WO2022255267A1

WO2022255267A1 - Centrifugal blower

Info

Publication number: WO2022255267A1
Application number: PCT/JP2022/021803
Authority: WO
Inventors: 麻里深田; 千秋駒田; 修三小田; 潤山岡; 誠文川島
Original assignee: 株式会社デンソー
Priority date: 2021-06-02
Filing date: 2022-05-27
Publication date: 2022-12-08
Also published as: JP2022185275A

Abstract

A centrifugal blower (1) comprises a main plate (10), a shroud (20), and a plurality of blades (30). Leading edges (31) of the blades (30) are provided radially inward of an inner peripheral wall (211) of an opening part (21) of the shroud (20). Lower parts (71) and higher parts (72) are provided on the surfaces of the leading edges (31) that face away from the main plate (10). The lower parts (71) are positioned radially inward of connecting locations (73) between the blades (30) and the inner peripheral wall (211) of the opening part (21) of the shroud (20) and nearer to the main plate (10) than the connecting locations (73), and are provided so as to extend along a plane perpendicular to an axis (CL). The higher parts (72) are positioned radially inward of the lower parts (71) and on the sides of the lower parts (71) that are opposite to the main plate (10). Recessed shapes (70) are formed by the lower parts (71) and the higher parts (72) in the surfaces of the leading edges (31) that face away from the main plate (10).

Description

centrifugal blower

Cross-references to related applications

This application is based on Japanese Patent Application No. 2021-92832 filed on June 2, 2021, the contents of which are incorporated herein by reference.

The present disclosure relates to a centrifugal blower that blows air taken in from one of the axial directions of rotation of an impeller in a direction away from the axial center.

Conventionally, a centrifugal fan is known in which an impeller having a main plate, a shroud, and a plurality of blades is rotatably provided inside a case (see Patent Document 1). The impeller of the centrifugal blower described in Patent Document 1 has a leading edge of the blade on the side closer to the axis of rotation than the inner peripheral wall of the opening provided in the center of the shroud. A surface of the front edge facing away from the main plate extends perpendicularly to the axis.

JP 2019-203481 A

According to the studies of the inventors, in the centrifugal fan, the air flowing from the air suction port provided in the case into the flow path (hereinafter referred to as "inter-blade flow path") formed between a plurality of blades. It has a characteristic that it flows toward the main plate and is less likely to flow along the surface of the shroud on the inter-blade flow path side (hereinafter referred to as the "back surface of the shroud"). Therefore, when the air flowing into the inter-blade passage from the air suction port separates from the rear surface of the shroud and the vortex generated by the separation (hereinafter referred to as "separation vortex") becomes larger, there arises a problem that noise increases. Regarding such a problem, the centrifugal fan described in Patent Document 1 has room for improvement in terms of blade shape.
An object of the present disclosure is to reduce noise in a centrifugal fan.

According to one aspect of the present disclosure, in a centrifugal fan,
a rotatably provided main plate;
an annular shroud facing the main plate and having an opening in the center through which air flows;
a plurality of blades arranged at predetermined intervals around an axis serving as a center of rotation between the shroud and the main plate and connected to the shroud and the main plate;
When defining a virtual circle centered on the axis on a virtual plane perpendicular to the axis, the side closer to the axis in the radial direction of the virtual circle is called the radial inner side, and the opposite side is called the radial outer side,
The leading edge of the wing is provided radially inward from the inner peripheral wall of the opening of the shroud,
The surface of the leading edge facing away from the main plate is located radially inward of the connection point between the inner peripheral wall of the opening of the shroud and the blade and is located closer to the main plate than the connection point, and is positioned relative to the axis. a lower portion provided along a vertical plane, and a higher portion located radially inside the lower portion and on the opposite side of the main plate to the lower portion,
The low portion and the high portion form a concave shape on the surface of the front edge facing away from the main plate.

According to this, the air flowing into the inter-blade passage from the opening of the shroud is caused by the Coanda effect in which the air flows along the concave shape formed on the leading edge of the blade, and the direction of the air flow is changed to the shape of the back surface of the shroud. get close to Therefore, separation of the air flowing into the inter-blade passage from the opening of the shroud is suppressed from the rear surface of the shroud, and the separation vortex is reduced, thereby reducing noise.

In addition, the efficiency of the blower is improved by suppressing the separation of air from the back surface of the shroud. Therefore, under the condition of the same air volume, the number of rotations of the blower can be lowered, and the vibration caused by the rotation is reduced, so that the noise can be reduced.

It should be noted that the reference numerals in parentheses attached to each component etc. indicate an example of the correspondence relationship between the component etc. and the specific component etc. described in the embodiment described later.

1 is a plan view of a centrifugal fan according to a first embodiment; FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1; FIG. It is a figure which shows a part of impeller and a part of upper case in the cross section of the III-III line of FIG. 4 is an enlarged view of the leading edge of the blade shown in FIG. 3 and its vicinity; FIG. FIG. 5 is an enlarged view of the V portion of FIG. 4; 5 is a cross-sectional view taken along the line VI-VI of FIG. 4; FIG. FIG. 5 is an explanatory diagram for explaining the flow of air from the air suction port to the inter-blade passage at the same location as in FIG. 4 ; In the centrifugal fan concerning a 1st embodiment, it is an experimental result which shows the relation between the depth of dent shape, and noise. 5 is an enlarged view of a portion corresponding to FIG. 4 in the centrifugal fan according to the second embodiment; FIG. It is an enlarged view of the part corresponding to FIG. 4 in the centrifugal fan which concerns on 3rd Embodiment. 5 is an enlarged view of a portion corresponding to FIG. 4 in a centrifugal fan of a comparative example; FIG.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In addition, in each of the following embodiments, the same or equivalent portions are denoted by the same reference numerals, and description thereof will be omitted.

(First embodiment)
A centrifugal fan according to the first embodiment will be described. Hereinafter, the centrifugal blower is simply referred to as "blower". As shown in FIGS. 1 to 3, the blower 1 of the first embodiment includes an impeller 2 composed of a main plate 10, a shroud 20, a plurality of blades 30, etc., a motor 40 for rotating the impeller 2, A case 50 that houses the impeller 2 and the motor 40 is provided. The blower 1 is used for various purposes such as, for example, a vehicle seat air conditioner, an air conditioner, or a ventilator.

In the following description, a virtual circle centered on the axis CL is defined on a virtual plane perpendicular to the rotation axis CL of the impeller 2. The radially opposite side of the imaginary circle from the axis CL is called the radially outer side. Also, the direction in which the axis CL extends is referred to as the "axis direction".

The configuration of the impeller 2 will be explained. The main plate 10 of the impeller 2 is rotatable by the torque output by the motor 40 . The main plate 10 includes a central portion 11 fixed to the rotating shaft 41 of the motor 40, a fixed portion 12 fixed to the radially outer wall of the central portion 11, and a radially outer side of the fixed portion 12. and an annular portion 13 joined to a plurality of blades 30 . The central portion 11 of the main plate 10 is formed in a mountain shape that gradually moves away from the air suction port 51 of the upper case 53 radially outward from the rotating shaft 41 side. Therefore, the central portion 11 of the main plate 10 directs the air sucked from the air suction port 51 of the upper case 53 to the flow path (hereinafter referred to as "inter-blade flow path") formed between the plurality of blades 30. It functions as a guiding guide surface. Note that the central portion 11 of the main plate 10 forms part of a motor rotor 42, which will be described later. The fixing portion 12 of the main plate 10 is used to fix the plurality of blades 30 and the shroud 20 integrally formed with the fixing portion 12 to the motor rotor 42 .

The shroud 20 is provided so as to face the main plate 10 in the axial direction. The shroud 20 has an opening 21 in the center through which air flows. Therefore, the shroud 20 is formed in an annular shape. The shroud 20 has a tubular shroud portion 22 extending from the inner peripheral edge on the opening 21 side toward the side opposite to the main plate 10 . The shroud 20 also has a plurality of shroud-side projections 23 extending cylindrically toward the side opposite to the main plate 10 at radially outer positions of the shroud tubular portion 22 . In this embodiment, three shroud-side projections 23 are provided.

The plurality of blades 30 are provided between the shroud 20 and the main plate 10 and arranged at predetermined intervals around the axis CL, which is the center of rotation of the impeller 2 . A plurality of wings 30 extend rearward in the direction of rotation from leading edge 31 toward trailing edge 32 . That is, the impeller 2 of this embodiment is a turbofan. An end portion 33 of the blade 30 on the shroud 20 side in the axial direction is connected to the shroud 20 . An end portion 34 of the blade 30 on the axial main plate 10 side is connected to the fixed portion 12 and the annular portion 13 of the main plate 10 . Therefore, the impeller 2 of this embodiment is a closed fan.

In this embodiment, the leading edge 31 of the blade 30 is provided radially inward of the inner peripheral wall 211 of the opening 21 of the shroud 20 . In the following description, the leading edge 31 of the blade 30 may be referred to as "wing leading edge 31". The shape of the blade leading edge 31 will be described later in detail.

The case 50 has an upper case 53 and a lower case 54. The upper case 53 is a member that covers the shroud 20 side of the impeller 2 . The lower case 54 is a member that covers the main plate 10 side of the impeller 2 and houses the motor 40 and the circuit board 60 . The upper case 53 and the lower case 54 are fixed to each other with a predetermined gap therebetween by means of struts and screws (not shown). In addition, in FIG. 1 , the position where a column or the like is provided between the upper case 53 and the lower case 54 is indicated by a circle with reference numeral 55 .

The upper case 53 has an upper case main body 56 , an air suction port 51 and a bell mouth 57 . The upper case body portion 56 covers the surface of the shroud 20 opposite to the main plate 10 . The air suction port 51 is provided at a position corresponding to the opening 21 of the shroud 20 in the upper case main body 56 . The bell mouth 57 extends cylindrically from the inner peripheral edge of the air suction port 51 toward the main plate 10 side. The bellmouth 57 is a part that introduces air into the impeller 2 from the outside. Therefore, the corner portion of the bell mouth 57 on the side opposite to the main plate 10 is curved, and the end portion of the bell mouth 57 on the side of the main plate 10 is also curved.

In addition, the upper case 53 has a plurality of case-side projections 52 extending cylindrically toward the shroud 20 at radially outer positions of the bell mouth 57 . In this embodiment, two case-side projections 52 are provided. The two case-side projections 52 are provided between the three shroud-side projections 23 provided on the shroud 20 . Therefore, a labyrinth portion 26 is formed by the case-side projection 52 and the shroud-side projection 23 in the gap channel 25 between the upper case 53 and the shroud 20 .

The lower case 54 has a lower case main body portion 58 that covers the main plate 10 side of the impeller 2 and a central tubular portion 59 provided in the center of the lower case main body portion 58 . A rotating shaft 41 of the motor 40 and a motor stator 43 are attached to the central cylindrical portion 59 . Note that, in this embodiment, for example, an outer rotor type brushless DC motor is employed as the motor 40 .

A rotating shaft 41 of the motor 40 is rotatably provided inside the central tubular portion 59 via a bearing 44 . A center portion 11 of a motor rotor 42 is fixed to an axial end portion of a rotating shaft 41 of the motor 40 . The motor rotor 42 includes the central portion 11 of the main plate 10 , the magnet holding portion 14 extending from the outer edge of the central portion 11 of the main plate 10 in the axial direction opposite to the shroud 20 , and the magnet holding portion 14 radially inward of the magnet holding portion 14 . and a magnet 45 provided in the . The fixing portion 12 of the main plate 10 is fixed to the radially outer wall of the magnet holding portion 14 by press fitting or the like. Thereby, the motor rotor 42 and the impeller 2 are joined. The magnets 45 provided radially inside the magnet holding portion 14 have magnetic poles of different types alternately arranged in the circumferential direction of the magnet holding portion 14 .

A motor stator 43 is provided radially inside the magnet 45 . The motor stator 43 is fixed to the radially outer surface of the central tubular portion 59 . The motor stator 43 has a three-phase coil 46 and a stator core 461 configured by Y-connection or Δ-connection, for example. A three-phase alternating current is supplied from a circuit board 60 to the three-phase coil 46 .

In the above-described configuration, when electric power and drive signals are supplied from the connector 47 to the circuit board 60, the circuit board 60 supplies three-phase alternating current to the three-phase coils 46 of the motor stator 43. The impeller 2 rotates together. When the impeller 2 rotates, as indicated by arrow AF1 in FIG. direction outward.

Next, the shape of the blade leading edge 31 will be described in detail.

As shown in FIG. 4 , the blade leading edge 31 is a portion of the blade 30 provided radially inward of the inner peripheral wall 211 of the opening 21 of the shroud 20 . A concave shape 70 is formed on a surface of the blade leading edge 31 facing away from the main plate 10 . A recessed shape 70 is formed by a lower portion 71 and a higher portion 72 .

The lower portion 71 is located radially inward of a connecting point 73 between the inner peripheral wall 211 of the opening 21 of the shroud 20 and the blade 30 and closer to the main plate 10 than the connecting point 73 . The low portion 71 is provided along a plane perpendicular to the axis CL. In this specification, "the lower portion 71 is provided along a plane perpendicular to the axis CL" includes the following states. That is, when the low-level portion 71 is viewed from the rotation direction of the blade 30, the low-level portion 71 is parallel to a virtual plane perpendicular to the axis CL, and the low-level portion 71 is parallel to the virtual plane. It also includes a slightly curved or tilted state.

The high-level portion 72 is located radially inward of the low-level portion 71 and on the side opposite to the main plate 10 with respect to the low-level portion 71 . The high portion 72 has substantially the same height as the connecting portion 73 between the inner peripheral wall 211 of the opening 21 of the shroud 20 and the blade 30 in the axial direction. In addition, the high portion 72 may be located closer to the main plate 10 than the connecting portion 73 in the axial direction, or may be located on the side opposite to the main plate 10 than the connecting portion 73 . .

The low portion 71 and the high portion 72 are connected by a smooth curved surface. Specifically, as shown in FIG. 5, which is an enlarged view of the V portion of FIG. there is The first curved surface 74 is a curved surface that is convex toward the air suction port 51 side (that is, the side opposite to the main plate 10 ) on the low portion 71 side of the high portion 72 . The second curved surface 75 is a curved surface that is radially outward of the first curved surface 74 (that is, is closer to the lower portion 71 than the first curved surface 74) and protrudes toward the main plate 10 side.

In FIG. 5, the point of contact between the arc of the portion radially inner than the first curved surface 74 and the arc of the first curved surface 74 is indicated by P1. In FIG. 5, the point of contact between the arc of the first curved surface 74 and the arc of the second curved surface 75 is denoted by P2. Furthermore, in FIG. 5, the point of contact between the arc of the second curved surface 75 and the arc of the radially outer portion of the second curved surface 75 is indicated by P3. Here, when the blade leading edge 31 is viewed from the rotational direction of the blade 30, the radius of curvature of the first curved surface 74 is R1, and the radius of curvature of the second curved surface 75 is R2. At this time, the curvature radius R1 of the first curved surface 74 and the curvature radius R2 of the second curved surface 75 have a relationship of R1>R2. Although illustration is omitted, a flat surface may be provided between the first curved surface 74 and the second curved surface 75, or the first curved surface 74 and the second curved surface 75 may have a flat surface in part thereof. may be

FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. That is, FIG. 6 is a cross-sectional view of the lower portion 71 of the blade leading edge 31 taken along a plane perpendicular to the direction in which the blade 30 extends from the leading edge 31 to the trailing edge 32 . In the cross section shown in FIG. 6, the curvature radius of the corner portion 36 of the low portion 71 on the suction surface 35 side is R3, and the curvature radius of the corner portion 38 of the low portion 71 on the pressure surface 37 side is R4. At this time, the curvature radius R1 of the first curved surface 74, the curvature radius R2 of the second curved surface 75, the curvature radius R3 of the corner portion 36 on the suction surface 35 side of the low portion 71, and the curvature radius R3 of the low portion 71 on the pressure surface 37 side are: The curvature radius R4 of the corner portion 38 has the relationships of R1>R3>R4 and R2>R3>R4.

Further, as shown in FIG. 4 , the blade 30 has an upright wall portion 39 between the lower portion 71 and the connection point 73 between the inner peripheral wall 211 of the opening 21 of the shroud 20 and the blade 30 . The standing wall portion 39 is provided parallel to the inner peripheral wall 211 of the opening portion 21 of the shroud 20 . A portion 391 where the standing wall portion 39 and the lower portion 71 are connected is curved. That is, both the radially outer portion 391 of the low portion 71 and the radially inner portion of the low portion 71 (that is, the second curved surface 75) are curved surfaces.

As shown in FIG. 4, in this embodiment, the distance Da between the point or surface of the low portion 71 that is closest to the main plate 10 and the point or surface of the high portion 72 that is farthest from the main plate 10 is defined as the depth of the concave shape 70. Sa Da". Further, as shown in FIG. 3, the distance Db between the main plate 10 and the shroud 20 on the trailing edge 32 side of the blade 30 is referred to as "blade outlet height Db." The depth Da of the concave shape 70 and the blade outlet height Db have a relationship of 0<Da≦Db×0.09. That is, the depth Da of the concave shape 70 is set to be greater than 0 and equal to or less than 9% of the blade outlet height Db. This is based on the results of experiments conducted by the inventors of the present disclosure, and the results of the experiments will be described later.

Furthermore, as shown in FIG. 3, in this embodiment, the outer diameter of the end of the bell mouth 57 on the main plate side is Dc, and the point or Let Dw be the outer diameter of a circle connecting the planes in the direction of rotation. At this time, the outer diameter Dc of the end portion of the bell mouth 57 on the main plate side and the outer diameter Dw of the point or surface of the lower portion 71 closest to the main plate 10 have a relationship of Dc<Dw. As a result, when the impeller 2 rotates, the air flowing into the inter-blade passage along the inner peripheral wall 571 of the bell mouth 57 hits the concave shape 70 formed in the leading edge 31 of the blade. Air flowing along 70 is susceptible to the Coanda effect.

Although the minimum value of the outer diameter Dc of the bell mouth 57 is not particularly specified, by making the outer diameter Dc of the bell mouth 57 larger than the inner diameter of the high portion 72, the inter-blade flow along the inner peripheral wall 571 of the bell mouth 57 Air entering the channel hits the recessed features 70, making them susceptible to the Coanda effect.

A stepped portion 82 in which concave portions 80 and convex portions 81 are alternately arranged in the axial direction is provided on the surface of the front edge 31 of the blade 30 facing radially inward. The stepped portion 82 is also called a serration portion. The stepped portion 82 is provided at a position on the leading edge 31 of the blade at a predetermined distance from the main plate 10 .

Here, a blower 100 of a comparative example will be described for comparison with the blower 1 of the first embodiment described above.

As shown in FIG. 11 , also in the fan 100 of the comparative example, the blade leading edge 31 is provided radially inward of the inner peripheral wall 211 of the opening 21 of the shroud 20 . However, in blower 100 of the comparative example, surface 101 of blade leading edge 31 facing away from main plate 10 is not recessed. That is, in the comparative example, when the blade leading edge 31 is viewed from the rotation direction of the blade 30, the surface 101 of the blade leading edge 31 facing the side opposite to the main plate 10 is the inner peripheral wall 211 of the opening 21 of the shroud 20. A surface perpendicular to the axis CL extends radially inward from a connection point 73 with the blade 30 .

In the comparative example, when the impeller 2 rotates, as indicated by the arrow AF2 in FIG. Among them, it has a characteristic that it is difficult to flow along the surface 201 on the inter-blade passage side. Hereinafter, the surface 201 of the shroud 20 on the inter-blade flow path side is referred to as a "shroud back surface 201". In the comparative example, due to the above characteristics, the air flowing into the inter-blade passage from the opening 21 of the shroud 20 is separated from the shroud back surface 201, and when the separation vortex SV generated by this separation increases, noise increases. occurs.

On the other hand, the blower 1 of the first embodiment has the following effects as shown in FIG. That is, in the blower 1 of the first embodiment, when the impeller 2 rotates, as indicated by the arrow AF3 in FIG. The orientation is close to the shape of the shroud back surface 201 . This is due to the Coanda effect in which air flows along the concave shape 70 formed in the leading edge 31 of the blade. The concave shape 70 is a shape effective for generating the Coanda effect on the air flowing into the inter-blade passage from the air suction port 51 . Therefore, the air that flows into the inter-blade passage after flowing along the concave shape 70 is suppressed from being separated from the shroud back surface 201 . Therefore, in the blower 1 of the first embodiment, the separation vortex SV near the shroud back surface 201 is reduced, so noise can be reduced.

FIG. 3 also shows the distance Dh between the end portion 221 of the shroud tubular portion 22 opposite to the main plate 10 and the lower portion 71 of the concave shape 70 . In the first embodiment, the recessed shape 70 is formed on the surface of the blade leading edge 31 facing away from the main plate 10, so that the end portion 221 of the shroud tubular portion 22 on the side opposite to the main plate 10 and the recessed shape A distance Dh between the fan 70 and the lower part 71 is longer than that of the blower 100 of the comparative example. Therefore, air flowing backward from the radially outer air outlet 24 of the impeller 2 to the opening 21 side of the shroud 20 through the clearance flow path 25 between the upper case 53 and the shroud 20 (hereinafter referred to as "backflow air"). , the flow velocity when colliding with the low portion 71 of the concave shape 70 can be slowed down. Since the magnitude of noise is generally proportional to the sixth power of the flow velocity, the noise can be reduced by slowing down the flow velocity.

Next, FIG. 8 shows the results of an experiment conducted on the relationship between the depth of the recessed shape 70 and noise in the blower 1 according to the first embodiment.

The horizontal axis of the graph in FIG. 8 indicates the depth Da of the recessed shape 70 as a ratio to the blade outlet height Db. It should be noted that the depth Da of the concave shape 70 being 0% is the same as the configuration of the blower 100 of the comparative example described above. On the other hand, the vertical axis of the graph in FIG. 8 indicates the noise level (that is, the A-weighted sound pressure level). In this experiment, a blower having a blade outlet height Db of 4 mm was used, and the noise level was measured when the motor 40 was energized and the impeller 2 was rotated at a constant number of revolutions.

As shown in the graph of FIG. 8, this experiment showed that the noise level could be reduced when the depth Da of the concave shape 70 was greater than 0 and less than or equal to 9%. In other words, it was found through experiments that the noise reduction effect can be obtained when the relationship between the depth Da of the concave shape 70 and the blade outlet height Db is 0<Da≦Db×0.09. Further, it was found that a greater noise reduction effect can be obtained by setting the depth Da of the concave shape 70 to 1 to 8%, more preferably 2 to 7%, of the blade outlet height Db. Specifically, in the blower used in the experiment, when the depth Da of the recessed shape 70 is 5% of the blade outlet height Db, the noise level can be reduced by 0.4 dBA compared to the blower 100 of the comparative example. was gotten.

The blower 1 of the first embodiment described above has the following effects.

(1) In the blower 1 of the first embodiment, a concave shape 70 is formed by a low portion 71 and a high portion 72 on the surface of the blade leading edge 31 facing away from the main plate 10 . According to this, the air flowing from the air inlet 51 of the upper case 53 through the opening 21 of the shroud 20 into the inter-blade flow path flows along the concave shape 70 formed in the leading edge 31 of the blade. Due to the Coanda effect, the direction of the airflow approaches the shape of the shroud back surface 201 . Therefore, separation of the air flowing into the inter-blade passage through the opening 21 of the shroud 20 from the shroud back surface 201 is suppressed, and the separation vortex SV is reduced, so that noise can be reduced.

In addition, by forming the concave shape 70 on the surface of the blade 30 facing away from the main plate 10, the end portion 221 of the shroud tubular portion 22 on the side opposite to the main plate 10 and the lower portion 71 of the concave shape 70 are formed. becomes farther. Therefore, the backflow air flowing back from the radially outer air outlet 24 of the impeller 2 to the opening 21 side of the shroud 20 through the clearance flow path 25 slows down the flow velocity when it collides with the low portion 71 of the concave shape 70. can do. Since the magnitude of noise is generally proportional to the sixth power of the flow velocity, the noise can be reduced by slowing down the flow velocity.

Furthermore, the efficiency of the blower 1 is improved by suppressing the separation of air from the shroud back surface 201 . Therefore, under the condition of the same air volume, the number of rotations of the blower 1 can be lowered, and the vibration caused by the rotation is reduced, so that the noise can be reduced.

(2) In the first embodiment, the outer diameter Dc of the bell mouth 57 of the upper case 53 and the outer diameter Dw of the point or surface of the lower portion 71 closest to the main plate 10 have a relationship of Dc<Dw. is doing.
According to this, the air flowing into the inter-blade passage along the inner peripheral wall 571 of the bell mouth 57 hits the concave shape 70 formed in the blade leading edge 31, so the Coanda effect in which the air flows along the concave shape 70 become more susceptible to Therefore, separation of air from the shroud back surface 201 is suppressed, and the separation vortex SV is reduced, thereby reducing noise.
Noise can also be reduced by slowing down the flow velocity of the backflow air when it collides with the low portion 71 of the concave shape 70 .

(3) In the first embodiment, the connection points between the low portion 71 and the high portion 72 (that is, the second curved surface 75 and the first curved surface 74) are curved surfaces.
According to this, turbulence of the airflow at the connecting portion between the low-level portion 71 and the high-level portion 72 can be suppressed, and noise can be reduced.

(4) In the first embodiment, both the radially inner portion (that is, the second curved surface 75) and the radially outer portion 391 of the lower portion 71 are curved surfaces.
According to this, turbulence of the airflow at the radially inner portion (that is, the second curved surface 75 ) and the radially outer portion 391 of the low portion 71 can be suppressed, and noise can be reduced.

(5) In the first embodiment, the curvature radius R1 of the first curved surface 74 connecting the low portion 71 and the high portion 72 and the curvature radius R2 of the second curved surface 75 have a relationship of R1>R2. is doing.
According to this, by increasing the radius of curvature R1 of the first curved surface 74 that encourages the air flowing in from the air suction port 51 of the upper case 53 to flow radially outward, the radial flow component due to the Coanda effect increases. do. Therefore, separation of air from the shroud back surface 201 in the inter-blade passage can be suppressed.

(6) In the first embodiment, the curvature radius R1 of the first curved surface 74, the curvature radius R2 of the second curved surface 75, the curvature radius R3 of the corner portion 36 on the negative pressure surface 35 side of the low portion 71, and the low portion 71 The curvature radius R4 of the corner portion 38 on the side of the pressure surface 37 has the following relationship. That is, R1 to R4 have the relationships of R1>R3>R4 and R2>R3>R4.
According to this, the airflow hitting the concave shape 70 formed in the leading edge 31 of the blade tends to flow in the descending order of the radius of curvature. Therefore, the radius of curvature R<b>1 of the first curved surface 74 and the radius of curvature R<b>2 of the second curved surface 75 increase the flow component in the radial direction, thereby suppressing separation from the shroud back surface 201 . Furthermore, by making the curvature radius R3 of the corner portion 36 of the low portion 71 on the suction surface 35 side larger than the curvature radius R4 of the corner portion 38 of the low portion 71 on the pressure surface 37 side, It is also possible to suppress separation of the airflow flowing into from the negative pressure surface 35 . Therefore, noise can be reduced by reducing the speed variation in the rotating direction of the blades 30 .

(7) In the first embodiment, the depth Da of the concave shape 70 and the blade outlet height Db have a relationship of 0<Da≦Db×0.09.
According to the result of the experiments conducted by the inventors, it was found that the noise reduction effect can be obtained by setting the depth Da of the concave shape 70 to 9% or less of the blade outlet height Db.

(8) In the first embodiment, the shroud 20 has the shroud cylindrical portion 22 that extends cylindrically from the inner peripheral edge on the side of the opening 21 toward the side opposite to the main plate 10 . Wing 30 also has standing wall portion 39 extending from connecting point 73 between inner peripheral wall 211 of opening 21 of shroud 20 and blade 30 toward main plate 10 in parallel with inner peripheral wall 211 of opening 21 of shroud 20 . ing.
This makes it easier for the airflow flowing along the concave shape 70 formed in the blade leading edge 31 to flow to the shroud back surface 201 . Therefore, separation of air from the shroud back surface 201 can be suppressed.

(Second embodiment)
A second embodiment will be described. 2nd Embodiment changes a part of dent shape 70 with respect to 1st Embodiment, Since it is the same as that of 1st Embodiment about others, only a different part from 1st Embodiment is demonstrated. .

As shown in FIG. 9, also in the fan 1 of the second embodiment, a concave shape 70 is formed on the surface of the blade leading edge 31 facing away from the main plate 10 . A recessed shape 70 is formed by a lower portion 71 and a higher portion 72 . In the second embodiment, the first curved surface 74 described in the first embodiment is not provided at the location where the low portion 71 and the high portion 72 are connected. A radially outer portion of the high portion 72 is substantially perpendicular. However, also in the second embodiment, the radially inner portion 751 and the radially outer portion 391 of the lower portion 71 are both curved surfaces. As a result, in the second embodiment, airflow turbulence at the radially inner portion 751 and the radially outer portion 391 of the lower portion 71 can be suppressed, and noise can be reduced.

It should be noted that the blower 1 of the second embodiment also has the same configuration as the first embodiment, except for the configuration described above, so that the same effects as the first embodiment can be obtained.

(Third Embodiment)
A third embodiment will be described. 3rd Embodiment also changes a part of dent shape 70 with respect to 1st Embodiment etc., and since it is the same as that of 1st Embodiment etc. about others, about a part different from 1st Embodiment etc., only explained.

As shown in FIG. 10, also in the fan 1 of the third embodiment, a concave shape 70 is formed on the surface of the blade leading edge 31 facing away from the main plate 10 . A recessed shape 70 is formed by a lower portion 71 and a higher portion 72 . In the third embodiment, as in the first embodiment, the portion where the low portion 71 and the high portion 72 are connected has a first curved surface 74 and a second curved surface 75 . The curvature radius R1 of the first curved surface 74 and the curvature radius R2 of the second curved surface 75 have a relationship of R1>R2. In addition, in the third embodiment, the portion 391 where the lower portion 71 and the standing wall portion 39 are connected is substantially perpendicular.

Also in the blower 1 of the third embodiment, by increasing the curvature radius R1 of the first curved surface 74 that promotes the flow of the air flowing in from the opening 21 of the shroud 20 radially outward, the radial flow due to the Coanda effect component increases. Therefore, separation of air from the shroud back surface 201 can be suppressed.

It should be noted that the blower 1 of the third embodiment also has the same configuration as that of the first embodiment, so that the same effects as those of the first embodiment can be obtained.

(Other embodiments)
(1) In each of the above embodiments, the impeller 2 included in the blower 1 was explained as a turbo fan, but it is not limited to this, and may be a sirocco fan, a radial fan, or a mixed flow fan, for example.

(2) In each of the above embodiments, the motor 40 is described as an outer rotor type brushless DC motor.

(3) In each of the above embodiments, the shroud 20 has the shroud cylindrical portion 22, the shroud-side projection 23, and the like. good.

(4) In each of the above embodiments, the main plate 10 has the central portion 11, the fixed portion 12, the annular portion 13, and the like. 12, annular portion 13, etc. may be integrally constructed.

(5) In each of the above embodiments, the blower 1 has been described as including the case 50 , but the present invention is not limited to this, and the blower 1 may not include the case 50 .

The present disclosure is not limited to the above-described embodiments, and can be modified as appropriate. Moreover, the above-described embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above-described embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential, unless it is explicitly stated that they are essential, or they are clearly considered essential in principle. stomach. In addition, in each of the above-described embodiments, when numerical values such as the number, numerical value, amount, range, etc. of the constituent elements of the embodiment are mentioned, when it is explicitly stated that they are particularly essential, and when they are clearly limited to a specific number in principle It is not limited to that specific number, except when In addition, in each of the above-described embodiments, when referring to the shape, positional relationship, etc. of the constituent elements, the shape, It is not limited to the positional relationship or the like.

Claims

In a centrifugal blower,
a rotatably provided main plate (10);
an annular shroud (20) provided facing the main plate and having an opening (21) in the center through which air flows;
A plurality of blades (30) arranged between the shroud and the main plate around an axis (CL) that is the center of rotation at predetermined intervals and connected to the shroud and the main plate,
A virtual circle centered on the axial center is defined on a virtual plane perpendicular to the axial center, the side closer to the axial center in the radial direction in the virtual circle is called the radial inner side, and the opposite side is called the radial outer side. When you say
A leading edge (31) of the wing is provided radially inward of an inner peripheral wall (211) of the opening of the shroud,
A surface of the front edge facing away from the main plate is located radially inside a connection point (73) between the inner peripheral wall of the opening and the blade and closer to the main plate than the connection point, A lower portion (71) provided along a plane perpendicular to the axis, and a higher portion located radially inward of the lower portion and on the opposite side of the main plate with respect to the lower portion. (72) is provided,
A centrifugal fan, wherein the low portion and the high portion form a concave shape (70) on a surface of the front edge facing away from the main plate.
an upper case main body (56) covering a surface of the shroud opposite to the main plate; an air suction port (51) provided in the upper case main body at a position corresponding to the opening; further comprising an upper case (53) having a bell mouth (57) cylindrically extending from the inner peripheral edge of the mouth toward the main plate,
Let Dc be the outer diameter of the bellmouth, and Dw be the outer diameter of a circle connecting points or surfaces of the lower portions provided on the plurality of wings that are closest to the main plate in the direction of rotation. Dc<Dw The centrifugal fan of claim 1, comprising:
The centrifugal fan according to claim 1 or 2, wherein the radially inner portion (75, 751) of the lower portion has a curved surface.
The centrifugal fan according to any one of claims 1 to 3, wherein both the radially inner portion and the radially outer portion (391) of the lower portion are curved surfaces.
The portion where the low-level portion and the high-level portion are connected is a first curved surface (74) that is a convex curved surface on the low-level portion side of the high-level portion and on the side opposite to the main plate, and the first curved surface (74). has a second curved surface (75) which is a convex curved surface toward the main plate side on the radially outer side,
2. When the leading edge is viewed from the rotational direction of the blade, the radius of curvature of the first curved surface is R1 and the radius of curvature of the second curved surface is R2, and the relationship is R1>R2. 5. The centrifugal blower according to any one of 1 to 4.
The portion where the low-level portion and the high-level portion are connected is a first curved surface (74) that is a convex curved surface on the low-level portion side of the high-level portion and on the side opposite to the main plate, and the first curved surface (74). has a second curved surface (75) which is a convex curved surface toward the main plate side on the radially outer side, and when the leading edge is viewed from the rotation direction of the blade, the radius of curvature of the first curved surface is R1 , the radius of curvature of the second curved surface is R2,
Furthermore, when the lower portion is viewed in a cross section perpendicular to the direction in which the blade extends from the leading edge to the trailing edge, the curvature radius of the corner portion (36) on the suction surface (35) side of the lower portion is Claim 1, wherein the relationships of R1>R3>R4 and R2>R3>R4 are satisfied, where R3 is the radius of curvature of the corner portion (38) on the side of the pressure surface (37) of the lower portion and R4 is the radius of curvature of the corner portion (38). 6. The centrifugal blower according to any one of 1 to 5.
Da is the distance between the point or surface of the lower part that is closest to the main plate and the point or surface of the higher part that is farthest from the main plate, and the distance between the main plate and the shroud on the trailing edge side of the wing 7. The centrifugal fan according to claim 1, wherein Db has a relationship of 0<Da≦Db×0.09.
The shroud has a shroud tubular portion (22) that extends in a tubular shape from an inner peripheral edge on the side of the opening toward the side opposite to the main plate,
2. The wing has a standing wall portion (39) extending from a connection point between the inner peripheral wall of the opening and the wing parallel to the inner peripheral wall 211 of the opening of the shroud toward the main plate. 8. The centrifugal fan according to any one of 1 to 7.