JP2018059517A - Centrifugal fan - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a centrifugal fan which is thin and which can reduce generation of noise.SOLUTION: A centrifugal fan 1 has a configuration in which an impeller 30 is stored having a plurality of blades 51 arrayed on a circumference between an upper casing 11 and a lower casing 21 in which an air suction port is formed. The centrifugal fan 1, according to the rotation of the impeller 30, exhausts the air introduced through an opening 13 to a lateral side of the impeller 30. The lower casing 21 has a recessed part which is made of a metal plate and which dents downward. On a bottom surface of the recessed part 22, a motor 60 is mounted. One part of a stator 67 of the motor 60 and a circuit board 69 on which a drive circuit of the motor 60 is mounted are stored inside the recessed part 22. At the recessed part 22, a hole part 25 is provided in which means for supplying power for rotating the motor 60 passes through.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a centrifugal fan, and more particularly to a centrifugal fan that reduces noise caused by blowing air.

  FIG. 17 is a perspective view showing an example of a conventional centrifugal fan. FIG. 17 is a side sectional view showing an example of a conventional centrifugal fan.

  As shown in FIGS. 17 and 18, a centrifugal fan (also referred to as a “centrifugal fan”) 801 generally includes an impeller in a casing 810 having a suction port 813 (833) and a blowout port 819. 830 is stored. The impeller 830 has a large number of blades 851 arranged around the rotation axis of the motor 860. The centrifugal fan 801 causes air sucked from the suction port 813 (833) to flow between the blades (blades) from the center of the impeller 830, and the air is blown by the fluid force due to the centrifugal action accompanying the rotation of the impeller 830. The vehicle 830 is blown toward the outside of the diameter. Air blown outward from the outer periphery of the impeller 830 is blown out from a blowout port 819 of the casing 810. A portion of each blade 851 on the suction port 813 side has a vertical edge.

  As shown in FIG. 18, the centrifugal fan 801 is thin. The centrifugal fan 801 has a motor 860 for rotating the impeller 830 at a substantially central portion of the casing 810. The motor 860 is an outer rotor type brushless motor disposed so that the rotor yoke 863 is attached to the impeller 830.

  Such a centrifugal fan 801 is widely used in home appliances, OA equipment, industrial equipment cooling, ventilation, air conditioning, vehicle blowers, and the like. The ventilation performance and noise of the centrifugal fan 801 are greatly influenced by the blade (blade) shape of the impeller 830 and the shape of the casing 810 (structure of the centrifugal fan 801).

  In order to reduce noise and improve air blowing performance, the shape of the impeller and the structure of the casing have been optimized, and various proposals have been made. For example, a centrifugal fan that reduces noise by optimizing the blade (blade) shape has been proposed (see, for example, Patent Document 1).

JP-A-63-289295

  By the way, in the thin centrifugal fan 801 as described above, a portion of the casing 810 located below the impeller 830 is configured using resin. Therefore, there is a problem that the centrifugal fan 801 has low rigidity and relatively large vibration and noise.

  The present invention has been made to solve such a problem, and an object thereof is to provide a centrifugal fan that is thin and can reduce the generation of noise.

  In order to achieve the above object, according to one aspect of the present invention, a casing composed of an upper casing and a lower casing in which an air suction port is formed, a lower casing, and the casing is accommodated between the upper casing and the lower casing. An impeller having a plurality of blades arranged on the circumference, a motor for rotating the impeller, and a circuit board on which a drive circuit of the motor is mounted. The centrifugal fan that can blow out the air sucked through the mouth toward the outside of the diameter of the impeller, the lower casing is made of a metal plate, has a recessed portion that is depressed downward, and the motor A part of the stator of the motor and the circuit board are accommodated inside the concave part, and the circuit board is disposed below the stator, and the motor part is provided in the concave part. Power for rotating connector or hole leads through to supply is provided a hole is provided on a portion of the bottom surface of at least the recess.

  Preferably, the hole is provided so as to lack at least a part of the side surface of the recess.

  Preferably, the side surface of the recess has a tapered shape that tapers downward.

  Preferably, a connector connected to the motor is attached to the hole.

  Preferably, the blow-out port from which the air discharged toward the outside of the diameter of the impeller is a side portion of the casing, and an opening portion excluding a column portion provided between the upper casing and the lower casing Is provided.

  According to these inventions, the lower casing is configured using a metal plate. Therefore, it is possible to provide a centrifugal fan that is thin and can reduce noise generation.

It is a top view which shows the centrifugal fan in one of the embodiments of this invention. It is sectional drawing in the AA of FIG. FIG. 3 is a partially enlarged view of FIG. 2. It is a figure explaining the shape of an impeller. It is a graph which shows the relationship between the shape of a lower shroud, and the performance of a centrifugal fan. It is a figure which shows an example of a structure of another centrifugal fan used as comparison object. It is the perspective view which looked at the lower casing from the lower side. It is a sectional side view in a different section from Drawing 2 of a centrifugal fan. It is a graph which shows the generation | occurrence | production state of a vibration when using the lower casing comprised with the metal plate of thickness 1.6mm and which was star-stamped. It is a graph which shows the generation | occurrence | production state of a vibration when using the lower casing which is comprised with the metal plate of thickness 1.6mm and which is not star-stamped. It is a graph which shows the generation | occurrence | production state of a vibration when using the lower casing comprised with the metal plate of thickness 1.2mm and which was star-stamped. It is a graph which shows the generation | occurrence | production state of the vibration when using the lower casing which is comprised with the metal plate of thickness 1.2mm and which is not star-stamped. It is a sectional side view which shows the structure of the centrifugal fan which concerns on the modified example of this Embodiment. It is a sectional side view which shows the structure of the centrifugal fan which concerns on the modified example different from the above-mentioned of this Embodiment. It is a figure explaining the shape of the impeller of a centrifugal fan. It is the perspective view which looked at the lower casing of the centrifugal fan which concerns on the modified example different from the above-mentioned of this Embodiment from the lower side. It is a perspective view which shows an example of the conventional centrifugal fan. It is a sectional side view which shows an example of the conventional centrifugal fan.

  Hereinafter, a centrifugal fan according to one embodiment of the present invention will be described.

  FIG. 1 is a plan view showing a centrifugal fan according to one embodiment of the present invention. 2 is a cross-sectional view taken along line AA in FIG. FIG. 3 is a partially enlarged view of FIG.

  With reference to FIGS. 1 to 3, the centrifugal fan 1 includes a casing 10, an impeller 30, and a motor 60. The centrifugal fan 1 is configured in a substantially square rectangular parallelepiped shape in plan view as a whole, except for a portion where the motor 60 is attached. The centrifugal fan 1 is thin and has a relatively small vertical dimension (height). The impeller 30 is attached to a rotor 63 that rotates together with the shaft 61 of the motor 60. The centrifugal fan 1 rotates the impeller 30 by the motor 60. The centrifugal fan 1 discharges air (an example of fluid) introduced from the suction port 33 to the side of the impeller 30 as the impeller 30 rotates. That is, the air introduced from the suction port 33 passes between the blades 51 of the impeller 30 and is blown toward the outside of the impeller 30 by a fluid force due to the centrifugal action accompanying the rotation of the impeller 30. The Air is exhausted from the outlet 19 of the casing 10 on the side of the impeller 30.

  The motor 60 is, for example, an outer rotor type brushless motor. The motor 60 is attached to the central portion of the lower casing 21 with a fastening member such as a screw or a bolt. The motor 60 has a cup-shaped rotor (rotor yoke) 63 that opens downward. An annular magnet 65 is attached to the inner surface of the side peripheral portion of the rotor 63. A shaft 61 is attached to the central portion of the rotor 63.

  The shaft 61 is rotatably supported by a pair of bearings 66 a attached to the bearing holder 66. A stator 67 is provided on the outer periphery of the bearing holder 66. The stator 67 is configured by a laminated stator core, an insulator wound around a coil attached to the stator core, and the like. The stator 67 is disposed to face the magnet 65 with a predetermined gap in the radial direction (left-right direction in FIG. 2). The stator 67 is connected to the circuit board 69. The circuit board 69 is, for example, a printed wiring board. An electronic component for controlling the motor 60 is mounted on the circuit board 69, and a drive circuit for the motor 60 is mounted.

  The casing 10 is configured by combining an upper casing 11 and a lower casing 21. Specifically, the upper casing 11 and the lower casing 21 are assembled to each other using screws 14 located at four corners in plan view, and the casing 10 is configured. The screw 14 is, for example, a bolt inserted from the lower casing 21 side. For example, the upper casing 11 and the lower casing 21 are assembled to each other so as to sandwich the column at the portion where the screw 14 is disposed. At this time, the support column may be formed integrally with either the upper casing 11 or the lower casing 21. The air outlet 19 is, for example, a side portion of the casing 10 excluding a fastening portion between the upper casing 11 and the lower casing 21 using the screw 14, and is provided between the upper casing 11 and the lower casing 21. .

  The impeller 30 is disposed so as to be housed in the casing 10. The impeller 30 has a disk shape as a whole. An upper casing 11 is disposed above the impeller 30, and a lower casing 21 is disposed below the impeller 30. That is, the centrifugal fan 1 is configured to hold the impeller 30 between the upper casing 11 and the lower casing 21.

  The impeller 30 roughly includes an upper shroud 31, a lower shroud 41, and a plurality of blades 51 disposed between the upper shroud 31 and the lower shroud 41. A suction port 33 that opens upward is formed at the center of the impeller 30. The suction port 33 is configured by being surrounded by an upper end portion 35 inside the upper shroud 31. As shown in FIG. 1, the plurality of blades 51 are arranged on the circumference at appropriate intervals.

  A lower shroud 41 into which the rotor 63 is fitted is disposed at the center of the impeller 30. A cylindrical portion (an example of an attachment portion) 43 formed so that the rotor 63 is disposed is provided at the center portion of the lower shroud 41. The rotor 63 is fitted into a cylindrical portion 43 provided in the central portion of the lower shroud 41 and holds the impeller 30. The rotor 63 is disposed so as to protrude upward in the suction port 33 toward the outside of the suction port 33. As shown in FIG. 3, the vertical height of the portion where the rotor 63 holds the cylindrical portion 43 is not more than half of the vertical height H of the centrifugal fan 1. Is set. Accordingly, the centrifugal fan 1 is made relatively thin, and the air sucked from the suction port 33 is not blocked by the rotor 63.

  Each blade 51 has the same curved shape. The blades 51 are rear-facing blades and are of a so-called turbo type. The shape of the blade 51 is a shape that is curved and inclined backward with respect to the rotation direction. The upper shroud 31, the lower shroud 41, and the blades 51 are formed by integral molding using, for example, a synthetic resin.

  The upper casing 11 is formed using a resin such as an engineering plastic. An opening 13 is formed at the center of the upper casing 11. The opening 13 is circular in plan view. The opening 13 is formed so that air is introduced into a suction port 33 provided in the impeller 30. The opening 13 has an inner diameter slightly larger than the suction port 33 constituted by the upper shroud 31. That is, in the present embodiment, the size of the opening 13 is substantially equal to the size of the suction port 33.

  The lower casing 21 is formed using, for example, a metal plate such as iron. A concave portion 23 that is recessed downward is formed in the central portion of the lower casing 21. The recess 23 is formed in a bowl shape. As shown in FIG. 2, in the present embodiment, a motor 60 and a drive circuit for the motor 60 such as a circuit board 69 are mounted in the recess 23. The motor 60 is mounted on the lower casing 21 with a fastening member such as a screw or a bolt, but instead of the fastening member, the lower portion of the bearing holder 66 is caulked and fixed to the recess 23 and mounted on the lower casing 21. Also good.

  The outer peripheral part of the lower casing 21 is a side plate bent in the axial direction (vertical direction in FIG. 2). By providing the side plate, the rigidity of the lower casing 21 is enhanced.

  Of the upper surface of the lower casing 21, the portion around the recess 23 is a partition wall 29 that faces the lower surface of the impeller 30. The partition wall 29 is formed in a flat shape so as to be close to the lower surface of the impeller 30.

  As shown in FIG. 2, the lower shroud 41 of the impeller 30 has a shaft (rotary axis of the impeller 30) 61 such that at least the outer peripheral side portion of each blade 51 faces the partition wall portion 29. It is provided only on the close side. That is, each blade | wing 51 is exposed to the site | part which faces the partition part 29 among the impellers 30. FIG. The surface of the lower casing 21 that faces the impeller 30 is a part of the wall surface that guides the air introduced from the suction port 33 to the side. The blades 51 are arranged opposite to the partition wall 29 with a predetermined gap in the axial direction. Note that at least a part of the lower part of each blade 51 may be exposed to the partition wall 29 side, or the entire part may be exposed to the partition wall 29 side.

  The outer diameter of the impeller 30 housed in the casing 10 is set to be smaller than the dimension of one side of the casing 10. Thereby, the rotating impeller 30 does not protrude from the outer edge of the casing 10, and contact with other members of the impeller 30, damage due to contact, and the like are prevented.

  The lower casing 21 has a function as a main plate for guiding air in the impeller 30 and also has a function as a substrate of the casing 10. For this reason, the setting of the gap formed between the impeller 30 and the partition wall 29 is important. When the gap is too large, the air sucked from the suction port 33 passes between the blades 51 and also flows into the gap. As a result, the pressure of the air blown out from the impeller 30 is reduced, and the blowing characteristics are deteriorated. On the other hand, when the gap is too small, there are the following problems. That is, if the dimensional accuracy of each part varies, the blades 51 may come into contact with the partition wall 29. In order to prevent such contact, it is necessary to manage the dimensional accuracy of each component with high accuracy, which increases the cost of the centrifugal fan 1. The gap is set appropriately in view of such problems.

  The value of the height h in the vertical direction from the lower end of each blade 51 to the upper end of the suction port 33 with respect to the inner diameter of the opening 13 (indicated by φd in FIG. 2) is 15% or more and 25%. Within the following range. That is, the relationship between the height h and the inner diameter φd of the opening 13 is expressed by the following equation.

0.15 ≦ h / φd ≦ 0.25
Here, in the present embodiment, as shown in FIG. 3, the upper surface of the lower shroud 41 is a curved surface 49 that forms a downwardly convex arcuate curve in the side cross section. The outer peripheral end 45 of the lower shroud 41 is located in the vicinity of the vertically lower side of the upper end 35 of the upper shroud 31. Further, in the lower shroud 41, an inner peripheral end portion 47 that is an upper end portion of the cylindrical portion 43 is an upper end portion of the lower shroud 41. The inner peripheral end portion 47 is located in the vicinity of the outer peripheral upper end portion 63 a of the rotor 63. The curved surface 49 is formed between the outer peripheral end portion 45 and the inner peripheral end portion 47. Of the curved surface 49, the outermost end 45 is at the lowermost position and the inner peripheral end 47 is at the uppermost position.

  FIG. 4 is a view for explaining the shape of the impeller 30.

  4 is the same cross section as the cross section shown in FIG. The shape of the lower shroud 41 will be further described with reference to FIG. In other words, in the present embodiment, the curved surface 49 passes through the upper end 35 inside the suction port 33 in the cross section passing through the rotation axis of the impeller 30 (hereinafter, simply referred to as a cross section), and the rotation of the impeller 30. It is formed in an arc shape centered on a point on a straight line L parallel to the axis. The curved surface 49 is formed so as to be located outside the circle C2 shown in FIG. In other words, the rotor 63 and the lower shroud 41 including the cylindrical portion 43 are configured so as to be positioned outside the circle C2 in a cross section (does not protrude into the circle C2). Thus, the air flow path between the upper shroud 31 and the lower shroud 41 from the suction port 33 to the blowout port 19 is configured to facilitate air flow.

  The circle C <b> 2 is a circle whose center A <b> 2 is located on the straight line L and passes through the outer peripheral end 45 that is the end edge of the lower shroud 41. The radius R2 of the circle C2 is 80 percent of the radius R of the circle C1. The circle C1 is a circle having the upper end portion 35 as the center A1. The radius R of the circle C <b> 1 is a distance from the upper end 35 to the outer peripheral end 45 in the vicinity of the upper portion 35 in the vertically lower portion of the surface of the lower shroud 41. That is, in the present embodiment, the radius R of the circle C1 is substantially equal to the height h in the vertical direction of the air flow path introduced from the suction port 33 shown in FIG.

  The curved surface 49 may have an arc shape whose center is not located on the straight line L in the cross section. Further, the curved surface 49 may not have an arc shape in the cross section. An elliptical arc shape or another curved shape may be used. In any case, the lower shroud 41 including the curved surface 49 has a radius of 80% of the distance from the upper end 35 to the surface of the curved surface 49 in the cross section, and the curved surface whose center is on the straight line L. 49 is located outside the circle C2 in contact with 49. Similarly, the rotor 63 is located outside the circle C2. In this case, the circle C2 may be a circle in which the center A2 is located on the straight line L, the radius R2 is 80% of the radius R of the circle C1, and is in contact with the surface of the lower shroud 41.

  In the present embodiment, since the lower shroud 41 has such a shape, the following effects can be obtained. That is, in the centrifugal fan 1, it is difficult to reduce the thickness of the motor 60 that rotates the impeller 30. For this reason, conventionally, the rotor portion of the motor protrudes to the central portion of the suction port and the air flow is obstructed, which may cause noise. However, according to the configuration of the present embodiment, the air flow path is configured so that air flows smoothly while the centrifugal fan 1 is thin. Therefore, generation of noise can be suppressed.

  FIG. 5 is a graph showing the relationship between the shape of the lower shroud 41 and the performance of the centrifugal fan 1.

  In FIG. 5, the size of the arc on the horizontal axis is the radius of the arc of the curved surface 49 centered on a vertical line passing through the upper end 35 (upper shroud inner periphery) and passing through the outer end 45 of the lower shroud 41 in the cross section. Is shown as a percentage relative to 100% when the radius is equal to the height h of the air flow path.

  As shown in FIG. 5, the noise value decreases monotonically as the arc size increases. Compared to when the arc size is 60% and 70%, the noise value is significantly lower when the arc size is 80%. Compared to the case where the arc size is 80 percent, when the arc size is 90 percent, the noise value is reduced, but the reduction amount is relatively small.

  The maximum static pressure does not change much regardless of the arc size. The maximum current that flows through the motor 60 during operation of the centrifugal fan 1 is the smallest when the arc size is around 80 percent, slightly higher when the arc size is 90 percent, and the arc size is 70 percent and 60 percent. Then it will rise significantly.

  Also from the relationship between the lower shroud 41 and the performance of the centrifugal fan 1 shown in this way, if the arc size is larger than 80%, the current flowing through the motor 60 is relatively reduced and the noise value is equivalent. It can be said that it can be made smaller. That is, in the present embodiment, since the curved surface 49 of the lower shroud 41 has the shape as described above, the noise value of the centrifugal fan 1 can be made relatively small.

  FIG. 6 is a diagram illustrating an example of the configuration of another centrifugal fan to be compared.

  A centrifugal fan 901 shown in FIG. 6 is to be compared with the centrifugal fan 1 according to the present embodiment. Similar to the centrifugal fan 1, the centrifugal fan 901 includes an upper casing 911, a lower casing 921, an impeller 930, a motor 960, and the like. The motor 960 includes a shaft 961 and a rotor 963. The impeller 930 includes an upper shroud 931, a lower shroud 941, and a plurality of blades 951. A portion of each blade 951 on the suction port 933 side has a tapered shape that decreases downward as it approaches the central portion of the impeller 930.

  Compared with the conventional centrifugal fan 801 (conventional centrifugal fan 801) as shown in FIG. 18 and the centrifugal fan 901 (comparative example centrifugal fan 901) shown in FIG. The centrifugal fan 1 of the form can be driven with a low noise value. That is, the noise values in the respective cases where these centrifugal fans 1, 801, 901 are driven at a certain speed are as follows.

  That is, the noise value of the conventional centrifugal fan 801 is, for example, 58 dBA.

  The noise value of the centrifugal fan 901 of the comparative example is 55 dBA, for example.

  On the other hand, the noise value of the centrifugal fan 1 of the present embodiment is, for example, 52 dBA.

  As described above, in the present embodiment, the curved surface 49 of the lower shroud 41 has the shape as described above, so that the noise value of the centrifugal fan 1 is compared with those of the conventional example and the comparative example. And can be made smaller.

  In this embodiment, in addition to the effect obtained by improving the air flow path as described above, the following effect can be obtained.

  That is, in the conventional structure as shown in FIG. 18, since the lower shroud of the impeller extends to the outer peripheral portion, a complicated mold such as a slide type is required to form the impeller integrally, In addition, the productivity of the impeller was extremely low. On the other hand, in the present embodiment, the impeller 30 is configured such that at least a part of the blade 51 is exposed to the partition wall 29 and faces the partition wall 29. Therefore, the configuration of the mold for integrally molding the impeller 30 can be made relatively simple, and the productivity of the impeller 30 can be improved.

  Moreover, in the conventional structure, the part located under an impeller among the casings was comprised using resin. For this reason, there is a problem that the centrifugal fan has low rigidity, and vibration and noise are relatively large. On the other hand, in the present embodiment, since the lower casing 21 is configured using a metal plate, the rigidity of the centrifugal fan 1 can be increased as compared with the case where resin is used. Therefore, vibration and noise of the centrifugal fan 1 can be reduced. Since the number of resin parts having a relatively complicated shape can be reduced, the manufacturing cost of the centrifugal fan 1 can be reduced.

  The casing 10 that houses the impeller 30 does not include a side wall except for a column portion provided between the upper casing 11 and the lower casing 21. Thus, since the side part of the casing 10 is opened and becomes the blowout port 19, the air ejected toward the radially outward side of the impeller 30 is not disturbed by the side wall of the casing 10. Therefore, noise due to air turbulence during blowing can be greatly suppressed. Moreover, since the casing 10 is not provided with a side wall and is formed in the dimension substantially the same as the outer diameter dimension of the impeller 30, the centrifugal fan 1 can be reduced in size.

  Here, in the centrifugal fan 1, the lower casing 21 has the following characteristics.

  FIG. 7 is a perspective view of the lower casing 21 as viewed from below. FIG. 8 is a side sectional view of the centrifugal fan 1 in a cross section different from that of FIG.

  As shown in FIG. 7, in the present embodiment, a hole 25 is formed in the lower casing 21. The hole 25 is formed in a side of the recess 23 where the bearing holder 66 is attached. The hole 25 is a hole having a substantially rectangular shape in plan view. Screw holes 14b in which the screws 14 are arranged are formed at the four corners of the lower casing 21.

  As shown in FIG. 8, a connector 71 is attached to the hole 25. The connector 71 is used to supply power to the motor 60 and is connected to the motor 60 inside the recess 23. A user can easily drive the centrifugal fan 1 by connecting a cable for supplying power to the connector 71.

  Further, in the lower casing 21, the lower surface of the partition wall portion 29 is star-stitched and provided with many small concave portions. Thereby, small irregularities are provided on the lower surface of the partition wall 29. In this way, the stiffening process is performed on the partition wall 29, whereby the rigidity in the partition wall 29 is improved, the distortion is corrected, and the flatness is increased. The star striking process may be formed, for example, on both upper and lower surfaces of the partition wall 29, or may be formed on portions other than the partition wall 29. The star striking process may be applied to at least the partition wall 29 of the lower casing 21.

  Here, by subjecting a part of the lower casing 21 to star machining, vibration and noise generated when the centrifugal fan 1 is driven can be made relatively small. In general, as the thickness of the metal plate constituting the lower casing 21 is reduced, the degree of occurrence of vibration and noise is increased. However, in the present embodiment, it is possible to suppress the generation of vibration and noise while using a thinner metal plate by performing star machining. Thereby, the weight of the centrifugal fan 1 can be reduced. Moreover, the manufacturing cost of the centrifugal fan 1 can be reduced.

  FIG. 9 is a graph showing the occurrence of vibration when the lower casing 21 made of a metal plate having a thickness of 1.6 millimeters and subjected to star machining is used. FIG. 10 is a graph showing the occurrence of vibration when the lower casing 21 made of a metal plate having a thickness of 1.6 mm and not subjected to star machining is used. FIG. 11 is a graph showing the occurrence of vibration when using the lower casing 21 made of a metal plate having a thickness of 1.2 millimeters and subjected to star machining. FIG. 12 is a graph showing the occurrence of vibration when the lower casing 21 made of a metal plate having a thickness of 1.2 millimeters and not subjected to star machining is used.

  9 to 12 are measurement results obtained assuming the configuration of the centrifugal fan 1 in which members other than the lower casing 21 are substantially the same. Star machining (hereinafter sometimes simply referred to as machining) is performed on the lower surface side of the lower casing 21 with a pitch of 2 millimeters and a depth of 0.5 millimeters.

  As can be seen from a comparison between FIG. 9 and FIG. 10, the magnitude of vibration occurring at a frequency near 120 Hz is significantly reduced when there is machining compared to when there is no machining. As can be seen from a comparison between FIG. 12 and FIG. 10, when the thickness of the lower casing 21 is reduced to 1.2 millimeters, the occurrence of vibration increases in the absence of processing. However, as can be seen by comparing FIG. 10 and FIG. 11, even when the thickness of the lower casing 21 is reduced, when processing is performed, compared to the case where processing is not performed with a thick metal plate. , Can greatly suppress the occurrence of vibration. In the case where there is processing, even if the thickness of the lower casing 21 is reduced, the vibration is slightly increased, but the vibration can be considerably reduced as compared with the case where there is no processing. Therefore, generation | occurrence | production of the vibration of the centrifugal fan 1 can be suppressed, comprising the lower casing 21 using the metal plate with comparatively thin thickness.

[Description of variant]
The shape of the rotor is not limited to that described above.

  FIG. 13 is a side sectional view showing a configuration of a centrifugal fan 101 according to a variation of the present embodiment.

  As shown in FIG. 13, the centrifugal fan 101 is different from the centrifugal fan 1 according to the above-described embodiment in that it includes a motor 160 having a rotor 163 having a different shape. Other configurations are the same between the centrifugal fan 101 and the centrifugal fan 1.

  The rotor 163 has a conical shape (cone shape) on the top surface, the length of the side portion attached to the lower shroud 41 being the same as that of the rotor 63 in the vertical direction, but increasing upward as it approaches the center. Have. Accordingly, the motor 160 has a shaft 161 that is slightly longer than the shaft 61.

  As described above, since the upper portion of the rotor 163 has a conical shape, an air guiding effect of air introduced from the suction port 33 is obtained. That is, the air introduced into the impeller 30 is guided to the flow path between the side upper shroud 31 and the lower shroud 41 as it approaches the top of the rotor 163. Thereby, air can be flowed smoothly.

  The upper portion of the rotor 163 may not be formed in a conical shape, and the above-described wind guide effect may be obtained. For example, by attaching a cover having a conical shape to the rotor 63 having a flat upper portion, the rotor 63 and the cover are configured so as to form a shape like the rotor 163 of this modification. May be.

  FIG. 14 is a side sectional view showing a configuration of a centrifugal fan 201 according to a modified example different from the above in the present embodiment.

  As shown in FIG. 14, the centrifugal fan 201 is different from the centrifugal fan 1 according to the above-described embodiment in that it includes an impeller 230 having a different shape. Other configurations are the same between the centrifugal fan 201 and the centrifugal fan 1.

  The impeller 230 has an upper shroud 231, a lower shroud 41, and a blade 51. The shape of the upper part of the upper shroud 231 is different from that of the upper shroud 31 in the above-described embodiment. In this modification, the upper end portion of the upper shroud 231 is located above the upper end portion of the opening 13 of the upper casing 11. That is, in the centrifugal fan 1, the vertical position of the upper end 235 of the suction port 33 is above the upper end of the opening 13.

  FIG. 15 is a view for explaining the shape of the impeller 230 of the centrifugal fan 201.

  In FIG. 15, the impeller 230 is partially enlarged so as to correspond to FIG. Also in this modified example, similarly to the above-described embodiment, the curved surface 49 passes through the upper end portion 235 inside the suction port 33 and is parallel to the rotation axis of the impeller 30 in the cross section passing through the rotation axis of the impeller 30. It is formed in an arc shape centered on a point on the straight line L2. The curved surface 49 is formed so as to be positioned outside the circle C2 in the cross section. In other words, the rotor 63 and the lower shroud 41 including the cylindrical portion 43 are located outside the circle C2 in the cross section. Here, also in this modification, the circle C2 is a circle whose center is on the straight line L2 and has a radius R2 of 80 percent of the circle C1. The circle C <b> 1 is a circle that passes through the outer peripheral end 45 in the vicinity of the lower end of the upper end 235 on the surface of the lower shroud 41 with the upper end 235 as the center A <b> 1.

  By configuring the impeller 230 in this manner, air flows between the upper shroud 231 and the lower shroud 41 from the suction port 33 to the blowout port so that air can easily flow. It is configured. Therefore, noise generation can be suppressed in the centrifugal fan 201.

  The vertical position of the upper end 235 of the suction port 33 may be the same as the upper end of the opening 13.

  FIG. 16 is a perspective view of the lower casing 421 of the centrifugal fan according to the modified example different from the above-described embodiment, as viewed from the lower side.

  The lower casing may not be provided with a hole for attaching the connector. That is, as shown in FIG. 16, unlike the above-described lower casing 21, the hole 25 is not formed in the lower casing 421. In the lower casing 421, a wiring hole 425 is formed in the recess 23, for example. The wiring hole 425 is provided to draw out the lead wire 471 connected to the drive circuit of the motor 60 from the inside of the centrifugal fan to the outside. The structure of other parts of the lower casing 421 is the same as that of the lower casing 21.

[Others]
The shape of the casing is not limited to a substantially regular square in plan view. The casing may have any arbitrary shape including a polygon, a circle, and an asymmetric shape. The fastening location between the upper casing and the lower casing is not limited to the inside of the four corners of the upper casing in plan view. For example, a screw or a column for connecting the upper casing and the lower casing to a place connected to the upper casing so as to protrude outward from an outer peripheral edge having a substantially square shape in plan view of the upper casing May be provided.

  In addition, in the location which fastens an upper casing and a lower casing, when providing a support | pillar between an upper casing and a lower casing, the shape of a support | pillar should just be as follows, for example. That is, the support column may have a substantially cylindrical shape having a size that allows a screw for connecting the upper casing and the lower casing to pass therethrough. By using the struts having such a shape, the air blown from the impeller is blown outward from the side surface of the casing with almost no resistance, so that the noise of the centrifugal fan can be reduced. it can.

  The lower casing may be configured using a material other than a metal plate, such as a resin material. The upper casing and the lower casing may be integrally formed.

  The above embodiment should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

DESCRIPTION OF SYMBOLS 1,101,201 Centrifugal fan 11 Upper casing 19 Outlet 21 Lower casing 23 Recess 25 Hole 29 Bulkhead 30,230 Impeller 31,231 Upper shroud 33 Suction port 35,235 Upper end 41 Lower shroud 43 Cylindrical part (Example of mounting part)
51 Blade 60, 160 Motor 61, 161 Shaft (an example of impeller rotation shaft)
63,163 Rotor 69 Circuit board (an example of a motor drive circuit)
71 connector

According to an aspect of the present invention for achieving the above object, the centrifugal fan comprises a lower casing is located above the lower casing, an impeller having a plurality of blades arranged on the circumference, the vane a motor for rotating the vehicle, and a circuit board driving circuit of the motor is mounted, with the rotation of the impeller, the blowing air was sucked through narrowing the mouth outward in the diameter of the impeller Ri can der, lower casing is made of metal, has a recess having a recess viewed bottom and sides downwards, a part of the motor and the circuit board are accommodated in the recess, The recess is provided with a hole through which means for supplying electric power for rotating the motor passes, and the hole has a substantially rectangular shape in plan view .

Preferably, the hole is provided in at least a part of the bottom surface .

Preferably, the hole is provided in a boundary region between the bottom surface and the side surface so as to lack a part of the bottom surface and a part of the side surface .

Preferably, the outer peripheral edge of the circuit board is close to the side surface of the recess .

Preferably, the means for supplying electric power for rotating the motor is a connector or a lead wire .

Claims (5)

A casing composed of an upper casing and a lower casing formed with an air inlet;
An impeller that is housed between the upper casing and the lower casing and includes a plurality of blades arranged on a circumference;
A motor for rotating the impeller;
A circuit board on which the drive circuit of the motor is mounted,
A centrifugal fan capable of blowing out the air sucked through the suction port toward the outside of the diameter of the impeller as the impeller rotates,
The lower casing is made of a metal plate, and has a concave portion that is recessed downward.
The motor is attached to the bottom surface of the recess,
A part of the stator of the motor and the circuit board are housed in the recess,
The circuit board is disposed below the stator,
The recess is provided with a hole through which a connector or a lead wire for supplying electric power for rotating the motor is passed,
The centrifugal fan is provided in at least a part of the bottom surface of the recess.   The centrifugal fan according to claim 1, wherein the hole is provided so as to lack at least a part of a side surface of the recess.   The centrifugal fan according to claim 1, wherein a side surface of the concave portion has a tapered shape that tapers downward.   The centrifugal fan according to claim 1, wherein a connector connected to the motor is attached to the hole. The blowout port from which the air discharged toward the outside of the diameter of the impeller is a side part of the casing, and is an opening excluding a column part provided between the upper casing and the lower casing The centrifugal fan according to any one of claims 1 to 4, wherein the centrifugal fan is provided in the portion.

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