JP5145188B2 - Multiblade centrifugal fan and air conditioner using the same - Google Patents

Description

  The present invention relates to a multiblade centrifugal fan that can be suitably applied to an air conditioner such as a building or an automobile, and an air conditioner using the same.

  A multi-blade centrifugal fan called a sirocco fan has a hub, a plurality of blades (also referred to as blades or blades) arranged radially on the outer periphery of the hub, and the blade facing the hub. And an impeller having an annular shroud provided on the end side. The cross-sectional shape in the direction orthogonal to the axial direction of the blade is generally a so-called two-dimensional shape that is substantially uniform in the axial direction (see, for example, Patent Document 1).

  On the other hand, some multi-blade centrifugal fans that emphasize fan performance include multi-blade centrifugal fans configured to skew the blades in the rotational direction and blades for higher performance, higher efficiency, or lower noise. A multiblade centrifugal fan configured to change the chord length of the blade in the axial direction by providing an inducer (see, for example, Patent Documents 2 and 3) has been proposed.

Japanese Patent No. 3844893 JP 2000-240590 A JP 2005-30349 A

  In the case of a multiblade centrifugal fan, the air sucked in the axial direction is changed in the centrifugal direction. It tends to be a biased flow. As a result, the shroud end near the blade suction port does not function effectively, leading to a reduction in air blowing efficiency, and a high-speed jet with a biased air flow on the blowout side of the impeller. There was a problem that it was an increase factor.

  In addition, as a means for solving the above problems, it is considered to adopt a configuration in which the blade is skewed in the rotational direction toward the axial direction, but it is difficult to injection mold the impeller with a resin material. There was a problem that the cost increased. Furthermore, although a fan has been proposed in which the inner diameter of the blade on the hub side is reduced to increase the chord length, the impeller can be used simply by reducing the inner diameter of the blade on the hub side and increasing the chord length. The problem that the airflow is difficult to reach near the central hub surface cannot be improved, and therefore the entire blade is not used effectively, resulting in a useless area, and the impeller becomes heavier by that amount, resulting in a decrease in efficiency. There was a problem.

  The present invention has been made in view of such circumstances, and a multi-blade centrifugal fan capable of achieving high performance, high efficiency and low noise with a simple configuration by devising the shape of the hub and blades. And it aims at providing the air conditioner using the same.

In order to solve the above problems, the multiblade centrifugal fan of the present invention and the air conditioner using the same employ the following means.
That is, the multiblade centrifugal fan according to the present invention has a hub whose central portion is convex on the suction side, a plurality of blades arranged radially on the outer periphery of the hub, and the hub of the blades facing the hub. A multiblade centrifugal system comprising: an impeller having an annular shroud provided on an end side; and a casing that pivotally supports the impeller and blows out air sucked from a suction port provided on a side surface in a circumferential direction. In the fan, the cross section on the outer peripheral portion side of the hub in the meridional cross section of the impeller has a curved shape including an arc centered around the rear edge of the shroud side end portion of the blade, and the plurality of sheets The inner diameter of the blade row in the vicinity of the hub is smaller than the inner diameter in the vicinity of the shroud, and the blade from the shroud side so that the leading edge of the blade is in smooth contact with the hub. Toward the connecting portion between the smooth concave curve, tangent of the connecting portion is characterized in that it is that is inclined to the suction side toward the center of rotation shape.

  In a multiblade centrifugal fan, the airflow sucked in the axial direction is changed in the centrifugal direction by the impeller, so the airflow cannot bend due to inertial force near the suction port, and the airflow reaches near the hub surface. There was a tendency to be difficult. As a result, in the impeller, the air flow tends to be slightly biased toward the hub side from the central portion in the axial direction, the entire blade is not used effectively, the air blowing efficiency is reduced, and the air flow blown out from the impeller A high-speed jet flow was generated at a position where the pressure was biased, and this was a cause of noise increase due to the secondary flow. However, according to the present invention, the section on the outer peripheral portion side of the hub in the meridional section of the impeller has a curved surface shape including an arc centered around the rear edge of the shroud side end of the blade, and a plurality of The inner diameter of the blade row near the hub is smaller than the inner diameter near the shroud, and a smooth concave curve is formed from the shroud side toward the hub connection so that the leading edge of the blade is in smooth contact with the hub. Since the tangent line of the part is inclined toward the suction side toward the rotation center, the flow area of the cross section perpendicular to the streamline is increased smoothly from the inlet side to the outlet side of the impeller, thereby The pressure can be stably recovered. In addition, since the hub functions as a guide that smoothly deflects the direction of the suction airflow from the axial direction to the centrifugal direction, the flow loss of the airflow inside the impeller can be reduced. In addition, since the axial height of the blade near the hub is gradually reduced toward the center of rotation, the airflow can flow smoothly between the blades, and speed deficit near the hub surface can be suppressed. Can do. In addition, since the chord length of the blade is increased on the hub side, the pressure between the blades near the hub side is increased, and a pressure gradient is formed in the axial direction from the hub side to the shroud side between the blades. The airflow on the shroud side increases and the entire blade functions effectively, and the blown airflow can be made uniform in the axial direction of the blade. As a result, the multi-blade centrifugal fan can be improved in performance, efficiency, and noise.

  Furthermore, the multiblade centrifugal fan of the present invention is the above-described multiblade centrifugal fan, wherein the leading edge of the blade is near the connecting portion connected to the hub, and the leading edge is counterclockwise toward the trailing edge. It is retreated so that it may be located in the side.

  According to the present invention, the leading edge of the blade is retreated so that the leading edge is positioned on the counter-rotating direction side toward the trailing edge side in the vicinity of the connection point connected to the hub. It is possible to smoothly flow between the blades along the part set as the swept wing, and since the centrifugal direction component is large in the part set as the swept wing, the static pressure can be increased by the blade itself. it can. Thereby, the pressure between the blades near the hub side is further increased, and the pressure gradient formed in the axial direction from the hub side to the shroud side between the blades can be further increased. As a result, the blown airflow can be made more uniform in the axial direction of the blade, and the multiblade centrifugal fan can be further improved in efficiency and noise.

  Furthermore, the multiblade centrifugal fan of the present invention is the above-described multiblade centrifugal fan, wherein the cross-sectional area from the circular suction passage of the impeller to the cylindrical blowout passage is suctioned. The flow path side is gradually increased from the flow path side to the blow flow path side, and the area of the blow flow path is approximately 1.5 to 4 times the area of the suction flow path.

  According to the present invention, the flow passage cross-sectional area from the suction flow path forming the circular shape of the impeller to the blowout flow path forming the cylindrical shape is gradually increased from the suction flow path side to the blow flow path side. Since the area of the path is approximately 1.5 to 4 times the area of the suction flow path, the flow path cross-sectional area in the impeller is not expanded suddenly from the suction side to the blow-out side, and gently It becomes gradually increased. As a result, the velocity energy (dynamic pressure) can be converted into static pressure while gradually reducing the velocity of the air flow in the impeller, and the static pressure can be gradually recovered, and thus the blowing performance can be improved.

Furthermore, the multiblade centrifugal fan of the present invention is the above-described multiblade centrifugal fan according to any one of the above-described multiblade centrifugal fans, wherein the shroud side end on a straight line passing through the rear edge of the shroud side end of the blade in the meridional section of the impeller. The length L of the line segment extending from the section to the fan rotation axis or the hub is such that the line segment L is perpendicular to the fan rotation axis Θ = 0 ° and parallel to the fan rotation axis. When Θ = 90 °, the following formula is satisfied.
L = L _{Θ = 0} * (1 + n * Θ / 90)
However, n = −0.3 to +0.5, and L _{Θ = 0} is L at Θ = 0 °.

According to the present invention, in the meridional section of the impeller, the length L of a line segment extending from the shroud side end on a straight line passing through the rear edge of the shroud side end of the blade to the fan rotation shaft or the hub is When the state where the minute L is perpendicular to the fan rotation axis is Θ = 0 ° and the state parallel to the fan rotation axis is Θ = 90 °,
L = L _{Θ = 0} * (1 + n * Θ / 90)
However, n = −0.3 to +0.5, and L _{Θ = 0} is L at Θ = 0 °.
Therefore, the cross-sectional area of the flow path in the impeller is gradually increased from the suction side to the blowout side, and gradually increases. As a result, the velocity energy (dynamic pressure) is converted into static pressure while gradually reducing the velocity of the airflow in the impeller, and the static pressure can be gradually recovered. Therefore, improvement in the blowing performance can be achieved.

  Furthermore, the air conditioner according to the present invention is characterized in that the multi-blade centrifugal fan described in any of the above is mounted as an air blowing fan.

  According to the present invention, the air blowing fan mounted on the air conditioner is the multiblade centrifugal fan described in any one of the above, so that the high performance, high efficiency, and low performance are achieved as described above. By mounting a noise-reduced multiblade centrifugal fan, an air conditioner equipped with the multiblade centrifugal fan can be similarly improved in performance, efficiency and noise.

  According to the multiblade centrifugal fan of the present invention, the static pressure can be stably recovered by smoothly increasing the flow passage area having a cross section perpendicular to the streamline from the inlet side to the outlet side of the impeller. In addition, since the hub functions as a guide that smoothly deflects the direction of the suction airflow from the axial direction to the centrifugal direction, the flow loss of the airflow inside the impeller can be reduced. In addition, since the axial height of the blade near the hub is gradually reduced toward the center of rotation, the airflow can flow smoothly between the blades, and speed deficit near the hub surface can be suppressed. Can do. In addition, since the chord length of the blade is increased on the hub side, the pressure between the blades near the hub side is increased, and a pressure gradient is formed in the axial direction from the hub side to the shroud side between the blades. Since the airflow on the shroud side increases and the entire blade functions effectively, and the blown airflow can be made uniform in the axial direction of the blade, the performance, efficiency, and noise of the multiblade centrifugal fan can be improved. Can be planned.

  Moreover, according to the air conditioner of the present invention, the air conditioner equipped with the multi-blade centrifugal fan is mounted by mounting the multi-blade centrifugal fan with high performance, high efficiency and low noise as described above. Similarly, high performance, high efficiency, and low noise can be achieved.

Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a perspective view of the multiblade centrifugal fan according to the first embodiment of the present invention, FIG. 2 is a longitudinal sectional view thereof, FIG. 3 is a plan view of the impeller thereof, FIG. Fig. 5 shows a meridional sectional view (longitudinal sectional view passing through the rotation axis) of the impeller, and Fig. 5 shows a transverse sectional view in a direction perpendicular to the axial direction of the blade.
The multiblade centrifugal fan 1 includes a scroll-shaped resin material casing 2.

  The casing 2 is composed of an upper side surface 3, a lower side surface 4, and an outer peripheral surface 5, and is formed in a spiral shape with the tongue 6 as a base point. An air suction port 8 having a bell mouth 7 is provided on the upper side surface 3 of the casing 2, and a blowout port 9 is extended in a tangential direction from the upstream side of the tongue 6. Inside the casing 2, an impeller 11 having a large number of blades 12 is rotatably supported via a rotation shaft 10 </ b> A of a motor 10 installed on the lower surface 4 side.

  The impeller 11 includes a bowl-shaped hub 13 whose central portion is convex toward the suction port 8, a plurality of blades 12 arranged radially on the outer periphery of the hub 13, and the hub 13 of the blade 12. The boss 13A provided at the center of the hub 13 is attached to the rotating shaft 10A of the motor 10 so that the motor 10 10 is rotated in the direction of arrow N (see FIG. 3).

  The shroud 14 of the impeller 11 is disposed so as to face the bell mouth 7 provided on the outer edge of the suction port 8 with a predetermined gap, and has an axial cross-sectional shape radially outward from the suction port 8. It is set as the shape which follows the air flow F which turns to the direction. Further, the hub 13 has a bowl-shaped configuration in which the center portion is convex toward the suction port 8 side. As shown in FIG. 4, the cross section of at least the outer peripheral side of the hub 13 is a circular arc having a radius R centered on the vicinity of the rear edge of the shroud side end of the blade 12 in the meridional cross section of the impeller 11. The curved surface shape 13B is included.

  Further, the blade 12 has a blade shape in which almost half of the blade 12 on the side of the shroud 14 than the central portion in the axial direction has a substantially parallel front edge and rear edge. In addition, almost half of the hub 13 side of the central portion in the axial direction gradually protrudes toward the inner diameter side of the impeller 11 so that the inner diameter in the vicinity of the hub 13 side of the plurality of blades 12 is shroud. The connecting portion from the shroud 14 side to the hub 13 is smaller than the inner diameter in the vicinity of the 14 side and the front edge of the blade 12 is smoothly connected to the curved surface including the arc having the radius R on the hub 13 side. Thus, a concave concave curve 12A is formed, and the tangent line of the connection portion is formed into a blade shape inclined toward the suction port 8 toward the rotation center Φ2.

  As shown in FIGS. 3 and 5, in the cross section in the direction perpendicular to the axial direction, the blade 12 has a rear edge on the inner peripheral side on the outer peripheral side (rear edge side) with respect to the central portion in the axial direction. The general forward wing portion 12B is configured to be positioned on the front side in the direction of rotation N. On the other hand, the inner peripheral side (front edge side) of the central portion in the axial direction is the rear side in the rotational direction N with the front edge facing the outer peripheral side (rear edge side) in the vicinity of the connection point connected to the hub 13. It is set as what is called retreating wing | blade part 12C retreated so that it may be located, and it is set as the structure connected between both by the smooth connection part 12D.

With the configuration described above, according to the present embodiment, the following operational effects can be obtained.
When the impeller 11 is rotated by driving the motor 10, the air flow F sucked in the axial direction from the suction port 8 is increased in pressure while being changed in the centrifugal direction in the impeller 11, and the trailing edge of each blade 12. To the tangential direction of the impeller 11 and blown out into the spiral casing 2. This blown air flow F is guided along the inner surface of the casing 2 to the blowout port 9 while being pressurized, and is blown from the blowout port 9 to the outside.

  Here, in the multiblade centrifugal fan 1 according to the present embodiment, the cross section on the outer peripheral portion side of the hub 13 in the meridional cross section of the impeller 11 has the vicinity of the rear edge of the shroud 14 side end portion of the blade 12 as the center Φ1. Since the curved surface shape 13B includes a circular arc, the flow passage area having a cross section perpendicular to the streamline of the air flow F can be smoothly increased from the inlet side to the outlet side of the impeller 11, and thereby the static pressure Can be stably recovered. Further, since the hub 13 whose outer peripheral side has a curved shape 13B including an arc can be functioned as a guide for smoothly deflecting the suction airflow F from the axial direction to the centrifugal direction, The flow loss of the air flow F can be reduced.

  In addition, the hub 13 has the curved surface shape 13B as described above, the inner diameter of the plurality of blades 12 in the vicinity of the hub 13 is smaller than the inner diameter in the vicinity of the shroud 14, and the leading edge of the blade 12 is the hub 13. The concave concave curve 12A is formed from the shroud 14 side toward the connection portion with the hub 13 so as to smoothly contact with the hub 13, and the tangent line of the connection portion is inclined toward the suction side toward the rotation center Φ2. The axial height of the blade 12 in the vicinity of the hub 13 is gradually reduced toward the rotation center Φ2. As a result, even if the leading edge of the blade 12 protrudes to the inner diameter side of the impeller 11 and the inner diameter portion of the blade 12 row becomes clogged, the air flow F can smoothly flow between the blades 12. And speed deficit in the vicinity of the hub 13 surface can be suppressed.

  In addition, since the chord length of the blade 12 is made longer on the hub 13 side, the isobaric line T on the blade 12 is, as shown in FIG. The pressure is increased and the state is curved with respect to the axial direction. For this reason, when viewed in the axial direction, a pressure gradient is formed in the axial direction between the blades 12 from the hub 13 side toward the shroud 14 side, and flows in a biased manner toward the hub 13 side by the inertial force V. The air flow F can be shifted to the shroud 14 side as indicated by the arrow W. Thereby, the blown airflow F can be made uniform in the axial direction of the blade 12, and the entire blade 12 can function effectively.

  Further, in the present embodiment, the inner peripheral side (front edge side) of the blade 12 is positioned on the rear side in the rotational direction N toward the outer peripheral side (rear edge side) in the vicinity of the connection portion connected to the hub 13. Therefore, the suction airflow F can be smoothly introduced between the blades 12 along the backward wing portion 12C, and the backward wing portion is referred to as the backward wing portion. Since the centrifugal direction component is large in the portion 12C, the static pressure can be increased by the blade 12 itself. For this reason, the pressure between the blades 12 near the hub 13 side is further increased, and the pressure gradient formed in the axial direction from the hub 13 side toward the shroud 14 side between the blades 12 can be further increased. As a result, the blown airflow F can be made more uniform in the axial direction of the blade 12, and the multiblade centrifugal fan 1 can be made more highly efficient.

  As described above, high performance, high efficiency, and low noise of the multiblade centrifugal fan 1 can be achieved. The above-described multiblade centrifugal fan 1 sucks indoor air from buildings, automobiles, and the like, circulates through a heat exchanger, and is used as a blower for circulating indoor air. Since the high performance, high efficiency, and low noise can be achieved in the same way, it is extremely beneficial.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
This embodiment is different from the first embodiment described above in that the area ratio of the suction flow path and the blow flow path of the impeller 11 is specified. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In this embodiment, as shown in FIGS. 7A and 7B, the cross-sectional area of the air flow path from the suction flow path 21 that forms the circular shape of the impeller 11 to the blowout flow path 22 that forms the cylindrical shape is In this case, the area 22A of the blowout flow path 22 is approximately 1.5 times the area 21A of the suction flow path 21 or from the suction flow path 21 side to the blowout flow path 22 side. It is supposed to be 4 times.

  As described above, by setting the area 22A of the blowout flow path 22 forming the cylindrical shape of the impeller 11 to be approximately 1.5 to 4 times the area 21A of the suction flow path 21 having a circular shape, the impeller 11 When the cross-sectional area of the air flow path extending from the suction flow path 21 to the blow-off flow path 22 is increased from the suction flow path 21 side to the blow-off flow path 22 side, the cross-sectional area of the air flow path is not rapidly increased. It becomes possible to increase gradually gradually.

  For this reason, the velocity energy (dynamic pressure) is converted into static pressure while gradually reducing the velocity of the air flow F in the impeller 11 with respect to the air flow F passing through the impeller 11, and the static pressure is gradually reduced. It can be made to recover, and, thereby, the ventilation performance in the multiblade centrifugal fan 1 can be improved.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS.
The present embodiment is different from the first and second embodiments described above in that the flow path cross-sectional area 23 in the impeller 11 that is gradually increased from the suction flow path 21 to the blowout flow path 22 is specified. Yes. Since other points are the same as those in the first and second embodiments, description thereof will be omitted.

In the present embodiment, as shown in FIG. 8, in a meridian plane cross section (longitudinal cross section passing through the rotation shaft 10 </ b> A) of the impeller 11, a straight shroud 14 passing through the rear edge of the shroud 14 side end of the blade 12. The length of a line segment from the side end to the fan rotation shaft 10A or the hub 13 is defined as L. The state where this line segment L is perpendicular to the fan rotation shaft 10A is Θ = 0 °, and the fan rotation shaft When the state parallel to 10A is Θ = 90 °, the following formula is satisfied.
L = L _{Θ = 0} * (1 + n * Θ / 90)
However, n = −0.3 to +0.5, and L _{Θ = 0} is L at Θ = 0 °.

The above equation shows the size of the flow path cross-sectional area 23 (see FIG. 9B) in the impeller 11 gradually increased from the suction flow path 21 to the blow flow path 22 shown in FIG. This is specified by the segment L, and represents the channel cross-sectional area 23 from the segment L _{Θ = 0} to the segment L _{Θ = 90} shown in FIG. Incidentally, when n is n = −0.3, L _{Θ = 90} = L _{Θ = 0} * 0.7, and when n is n = + 1.5, L _{Θ = 90} = L _{Θ = 0} * 1.5, which indicates that the area 22A of the blowout flow path 22 is approximately 1.5 to 4 times the area of the suction flow path 21 to 21A.

As described above, in the meridional section of the impeller 11, the length of a line segment extending from the shroud 14 side end on the straight line passing through the rear edge of the shroud 14 side end of the blade 12 to the fan rotating shaft 10 </ b> A or the hub 13. Is L, and when the line segment L is perpendicular to the fan rotation axis 10A and Θ = 0 °, and the state parallel to the fan rotation axis 10A is Θ = 90 °, L = L _{Θ = 0} * (1 + n * Θ / 90), where n = −0.3 to +0.5, and L _{Θ = 0} is L at Θ = 0 °. By satisfying the above equation, the flow passage cross-sectional area 23 from the suction side to the blow-out side of the impeller 11 is not suddenly increased, but gradually increases gradually. For this reason, it is possible to gradually reduce the static pressure by gradually reducing the velocity of the air flow in the impeller 11 to convert the velocity energy (dynamic pressure) into the static pressure. Thereby, the ventilation performance of the multiblade centrifugal fan 1 can be improved.

  In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably. For example, the multiblade centrifugal fan 1 according to the present invention is not limited to the above-described air conditioner, and can of course be widely applied as a blower for other devices. Moreover, although the said embodiment demonstrated the example which made the casing 2 and the impeller 11 resin, both need not necessarily be resin, and of course it is good also as another material.

1 is a perspective view of a multiblade centrifugal fan according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the multiblade centrifugal fan shown in FIG. It is a top view of the impeller of the multiblade centrifugal fan shown in FIG. It is meridional sectional drawing of the impeller of the multiblade centrifugal fan shown in FIG. It is a cross-sectional view of the direction orthogonal to the axial direction of the blade of the multiblade centrifugal fan shown in FIG. It is a schematic diagram which shows the pressure gradient between each braid | blade of the multiblade centrifugal fan shown in FIG. It is the perspective view (A) of the impeller of the multiblade centrifugal fan which concerns on 2nd Embodiment of this invention, and the schematic diagram (B) showing the area of the suction flow path and the blowing flow path. It is a longitudinal cross-sectional view of the multiblade centrifugal fan which concerns on 3rd Embodiment of this invention. FIG. 9 is a perspective view (A) of the impeller of the multiblade centrifugal fan shown in FIG. 8 and a schematic diagram (B) showing a flow path cross-sectional area at the angle Θ position.

Explanation of symbols

1 Multiblade Centrifugal Fan 2 Casing 8 Suction Port 9 Blowout Port 10A Rotating Shaft 11 Impeller 12 Blade 12A Concave Curve 12C Retreating Wing 13 Hub 13B Curved Shape 14 Shroud 21 Suction Channel 21A Suction Channel Area 22 Blowout Channel 22A Area of blowout channel 23 Channel cross-sectional area Φ1 Center of arc Φ2 Center of rotation L Line segment

Claims (5)

The hub has a hub whose central portion is convex on the suction side, a plurality of blades radially arranged on the outer periphery of the hub, and an annular shroud provided on the end side of the blade facing the hub. In a multiblade centrifugal fan comprising an impeller and a casing that pivotally supports the impeller and blows out air sucked in from a suction port provided on a side surface in a circumferential direction.
The cross section on the outer peripheral side of the hub in the meridional cross section of the impeller is a curved shape including an arc centered around the rear edge of the shroud side end of the blade,
The inner diameter of the plurality of blade rows in the vicinity of the hub is smaller than the inner diameter in the vicinity of the shroud, and the leading edge of the blade is smoothly contacted with the hub from the shroud side toward the connection portion with the hub. A multiblade centrifugal fan characterized in that it has a smooth concave curve, and the tangent line of the connection portion is inclined toward the suction side toward the center of rotation.   2. The front edge of the blade is retracted so that the front edge is positioned on the counter-rotation direction side toward the rear edge side in the vicinity of the connection point connected to the hub. The multiblade centrifugal fan described in 1.   The flow passage cross-sectional area from the suction flow path that forms the circular shape of the impeller to the blowout flow path that forms a cylinder is gradually increased from the suction flow path side to the blow flow path side, and the area of the blow flow path is The multiblade centrifugal fan according to claim 1 or 2, wherein the area of the suction flow path is approximately 1.5 to 4 times. In the meridional section of the impeller, the length L of a line segment extending from the shroud side end on the straight line passing through the rear edge of the blade shroud end to the fan rotation shaft or the hub is the line segment L 2 satisfies the following expression when Θ = 0 ° is a state perpendicular to the fan rotation axis and Θ = 90 ° is a state parallel to the fan rotation axis. 4. The multiblade centrifugal fan according to any one of items 3 to 3.
L = L _{Θ = 0} * (1 + n * Θ / 90)
However, n = −0.3 to +0.5, and L _{Θ = 0} is L at Θ = 0 °. An air conditioner in which the multiblade centrifugal fan according to any one of claims 1 to 4 is mounted as an air blowing fan.

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