TWI636193B - Air supply unit - Google Patents

Abstract

The problem of the present invention is to provide a blower unit which has less manufacturing man-hours, lower pressure loss and high efficiency. In order to solve the above problem, the air blowing unit 1 according to the present invention includes a housing 3 having an air inlet 15 and an air outlet 17, and a side portion surrounded by a plurality of side surfaces 13; and a centrifugal fan 5 housed in the housing The interior of 3. The width dimension Wo of the air outlet 17 provided in the bottom surface 11 of the frame 3 is formed to be smaller than the distance Wc1 between the pair of opposite side faces 13, 13 of the plurality of side faces 13. A disk-shaped rectifying plate 7 is disposed between the centrifugal fan 5 and the air outlet 17 inside the casing 3, and the disk-shaped rectifying plate 7 has an outer diameter larger than the outer diameter Df of the centrifugal fan 5, And the peripheral edge is formed into a circular shape.

Description

Air supply unit

The invention relates to a blower unit.

In the past, a centrifugal fan (without a spigot fan) that does not use a casing is used for air supply of an air conditioner (hereinafter referred to as an air conditioner) or cooling of an industrial machine (refer to, for example, Patent Document 1). . The air conditioner shown in Patent Document 1 is a heat pump type air conditioner, and the centrifugal fan is disposed in the fan chamber, and the outer shape is required to be small. Therefore, there is a problem in that the space of the fan chamber (air supply unit) is limited, and the distance between the fan and the air outlet is not sufficiently ensured, and the efficiency is low. In order to solve this problem, a conical curved guide is arranged near the pipe (duct) connection port on the inner wall of the fan chamber.

[Advanced technical literature]

(Patent Literature)

Patent Document 1: Japanese Patent Laid-Open Publication No. 2005-16791

However, such prior air conditioners are mostly designed in accordance with the space of the installation site of the building, so-called custom production. Therefore, there is a problem that the size of the fan chamber is also changed correspondingly with the setting of the site, and the conical surface guide must be separately prepared for each air conditioner, resulting in manufacturing. The working hours increase. Further, it is desired to further improve pressure loss, efficiency, and the like.

Accordingly, the present invention provides a blower unit that has fewer manufacturing man-hours, lower pressure loss, and higher efficiency.

The air blowing unit according to the present invention includes: a casing having an intake port and an air outlet, the side portion being surrounded by a plurality of side faces; and a centrifugal fan housed inside the casing; and being disposed in the casing The width dimension of the air outlet on the bottom surface is formed to be smaller than the distance between the pair of opposite sides of the plurality of side surfaces. A rectifying plate having an outer diameter larger than an outer diameter of the centrifugal fan and having an outer peripheral edge formed in a circular shape is disposed between the centrifugal fan and the air outlet inside the casing.

The width dimension of the air outlet is smaller than a distance between a pair of opposite side faces of the plurality of side faces. Therefore, a corner portion is formed in a portion where the side surface and the bottom surface intersect each other inside the frame body. Therefore, since the air blown out from the centrifugal fan collides with the bottom surface of the corner portion to form a vortex, the wind speed distribution of the air discharged from the air outlet becomes uneven at each portion along the radial direction, resulting in unevenness. The pressure loss increases.

On the other hand, in the air blower according to the present invention, since the flow regulating unit is disposed, the airflow blown from the centrifugal fan is rectified, and the eddy current is reduced as compared with the case where the flow regulating plate is not provided. Therefore, the wind speed distribution of the air discharged from the air outlet becomes equal at each portion along the radial direction, and thus the pressure loss ⁱ is small. Moreover, since only the rectifying plate is provided, the number of manufacturing man-hours is also small.

1‧‧‧Air supply unit

3‧‧‧ frame

5‧‧‧ centrifugal fan

7‧‧‧Round plate rectifier (rectifier)

9‧‧‧ top surface

11‧‧‧ bottom

13‧‧‧ side

14‧‧‧ corner

15‧‧‧air inlet

17‧‧‧ outlet

19‧‧‧ Pipes

21‧‧‧ motherboard

23‧‧‧ suction port

25‧‧‧ side panels

27‧‧‧ leaves

29‧‧‧Motor

31‧‧‧Support feet

41‧‧‧Ring rectifying plate (rectifier plate)

41a‧‧‧round holes

51‧‧‧Cone-shaped rectifying plate (rectifier plate)

51a‧‧‧round holes

53‧‧‧ side

61, 63‧‧‧ eddy current

65, 67‧‧‧ eddy current

69, 71‧‧ ‧ eddy current

73, 75‧‧‧ eddy current

Fig. 1 is a perspective view showing a blower unit according to a first embodiment of the present invention, and a side wall constituting a front side of the frame body is omitted.

Fig. 2 is a perspective view showing the centrifugal fan and the disk-shaped flow regulating plate of Fig. 1;

Fig. 3 is a perspective view showing a disk-shaped flow regulating plate according to the first embodiment.

Fig. 4 is a perspective view showing an annular flow regulating plate according to a second embodiment.

Fig. 5 is a perspective view showing a truncated cone-shaped flow regulating plate according to a third embodiment.

Fig. 6 is a schematic view showing the airflow in the casing according to the first embodiment.

Fig. 7 is a schematic view showing the air flow in the casing according to the second embodiment.

Fig. 8 is a schematic view showing an air flow in a casing according to a third embodiment.

Fig. 9 is a schematic view showing an air flow in a casing according to a comparative example.

Fig. 10 is a graph showing the relationship between the air volume and the static pressure for the examples and comparative examples of the present invention.

Fig. 11 is a graph showing the relationship between the air volume and the static pressure efficiency for the present invention example and a comparative example.

Figure 12 is a view showing an air flow and a static pressure for the present invention and a comparative example. A diagram of the relationship, and various changes are made to the inner and outer diameters of the annular rectifying plate.

Fig. 13 is a graph showing the relationship between the air volume and the static pressure efficiency for the present invention example and the comparative example, and various changes are made to the inner diameter and the outer diameter of the annular flow regulating plate.

Fig. 14 is a graph showing the relationship between the air volume and the static pressure for the examples and comparative examples of the present invention, and various changes are made to the outer diameter of the annular flow regulating plate.

Fig. 15 is a graph showing the relationship between the air volume and the static pressure efficiency for the examples and comparative examples of the present invention, and various changes are made to the outer diameter of the annular flow regulating plate.

Fig. 16(a) is a perspective view showing the dimensions of a centrifugal fan and a truncated cone-shaped rectifying plate.

Fig. 16(b) is a graph showing the relationship between the air volume and the static pressure for the present invention example and a comparative example.

Fig. 17 is a graph showing the relationship between the air volume and the static pressure efficiency for the examples and comparative examples of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

[First Embodiment]

As shown in Fig. 1, the air blowing unit 1 according to the first embodiment of the present invention includes a housing 3, a centrifugal fan 5, and a disk-shaped rectifying plate 7 (rectifying plate).

The frame body 3 is formed into a rectangular parallelepiped box and is composed of the following parts: a top surface 9 disposed on the upper side; a bottom surface 11 disposed on the lower side; and four side surfaces 13 surrounded by the surrounding sides unit. Further, in the first drawing, the side surface 13 on the front side is omitted so as to clearly show the inside of the casing 3. On the aforementioned top surface 9, a circular hole is formed in the center, and this hole becomes an air inlet port 15. A rectangular hole is formed in the bottom surface 11, and the hole serves as an air outlet 17. Further, a pipe 19 having a square tubular shape is connected below the air outlet 17.

Here, the size of the top surface 9 is set such that the width dimension in the lateral direction is Wc1 and the depth dimension in the front-rear direction is Wc2. Therefore, the distance between the pair of side faces 13, 13 opposed in the left-right direction is also set to Wc1. Wc1 is preferably, for example, 1134 mm, and Wc2 is preferably, for example, 1134 mm. Further, the height of the side surface 13 is set to Hc, and Hc is preferably, for example, 850 mm. The width dimension Wo of the air outlet 17 is preferably, for example, 630 mm. Further, the width dimension Wo of the air outlet 17 is set to be smaller than the distance Wc1 between the side faces 13 and 13.

As shown in FIG. 1 and FIG. 2, the centrifugal fan 5 includes a main plate 21 that is disposed on the lower side and has a disk shape, and the side plates 25 face upward from the main plate 21 with a predetermined interval therebetween. Arranged and provided with a suction port 23 at the center; and the vane 27 is disposed between the main plate 21 and the side plate 25 in the circumferential direction at a predetermined interval. These main plates 21, side plates 25, and vanes 27 are all formed by press forming a steel plate or an aluminum plate, and then integrally joined by welding, caulking, or the like. Further, the material is not limited to a steel sheet or aluminum, and may be a resin or the like. The centrifugal fan 5 is rotated by the motor 29 disposed on the lower side, whereby the air A is centrifuged The side of the fan 5 is blown out. Further, the motor 29 is supported by the casing 3.

As shown in Fig. 2, the outer diameter of the side plate 25 (the outer diameter of the centrifugal fan 5) is set to Df, and the inner diameter of the side plate 25 is set to df. Further, the height of the centrifugal fan 5 is set to Hf. The aforementioned Df is preferably, for example, 630 mm, df is preferably 440 mm, and Hf is preferably 260 mm.

Inside the frame body 3, a disk-shaped rectifying plate 7 (rectifier plate) is disposed between the centrifugal fan 5 and the air outlet 17, and the disk-shaped rectifying plate 7 has an outer diameter larger than that of the centrifugal fan 5 The outer diameter is, and the outer peripheral edge is formed into a circular shape. Further, the shortest distance between the outer peripheral edge portion of the disk-shaped flow regulating plate 7 and the side surface 13 can be appropriately determined depending on the amount of air blown by the centrifugal fan 5. Moreover, the annular rectifying plate and the truncated cone-shaped rectifying plate which will be described later are also determined in the same manner. The distance between the lower end of the centrifugal fan 5 and the disk-shaped flow regulating plate 7 in the vertical direction is h, and this h is preferably, for example, 50 mm.

As shown in FIG. 3, the disk-shaped rectifying plate 7 (rectifier plate) is a disk having an outer diameter set to Dpa, and the outer diameter Dpa is formed larger than the outer diameter Df of the centrifugal fan 5. Specifically, the outer diameter Dpa of the disk-shaped flow regulating plate 7 is set to 150 to 170% of the outer diameter Df of the centrifugal fan 5. That is, Dpa=1.5Df~1.7Df. Further, the disk-shaped flow regulating plate 7 is supported by the side surface 13 of the casing 3 by four support legs 31 (partially not shown). Further, in the present embodiment, the material of the disk-shaped flow regulating plate 7 is a steel plate, and may be a resin or the like.

In the air blowing unit 1 having the above configuration, the air A is introduced from the air inlet 15 which has been formed on the top surface 9 of the frame 3, and the air A enters the centrifugal fan 5 from the air inlet 23 and rotates along The blade 27 is discharged to the side portion, and then flows from the side of the outer peripheral edge of the disk-shaped rectifying plate 7 to the lower side, and flows into the duct 19 from the air outlet port 17 which has been formed on the bottom surface 11.

[Second Embodiment]

Next, the second embodiment will be described, and the same configurations as those of the first embodiment will be omitted.

In the second embodiment, an annular rectifying plate 41 (rectifier plate) is disposed in the air blowing unit 1 of the first embodiment described in the first embodiment instead of the disk-shaped rectifying plate 7. The position at which the annular flow regulating plate 41 is disposed is the same as that of the first embodiment.

As shown in Fig. 4, the annular flow regulating plate 41 is formed in a flat plate shape, and the outer diameter is set to Dpb and the inner diameter is set to dpb. The top view of the outer peripheral edge and the inner peripheral edge are formed in a circular shape, and the center of the annular rectifying plate 41 coincides with the central axis of the centrifugal fan 5. In this way, the annular flow regulating plate 41 is formed in a flat plate shape in which a circular hole 41a is formed in a central portion of the circular plate.

Further, the outer diameter Dpb of the annular flow regulating plate 41 is formed to be larger than the outer diameter Df of the centrifugal fan 5. Specifically, the outer diameter Dpb of the annular flow regulating plate 41 is set to 150 to 170% of the outer diameter Df of the centrifugal fan 5. That is, Dpb = 1.5 Df ~ 1.7 Df.

Further, the difference in size (Dpb-dpb) between the outer diameter Dpb and the inner diameter dpb of the annular flow regulating plate 41 is set to 20 to 60% of the outer diameter Df of the centrifugal fan 5. Specifically, (Dpb-dpb) = 0.2 Df to 0.6 Df.

[Third embodiment]

Next, a third embodiment will be described, and the first embodiment will be described. The same configurations as those in the second embodiment are omitted.

In the third embodiment, the trough-shaped rectifying plate 51 (rectifier plate) is disposed in the air blowing unit 1 of the first embodiment described in the first embodiment instead of the disc-shaped rectifying plate 7. The position at which the truncated cone-shaped rectifying plate 51 is disposed is the same as that of the first embodiment.

As shown in Fig. 5, the truncated cone-shaped rectifying plate 51 has a circular hole 51a formed in a central portion thereof and is formed in a truncated cone shape, and its side surface 53 is accompanied by a downstream side of the airflow from the center to the outer periphery ( The lower side of Fig. 5) is inclined. The outer diameter is set to Dpc and the inner diameter is set to dpc. Further, in the side view, the inclination angle θ of the side surface 53 and the horizontal plane is preferably 0° to 20°.

Further, the outer diameter Dpc of the truncated cone-shaped rectifying plate 51 is formed to be larger than the outer diameter Df of the centrifugal fan 5. Specifically, the outer diameter Dpc of the truncated cone-shaped rectifying plate 51 is set to be 150 to 170% of the outer diameter Df of the centrifugal fan 5. That is, Dpc = 1.5 Df ~ 1.7 Df.

[Examples]

Next, the present invention will be described in further detail by way of examples.

(First embodiment)

First, as shown in Fig. 6, in correspondence with the first embodiment, the disk-shaped rectifying plate 7 is placed below the centrifugal fan 5, and the airflow in the casing 3 is simulated. The side portion of the frame 3 is surrounded by the side surface 13, and an air outlet 17 is formed at a central portion of the bottom surface 11. The size of the air outlet 17 is formed to be smaller than the distance between the opposing pair of side faces 13, 13. Further, on the bottom of the frame 3, a corner portion 14 is formed which is defined by the lower portion of the side surface 13 and the outer peripheral portion of the bottom surface 11.

The simulation software was Fluent (registered trademark) using ANSYS (ANSYS Japan KK), and the air volume was set to 14000 m ³ /h. The plurality of arrows indicate the size and direction of the airflow of the air A in each part in the casing 3. The black dot indicates the position of the measurement point, the length of the arrow indicates the magnitude of the wind speed, and the direction of the arrow indicates the direction of the airflow. .

The air A is blown from the centrifugal fan 5 to the side, and then is wound from the outer peripheral side of the disk-shaped flow regulating plate 7 to the lower side, and is surrounded by the disk-shaped flow regulating plate 7, the side surface 13 of the frame 3, and the bottom surface 11. Forming weaker eddy currents 61, 63. That is, the flow rate of the air A constituting the eddy currents 61, 63 is smaller than that of the comparative example of Fig. 9 to be described later. In Fig. 6, since the cross section is shown, it appears that a pair of eddy currents 61 and 63 are generated on the right and left sides, but the eddy currents 61 and 63 are integrally formed in an annular shape along the circumferential direction. Further, in the air outlets 17 of the bottom surface 11, air A of substantially the same direction and substantially the same size is blown at almost uniform intervals along the respective portions in the width direction. As a result, the wind speed distribution in the air outlet 17 is good, and the pressure loss is small.

(Second embodiment)

Next, as shown in Fig. 7, in correspondence with the second embodiment, the annular flow regulating plate 41 is disposed below the centrifugal fan 5, and the air flow of the air A in the casing 3 is simulated. The simulation conditions are the same as in the first embodiment.

The air A is blown from the centrifugal fan 5 to the side, and then is wound from the outer peripheral side of the annular flow regulating plate 41 to the lower side, and is surrounded by the annular flow regulating plate 41, the side surface 13 of the casing 3, and the bottom surface 11. At the same time, weaker eddy currents 65, 67 are formed. Further, the air A is directed from the hole in the central portion of the annular flow regulating plate 41. Flowing below. Here, since the airflow on the inner circumferential side of the eddy currents 65, 67 faces upward, the airflow flowing from the hole in the central portion of the annular flow regulating plate 41 faces downward, and therefore the two are opposed to each other, resulting in the eddy currents 65, 67 being smaller in size. The eddy currents 61, 63 of the first embodiment. Further, at the air outlet 17 of the bottom surface 11, air A of substantially the same direction and substantially the same size is blown at a substantially uniform interval in a wide range of the central portion in the radial direction. As a result, the wind speed distribution in the air outlet 17 is better and the pressure loss is smaller than in the first embodiment.

(Third embodiment)

Next, as shown in Fig. 8, in accordance with the third embodiment, a truncated cone-shaped rectifying plate 51 is disposed below the centrifugal fan 5, and the flow of the air A in the casing 3 is simulated. The simulation conditions are the same as in the first embodiment and the second embodiment.

The air A is blown from the centrifugal fan 5 to the side, and then is wound from the outer peripheral side of the truncated cone-shaped rectifying plate 51 to the lower side, and is surrounded by the truncated cone-shaped rectifying plate 51, the side surface 13 of the casing 3, and the bottom surface 11. At the same time, weaker eddies 69, 71 are formed. Further, in the air outlet 17 of the bottom surface 11, air A of substantially the same direction and substantially the same size is blown at a substantially uniform interval in a wide range of the central portion in the radial direction. As a result, the wind speed distribution in the air outlet 17 is better and the pressure loss is smaller than in the first embodiment and the second embodiment.

(Comparative example)

Next, as shown in Fig. 9, as a comparative example, a rectifying plate was not disposed below the centrifugal fan 5, and at this time, the airflow of A in the casing 3 was carried out. simulation. The simulation conditions are the same as those of the first to third embodiments.

The air A is blown from the centrifugal fan 5 to the side, and then, at a portion surrounded by the centrifugal fan 5, the side surface 13 and the bottom surface 11 of the casing 3, the airflow speed is faster than that of the first to third embodiments described above. Eddy currents 73, 75. Further, in the air outlet 17 of the bottom surface 11, the wind speed is reduced at the central portion in the radial direction, and the wind speed is increased in the outer side in the width direction. As a result, compared with the first to third embodiments, the wind speed distribution in the air outlet 17 becomes uneven, resulting in a large pressure loss. Further, it has been confirmed that a portion 77 having a particularly high wind speed is generated in the vicinity of the lower right side of the centrifugal fan 5, and it is estimated that a pressure loss occurs at this portion.

[Relationship between static pressure and static pressure efficiency and air volume]

Hereinafter, the relationship between the static pressure and the static pressure efficiency and the air volume will be described using Figs. 10 to 17 . In addition, the simulation software is using Fluent of ANSYS.

In the tenth and eleventh drawings, the case where the rectifying plate 1008 has no holes is a case where a disk-shaped rectifying plate having an outer diameter of 1008 mm is used (invention example); "the rectifying plate 1008-750 has a hole" means The case of an annular rectifying plate (inventive example) having an outer diameter of 1008 mm and an inner diameter of 750 mm was used. In addition, the "comparative example (cited document)" is a case where the conical curved guide of the cited document 1 cited in the above-mentioned background art is used, and the "comparative example (without rectifying plate)" is a case where the rectifying plate is not provided. As shown in Figs. 10 and 11, it can be seen that the present invention exemplifies a higher static pressure and static pressure efficiency than the comparative example in the range of almost all air volumes.

In Fig. 12 and Fig. 13, the annular rectifying plate (example of the present invention) and a comparative example were compared. In addition, regarding the size of the annular rectifying plate, relative to The outer diameter is 1008 mm, and the inner diameter changes to 625 mm, 750 mm, and 875 mm. Further, with respect to the outer diameter of 945 mm, the inner diameter changes to three types of 625 mm, 750 mm, and 875 mm. As shown in Fig. 12 and Fig. 13, it can be seen that in the range of almost all air volumes, the present invention exemplifies higher static pressure and static pressure efficiency than the comparative examples.

In Fig. 14 and Fig. 15, the annular rectifying plate (example of the present invention) and a comparative example were compared. In addition, regarding the size of the annular flow regulating plate, the outer diameter changes to 819 mm, 882 mm, 945 mm, and 1008 mm with respect to the inner diameter of 750 mm. As shown in Fig. 14 and Fig. 15, it can be seen that the present invention exemplifies higher static pressure and static pressure efficiency with respect to the comparative example in the range of almost all air volumes.

In Fig. 16 and Fig. 17, the truncated cone-shaped rectifying plate 51 (example of the present invention) and a comparative example were compared. Further, as shown in Fig. 16(a), the truncated cone-shaped rectifying plate 51 is disposed only 50 mm below the centrifugal fan 5. Regarding the size of the truncated cone-shaped rectifying plate 51, the outer diameter was 1008 mm and the inner diameter was 750 mm. Further, the inclination angle of the side surface 53 is changed to 0 (no inclination), 10 or 20 degrees. As shown in Figs. 16(b) and 17 , it can be seen that in the range of almost all air volumes, the present invention exemplifies higher static pressure and static pressure efficiency than the comparative examples.

Further, the present invention exemplifies the foregoing embodiment, since the size of each portion of the air blowing unit 1 exhibits similar characteristics in a similarly shaped air blowing unit, and according to the proportional law of the blower, static pressure, static pressure efficiency, and The value of the air volume is not limited to the embodiment, and various modifications can be made without departing from the scope of the invention.

Next, the effects of the present embodiment will be described.

(1) The air blowing unit 1 according to the present embodiment includes a casing 3 having an intake port 15 and an air outlet 17, and the side portion is surrounded by the plurality of side faces 13; and the centrifugal fan 5 is housed in the casing 3 And the width dimension Wo of the air outlet 17 provided on the bottom surface 11 of the frame 3 is formed to be smaller than the distance Wc1 between the opposing pair of side faces 13, 13 of the plurality of side faces 13 . A rectifying plate (a disk-shaped rectifying plate 7, an annular rectifying plate 41, and a truncated-cone rectifying plate 51) is disposed between the centrifugal fan 5 and the air outlet 17 inside the casing 3, and the rectifying plate The outer diameter is larger than the outer diameter Df of the centrifugal fan 5 described above, and the outer peripheral edge is formed in a circular shape.

Since the width dimension Wo of the air outlet 17 is smaller than the distance Wc1 between the opposing pair of side faces 13 and 13 of the plurality of side faces 13, the side face 13 and the bottom face 11 intersect in the inside of the frame body 3. At the portion, a corner portion 14 is formed. Therefore, since the air A blown out from the centrifugal fan 5 collides with the bottom surface 11 of the corner portion 14 along the side surface 13, a vortex is formed, so that the wind speed distribution of the air A discharged from the air outlet 17 is in the radial direction. The location becomes unequal, resulting in an increase in pressure loss.

On the other hand, in the present invention, since the rectifying plate 7, the rectifying plate 41, and the rectifying plate 51 are disposed, the airflow of the air A blown from the centrifugal fan 5 is rectified, compared to the case where the rectifying plate is not provided. The eddy current becomes smaller. Therefore, the wind speed distribution of the air A discharged from the air outlet 17 becomes uniform at each portion along the radial direction, and thus the pressure loss becomes small.

(2) The above-mentioned flow regulating plate is a disk-shaped flow regulating plate 7 formed as a circular plate. In this way, since the shape of the rectifying plate is very simple, the number of manufacturing man-hours is also small.

(3) The rectifying plate is an annular rectifying plate 41 having a circular hole 41a formed in a central portion of the circular plate. In this way, since the shape of the rectifying plate is very simple, the number of manufacturing man-hours is also small. Further, as described in the second embodiment, since the airflow on the inner circumferential side of the eddy currents 65 and 67 faces upward, the airflow flowing from the hole 41a in the central portion of the annular flow regulating plate 41 faces downward, and therefore the two are in contact with each other. This causes the size of the eddy currents 65, 67 to become smaller.

(4) The rectifying plate is a truncated cone-shaped rectifying plate 51 having a circular hole 51a formed in a central portion thereof and formed in a truncated cone shape, and the side surface 53 is from the center to the outer periphery. Tilt to the downstream side of the airflow. Therefore, since the air A blown from the centrifugal fan 5 flows obliquely along the inclined side surface 53, and also flows from the hole 51a of the central portion to the downstream side, the eddy current becomes smaller.

(5) The outer diameters (Dpa, Dpb, Dpc) of the rectifying plate are set to be 150 to 170% of the outer diameter Df of the centrifugal fan 5. When it is less than 150%, the outer diameter of the rectifying plate is too small, so that the rectifying effect of the air A by the rectifying plate becomes small. Further, when it is more than 170%, the outer diameter of the rectifying plate is too large, so that the gap between the rectifying plate and the side surface 13 of the frame 3 is too small, and the flow velocity of the air A flowing from the slit to the downstream side becomes large, resulting in an increase in pressure loss. , performance is reduced.

(6) The difference in size (Dpb-dpb) between the outer diameter Dpb and the inner diameter dpb of the annular flow regulating plate 41 is set to 20 to 60% of the outer diameter Df of the centrifugal fan 5. When the dimensional difference (Dpb-dpb) of the annular flow regulating plate 41 is less than 20% of the outer diameter Df of the centrifugal fan 5, since the area to be rectified on the annular flow regulating plate 41 is too small, the rectifying effect is insufficient. Also, when it is greater than 60%, due to The amount of air A passing through the center hole is too small, and the effect of reducing the eddy current is small, which is not preferable.

(7) The inclination angle θ of the side surface 53 of the truncated cone-shaped rectifying plate 51 is set to be 0 to 20° in the side view. When the inclination angle θ is larger than 20°, the side surface 53 is too close to the vertical direction, resulting in a small rectifying effect of the air A.

Claims (7)

A blower unit comprising: a casing having an upper air inlet and a lower air outlet, the side portion being surrounded by a plurality of side surfaces; and the centrifugal fan being housed inside the casing; a centrifugal fan having: a main plate; a side plate disposed above the main plate and having an air suction port; and a blade disposed between the main plate and the side plate, and spaced apart in a circumferential direction and at a specific interval a plurality of the air outlets provided on the bottom surface of the frame body are formed to be smaller than a distance between the pair of opposite side faces of the plurality of side faces, and are inside the frame body a corner portion is formed at a portion where the side surface intersects the bottom surface, and a centrifugal portion is disposed between the centrifugal fan and the air outlet in the interior of the frame body and below the centrifugal fan a flat plate rectifying plate having an outer diameter larger than an outer diameter of the centrifugal fan, and the outer peripheral edge is formed in a circular shape from the aforementioned suction port of the centrifugal fan The sucked air is blown out in the side direction of the centrifugal fan along the blade, and then is formed from the side of the outer peripheral edge of the flow regulating plate to the lower side, and is discharged from the air outlet, and the air outlet is The width dimension is smaller than the outer diameter of the aforementioned rectifying plate. The air blowing unit according to claim 1, wherein the rectifying plate is a disk-shaped rectifying plate formed as a circular plate. The air blowing unit according to claim 1, wherein the rectifying plate is an annular rectifying plate, and the annular rectifying plate has a circular hole formed in a central portion of the circular plate. The air blowing unit according to claim 3, wherein a difference in size between an outer diameter and an inner diameter of the annular flow regulating plate is set to be 20 to 60% of an outer diameter of the centrifugal fan. A blower unit comprising: a casing having an upper air inlet and a lower air outlet, the side portion being surrounded by a plurality of side surfaces; and the centrifugal fan being housed inside the casing; a centrifugal fan having: a main plate; a side plate disposed above the main plate and having an air suction port; and a blade disposed between the main plate and the side plate, and spaced apart in a circumferential direction and at a specific interval a plurality of the air outlets provided on the bottom surface of the frame body are formed to be smaller than a distance between the pair of opposite side faces of the plurality of side faces, and are inside the frame body a corner portion is formed at a portion where the side surface intersects the bottom surface, and a centrifugal portion is disposed between the centrifugal fan and the air outlet in the interior of the frame body and below the centrifugal fan The rectifying plate has an outer diameter larger than an outer diameter of the centrifugal fan, and the outer peripheral edge is formed into a circular shape. The air sucked from the intake port of the centrifugal fan is blown out toward the side of the centrifugal fan along the vane, and then is wound from the side of the outer peripheral edge of the rectifying plate to the lower side, and from the foregoing The air outlet is configured to be exhausted, and the rectifying plate is a truncated cone-shaped rectifying plate having a circular hole formed in the center portion through which air passes, and is formed in a truncated cone shape, and the side surface is formed The center is inclined toward the downstream side of the airflow toward the outer circumference. The air blowing unit according to any one of claims 1 to 3, wherein the outer diameter of the rectifying plate is set to be 150 to 170% of an outer diameter of the centrifugal fan. The air blowing unit according to claim 5, wherein the inclination angle of the side surface of the truncated cone-shaped rectifying plate is set to 0 to 20° in the side view.