JP4830519B2 - Centrifugal fan - Google Patents

Description

  The present invention belongs to a technical field related to a centrifugal fan provided with an impeller.

  Conventionally, a blade comprising a hub that is rotationally driven, a shroud that is disposed so as to face the hub and has a suction port for sucking air, and a plurality of blades that are connected and fixed between the hub and the shroud. Various centrifugal noise reduction techniques have been proposed for reducing the noise generated when a centrifugal fan is driven. For example, in the technique disclosed in Patent Document 1, turbulent noise due to the flow velocity difference in the airflow is reduced by devising the shape of the blade disposed in the impeller.

  Specifically, the blade is formed so that the connection position between the shroud and the blade is positioned rearward in the rotational direction with respect to the connection position between the hub and the blade at the trailing edge of the blade. In other words, the positive pressure surface (the front surface in the rotational direction of the blade) of the blade is inclined toward the rear side in the rotational direction from the hub side of the blade toward the shroud side with respect to the hub.

Therefore, when the airflow guided into the impeller is passed between the blades, a flow velocity component in the direction from the hub side to the shroud side in the direction of the hub rotation axis is added, and the airflow is generated in the vicinity of the shroud wall surface. The airflow velocity formed by bending from the hub rotation axis direction to the radial direction and being affected by the fluid viscosity is positively flowing toward a low region (hereinafter referred to as a low flow velocity region). Become. This flow action amplifies the airflow velocity in the vicinity of the shroud wall, and as a result, the distribution of the airflow velocity at the impeller exit in the direction of the hub rotation axis is made uniform. It is illustrated.
JP-A-10-196591

  However, in the conventional centrifugal fan, the airflow velocity distribution near the shroud wall surface near the shroud wall at the impeller exit is made uniform, but there is still a low flow velocity region near the hub wall due to the effect of fluid viscosity. It was the cause of turbulent noise due to the air velocity difference.

  The present invention has been made in view of such a point, and an object of the present invention is to equalize the airflow velocity distribution in the hub rotation axis direction at the impeller exit, from the hub to the shroud at the clogged impeller exit. The purpose is to reduce turbulent noise during the operation of the centrifugal fan by making the air velocity constant substantially throughout.

  To achieve the above object, according to the present invention, the trailing edge of the blade extends in the direction of approaching the hub toward the front side in the rotational direction near the shroud wall surface, and shroud toward the front side in the rotational direction near the hub wall surface. It was made to extend in the direction approaching.

  Specifically, in the first invention, a hub (5) that is driven to rotate about the central axis (15), and a suction port that is disposed so as to face the hub (5) and sucks air into the central part. A shroud (4) having a mouth (4b), and connected to and fixed to the outer periphery of the hub (5) and the shroud (4), and spaced apart from each other in the circumferential direction around the central axis (14). A centrifugal fan including an impeller (3) including a plurality of disposed blades (6) is a target.

And in the 1st connection position (6h) which is a connection position of the said hub (5) and the said blade | wing (6) in the rear edge of the said blade | wing (6), the 1st tangent line (21) which contact | connects this rear edge, It extends so as to approach to the shroud (4) towards the rotational direction front side of the blade (6), and, at the trailing edge of the wing (6), the shrouded headers de (4) and between the blade (6) second tangent line in the second connecting position is coupled position (6s) in contact with said trailing edge (22), extends so as to approach to said hub (5) toward a rotational direction front side of the blade (6), the The angle formed by the first tangent (21) and the straight line projected from the first tangent (21) onto the tangent plane (23) of the hub (5) at the first connection position (6h) is the first angle (θ1). The second tangent line (22) and the second tangent line (22) are connected to the second connection position. 6s), when the angle formed by the straight line projected on the tangential plane (24) of the shroud (4) is the second angle (θ2), the second angle (θ2) is greater than the first angle (θ1). that it has been set so as to be smaller.

  With this configuration, it is possible to reduce the turbulent noise due to the air flow velocity difference at the impeller outlet (3a). That is, in the conventional centrifugal fan, the air current is bent in the radial direction from the hub rotation axis direction and is affected by fluid viscosity in the vicinity of the shroud wall surface (4a) and the hub wall surface (5a) at the impeller outlet (3a). The low flow velocity range due to this was spreading. However, according to the configuration of the present invention, the pressure surface of the blade at the trailing edge of the blade can be inclined toward the front side in the rotation direction in the vicinity of the shroud wall surface (4a) and the hub wall surface (5a). The airflow is positively flowed toward the shroud wall surface (4a) and the hub wall surface (5a) when passing between the blades (6). As a result, the vicinity of the hub wall surface (5a) and the shroud wall surface (4a) The airflow velocity in the low flow velocity region in the vicinity is amplified. Therefore, the distribution of the air flow velocity direction at the impeller outlet (3a) in the direction of the hub rotation axis can be made uniform over substantially the entire area from the hub (5) to the shroud (4). Flow noise can be reduced.

In addition, by setting the second angle (θ2) to be smaller than the first angle (θ1), it is possible to increase the ratio of the airflow toward the shroud wall surface (4a) rather than the airflow toward the hub wall surface (5a). Therefore, the airflow is bent more rapidly than the vicinity of the hub wall surface (5a), and is formed near the shroud wall surface (4a) toward the low flow velocity region where the airflow speed is lower than that near the hub wall surface (5a). Thus, the airflow can be positively flowed, whereby the hub rotation axial distribution of the airflow velocity at the impeller outlet (3a) can be easily made uniform. Therefore, the turbulent noise caused by the airflow speed difference can be further reliably reduced.

  As described above, according to the centrifugal fan of the present invention, the trailing edge of the blade (6) extends in the direction of approaching the hub (5) toward the front side in the rotational direction in the vicinity of the shroud wall surface (4a), Further, in the vicinity of the hub wall surface (5a), the airflow velocity direction distribution at the impeller outlet (3a) is made uniform in the hub rotation axis direction by extending in the direction approaching the shroud (4) toward the front side in the rotation direction. Thus, it is possible to reduce turbulent noise during operation of the centrifugal fan.

A first tangent line (21) contacting the rear edge at a first connection position (6h) which is a connection position of the hub (5) and the blade (6) at the rear edge of the blade (6); The angle formed between the first tangent (21) and the straight line projected on the tangent plane (23) of the hub (5) at the first connection position (6h) is defined as the first angle (θ1), and the blade (6) The second tangent line (22) in contact with the rear edge at the second connection position (6s), which is the connection position of the shroud at the rear edge and (4) the blade (6), and the second tangent line (22) are When the angle formed by the straight line projected on the tangential plane (24) of the shroud (4) at the second connection position (6s) is the second angle (θ2), the second angle (θ2) is the first angle. Formed near the shroud wall (4a) by setting it smaller than the angle (θ1) The can be actively flowing air stream towards the slow low flow region airflow rate than the hub wall (5a) near. Thereby, the hub rotation axial distribution of the air velocity at the impeller outlet (3a) can be easily uniformized. Therefore, the turbulent noise caused by the airflow speed difference can be further reliably reduced.

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

  FIG. 1 shows a cross-sectional view of an air conditioner (1) equipped with a centrifugal fan (2) according to an embodiment of the present invention. The air conditioner (1) includes a centrifugal fan (2) and a heat exchanger (10) housed in a casing (8). The centrifugal fan (2) includes an impeller (3) and the impeller (3). And a bell mouth (7) for guiding the sucked air into the impeller. The air conditioner (1) is usually embedded in the ceiling of the room, etc., and is installed so that the air suction port of the bell mouth (7) faces the room and faces vertically downward.

  The impeller (3) includes a hub (5) that is driven to rotate about a central axis (15), and a suction port (not shown) that is disposed so as to face the hub (5) and sucks air into the center. 4b) and is connected and fixed to the outer periphery of the shroud (4) and the hub (5) and the shroud (4), and circumferentially around the central axis (15) (hereinafter referred to as the hub rotation axis (15)). And a plurality of blades (6) (see FIG. 2) arranged at predetermined intervals from each other, and the motor (11) connected to the hub (5) rotates around the hub rotating shaft (15). Is driven to rotate. An impeller outlet (3a), which is surrounded by the shroud (4), the hub (5), and the plurality of blades (6) on the outer peripheral side surface of the impeller (3) and constitutes an air outlet, is circumferential. It is formed over the entire circumference. The said hub (5) consists of a disk-shaped member, and is formed so that the rear edge of a blade | wing (6) may be located on the outer periphery of this disk. In the shroud (4), the inner wall surface smoothly expands radially outward toward the hub side with respect to the suction port (4b), and the trailing edge of the blade (6) is positioned on the outer peripheral edge of the inner wall surface. It is formed as follows. A bell mouth (7) attached and fixed to the casing (8) is inserted into the suction port (4b) of the shroud (4).

  Further, on the outer periphery of the impeller (3), the heat exchanger (10) formed annularly around the hub rotation shaft (15) is disposed so as to surround the impeller (3).

  Hereinafter, the shape of the blade (6), which is one of the features of the present invention, will be described in detail. The blade (6) has a three-dimensional shape in which the shape of the blade cross section perpendicular to the hub rotation shaft (15) (hereinafter referred to as the blade cross section) continuously changes toward the hub rotation axis direction. In the blade cross section, the distance (r) (see FIGS. 4 to 6) between the position of the blade trailing edge and the hub rotation shaft (15) is always constant. More specifically, as shown in FIGS. 4 and 5, which are cross-sectional views of the blade (6) at the IV-IV line position and VV line position (see FIG. 3), the shroud from the hub side of the blade (6). In the state where the distance (r) between the blade trailing edge position and the hub rotation shaft (15) (the same value as the radius of the hub (5)) is kept constant, the trailing edge position of the blade (6) is It moves continuously toward the front side in the rotation direction, and the exit angle (βh) increases continuously with this movement. On the other hand, as shown in FIGS. 5 and 6 which are cross-sectional views of the blade (6) at the VV line position and the VI-VI line position (see FIG. 3), it is located on the shroud side from the VV line position. In the blade cross section, the rear edge position of the blade (6) moves from the hub side toward the shroud side toward the rear side in the rotational direction, and the outlet angle (βh) continuously decreases accordingly. At this time, an angle formed by a straight line connecting the hub rotation shaft (15) and the rear edge with respect to an arbitrary reference plane (X) including the hub rotation shaft (15) is θα, and the hub rotation at the blade trailing edge position is performed. If the position in the axial direction is Z, Z is expressed as a quadratic function of θα.

  Therefore, as shown in FIG. 7, the rear edge of the blade (6) is the first connection position (6h), which is the connection position of the blade (6) and the hub (5) at the rear edge, and the blade (6) and the shroud. It has a shape curved in an arc toward the front in the rotational direction with respect to a straight line connecting the second connection position (6s), which is a connection position with (4), and at this time, at the first connection position (6h) The first tangent line (21) in contact with the blade trailing edge extends toward the front side in the rotational direction of the blade (6) so as to approach the shroud (4), and is in contact with the blade trailing edge at the second connection position (6s). The two tangent lines (22) extend toward the front side in the rotation direction of the blade (6) so as to approach the hub (5). That is, the first angle formed by the first tangent line (21) and the straight line projected from the first tangent line (21) onto the tangent plane (23) of the hub (5) at the first connection position (6h). The angle (θ1) and the second tangent line (22) and the straight line formed by projecting the second tangent line (22) onto the tangential plane (24) of the shroud (4) at the second connection position (6s) are formed. The second angle (θ2), which is an angle, is both set in the range of more than 0 ° and less than 90 °.

  When the impeller (3) configured as described above is rotated around the hub rotation shaft (15) by the driving force of the electric motor (11), air passes through the bell mouth (7) and enters the center of the shroud (4). The suction port (4b) formed is sucked into the impeller. The sucked air changes its direction radially outward along the flow path sandwiched between the shroud wall surface (4a) and the hub wall surface (5a), and flows between the rotating blades (6). And when passing between each blade | wing (6), a static pressure and a dynamic pressure are added, and it discharge | emits to the radial direction outer side from the said impeller exit (3a). The discharged air is further heated or cooled when passing through the heat exchanger (10), and then blown out from the outlet (9) to adjust the room temperature and the room humidity.

  As described above, in the embodiment, the first tangent line (21) and a straight line obtained by projecting the first tangent line (21) onto the tangential plane (23) of the hub (5) at the first connection position (6h) are as follows. The first angle (θ1), which is an angle formed, and the second tangent line (22) and the second tangent line (22) to the tangential plane (24) of the shroud (4) at the second connection position (6s). The second angle (θ2), which is an angle formed with the projected straight line, is both set in the range of more than 0 ° and less than 90 °. According to this configuration, as shown in FIG. 8, the pressure surface of the blade (6) at the blade trailing edge can be inclined toward the front side in the rotational direction in the vicinity of the shroud wall surface (4a) and the hub wall surface (5a). Therefore, the airflow is positively flowed toward the shroud wall surface (4a) and the hub wall surface (5a) when passing between the blades (6). Therefore, the airflow velocity in the low flow velocity region formed near the hub wall surface (5a) and near the shroud wall surface (4a) due to the bending of the airflow direction and the influence of fluid viscosity can be amplified. The distribution of the air velocity in 3a) in the hub rotation axis direction can be made uniform (see FIG. 10). Therefore, it is possible to reduce turbulent noise caused by the difference in airflow speed.

FIG. 9 shows the result of an actual noise test. Here, the noise reduction amount is the specific noise of the conventional centrifugal fan (2) in which the first angle (θ1) is set to 90 ° and the second angle (θ2) is set to 77 °, and the conventional centrifugal fan (2 ) With respect to the specific noise reduction amount of the centrifugal fan (2) according to the embodiment of the present invention, and the larger this value, the greater the noise reduction effect. According to the test results, when the first angle (θ1) is in the range of 40 ° to 80 ° and the second angle (θ2) is in the range of 35 ° to 65 °, the noise reduction amount is It becomes 0.3 or more, and especially a big noise reduction effect can be acquired. The second angle (θ2) is set to be smaller than the first angle (θ1). Thereby, the ratio of the airflow which goes to a shroud wall surface (4a) can be increased rather than the airflow which goes to a hub wall surface (5a). Therefore, the airflow is bent more rapidly than the vicinity of the hub wall surface (5a), and is formed near the shroud wall surface (4a) toward the low flow velocity region where the airflow speed is lower than that near the hub wall surface (5a). Thus, the airflow can be positively flowed, whereby the hub rotation axial distribution of the airflow velocity at the impeller outlet (3a) can be easily made uniform. Therefore, the turbulent noise caused by the airflow speed difference can be further reliably reduced.
(Other embodiments)
The configuration of the present invention is not limited to the above-described embodiment, but includes various other configurations. That is, in the above embodiment, the rear edge of the blade (6) is an angle formed by a straight line connecting the hub rotation axis (15) and the rear edge with respect to an arbitrary reference plane (X) including the hub rotation axis (15). Is formed such that Z is a quadratic function of θα, where Z is the quadratic function of θα. It may be changed linearly in proportion to

  In addition, the distance (r) (see FIGS. 4 to 6) between the position of the trailing edge of the blade and the hub rotation shaft (15) in any blade cross section is always constant, but this is not the only case. Instead of this, the distance (r) may be changed.

  INDUSTRIAL APPLICABILITY The present invention is useful for a centrifugal fan provided with an impeller, and is particularly useful when mounted on an indoor air conditioner or the like where noise is a problem.

It is sectional drawing of the air conditioner carrying the centrifugal fan which concerns on embodiment of this invention. It is a perspective view of the impeller mounted in the said centrifugal fan. It is an enlarged view of the blade | wing in FIG. It is the IV-IV sectional view taken on the line of FIG. It is the VV sectional view taken on the line of FIG. It is the VI-VI sectional view taken on the line of FIG. It is a VII direction arrow line view of FIG. It is the VIII-VIII sectional view taken on the line of FIG. It is a graph which shows the noise reduction effect of the centrifugal fan which concerns on embodiment of this invention with respect to the conventional centrifugal fan. It is a schematic diagram which shows the hub rotation-axis direction distribution of the airflow speed in the impeller exit of the centrifugal fan which concerns on embodiment of this invention.

U rotation direction θ1 first angle θ2 second angle 2 centrifugal fan 3 impeller 4 shroud 4b suction port 5 hub 6 blade 6h first connection position 6s second connection position 15 central axis (hub rotation axis)
21 First tangent line 22 Second tangent line 23 Tangent plane in contact with hub at first coupling position 24 Tangent plane in contact with shroud at second coupling position

Claims (1)

A hub (5) that is driven to rotate about a central axis (15), and a shroud (4) that is disposed so as to face the hub (5) and has a suction port (4b) for sucking air at the center. And a plurality of blades (6) connected and fixed to the outer peripheral portions of the hub (5) and the shroud (4) and arranged around the central axis (15) at predetermined intervals in the circumferential direction. A centrifugal fan equipped with an impeller (3) comprising:
A first tangent line (21) in contact with the rear edge at the first connection position (6h), which is a connection position between the hub (5) and the blade (6), at the rear edge of the blade (6) is the blade. towards the rotational direction front (6) extending so as to approach to the shroud (4), and, at the trailing edge of the wing (6), the connecting position of the shrouded headers de (4) and the blade (6) second coupling position a second tangent to the trailing edge in (6s) (22) is extending so as to approach to said hub (5) toward a rotational direction front side of the blade (6),
An angle formed by the first tangent (21) and a straight line projected from the first tangent (21) onto the tangent plane (23) of the hub (5) at the first connection position (6h) is a first angle (θ1). ) And the angle formed between the second tangent line (22) and the straight line projected from the second tangent line (22) onto the tangential plane (24) of the shroud (4) at the second connection position (6s) is the second angle. A centrifugal fan , wherein the second angle (θ2) is set to be smaller than the first angle (θ1) when the angle (θ2) is set .

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