radially outer side. 2 regions. In the second region, the first blade 25 or the second blade 26 is divided. That is, from the hub portion 21 in the radial direction, the rectifying plate 30 branches after passing through a certain region, and is divided into a first blade 25 and a second blade 26 (details will be described later).

  Further, the annular rectifying plate 30 provided on the outer periphery of the hub portion 21 can increase the strength of the base of the blade 22 extending outward from the hub portion 21. That is, the blade 22 can be fixed by both the hub portion 21 and the rectifying plate 30 by forming a part of the surface of the blade 22 integrally with the flat portion of the rectifying plate 30 (the thick line portion of B). By doing so, the blade 22 can withstand the rotational force of the blade portion 15 even when the number of blades of the blade 22 is increased in order to improve the performance of the blade portion 15 and the blade thickness of each blade cannot be reduced. it can.

The outer diameter of the rectifying plate 30 is preferably the same as or slightly smaller than the outer diameter of the intake port 14a and the intake port 14b (see FIG. 1). That is, the outer diameter of the rectifying plate 30 ≦ the outer diameter of the intake port 14a and the intake port 14b. With this configuration, the air sucked from the upper and lower directions of the intake port 14a and the intake port 14b does not collide with the air on the wide side surface of the blade 22 that is not divided into the first blade 25 and the second blade 26. The blade 22 can be effectively embraced and sent out to the outer peripheral side of the blade 22 along the curved surface of the blade 22. Note that the same effect can be obtained even when the intake port is only on one side.

  That is, the blade portion 15 has a portion of the rectifying plate 30 that also serves to direct the wind in the centrifugal direction, and a wide portion that is not divided into two outside the rectifying plate 30 that serves to suck a large amount of outside air and push it out in the centrifugal direction. , And three regions divided into two parts which serve to reduce the vortex of air to be discharged (which causes noise) and prevent recombination.

  In some cases, the current plate 30 may not be provided, but as described above, a problem remains in the strength of the blade 22. Further, the outer diameter of the rectifying plate 30 may be larger than the outer diameter of the intake port 14a or the intake port 14b. However, if the outer diameter of the rectifying plate 30 is increased, the size of the blade portion 15 may be increased accordingly. is there.

  In the present embodiment, the first blade 25 and the second blade 26 have a long distance from the hub portion 21 and the length of the blade is long. In other words, the first blade 25 is preferably disposed on the side of the intake port 14b where the opening of the intake port is large.

  The distance from the hub portion 21 of the first blade 25 or the second blade 26 may be the same length, but the longer blade, that is, the first blade 25 has a larger intake opening. By disposing on the 14b side, a large amount of air that can be inhaled can be easily carried out to the outside of the blade portion 15.

  At this time, the tips of the blades 22, that is, the first blade 25 and the second blade 26 are located outside the outer diameter of the intake port so as to be hidden from the intake ports 14a and 14b (see FIG. 1). Desirably, the size of the air inlet is preferably changed in accordance with the ratio of the lengths of the first blade 25 and the second blade 26.

  That is, the gap between the upper end and the lower end of the blade 22 in the thickness direction of the blade portion 15 and the cover 12b and the bottom wall 12ab (see FIG. 1) of the fan casing 12 is narrowed, and noise generated due to a difference in atmospheric pressure at the tip of the blade 22 It is possible to prevent the air vortex that causes the air from overcoming the surface of the blade 22 and moving to the adjacent blade to merge with the adjacent air vortex.

  The first blade 25 is a so-called forward blade that curves forward in the rotational direction, and the second blade 26 is a so-called backward blade that curves backward in the rotational direction.

  By curving the blade 22 in this way, since the blade 22 has a streamlined surface in the radial direction, the air sucked from the axial direction of the centrifugal fan device 11 can be smoothly discharged without resistance. The air blowing efficiency of the eleven blades 22 can be improved.

  The shape of the blade 22 of the blade portion 15 will be described with reference to FIG. 3A and 3B are enlarged views of a blade of the centrifugal fan device according to the embodiment of the present invention, in which FIG. 3A is a top view of the centrifugal fan, and FIG. 3B is a side view of the centrifugal fan viewed from the AA direction of FIG. FIG.

  In FIG. 3, as described above, the first blade 25 is curved forward in the rotational direction, and the second blade 26 is curved backward in the rotational direction. The end Q of the second blade 26 is positioned between the pitches P between the ends of the first blade 25 (details will be described later).

Preferably, the end Q of the second blade 26 is located in the middle of the pitch P between the ends of the first blade 25. By arranging in this manner, the distance between the air vortex generated by the first blade 25 and the air vortex generated by the second blade 26 (distance in the circumferential direction of the blade portion 15) can be most separated. (Details will be described later).

  Further, a point C, which is a branch point that starts to branch into the first blade 25 and the second blade 26, is larger than the outer diameter of the intake port 14a and the intake port 14b (see FIG. 1) in the radial direction of the blade portion 15. Located outside.

  By configuring in this way, the blade 22 is still branched by removing it from the surface of the intake port 14a and the intake port 14b (see FIG. 1) and overlapping the point C, which is a branch point where the blade 22 begins to branch. A large amount of outside air can be sucked from the intake port 14a and the intake port 14b (see FIG. 1) at a wide side portion that is not present, and this can be used as air for cooling the blowout.

  Depending on the size of the blade portion 15, the length of the first blade 25 and the second blade 26 is such that air vortices generated by the first blade 25 and the second blade 26 do not recombine ( It is only necessary to have a curved surface (the length from the point C which is a branch point to the outer periphery of the blade portion 15).

  Here, the outer diameter of the rectifying plate 30, the outer diameter of the intake port 14 a and the intake port 14 b, the position of the point C that is the branching point of the blade 22, and the outer diameter of the blade portion 15 are summarized. Here, the radius and the distance from the center of the blade portion 15 are shown. That is, the outer diameter of the rectifying plate 30 ≦ the outer diameter of the intake port 14a or the intake port 14b <the distance to the point C that is the branching point of the blade 22 <the outer diameter of the blade portion 15.

  As described above, since the first blade 25 and the second blade 26 have a long distance from the hub portion 21 and the length of the blade is long as shown in FIG. Further, a step is formed at the boundary between the first blade 25 and the second blade 26. By providing this step, the distance between the air vortex generated by the first blade 25 and the air vortex generated by the second blade 26 (the axial distance of the blade portion 15) can be increased. The distance between the air vortex generated by the first blade 25 and the air vortex generated by the second blade 26 can be separated three-dimensionally (diagonally up and down).

  In addition, the first blade 25 and the second blade 26 are longer with respect to the length (also the diameter) of the first blade 25 and the second blade 26. Thereby, the cooling performance of the centrifugal fan device can be improved.

  In the present embodiment, the outer diameter of the first blade 25 is 44 mmφ, the outer diameter of the second blade 26 is 42 mmφ, the outer diameter of the rectifying plate 30 is 32 mmφ, the outer diameter of the intake port 14 a and the intake port 14 b is 32 mmφ, and branching. The diameter of the line connecting the points C is 33.5 mmφ. At this time, the balance between the noise and the air volume is good, and the cooling performance of the centrifugal fan device is the best under the same noise conditions.

  Note that the lengths of the first blade 25 and the second blade 26 are not limited to this, but the form of this embodiment is appropriate in consideration of the location of the air vortex that causes fan noise. It is.

  Further, the width of each blade in the rotational axis direction of the blade portion 15 of the first blade 25 and the second blade 26 is the width of the second blade 26 side, that is, the side provided with the portion that receives the rotary bearing. Increasing the size upward is better for the strength of the blade portion 15.

The arrangement of each element of the blade unit 15 will be described with reference to FIG. FIG. 4 is an enlarged view of the blade of the centrifugal fan device in the embodiment of the present invention, and FIG. 5 is a characteristic diagram showing the cooling performance of the centrifugal fan device in the embodiment of the present invention.

  First, a procedure for determining the position of each element of the blade unit 15 will be described. When the size of an electronic device or the like on which the centrifugal fan device 11 is mounted is determined, the size of the centrifugal fan device 11, that is, the diameter (R1) of the blade portion 15 can be determined. Then, the diameter (R5) of the inlets 14a and 14b of the centrifugal fan device 11 is determined by the diameter (R1) of the blade part 15 and the air path resistance of the system including the electronic equipment, and the diameter (R1) of the blade part 15 is determined. ) And the diameters (R5) of the intake ports 14a and 14b, the diameter (R4) of the line connecting the diameter (R3) of the rectifying plate 30 and the point C as a branch point is determined.

  Next, the diameter of the first blade 25 of the blade 22 (same as R1) and the diameter of the second blade 26 (R2) are determined where the cooling performance of the centrifugal fan device 11 can be maximized. .

  FIG. 5 shows the result of earnest examination of the cooling performance of the centrifugal fan device 11.

  Assuming that the size of an electronic device or the like on which the centrifugal fan device 11 is mounted is determined in advance, as an example, when the R1 = 44 mmφ and R5 = 32 mmφ according to the above-described procedure, The result of cooling performance is shown.

  Note that a temperature at which an element such as a CPU in the electronic device is measured is selected as an index indicating the cooling performance (a lower temperature indicates higher cooling performance). Moreover, this result shows an example of the centrifugal fan device 11 representatively, and the absolute value of the numerical value shown in the figure varies depending on the conditions, but the tendency is the same.

  FIG. 5A shows the measured temperature with respect to the diameter (R3) of the current plate 30 when R1 = 44 mmφ and R5 = 32 mmφ. As shown in FIG. 5A, the measured temperature is lower when R3 is smaller than 32 mmφ.

  In particular, the measurement temperature is higher when the diameter (R3) of the current plate 30 is larger. This is because the portion of the blade 22 that is not divided (the portion from the end of the rectifying plate 30 to the point C) becomes narrow, and the intake air cannot be effectively sucked from the intake ports 14a and 14b. This is because there is a decrease.

  That is, the diameter (R3) of the rectifying plate 30 may be equal to or smaller than the diameter (R5) of the intake ports 14a and 14b, but the cooling performance is obtained when the diameter (R3) of the rectifying plate 30 is equal to the diameter (R5) of the intake ports 14a and 14b. Can satisfy you the most.

  FIG. 5B shows the measured temperature with respect to the diameter (R4) of the line connecting the C points as branch points when R1 = 44 mmφ and R3 = R5 = 32 mmφ. As shown in FIG. 5B, the measured temperature is low when R4 is 33.5 mmφ.

  The measurement temperature is high regardless of whether the diameter (R4) of the line connecting the C points as the branch points is large or small. This is because when R4 is large, the curvatures of the first blade 25 and the second blade 26 become steep in order to secure a certain distance between the end portions of the first blade 25 and the second blade 26. As a result, the flow of the wind does not become smooth, and when R4 is small, the undivided portion of the blade 22 (the portion from the end of the rectifying plate 30 to the point C) becomes narrow, and the intake ports 14a, 14b This is because the air cannot be effectively sucked from the air and the amount of air blown is reduced.

  That is, the diameter (R4) of the line connecting the C points as the branch points should be larger than the diameter (R3) of the rectifying plate 30 (R4> R3).

  FIG. 5C shows the measured temperature with respect to the diameter (R2) of the second blade 26 when R1 = 44 mmφ, R3 = R5 = 32 mmφ, and R4 = 33.5 mmφ. As shown in FIG. 5C, the measured temperature is low when R2 is 42 mmφ.

  The measurement temperature is high whether the diameter (R2) of the second blade 26 is large or small. This is because when R2 is large, the noise increases, and at the same noise, the rotational speed of the blade portion 15 of the centrifugal fan device decreases and the air volume decreases. When R2 is small, the air volume decreases because the blade diameter is small. Because it will decrease.

  Thus, the diameter (R1) of the blade portion 15, the diameter (R2) of the second blade 26, the diameter (R3) of the rectifying plate 30, the diameter (R4) of the line connecting the C points as branch points, and the intake air It can be seen that there is an appropriate relationship (R3 ≦ R5 <R4 <R2 ≦ R1) between the diameters (R5) of the mouths 14a and 14b in order to sufficiently exhibit quietness and cooling performance.

  Thus, the blade portion 15 described above is divided into two parts, a part of the rectifying plate 30 that also serves to direct the wind in the centrifugal direction, and an outside of the rectifying plate 30 that serves to suck in a large amount of outside air and push it out in the centrifugal direction. Three areas are formed: a large part that is not wide, and a part that is divided into two parts that serve to reduce the vortex of air being exhaled (which causes noise) and prevent recombination.

  Here, the setting ranges of R2, R3, R4, and R5 that satisfy the noise and cooling performance are 0.9 × R1 ≦ R2 ≦ R1, 0.55 × R1 ≦ R3 ≦ 0.8 × R1, 0.65 ×. R1 ≦ R4 ≦ 0.85 × R1, 0.65 × R1 ≦ R5 ≦ 0.8 × R1.

  In addition, each numerical value shown in the present embodiment is the most balanced combination in order to sufficiently exhibit the noise and the cooling performance. That is, R1 = 44 mmφ, R2 = 42 mmφ (R2 / R1 = 0.95), R3 = 32 mmφ (R3 / R1 = 0.73), R4 = 33.5 mmφ (R4 / R1 = 0.76) and R5 = 32 mmφ (R5 / R1 = 0.73).

  That is, in this embodiment, the outer diameter of the rectifying plate 30 ≦ the outer diameter of the intake port 14a and the intake port 14b <the diameter of the line connecting the points C as the branching point of the blade 22 <the diameter of the second blade 26 <the blade portion. By setting the outer diameter to 15 (the diameter of the first blade 25), the outside air can be effectively sucked into the centrifugal fan, and the cooling performance can be improved without increasing the rotational speed of the centrifugal fan.

  Further, the tip of the blade of the centrifugal fan is branched to disperse the air pushed out from the blade, so that the blown-out air can be sent out in a wide range, enabling a wide range of cooling, and further, at the tip of the blade 22 It is also possible to reduce air vortices that cause noise to be generated.

  Therefore, both the silence of the centrifugal fan and the cooling performance can be achieved.

  In addition, by providing a wide blade side surface that is integrated with the upper and lower sides of the blade 22 and is not divided, the wide side surface portion overlaps or is close to the intake ports 14a and 14b, so that a large amount can be effectively produced from the intake ports 14a and 14b. Outside air can be sucked in, and a sufficient amount of air can be secured for cooling.

Here, the shape of the tip of the blade 22 will be described with reference to FIG. FIG. 6 is a diagram showing the shape of the blade of the centrifugal fan device according to the embodiment of the present invention.

  The blade 22 extends from the hub portion 21 (see FIG. 2), and is joined to or integrally formed with the rectifying plate 30 so that the strength of the blade 22 is increased.

  As shown in FIG. 6, the blade 22 extending radially outward from the current plate 30 is divided and branched into two blade portions at point C. The position of the point C is determined by the outer diameter of the blade portion 15, the outer diameters of the intake ports 14a and 14b, and the desired fan performance.

  The first blade 25 is curved forward in the rotational direction, and the second blade 26 is curved backward in the rotational direction. Each blade portion is curved with a gentle curvature. The first blade 25 is curved along a part of the circumference of the circle M, and the second blade 26 is curved along a part of the circumference of the circle N.

  When the end of the first blade 25 which is the end of each blade portion is X, Y, the end of the second blade 26 is Z, and the center of the blade portion 15 is O, the line segment OZ has an angle XOY of two. A point that becomes a line segment to be equally divided was defined as Z. Thereby, the vortex of the air generated by the upper and lower blades is discharged at the most distant position, and the effect that these vortices do not recombine can be exhibited particularly.

  In this embodiment, the line segment OZ is a line obtained by bisecting the angle XOY, but the line segment OZ is within the angle XOY, and (1/3) × ∠XOY <∠XOZ <(2/3). ) × ∠XOY, the air vortex generated by the upper and lower blades can be prevented from recombining, and the adjacent blades of the first blade 25 and the second blade 26 overlap. It does not match and does not interfere with the blowing performance of the blade.

  That is, the blade 22 has a first region (inside the point C) that is integral in the thickness direction of the blade portion 15 in the radial direction and a second region (from the point C) that is divided into two in the thickness direction of the blade portion 15. The two tip portions divided in the second region extend in different directions in the circumferential direction of the blade portion 15.

  The center of the circle M along which the first blade 25 is aligned is on the front side in the rotational direction, and the center of the circle N along which the second blade 26 is aligned is on the rear side in the rotational direction.

  In this embodiment, the outer diameter of the blade portion 15 is 44 mmφ, the outer diameter of the rectifying plate 30 is 32 mmφ, the outer diameters of the intake port 14 a and the intake port 14 b are 32 mmφ, and the diameters of the circle M and the circle N at that time are 33 mmφ. It is.

  However, the diameters of the circle M and the circle N are not necessarily equal. What is necessary is just to determine the value of a diameter suitably so that the 1st braid | blade 25 and the 2nd braid | blade 26 may become alternate seeing from the centrifugal fan apparatus 11 upper direction.

  Further, the present invention is not limited to these numerical values. Depending on the size of the centrifugal fan device 11 and the wind path resistance, the outer diameter of the blade portion 15 is 40 to 60 mmφ, the outer diameter of the rectifying plate 30 is 26 to 45 mmφ, and the intake port 14a. The outer diameter of the intake port 14b is appropriately set within 30 to 45 mmφ.

  The other form of the baffle plate 30 is demonstrated using FIG. 7 is a perspective view of another form of the current plate of the blade of the centrifugal fan device according to the embodiment of the present invention. FIG. 7A is a current plate in which the current plate 30 is in a ring shape. (B) is a case where the current plate 30 is not attached.

  As shown in FIG. 7A, since the rectifying plate 30 has a ring shape, the outside air sucked from the intake port 14a and the intake port 14b is also present on the side surface of the blade 22 between the hub portion 21 and the rectifying plate 30. It can be easily held and the amount of outside air to be taken in can be increased.

  The reinforcing ring of the rectifying plate 30 is provided closer to the tip of the blade portion 15, which contributes to increasing the strength of the blade 22, but if it is too close to the tip of the blade portion 15, the blowing efficiency of the blade 22 decreases, There is a possibility that the lengths of the branched first blade 25 and second blade 26 cannot be secured. Therefore, the size may be set to satisfy the relational expression of the outer diameter of the rectifying plate 30 described above. The inner diameter of the rectifying plate 30 at this time, that is, the ring width of the rectifying plate 30 may be appropriately set to a width that can strengthen the blade of the blade 22.

  Further, when the number of blades 22 is small and the thickness of each blade can be sufficiently increased and the strength of the blade 22 is sufficient, the rectifying plate 30 does not have to be attached as shown in FIG.

  Thus, the weight of the blade part 15 can be further reduced by making the current plate 30 into a ring shape or not providing the current plate 30.

  The operation of the blade unit 15, particularly the air flow in the fan, will be described with reference to FIG. FIG. 8 is a diagram illustrating the operation of the blades of the centrifugal fan device according to the embodiment of the present invention.

  In FIG. 8, the blade portion 15 rotates in the clockwise direction R, and the outside air sucked in from both directions of the intake port 14a and the intake port 14b is first along the blade 22 branched from the middle thereof. In the vicinity of the tips of the blade 25 and the second blade 26, vortices A and B are formed as indicated by thick arrows.

  Then, the vortex generated in the vicinity of the tip portions of the first blade 25 and the second blade 26 is exhausted from the tip portions of the first blade 25 and the second blade 26 to the outside without being coupled again. . That is, the vortex is pushed out in the direction along the curve of the blade surface and the resultant direction of the rotation direction of the blade portion 15.

  That is, the vortex A pushed out from the first blade 25 that is the forward blade is pushed toward the rotation direction of the blade portion 15 to become a vortex, and the vortex B pushed out from the second blade 26 that is the backward blade is The vortex D is pushed out to the rear side in the rotation direction of the blade portion 15.

  Furthermore, the moving speed (air flow) of the vortex pushed out by the rotational force of the blade portion 15 is faster than the moving speed of the vortex D.

  In FIG. 8, the vortex A and the vortex B are illustrated at positions apart from each other for ease of explanation, but in fact, the same can be said for the first blade 25 and the second blade 26 above and below the blade 22.

  As a result, the vortices diverted by the first blade 25 and the second blade 26 branching the blade 22 have different directions and speeds to be pushed out, so that the vortices after the diversion can be easily recombined. Can be prevented.

Therefore, by having the blade branched into two having different shapes and extending directions, the air that should have become one large vortex can be divided into two small vortices. Thus, noise can be reduced by reducing the air vortex, and the noise of the centrifugal fan device 11 can be reduced.

  In other words, the blade 22 is provided with the first blade 25 and the second blade 26 that extend in curves in different directions, thereby diverting the vortex flow direction differently and making it difficult for the divided vortex to be combined. Therefore, the vortex generated at the tip of the blade 22 is reduced, the noise generated by reducing this vortex can be reduced, and the noise of the centrifugal fan device 11 can be reduced.

  Further, the wind pushed out from the blade 22 in different directions of the first blade 25 and the second blade 26 can be dispersed, and the blown-out wind can be sent out over a wide range, thereby enabling a wide range of cooling.

  In addition, since the cooling air can be blown over a wide range, the heat radiating portion such as the heat generating member and the heat pipe can be widely arranged and cooled around the centrifugal fan device 11, and the heat radiating and cooling can be enhanced.

  The first blade 25 and the second blade 26 preferably have the same height in the rotation axis direction, that is, the width of the blade, and the same width can divide the generated air vortex equally, resulting in greater noise. Therefore, the same width is preferable because the noise is reduced as compared with the case where the width is different.

  Further, in this embodiment, the first and second blade portions having different directions extending from the branch point C (see FIG. 3) divide the place where the air vortex is generated. A third blade portion may be provided.

  In addition, by mounting the above-described centrifugal fan device on an electronic device such as a notebook P, it is possible to provide an electronic device that ensures sufficient silence while satisfying air cooling performance.

  Here, another shape of the first blade 25 and the second blade 26 will be described with reference to FIG. FIG. 9 is a diagram showing the shape of another blade of the centrifugal fan device according to the embodiment of the present invention.

  In FIG. 9A, the blade shape of the first blade 25 is a flat plate, and the blade shape of the second blade 26 is a reverse blade. In FIG. 9B, the blade shape of the first blade 25 is a forward wing, and the blade shape of the second blade 26 is a flat plate.

  Both of them are the same as in the case of the present embodiment described above in terms of air flow and function, and the same effects can be obtained. However, in this embodiment, the wind can be sent out in a wider range, and a wide range of cooling is possible.

  As described in the examination results below, the outside air sucked from the intake port 14a and the intake port 14b is easy to be smoothly blown without resistance because a forward blade and a reverse blade are combined rather than a centrifugal fan of a blade using a flat plate. The blade centrifugal fan is better in terms of air cooling performance and fan noise.

  That is, as a result of intensive studies by the inventor, the noise value at the same rotation speed is 3 dB when the first blade 25 is a forward blade and the second blade 26 is a backward blade as compared with the conventional example. The improvement can be improved by 2 dB in the case where the blade shape of the first blade 25 is a flat plate and the blade shape of the second blade 26 is a reverse blade.

  Further, in the cooling performance at the same noise of the fan as compared with the conventional example, in the case where the first blade 25 is a blade that is a forward blade and the second blade 26 is a backward blade, the temperature can be lowered by 4.5 ° C. In the case where the blade shape of the first blade 25 is a flat plate and the blade shape of the second blade 26 is a reverse blade, the temperature could be lowered by 2.5 ° C.

  A blade for a centrifugal fan device, a centrifugal fan device, and an electronic device including the same according to the present invention can cool an MPU and various heat-generating electronic components mounted in a housing, and require a quieter note. It is useful for P, P server, audio equipment, video equipment, etc.

DESCRIPTION OF SYMBOLS 11 Centrifugal fan apparatus 12 Fan casing 12a Frame 12b Cover 12aa Side wall 12ab Bottom wall 13 Exhaust port 14a Inlet port 14b Inlet port 15 Blade part 21 Hub part 22 Blade 25 First blade 26 Second blade 30 Current plate

Claims (4)

A hub,
A blade portion having a plurality of blades extending in the radial direction around the hub portion;
A rectifying plate extending in a radial direction about the hub portion and rectifying the wind generated by the blade portion, and
The blade portion has a first region that is integral in the thickness direction of the blade portion on the radially inner side, and a second region that is divided into a plurality in the thickness direction of the blade portion on the radially outer side. ,
The diameter of one blade divided into a plurality in the second region and the diameter of the other blade are larger than the diameter of the current plate, and the diameter of the one blade divided into a plurality in the second region is A blade for a centrifugal fan device, wherein the blade is larger in diameter than the other blade divided into a plurality in the second region. A drive unit;
A hub portion for housing the driving portion;
A blade portion having a plurality of blades extending in the radial direction around the hub portion;
A rectifying plate extending in a radial direction about the hub portion and rectifying the wind generated by the blade portion, and
The blade portion has a first region that is integral in the thickness direction of the blade portion on the radially inner side, and a second region that is divided into a plurality in the thickness direction of the blade portion on the radially outer side. ,
The diameter of one blade divided into a plurality in the second region and the diameter of the other blade are larger than the diameter of the current plate, and the diameter of the one blade divided into a plurality in the second region is A centrifugal fan device having a diameter larger than that of the other blade divided into a plurality in the second region. A casing that houses the hub portion and the blade portion, and has an air inlet on each of the surfaces facing the rotation axis direction of the blade portion,
The two intake ports have different opening areas,
3. The centrifugal fan device according to claim 2, wherein the one blade is disposed on a surface of the two intake ports having an intake port having a large intake area. An electronic apparatus comprising the centrifugal fan device according to any one of claims 2 and 3.

Images