JPH05164092A - Blower - Google Patents

Abstract

PURPOSE:To prevent leak air flow of a blade, to reduce blowing noise and to improve blowing performance by fixing an orifice ring at the tip end of the blade on the outer circumferential part of an axial impeller and so on and by providing a second orifice ring close to its discharge side. CONSTITUTION:An axial blower is provided with an impeller 8 consisting of a plurality of blades 9 on the periphery of a hub 10 mounted on a motor 14, and a first orifice ring 11 is provided integrally with the blade 9 on the outer circumferential part of the blade 9. Also, on the discharge side of this orifice ring 11, a second orifice ring 12 is provided close to this orifice ring 11. And as for the first orifice ring 11, its axial length is made short in a portion where the outer circumferential end 9c of the blade 9 is sufficiently away from a suction side end 11a of the orifice ring 11 but close to the suction side, while the axial length of the first orifice ring 11 is made longer in a portion where the blade outer circumferential end 9c is located on the suction side than an end 11b.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a blower used in an air conditioner or the like.

[0002]

2. Description of the Related Art Conventionally, blowers have been widely used in air conditioners for business and home use, and in particular, in recent years, due to downsizing of equipment and diversification of equipment installation conditions, higher performance and lower performance have been achieved. The demand for noise reduction is increasing.

Hereinafter, with reference to the drawings, an actual flat plate 1-1
A blower such as a conventional air conditioner proposed in Japanese Patent No. 25898 will be described.

9 and 10 show the structure of a conventional blower such as an air conditioner, where 1 is an axial flow blower main body and 2 is a blower.
Is an impeller, 3 is a blade of the impeller 2, 3a is a rear edge of the blade 3, 3b is a front edge of the blade 3, and 4 is a hub for fixing the blade 3. Reference numeral 5 denotes a bellmouth-shaped orifice ring that surrounds the outer peripheral portion of the trailing edge of the blade 3. A motor 6 rotates the impeller 2.

The operation of the axial-flow blower configured as described above will be described below. First, the rotation of the motor 6 causes the impeller 2 to rotate in a predetermined direction, causing air to flow into the front edge portion 3
Inhaled from b. At this time, along with the airflow E in the axial direction, the airflow F in the centripetal direction from the outer peripheral portion of the impeller 2 is generated.
Flows in. Further, static pressure and dynamic pressure are applied in the impeller 2 by the action of the vanes 3, and the static pressure and the dynamic pressure are discharged from the trailing edge portion 3a of the impeller 2 to perform an air blowing action.

[0006]

However, in the above-described structure, the outer peripheral end 3c of the blade 3 sucks in from the end of the orifice ring 5 as shown in FIG. 11 showing the state of air flow inside the axial blower 1. In the portion located in the vicinity of the side, there is a leakage airflow G from the pressure surface side 3d of the blade 3 to the suction surface side 3e, so that the airflow collides with the airflow F flowing from the outer peripheral portion of the impeller 2 in the centripetal direction. However, there is a drawback that the turbulent flow noise is largely generated and the blower noise of the entire axial flow fan 1 increases.

Further, as shown in FIG. 12, the outer peripheral end 3c of the blade 3 is
At a portion where is sufficiently distant from the end of the orifice ring 5 on the suction side, the airflow F flowing in the centripetal direction flows into the impeller 2 without resistance, so the airflow F flowing in the centripetal direction has a blowing performance. It greatly contributes, and there is also a drawback that if the orifice ring 5 is extended in the axial direction and the airflow F flowing in the centripetal direction is blocked, the blowing performance is significantly deteriorated.

Therefore, the leakage airflow from the pressure surface side of the blade to the suction surface side collides with the airflow flowing in the centripetal direction from the outer peripheral portion of the impeller without suppressing the airflow flowing in the centripetal direction and deteriorating the blowing performance. There was a problem that it had to be prevented.

In view of the above-mentioned problems, the present invention provides an outer peripheral end of a blade even when there is not only an axial airflow in the impeller but also an airflow sucked radially from the outer peripheral portion of the impeller near the inlet of the orifice ring. In the part where is located sufficiently away from the end of the orifice ring on the suction side, the outer peripheral edge of the blade is located near the suction side from the end of the orifice ring without blocking the inflow of airflow in the centripetal direction. In the part, the leakage air flow from the pressure surface side of the blade to the suction surface side,
(EN) A blower that prevents collision with an airflow flowing in the centripetal direction from the outer peripheral portion of an impeller, suppresses turbulence of the airflow, and reduces blast noise.

[0010]

In order to solve the above problems, the blower of the present invention has a first orifice ring fixed to the blade tip of the outer peripheral portion of an axial flow impeller or a mixed flow impeller,
The impeller and the first orifice ring are integrally rotatable, and a second orifice ring is provided on the discharge side of the first orifice ring in the vicinity of the first orifice ring, and the outer peripheral end of the blade is The axial length of the first orifice ring is shortened at a portion sufficiently distant from the suction side end portion of the first orifice ring,
The axial length of the first orifice ring is made longer at the portion where the outer peripheral end of the blade is located closer to the suction side than the end portion of the first orifice ring.

According to another aspect of the present invention, a first orifice ring is fixed to a tip of a blade on an outer peripheral portion of an axial flow impeller or a mixed flow impeller, and the impeller and the first orifice ring are integrally rotatable. First on the discharge side of the first orifice ring
Second orifice ring is provided in the vicinity of the orifice ring of the first orifice ring, and the outer peripheral end of the blade is sufficiently separated from the suction side end of the first orifice ring to the suction side. The curvature is made small, and the curvature of the tip of the first orifice ring is made large at the portion where the outer peripheral end of the blade is located nearer the suction side than the end portion of the first orifice ring.

[0012]

With this configuration, the first orifice ring and the impeller are fixed at the blade tip of the outer peripheral portion and rotate integrally, and the outer peripheral edge of the blade is positioned sufficiently away from the first orifice ring on the suction side. In the portion where the air flow in the centripetal direction is not blocked, the outer edge of the trailing edge of the blade is located closer to the suction side than the end of the first orifice ring in the first orifice ring. The wall surface prevents the airflow from leaking from the pressure surface side of the blade to the suction surface side, and prevents collision with the inflow airflow from the outer peripheral portion of the impeller toward the centripetal direction.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A blower according to an embodiment of the present invention will be described below with reference to the drawings. The same parts as those of the conventional example are designated by the same reference numerals and the description thereof will be omitted.

1 and 2 show the structure of a blower according to the first embodiment of the present invention. Reference numeral 7 is an axial blower body, 8 is an impeller, 9 is a blade of the impeller 8, 9a is a rear edge of the blade 9, 9b is a front edge of the blade 9, and 10 is a hub for fixing the blade 9. .. Reference numeral 11 denotes a first orifice ring provided on the outer peripheral portion between the front edge portion 9b and the rear edge portion 9a of the blade 9, which is adhesively fixed to the outer peripheral portion of the blade 9 and is rotatable integrally with the impeller 8.

Further, in the portion where the outer peripheral end 9c of the blade 9 is sufficiently separated from the suction side end 11a of the first orifice ring 11 on the suction side, the first orifice ring 1 is formed.
1 has its axial length shortened, and the outer peripheral end 9 of the blade 9 is
The axial length of the first orifice ring 11 is made longer in the portion where c is located closer to the suction side than the end portion 11b of the first orifice ring 11.

Numeral 12 is a second orifice provided on the discharge side of the first orifice ring 11 in the vicinity of the first orifice ring 11.
This is the orifice ring. Reference numeral 14 is a motor for rotating the impeller 8.

The operation of the axial blower configured as described above will be described below. First, the rotation of the motor 14 rotates the impeller 8 in a predetermined direction, air is sucked from the front edge portion 9b and the first orifice ring 11, and static pressure and dynamic pressure are added by the action of the blade 9, The air is discharged from the trailing edge portion 9a of the impeller 8, passes through the second orifice ring 12, and is discharged to the outside of the impeller 8 to perform a blowing action.

Here, in the vicinity of the inlet of the first orifice ring 11, an air flow I which is sucked in radially from the outer peripheral portion of the impeller 8 is generated, but as shown in FIG. At a portion located sufficiently away from the orifice ring 11 on the suction side, the air flow I in the centripetal direction flows into the impeller 8 as it is.

On the other hand, as shown in FIG. 4, at the portion where the outer peripheral edge 9c on the trailing edge side of the blade 9 is located closer to the suction side than the end portion 11 of the first orifice ring, the wall surface of the first orifice ring 11 is The airflow I that prevents leakage from the pressure surface side 9d of the blade 9 to the suction surface side 9e and is sucked in the radial direction I
And the leaked airflow from the pressure surface side of the blade 9 to the negative pressure surface side do not collide with each other, and the generation of turbulent noise due to the collision of flows is prevented.

Moreover, since the first orifice ring 11 and the impeller 8 are fixed at the outer peripheral blade tips and rotate integrally, the relative position of the blade 9 and the first orifice ring 11 in the circumferential direction is determined. It does not change due to the rotation of the impeller 8,
You can always maintain a stable state.

As described above, according to this embodiment, the impeller 8
And the first orifice ring 11 are integrally rotatable,
By increasing the axial length of the first orifice ring in the portion where the outer peripheral end of the blade 9 is located closer to the suction side than the end of the first orifice ring 11, the wall surface of the first orifice ring 11 is Leak airflow from the pressure surface side 9d of the blade 9 to the suction surface side 9e is not generated, and the collision of the airflow I sucked in the radial direction and the leak airflow from the pressure surface side of the blade 9 to the suction surface side is prevented.

Therefore, it is possible to prevent the leakage airflow of the blades from colliding with the inflow airflow in the centripetal direction, to suppress the increase of the turbulence of the airflow in the vicinity of the orifice, and to suppress the increase of the ventilation noise and the reduction of the ventilation efficiency due to the turbulence. You can Moreover, the blowing performance can be improved because the generation of leakage airflow is prevented.

The first orifice ring 11 and the second orifice ring 11
Since the orifice rings 12 are provided close to each other, the airflow on the surface of the orifice rings adheres to the surface of each orifice ring and flows, and there is almost no leakage of the airflow, and there is no risk of degrading the blowing performance. Although the axial flow impeller has been described as an example of the impeller in the present embodiment, a similar effect can be obtained with a mixed flow impeller.

A blower according to a second embodiment of the present invention will be described below with reference to the drawings. 5 and 6 show the structure of the blower in the second embodiment of the present invention. The difference from the first embodiment is that the outer peripheral edge 9c of the blade 9 is sufficiently farther away from the suction side end 15a of the first orifice ring 15 on the suction side than the suction side end of the first orifice ring 15. The curvature of the portion 15a is made small, and the outer peripheral end 9c of the blade 9 has the first orifice ring 15
In the portion located closer to the suction side than the end portion, the curvature of the suction side end portion 15b of the first orifice ring 15 is increased.

The operation of the axial blower configured as described above will be described below. First, the rotation of the motor 14 causes the impeller 8 to rotate in a predetermined direction, air is sucked from the leading edge side 9b and the first orifice ring 15, and static and dynamic pressures are added by the action of the blade 9. The air is discharged from the trailing edge portion 9a of the wheel 8, passes through the second orifice ring 12, and is discharged to the outside of the impeller 8 to perform a blowing action.

Here, in the vicinity of the inlet of the first orifice ring 15, an air flow I which is sucked in from the outer peripheral portion of the impeller 8 in the radial direction is generated, but as shown in FIG. In a portion located sufficiently away from the orifice ring 15 on the suction side, the air flow I in the centripetal direction flows without resistance along the orifice end portion 15a having a small curvature.

On the other hand, the outer peripheral edge 9c on the trailing edge side of the blade 9 is the first
In a portion located near the suction side from the end of the orifice ring 15, the wall surface of the first orifice ring 15 prevents leakage from the pressure surface side 9d of the blade 9 to the suction surface side 9e, and sucks in the radial direction. The generated air flow I does not collide with the leaked air flow from the pressure surface side 9d of the blade 9 to the negative pressure surface side 9e, and the generation of turbulent noise due to the flow collision is prevented.

Moreover, since the curvature of the end portion of the first orifice ring 15 is small in the portion where the inflow is large in the centripetal direction, the wall surface of the orifice ring 15 is collided with the airflow I from the outer peripheral portion of the impeller 8 in the centripetal direction. Even then, the air flow I adheres to the wall surface of the orifice ring 15, and the air flow is not disturbed by separation or the like, and the efficiency of the air flow into the impeller 8 is improved.

Since the first orifice ring 15 and the impeller 8 are fixed at the tip of the outer peripheral blade and rotate integrally, the relative position of the blade 9 and the first orifice ring 15 in the circumferential direction is It does not change due to the rotation of the impeller 8 and can always maintain a stable flow state.

As described above, according to this embodiment, the impeller 8
And the first orifice ring 15 are integrally rotatable,
At the portion where the outer peripheral end 9c of the blade 9 is sufficiently distant from the suction side end portion 15a of the first orifice ring 15 on the suction side, the curvature of the tip end portion 15a of the first orifice ring 15 is made small, and the outer peripheral end of the blade 9 is reduced. By increasing the curvature of the tip portion 15b of the first orifice ring 15 at the portion where 9c is located closer to the suction side than the end portion of the first orifice ring 15, from the pressure surface side of the blade 9 to the suction surface side. To prevent a collision with the air flow I directed from the outer peripheral portion of the impeller 8 toward the centripetal direction.

Therefore, it is possible to prevent the leakage airflow of the blades from colliding with the inflow airflow in the centripetal direction, to suppress the increase of the turbulence of the airflow near the orifice, and to suppress the increase of the ventilation noise and the reduction of the ventilation efficiency due to the turbulence. You can

Moreover, the generation of leakage airflow is prevented, and the efficiency of inflow of airflow into the impeller 8 is improved, so that the air blowing performance can be improved. The first orifice ring 15
Since the second orifice ring 12 and the second orifice ring 12 are provided close to each other, the air flow on the surface of the orifice ring adheres to the surface of each orifice ring and flows, so that there is almost no leakage of the air flow and there is no risk of degrading the blowing performance. Although the axial flow impeller has been described as an example of the impeller in the present embodiment, a similar effect can be obtained with a mixed flow impeller.

[0033]

As described above, in the blower of the present invention, the first orifice ring is fixed to the blade tip of the outer peripheral portion of the axial flow impeller or the mixed flow impeller, and the impeller and the first orifice ring are connected. A second orifice ring is provided on the discharge side of the first orifice ring in close proximity to the first orifice ring, and the outer peripheral end of the vane is the suction side end of the first orifice ring. The axial length of the first orifice ring is shortened at a portion farther away from the suction side, and the outer circumferential end of the blade is closer to the suction side than the end portion of the first orifice ring. No. 1 has a structure in which the axial length of the orifice ring is increased to prevent the leakage airflow of the blades, prevent the collision with the inflow airflow in the centripetal direction, and suppress the increase in the turbulence of the airflow near the orifice. It is possible to suppress deterioration in increased blowing efficiency of the blower noise due turbulence. Moreover, the blowing performance can be improved because the generation of leakage airflow is prevented.

Further, a first orifice ring is fixed to the tip of the outer peripheral portion of the axial flow impeller or the mixed flow impeller, and the impeller and the first orifice ring are made rotatable as a unit. A second orifice ring is provided close to the first orifice ring on the discharge side of the orifice ring, and the outer peripheral end of the blade is sufficiently separated from the suction side end of the first orifice ring to the suction side. Then, the curvature of the tip of the first orifice ring is made small,
In the portion where the outer peripheral edge of the blade is located closer to the suction side than the end portion of the first orifice ring, the curvature of the tip of the first orifice ring is made large, so that the leakage airflow of the blade and the inflow airflow in the centripetal direction are generated. Can be prevented, an increase in turbulence of the air flow near the orifice can be suppressed, and an increase in blast noise and a decrease in blast efficiency due to the turbulence can be suppressed. Moreover, since the airflow that flows in around the entire circumference of the first orifice ring is prevented, it is possible to prevent turbulent noise generated at the end surface of the orifice ring and improve the blowing performance.

[Brief description of drawings]

FIG. 1 is a bottom view of a blower according to an embodiment of the present invention.

FIG. 2 is a sectional view of the blower of the same embodiment.

FIG. 3 is a sectional view of an essential part showing an air flow of a blower according to the embodiment.

FIG. 4 is a sectional view of an essential part showing an air flow of a blower according to the embodiment.

FIG. 5 is a bottom view of the blower according to the second embodiment of the present invention.

FIG. 6 is a sectional view of the blower of the same embodiment.

FIG. 7 is a cross-sectional view of a main part showing an air flow of a blower according to the embodiment.

FIG. 8 is a cross-sectional view of a main part showing an air flow of a blower according to the embodiment.

FIG. 9 is a bottom view of a conventional blower

FIG. 10 is a sectional view of a conventional blower.

FIG. 11 is a cross-sectional view of a main part showing an air flow around a conventional blower.

FIG. 12 is a cross-sectional view of essential parts showing an air flow around a conventional blower.

[Explanation of symbols]

 8 Impeller 9 Blade 11 First Orifice Ring 11a End of First Orifice Ring 11b End of First Orifice Ring 12 Second Orifice Ring 15 First Orifice Ring 15a End of First Orifice Ring 15b End of first orifice ring

Claims (2)

[Claims] 1. A first orifice ring is fixed to a blade tip of an outer peripheral portion of an axial flow impeller or a mixed flow impeller so that the impeller and the first orifice ring are rotatable integrally. A second orifice ring is provided on the discharge side of the second orifice ring in the vicinity of the first orifice ring, and the outer peripheral end of the blade is sufficiently separated from the suction side end of the first orifice ring on the suction side. In the portion, the axial length of the first orifice ring is shortened, and in the portion where the outer peripheral end of the blade is located closer to the suction side than the end portion of the first orifice ring, the first orifice ring A blower with a long axial length. 2. The first orifice ring is fixed to the blade tip of the outer peripheral portion of the axial flow impeller or the mixed flow impeller so that the impeller and the first orifice ring are rotatable integrally. A second orifice ring is provided close to the first orifice ring on the discharge side of the first orifice ring, and the outer peripheral end of the blade is sufficiently separated from the suction side end of the first orifice ring to the suction side. In the portion where the first orifice ring has a small curvature, the outer peripheral edge of the blade is located in the vicinity of the suction side with respect to the end of the first orifice ring, and the first edge ring has the first curvature.
Blower with a large curvature at the tip of the orifice ring.