JP3138614B2 - Blower - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a blower using a once-through fan used for an indoor unit of an air conditioner, a ventilator, and the like.

[0002]

2. Description of the Related Art FIG. 36 is a cross-sectional view for explaining a streamline of an air flow in a blower using a conventional general cross-flow fan. In the figure, 1 is an impeller, 2 is a stabilizer, 3 is a rear guider, 4 is an inlet, 5 is an outlet, 12 is a casing cover, and most of the airflow sucked from the inlet 4 passes through the impeller 1. , Stabilizer 2, rear guider 3,
The air is discharged from the outlet 5 to the outside through the flow path constituted by the nozzle 11. This is a once-through flow 101. Also, 1
Reference numeral 00 denotes a circulating flow, which is a leakage flow 100a flowing between the impeller 1 and the stabilizer 2 from the outlet 5 to the inlet 4.
And a swirling flow 100b in the impeller 1. 10
Reference numerals 2 and 103 indicate positions on the impeller 1. As described above, inside the once-through fan, there is a circulating flow 100 not directly involved in the external work of the impeller and a once-through flow 101 directly involved in the external work of the impeller. However, the large circulating flow 100 existing near the stabilizer 2 hindered the once-through flow 101, making it difficult to increase the airflow.

As a prior art for increasing the air volume of the impeller 1, there is a blower using a cross-flow fan described in Japanese Patent Application Laid-Open No. 5-195981. FIG. In the drawing, 7 is a guide blade, 8 is a rotation center of the impeller 1, and 13 is an individual rotation blade. In this example, a circle concentric with the rotation center 8 of the impeller 1 is provided on the suction side of the impeller 1. A plurality of guide blades 7 are arranged in an arc. As described above, the guide blade 7 is used as a stationary blade cascade, and the once-through flow 101 flowing into the impeller 1 is given a pre-swirl in a direction opposite to the rotational direction, so that the angle of attack with respect to the rotary blade 13 is increased. 1 is increased.

[0004]

However, FIG.
Also in the conventional example shown in (1), a pre-swirl is given to the once-through flow flowing into the impeller 1 by using the stationary blade cascade 7 in the direction opposite to the rotation direction of the impeller 1 to increase the angle of attack with respect to the rotating blade 13. This increases the static pressure work and increases the once-through flow. However, depending on the set airflow, the angle of attack with respect to the rotating blades 13 is too large, and the rotating blades 13 may stall. It was difficult. In addition, while trying to improve the air volume by focusing on the once-through flow 101, no control is performed on the circulating flow 100 existing near the stabilizer, so that there is a limit in increasing the air volume. There was a problem.

The present invention has been made to solve such a conventional problem. The present invention is directed to controlling the circulating flow 100 and making the circulating flow 100 smaller to make the once-through flow 101 relatively larger. Further, it is intended to improve the aerodynamic performance by increasing the area where the impeller 1 performs the static pressure work. In addition, by increasing the impeller passage area of the once-through flow 101, the wind speed of the airflow passing through the impeller 1 at the same air volume is reduced, and accordingly, noise such as wind noise generated from the impeller 1 is reduced. And

[0006]

According to a first aspect of the present invention, there is provided an air blower using a once-through fan having an impeller, a stabilizer positioned close to and opposed to the impeller, and a rear guider forming a flow path. In the blower, on a section perpendicular to the rotation axis of the impeller, provided on a suction side of a straight line connecting a rotation axis of the impeller and a tip of the stabilizer as viewed from a suction side of the cross-flow fan, A resistor that returns a leakage flow flowing from the blow-off side of the cross-flow fan to the suction side between the car and the stabilizer into the impeller ;
Place the impeller and stabilizer between the resistor and the stabilizer.
There is a gap between the riser and the suction side.
It is those that.

A blower according to a second aspect of the present invention is the blower according to the first aspect, wherein the length between the closest position between the resistor and the stabilizer on a cross section perpendicular to the rotation axis of the impeller. the S _1, the diameter of the impeller when the D, S ₁
/ D is set to 0.05 or more and 0.50 or less.

According to a third aspect of the present invention, in the blower according to the first aspect, the center of gravity of the cross section of the resistor and the rotation axis of the impeller are arranged on a cross section perpendicular to the rotation axis of the impeller. Assuming that the projected length of the resistor with respect to the straight line passing through is S ₂ and the diameter of the impeller is D, S ₂ / D is greater than 0 and equal to or less than 0.30.

A blower according to a fourth aspect of the present invention is the blower according to the first aspect, wherein the blower is disposed between the closest position between the resistor and the impeller on a cross section perpendicular to the rotation axis of the impeller. Assuming that the length is S ₃ and the diameter of the impeller is D, S ₃ /
D is 0.02 or more and 0.15 or less.

According to a fifth aspect of the present invention, there is provided a blower according to the first aspect, wherein the center of gravity of the cross section of the resistor and the rotation axis of the impeller are formed on a cross section perpendicular to the rotation axis of the impeller. Assuming that the projected length of the resistor relative to a straight line passing through the cross-section center of gravity of the resistor and perpendicular to the straight line passing through the resistor is S ₄ and the diameter of the impeller is D, S ₄ / D is greater than 0 and equal to or less than 0.10. It was done.

A blower according to a sixth aspect of the present invention includes a plurality of resistors along the impeller.

A blower according to a seventh aspect of the present invention is the blower according to any one of the first to sixth aspects, wherein a heat exchanger is provided on the suction side or the blowout side of the once-through fan.

[0013]

In the blower according to the first aspect of the present invention, on a cross section perpendicular to the rotation axis of the impeller, the suction side is a straight line connecting the rotation axis of the impeller and the tip of the stabilizer as viewed from the suction side of the once-through fan. A resistor that returns a leakage flow flowing from the outlet side to the suction side of the once-through fan between the impeller and the stabilizer into the impeller , and
Between the antibody and stabilizer, the impeller and stabilizer
Between the inlet and the suction side of the once-through fan
Because of the gap, the area of the circulating flow can be suppressed, the flow-through portion can be increased, and the air volume at the same rotation speed of the impeller can be increased. Further, since the area of the flow-through portion is increased, the wind speed passing through the impeller at the same air volume is reduced, and accordingly, noise such as wind noise generated from the impeller can be reduced.

According to a second aspect of the present invention, in the blower according to the first aspect, the length between the closest position between the resistor and the stabilizer on a cross section perpendicular to the rotation axis of the impeller is determined. S ₁ , when the diameter of the impeller is D,
Since S ₁ / D is not less than 0.05 and not more than 0.50, it is possible to obtain a blower in which the air volume is further increased and the noise is further reduced.

In the blower according to a third aspect of the present invention, in the blower according to the first aspect, a cross section perpendicular to the rotation axis of the impeller passes through the cross-sectional center of gravity of the resistor and the rotation axis of the impeller. Assuming that the projected length of the resistor with respect to the straight line is S ₂ and the diameter of the impeller is D, S ₂ / D is greater than 0 and 0.30 or less. It is possible to suppress an increase in pressure loss of the resistor and prevent a decrease in air volume, thereby obtaining a blower in which air volume is further increased and noise is further reduced.

According to a fourth aspect of the present invention, in the blower according to the first aspect, the length between the closest position between the resistor and the impeller on a cross section perpendicular to the rotation axis of the impeller. Assuming that S ₃ is D and the diameter of the impeller is D, S ₃
Since / D is not less than 0.02 and not more than 0.15, it is possible to obtain a blower in which the air volume is further increased and the noise is further reduced.

In the blower according to a fifth aspect of the present invention, in the blower according to the first aspect, the cross section perpendicular to the rotation axis of the impeller passes through the cross-sectional center of gravity of the resistor and the rotation axis of the impeller. Assuming that the projected length of the resistor relative to a straight line that is perpendicular to the straight line and passes through the center of gravity of the cross section of the resistor is S ₄ , and the diameter of the impeller is D, S ₄ / D is greater than 0 and 0.10 or less. Therefore, it is possible to suppress an increase in pressure loss of the resistor with respect to the through-flow flowing from the suction port of the blower, prevent a decrease in the airflow, and obtain a blower in which the airflow is further increased and the noise is further reduced.

In the blower according to the sixth aspect of the present invention, since a plurality of resistors are provided along the impeller, a blower with a larger air volume and a lower noise can be obtained.

In the blower according to the seventh aspect of the present invention, since the heat exchanger is provided on the suction side or the blowout side of the once-through fan, the amount of air at the same rotation speed of the impeller can be increased, so that the input power is changed. Without exchanging heat, the amount of heat exchange can be increased.

[0020]

【Example】

Embodiment 1 FIG. FIG. 1 is a cross-sectional view showing a blower according to Embodiment 1 of the present invention, showing a cross section perpendicular to the rotation axis of the impeller. FIG. 2 is an explanatory diagram showing streamlines of the airflow inside the blower shown in FIG. 1. In the drawing, reference numeral 1 denotes an impeller, 2 denotes a stabilizer positioned close to / opposed to the impeller 1, 2a denotes a tip of the stabilizer viewed from a suction side, 3 denotes a rear guider that forms a flow path, and 3a denotes a suction side. The tip of the rear guider, 4 is a suction port, 5 is an outlet, 6 is a resistor, 8 is a rotating shaft of the impeller 1, 11 is a nozzle, 12 is a casing cover, and R is a rotation direction of the impeller 1. The impeller 1, the stabilizer 2, and the rear guider 3 form a once-through fan. Most of the airflow sucked from the inlet 4 passes through the impeller 1, the stabilizer 2, the rear guider 3, the nozzle 1
The air is discharged from the outlet 5 to the outside through the flow path constituted by 1. This is a once-through flow 101. Reference numeral 100 denotes a circulation flow, which includes a leakage flow 100a flowing from the outlet 5 to the suction port 4 between the impeller 1 and the stabilizer 2, and a swirling flow 100b in the impeller 1. 102, 103,
104 represents a position on the impeller 1. In this embodiment, the resistor 6 is connected to the rotating shaft 8 of the impeller 1 as shown in FIG.
And the tip 2 of the stabilizer viewed from the suction side 4 of the once-through fan
a is provided on the suction side 4 with respect to a straight line connecting the a and the cross section taken along a plane perpendicular to the rotation axis 8 of the impeller 1, is a rectangular flat plate type, and is provided between the impeller 1 and the stabilizer 2. Flow 1 flowing from the outlet side 5 to the suction side 4 of the once-through fan
00a into the impeller 1.

As described above, according to this embodiment, the leakage flow 100a flowing between the impeller 1 and the stabilizer 2 is suppressed by the resistor 6, and the impeller 1 is forced to flow into the impeller 1. 1. The circulation flow 100, which is a flow not directly involved in external work, was reduced. As a result, the suction area of the conventional impeller 1 shown in FIG.
2 to 103, but the resistance 6
0a, the suction area becomes from the position 102 to 104, the area for performing the static pressure work in the impeller 1 increases by the area from the position 103 to 104, and the once-through flow 101 also increases. did it. In addition, since the area of the suction area of the impeller 1 is increased by the area from the position 103 to the position 104, the wind speed of the impeller 1 at the same airflow decreases, and the noise such as wind noise generated from the impeller 1 is reduced. Can be reduced.

In FIG. 1, the rotating shaft 8 of the impeller 1
A straight line connecting the rotation shaft 8 of the impeller 1 and the tip 2a of the stabilizer 2 viewed from the suction side 4 of the cross-flow fan, the rotation shaft 8 of the impeller 1, and the tip 3 of the rear guider 3
It can be seen that there is a leakage flow 100a flowing from the outlet side 5 of the cross-flow fan to the suction side 4 on the side of the stabilizer 2 in a region where the angle α of the suction side 4 of the cross-flow fan formed by a straight line connecting to the straight line a. As can be seen from the 36 conventional examples. Therefore, it is preferable to dispose the resistor 6 in this region.

FIG. 1 shows a blower having a casing cover 12 on the suction side of the impeller 1.
Although the suction port 4 is installed in front of the blower, for example,
As shown in FIG. 3, not only the suction port 4a on the front surface, but also a blower provided with a suction port 4b on the top surface, and not only the suction ports 4a and 4b on the front surface and the top surface as shown in FIG. Although there is a blower provided with a suction port 4c, there is a leakage flow 100a flowing between the impeller 1 and the stabilizer 2 regardless of the location of the suction port 4, so that the resistor 6 is installed It is possible to improve the aerodynamic performance of the car 1 and reduce noise.

Further, in FIG. 1, the resistor 6 is of a flat plate type having a rectangular cross section, but any shape may be used as long as it acts as the resistor 6. For example,
A columnar resistor 6 having a circular cross section as shown in FIG.
And a rod-shaped resistor 6 having an elliptical cross section as shown in FIG. 6, and a plate-shaped resistor 6 having a curved cross section as shown in FIG. Further, the resistor 6 may be provided over the entire length direction along the rotation axis of the impeller 1, or may be provided on at least a part of the length direction. Furthermore, a plurality of pieces may be arranged at intervals in the length direction.

Embodiment 2 FIG. FIG. 8 is a cross-sectional view illustrating a blower according to Embodiment 2 of the present invention, and shows a cross section perpendicular to the rotation axis of the impeller. In FIG, S ₁ is the length between the position closest to the resistor 6 and the stabilizer 2 on the cross-section, D is the diameter of the impeller 1 on the cross section. FIG. 9 shows the ratio S ₁ / of the length S ₁ between the closest positions of the resistor 6 and the stabilizer 2 to the diameter D of the impeller 1.
FIG. 10 shows the measured value of the air volume on the air outlet side at a rotation speed of 750 rpm of the impeller 1 when D is changed. FIG. 10 shows the air volume of 7 m ³ / mi.
11 is a graph showing actual measured values of the noise at n, together with the case of a conventional blower without the resistor 6. In addition,
The measurement conditions are as shown in the table.

[0026]

[Table 1]

In FIG. 9, it can be seen that the air volume at the same rotational speed is larger than that of the conventional air blower without a resistor when S ₁ / D is 0.025 or more and 0.50 or less.
This is because the leakage flow 100a flowing between the impeller 1 and the stabilizer 2 can efficiently collide with the resistor 6 and be forced to flow into the impeller 1, particularly in the above range, and the circulating flow 100 And at the same time, the flow-through 10
1 indicates that the air volume can be increased since the value of 1 is relatively large. Note that, as S ₁ / D increases, the resistor 6 moves away from the stabilizer 2, the effect of suppressing the leakage flow 100 a decreases, and the air volume approaches a state without the resistor. In FIG. 10, the noise is S ₁ /
When D is in the range of 0.05 or more and 0.50 or less, it can be seen that the noise is lower than that of the blower without the resistor. This is because the number of rotations of the impeller 1 at the same amount of air has decreased due to an increase in the amount of air compared to the conventional blower, and the suction area at the impeller 1 has increased due to the installation of the resistor 6. It is considered that the noise is reduced due to a decrease in the wind speed of the airflow passing through the impeller 1 at the air volume. Therefore, S ₁ / D at which the air volume is equivalent to that of the conventional air blower is 0.1.
In a region larger than 5, the noise is equivalent to the state without the conventional resistor. Further, when the resistor 6 approaches the stabilizer 2, S
_{When 1} / D is less than 0.05, the leakage flow 100
Since the flow velocity of “a” increases and the pressure fluctuation in the resistor 6 increases, noise increases. Therefore, the length S ₁ between the closest position between the resistor 6 and the stabilizer 2
When the ratio S ₁ / D to the diameter D of the impeller is 0.05 or more and 0.50 or less, the air volume is increased as compared with a conventional blower using a cross-flow fan without a resistor, and further low noise can be realized. Note that the resistor 6 and the stabilizer 2 are formed as long as the impeller 1 along the rotation axis 8 of the impeller 1, but due to manufacturing errors and bending during operation, etc., the resistance element 6 and the stabilizer 2 are perpendicular to the rotation axis 8 of the impeller. a length S ₁ between the most adjacent position of the resistor 6 and the stabilizer 2 on cross section is slightly different with each cross section. Also in this case, it is preferable that S ₁ / D in each section is within the above range.

Although the above characteristic diagram only measures the case where the diameter D of the impeller 1 is 100 mm, it is shown in the literature ("Turbo Blower and Compressor" by Takefumi Ikui and Masahiro Inoue, Corona, p. 784). As described above, if the shape of the blower is similar, the following equation is established. (Air volume) / {(number of revolutions) × (diameter of impeller) ³ } = constant In addition, the following equation holds for noise. (Noise) -10 log {(diameter of impeller) ⁸ x (number of revolutions) ⁶ } = constant This means that by fixing the diameter D of the impeller 1, the air volume is proportional to the number of revolutions of the impeller 1. Even if the diameter of the impeller 1 changes, the characteristics do not change as long as the air volume is compared at the same impeller diameter and the same rotation speed. When the diameter of the impeller 1 is fixed, the number of revolutions is proportional to the air volume, so that (noise) −10 log (air volume) ⁶ = constant, and the noise is determined by the air volume. Therefore, as long as the noise is compared with the same impeller diameter and the same air volume, the characteristics do not change. By these, S to the diameter D of the impeller 1
By defining the ratio of the dimension of ₁ and the number of resistors 6, the streamline distribution as shown in FIG. 2 becomes the same, and the same effect of the resistor 6 can be obtained. Note that S ₂ , S ₃ ,
The same is true for S _4.

Embodiment 3 FIG. FIG. 11 is a cross-sectional view illustrating a blower according to Embodiment 3 of the present invention, and shows a cross section perpendicular to the rotation axis of the impeller. In the drawing, S ₂ is the center of gravity 7 of the cross section of the resistor 6 on the cross section and the rotating shaft 8 of the impeller 1.
Is the projection length of the resistor 6 with respect to the straight line 9 passing through. FIG. 12 is an actual measured value of the air volume on the air outlet side at a rotation speed of 750 rpm when the ratio S ₂ / D of the projected length S ₂ of the resistor 6 to the straight line 9 with respect to the diameter D of the impeller 1 is changed.
Is a graph showing actual measured values of noise at an air flow of 7 m ³ / min, together with the case of a conventional blower without the resistor 6. The measurement conditions are as shown in the table.

In FIG. 12, it can be seen that the air volume at the same rotational speed is greater than that of the conventional air blower without a resistor in the range where S ₂ / D is greater than 0 and equal to or less than 0.30. This is because the leakage flow 100a flowing between the impeller 1 and the stabilizer 2 particularly in the range described above is reduced by the resistor 6
And the forced flow into the impeller 1, thereby reducing the circulating flow 100 and simultaneously
Indicates that the air volume can be increased because the air volume is relatively large. The projected length S of the resistor 6
_When S ₂ / D at which ₂ increases becomes larger than 0.3, the resistor 6 causes a pressure loss with respect to the flow-through flow 101 flowing from the outside of the blower, and the air volume decreases. When the projected length S ₂ of the resistor 6 becomes short and approaches 0 (for example, S _{2 in} actual measurement)
(/ D is 0.02, which is smaller than 0.02), the effect of the resistor 6 is reduced, and the air flow asymptotically approaches the state without the resistor. In FIG. 13, the noise is S ₂ / D
Is greater than 0 and less than or equal to 0.30, which is lower in noise than the blower without the resistor. This is because the air volume increased from the conventional air blower, so that the impeller 1 at the same air volume was used.
The reduction in the number of revolutions and the reduction in noise due to the reduction in the wind speed passing through the impeller 1 at the same airflow due to the increased suction area in the impeller 1 due to the installation of the resistor 6 are doing. Therefore, in the range where S ₂ / D is larger than 0.3 where the air volume is smaller than that of the conventional blower, the noise is also worse than in the conventional state without the resistor. When the projected length S ₂ of the resistor 6 is short and S ₂ / D is close to 0,
Since the effect as the resistor is reduced and the amount of increase in the air volume is reduced, noise with the same air volume approaches a state without the resistor. Therefore, the cross-sectional center of gravity 7 of the resistor 6 and the rotating shaft 8 of the impeller 1
The ratio S ₂ / D of the projected length S ₂ of the resistor 6 to the diameter of the impeller 1 with respect to the straight line 9 passing through
In the following, the air volume is increased as compared with a conventional blower using a cross-flow fan without a resistor, and further low noise can be realized.
Note that the resistor 6 is arranged along the rotation axis 8 of the impeller 1.
Have been just as long form and by such bending during manufacturing errors and operation, the projection length S ₂ of the resistor is slightly different with each cross section. Also in this case, it is preferable that S ₂ / D in each section is within the above range.

Embodiment 4 FIG. FIG. 14 is a cross-sectional view illustrating a blower according to Embodiment 4 of the present invention, and shows a cross section perpendicular to the rotation axis of the impeller. In FIG, S ₃ is the length between the closest position to the resistor 6 and the impeller 1 on the cross section, 13 denotes a rotary blade of the impeller 1. FIG.
Length S ₃ between the closest position between resistor 6 and impeller 1
16 shows the actual measured value of the air flow at a rotation speed of 750 rpm of the impeller 1 when the ratio S ₃ / D to the diameter D of the impeller 1 was changed. FIG. 16 shows the actual measured value of the noise at an air flow of 7 m ³ / min. 7 is a graph shown in combination with a conventional blower having no symbol. The measurement conditions are as shown in the table.

In FIG. 15, it can be seen that the air volume at the same rotation speed is larger than that of the conventional air blower without a resistor in the range where S ₃ / D is 0.15 or less. This is because the leakage flow 100a flowing between the impeller 1 and the stabilizer 2 can collide with the resistor 6 and be forced to flow into the impeller 1, particularly in the above range, and the circulation flow 10
0 indicates that the flow rate can be increased since the once-through flow 101 becomes relatively large at the same time. Further, in a range where S ₃ / D at which the length S ₃ between the closest position between the resistor 6 and the impeller 1 becomes larger than S ₃ / D is larger than 0.15, the effect as the resistor 6 is reduced and the air volume is reduced. . In FIG. 16, the noise S ₃ / D is 0.02.
In the range of 0.15 or less, it can be seen that the noise is lower than that of the blower without the resistor. This is due to the fact that the airflow increased from the conventional blower, resulting in a decrease in the rotation speed of the impeller 1 at the same airflow, and the installation of the resistor 6 increased the suction area of the impeller 1. It is considered that the noise is reduced due to a decrease in the wind speed of the airflow passing through the impeller 1 at the same air volume. Therefore, in the range where S ₃ / D is larger than 0.15 at which the air volume is equivalent to that of the conventional air blower, the noise is also at the same level as in the state without the conventional resistor. When S ₃ / D at which resistor 6 approaches impeller 1 is smaller than 0.02, rotating blades 13 of impeller 1 are rotated.
When passing through the vicinity of the resistor 6, it receives a large lift fluctuation and generates a rotating sound, so that the noise becomes larger than that of the blower without the resistor. Therefore, when the ratio S ₃ / D of the length S ₃ between the closest position between the resistor 6 and the impeller 1 to the diameter D of the impeller 1 is 0.02 or more and 0.15 or less, the flow through without the conventional resistor is performed. The air volume is larger than that of a blower using a fan, and low noise can be realized. The resistor 6 is formed along the rotation axis 8 of the impeller 1 as long as the impeller 1, but due to a manufacturing error, deflection during operation, or the like, the resistor 6 has a cross section perpendicular to the rotation axis 8 of the impeller. the resistor 6 and the impeller 1 length S ₃ at positions closest to that there is a slightly different by each cross section in the. Also in this case, it is preferable that S ₃ / D in each section is within the above range.

Embodiment 5 FIG. FIG. 17 is a cross-sectional view illustrating a blower according to Embodiment 5 of the present invention, and shows a cross section perpendicular to the rotation axis of the impeller. In the figure, S ₄ is the cross-sectional center of gravity 7 of the resistor 6 on the cross section and the rotating shaft 8 of the impeller 1.
Represents the projected length of the resistor 6 with respect to a straight line 10 which is perpendicular to the straight line 9 connecting the FIG.
Is perpendicular to a straight line 9 connecting the cross-section center of gravity 7 of the resistor 6 and the rotation axis 8 of the impeller on an arbitrary cross-section perpendicular to the rotation axis 8 of the impeller 1 and passes through the cross-section center of gravity 7 of the resistance body 6. Straight line 10
When the ratio S ₄ / D of the projected length S ₄ of the resistor to the diameter D of the impeller 1 is changed, the rotation speed 75 of the impeller 1
The measured value of the air volume at 0 rpm, FIG. 19 shows the air volume of 7 m ³ /
It is the graph which showed the actual measurement value of the noise in min with the conventional blower which does not have the resistor 6, respectively. The measurement conditions are as shown in the table.

In FIG. 18, it can be seen that the air volume at the same rotation speed is larger than that of the conventional air blower without a resistor in the range where S ₄ / D is 0.10 or less. This is because the leakage flow 100a flowing between the impeller 1 and the stabilizer 2 collides with the resistor 6 and forcibly flows into the impeller 1, particularly in the above-mentioned range.
0 indicates that the flow rate can be increased since the once-through flow 101 becomes relatively large at the same time. Also, the projected length S ₄ of the resistor 6 becomes larger, S ₄ /
When D is greater than 0.10, the resistor has a pressure loss with respect to the once-through flow 101 flowing from the suction port, and the air volume decreases. In FIG. 19, the noise is S
_{When 4} / D is 0.10 or less, the noise level is lower than that of a blower without a resistor. This is because the air volume is more
Due to the increase, the number of revolutions of the impeller 1 at the same airflow is reduced, and the impeller 1 of the airflow at the same airflow due to the increased suction area at the impeller 1 by installing the resistor 6. The noise is reduced by the decrease in the passing wind speed. Therefore, in the range where S ₄ / D at which the air volume is lower than that of the conventional blower is greater than 0.10, the noise is also at the same level as in the state without the conventional resistor. Note that FIG.
, The cross-sectional center of gravity 7 of the resistor 6 and the rotating shaft 8 of the impeller 1
Perpendicular to the straight line 9 connecting the bets, S ₄ projection is the length of the resistor 6 for straight 10 passing through the cross-section gravity center 7 of the resistor 6, the resistor 6 is thinner the thickness thereof parallel to the line 9 Although it approaches 0 as much as possible, it is apparent that S ₄ / D is larger than 0 since it is impossible to make the thickness 0. Therefore, when the ratio S ₄ / D of the projected length S ₄ of the resistor 6 to the diameter D of the impeller 1 is larger than 0 and equal to or smaller than 0.10, the air volume is increased as compared with a conventional blower using a cross-flow fan without a resistor. In addition, low noise can be realized. Although resistor 6 is the rotary shaft 8 formed long about the same as the impeller 1 along the impeller 1 by such bending during manufacturing errors and operation, the projection length S ₄ of the resistor each May vary slightly by cross section. Also in this case, it is preferable that S ₄ / D in each section is within the above range.

Embodiment 6 FIG. FIG. 20 is a cross-sectional view illustrating a blower according to Embodiment 6 of the present invention. In the figure,
6a, 6b and 6c indicate respective resistors. FIG.
, In Example 6 of the present invention, the measured value of the volume of air at a rotation speed 750rpm of the impeller 1 when the number of the resistor is changed, FIG. 22 each resistor the measured value of the noise at the air volume 7m ³ / min 7 is a graph shown in combination with a conventional blower having no symbol. The measurement conditions are as shown in the table. Each of the resistors 6a, 6b, and 6c is a third embodiment to a fifth embodiment.
Are within the range of S ₂ / D, S ₃ / D, S ₄ / D,
Further, the resistor 6a located closest to the stabilizer 2
Is in the range of S ₁ / D shown in the second embodiment. The distance between the resistors 6a, 6b and 6c, that is, the length between the closest positions of the resistors is 10 mm.

In FIG. 21, it can be seen that the air volume at the same number of rotations is larger than that of the conventional air blower without resistors when the number of resistors is one or more and five or less. This is the leakage flow 1 flowing between the impeller 1 and the stabilizer 2.
00a collides with the resistor 6a and is forced to flow into the impeller 1. However, the airflow flowing without colliding with the resistor 6a due to the leakage flow 100a is applied to the impeller 1 by the next resistors 6b and 6c. This makes it possible to reduce the circulating flow 100 and increase the flow rate since the once-through flow 101 becomes relatively large. When the number of resistors becomes six or more, the once-through flow 1
On the other hand, since the resistor has a pressure loss, the air volume is reduced as compared with the case without the resistor. In FIG. 22, the number of resistors is one or more and five or less, and the noise is lower than that of the blower without the resistors. This is because the air volume increased from the conventional air blower, so that the impeller 1 at the same air volume was used.
The reduction in the number of revolutions and the reduction in noise due to the reduction in the wind speed passing through the impeller 1 at the same airflow due to the increased suction area in the impeller 1 due to the installation of the resistor 6 it seems to do. For this reason, in the range of six or more resistors whose air volume is lower than that of the conventional blower, the noise is worse than in the state without the conventional resistors. In addition, when the rotating blades 13 of the impeller 1 pass near the resistor, a large fluctuation in lift is generated and a rotating sound is generated. Increasing the number of resistors increases the number of times the rotating blades 13 undergo lift fluctuations, increasing the number of rotating sound sources and increasing noise. Therefore, by limiting the maximum value of the number of resistors, it is possible to obtain a blower that reduces the pressure loss and the sound source of the rotating sound, and has an effect of appropriately increasing the air volume and reducing the noise. Therefore, in this example, when the number of resistors is one or more and five or less, the air volume is increased as compared with a conventional blower using a cross-flow fan without resistors, and further low noise can be realized.

As described above, when the number of resistors is increased, a pressure loss occurs with respect to a flow through which flows in from outside the blower, and
This causes a decrease in air volume. In addition, when the rotating blades 13 of the impeller 1 pass near the resistor, a large fluctuation in lift is generated and a rotating sound is generated. Increasing the number of resistors increases the number of times the rotating blades undergo lift fluctuations, increasing the number of rotating sound sources and increasing noise. Therefore, by limiting the maximum value of the number of resistors, it is possible to obtain a blower that reduces the pressure loss and the sound source of the rotating sound, and has an effect of appropriately increasing the air volume and reducing the noise. In the above embodiment, the effect was obtained when the number of resistors was one or more and five or less, but there may be a case where the number may be five or more depending on conditions.

In FIG. 20, the rotating shaft 8 of the impeller 1 and the tip 2a of the stabilizer 2 viewed from the suction side 4 of the cross-flow fan are connected on an arbitrary cross section perpendicular to the rotating shaft 8 of the impeller 1. The angle α of the suction side 4 of the cross-flow fan, which is formed by a straight line connecting the rotating shaft 8 of the impeller 1 and the tip 3a of the rear guide 3
It can be seen from FIG. 36 that the leakage flow 100a flowing from the blow-off side 5 to the suction side 4 of the once-through fan exists on the side of the stabilizer 2 in the area where the is divided into two equal parts. Therefore, a plurality of resistors 6a, 6b,
6c is preferably arranged.

In the above-described embodiments 2 to 6, the case where the resistor 6 is of a flat plate type having a rectangular cross section has been described. However, the present invention is not limited to this. For example, as shown in FIG. Columnar resistor 6 with a circular cross section
Alternatively, a rod-shaped resistor 6 having an elliptical cross-sectional shape as shown in FIG. 6 or a plate-shaped resistor 6 having a curved cross-sectional shape as shown in FIG. 7 may be used. The same effect as the example can be obtained.

Embodiment 7 FIG. FIG. 23 is a cross-sectional view showing a blower according to Embodiment 7 of the present invention. In the figure, 14
Is a heat exchanger. By providing the heat exchanger 14 on the suction side or the blow-out side of the once-through fan, a blower using the once-through fan can function as an air conditioner. As described above, in the conventional air conditioner using a once-through fan, the resistor 6 is installed in the vicinity of the stabilizer 2 so that the airflow of the air conditioner at the same rotation speed of the impeller 1 can be increased. Therefore, it is possible to increase the heat exchange amount without changing the motor input value.

Although FIG. 23 shows a structure in which one heat exchanger 14 is installed on the suction side of the impeller 1, the impeller 1 and the stabilizer 2 can be used regardless of the installation location, form and number of heat exchangers. Because there is a leak flow 100a flowing between
By installing the resistor 6, the aerodynamic improvement and low noise of the impeller 1 are realized. For example, FIG.
FIG. 4 is a cross-sectional view showing an example in which a resistor 6 is installed in a leakage flow 100a flowing between an impeller 1 and a stabilizer 2 in a blower in which two heat exchangers are installed at 4a and an obliquely upper side 14b. . Also, instead of installing two heat exchangers in FIG. 24, it is also possible to bend one heat exchanger and install it in the same positional relationship. FIG. 25 shows the impeller 1
Three heat exchangers 14a, 1
It is a cross-sectional view showing an example in which a resistor 6 is installed in a leak flow 100a flowing between an impeller 1 and a stabilizer 2 in a blower in which 4b and 14c are arranged. Also, in FIG. 25, instead of installing three heat exchangers, two heat exchangers are used, and one of them is folded and installed on the front, diagonally above and back, or one heat exchanger is used. It is also possible to bend two places of the vessel and install them on the front, diagonally above and behind. FIG. 26 shows two diagonally upper and lower surfaces of the impeller 1.
A leak flow 100 flowing between the impeller 1 and the stabilizer 2 is supplied to the blower in which the heat exchangers 14b and 14c are arranged.
FIG. 3 is a cross-sectional view showing an example in which a resistor 6 is installed in FIG.
In FIG. 26, instead of installing two heat exchangers, one heat exchanger may be bent and installed diagonally above and behind. 23 to FIG.
6 shows the case where the heat exchanger is installed on the suction side of the once-through fan, but it may be installed on the outlet side.

Embodiment 8 FIG. FIG. 27 is a cross-sectional view showing a blower according to Embodiment 8 of the present invention. In the figure, 15
Is a pipe of a heat exchanger, and 16 is a member for attaching a resistor, and is made of, for example, a wire. In this example, the resistor 6 is supported by the pipe 15 of the heat exchanger 14 via the mounting member 16. FIG. 28 is a perspective view showing how the resistor 6 is fixed to the mounting member 16. The resistor 6 is fixed to the mounting member 16 by welding, for example, when the resistor 6 is a metal plate, or by increasing the contact area of the resistor 6 with the mounting member 16 when the resistor 6 is plastic. With an adhesive. In addition, the attachment to the heat exchanger 14 is performed by attaching the wire-like attachment member 16 to the heat exchanger 14.
27, or as shown in FIG.
5 so that the heat exchanger 14
It can be attached and detached integrally with the heater, making it easier to perform production and maintenance. In addition, when the blower receives an external impact, the resistor 6 does not collide with the heat exchanger 14 and is not damaged.

Embodiment 9 FIG. FIG. 29 is a cross-sectional view showing a blower according to Embodiment 9 of the present invention. In this example, the resistor 6 is supported by the stabilizer 2. FIG. 30 shows the resistor 6
FIG. 4 is a perspective view showing a state in which is supported by the stabilizer 2. By adopting a structure in which the resistor 6 is attached to the stabilizer 2 in this manner, it is possible to improve the attachment property and the productivity and to improve the accuracy of the distance between the resistor 6 and the stabilizer 2. Further, by fixing to the stabilizer 2 which is a member which is hardly deformed when receiving an external impact, the contact with the impeller 1 can be prevented, and the resistor 6 itself in the rotation axis direction of the impeller 1 can be prevented. Can be prevented from being deformed. In addition, by integrally forming the resistor 6 as a part of the stabilizer 2, it is possible to manufacture the stabilizer 2 by changing the shape thereof, and it is possible to reduce the cost for manufacturing the integrally formed product. As described in the second embodiment, since the stabilizer 2 and the resistor 6 are separated from each other to some extent, the effect of increasing the air volume and reducing the noise can be obtained.
As shown in FIG. 30, a mounting member 16 is attached between the resistor 6 and the stabilizer 2 to provide a hole 17. The distance between the stabilizer 2 and the resistor 6 is adjusted by adjusting the size of the hole 17.

Embodiment 10 FIG. FIG. 31 shows Embodiment 1 of the present invention.
1 is a cross-sectional view showing a blower according to FIG. In this example, the resistor 6 is attached to a part of the nozzle 11. As shown in FIG. 32, the mounting member 16 is attached to the resistor 6 and the nozzle 11
By adopting a method of fitting into or inserting the resistor, the resistor 6 can be easily installed and maintained, and the positioning accuracy of the distance from the stabilizer 2 can be improved. In addition, by integrally forming the resistor 6 with the nozzle 11, it is possible to manufacture the nozzle 11 by changing the shape of the nozzle 11, and it is possible to reduce the cost for manufacturing as an integrally formed product. Also, as described in the second embodiment, it is effective to increase the air volume and reduce noise if the stabilizer 2 and the resistor 6 are separated to some extent, and therefore, FIG.
As shown in FIG. 2, a mounting member 16 is provided between the resistor 6 and the stabilizer 2 to provide a hole 17. The distance between the stabilizer 2 and the resistor 6 is adjusted by adjusting the size of the hole 17.

Embodiment 11 FIG. FIG. 33 shows Embodiment 1 of the present invention.
FIG. 2 is a perspective view showing a main part of the blower of FIG. In this example, the resistor 6 is supported by the side plate 18 of the blower. FIG.
4 is a cross-sectional view showing a partial cross-section with the side plate 18 removed, and FIG. 35 is an enlarged perspective view showing the resistor 6. In this example, the mounting member 16 is provided on the resistor 6 and can be mounted when the side plate 18 is assembled. By adopting a method in which the resistor 6 is fitted to the side plates 18 on both sides of the blower, the positioning accuracy of the resistor 6 can be improved.

[0046]

As described above, according to the first aspect of the present invention, on the cross section perpendicular to the rotation axis of the impeller, the rotation axis of the impeller and the tip of the stabilizer viewed from the suction side of the once-through fan. provided on the suction side of a straight line connecting the leakage flow that flows to the suction side from the outlet side of the cross-flow fan between the impeller and the stabilizer comprises a resistor back into the impeller, or
Between the resistor and the stabilizer,
And the stabilizer, and the suction side of the once-through fan.
Because it has a communicating gap, it suppresses the area of circulating flow,
The flow rate can be increased at the same impeller speed by increasing the once-through flow portion. Further, since the area of the flow-through portion is increased, the wind speed passing through the impeller at the same air volume is reduced, and accordingly, noise such as wind noise generated from the impeller can be reduced.

According to the second aspect of the present invention, in the blower according to the first aspect, on a cross section perpendicular to the rotation axis of the impeller, the length between the closest positions between the resistor and the stabilizer is set to S. _1. Assuming that the diameter of the impeller is D, since S ₁ / D is 0.05 or more and 0.50 or less, the air volume is further increased, and a blower with further reduced noise is obtained.

According to a third aspect of the present invention, in the blower according to the first aspect, on a cross section perpendicular to the rotation axis of the impeller, a straight line passing through the center of gravity of the cross section of the resistor and the rotation axis of the impeller. Assuming that the projected length of the resistor is S ₂ and the diameter of the impeller is D, S ₂ / D is greater than 0 and equal to or less than 0.30, so that the resistance to the through-flow flowing from the suction port of the blower is provided. It is possible to suppress an increase in body pressure loss and prevent a decrease in air volume, and to obtain a blower in which air volume is further increased and noise is further reduced.

According to a fourth aspect of the present invention, in the blower according to the first aspect, the length between the closest position between the resistor and the impeller on a cross section perpendicular to the rotation axis of the impeller. Is S ₃ , and D is the diameter of the impeller, and S ₃ / D is 0.
Since it was set to 02 or more and 0.15 or less, the air volume increased further,
A blower with lower noise is obtained.

According to a fifth aspect of the present invention, in the blower according to the first aspect, on a cross section perpendicular to the rotation axis of the impeller, a straight line passing through the center of gravity of the cross section of the resistor and the rotation axis of the impeller. Assuming that the projected length of the resistor with respect to a straight line passing through the center of gravity of the cross section of the resistor and perpendicular to the axis is S ₄ , and the diameter of the impeller is D, S ₄ / D is larger than 0 and 0.10 or less. In addition, it is possible to suppress an increase in pressure loss of the resistor due to a flow through the air flowing from the suction port of the blower, prevent a decrease in the airflow, and obtain a blower in which the airflow is further increased and the noise is further reduced.

According to the sixth aspect of the present invention, since a plurality of resistors are provided along the impeller, an air blower having a further increased air volume and reduced noise can be obtained.

According to the seventh aspect of the present invention, since the heat exchanger is provided on the suction side or the discharge side of the once-through fan, the amount of air at the same rotation speed of the impeller can be increased, so that the input power is changed. Without increasing the heat exchange amount.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a blower according to Embodiment 1 of the present invention.

FIG. 2 is an explanatory diagram showing streamlines of an airflow inside the blower shown in FIG.

FIG. 3 is a cross-sectional view showing a modified example of the suction port of the blower according to Embodiment 1 of the present invention.

FIG. 4 is a cross-sectional view showing a modified example of the suction port of the blower according to Embodiment 1 of the present invention.

FIG. 5 is a cross-sectional view showing a modified example of the resistor of the blower according to Embodiment 1 of the present invention.

FIG. 6 is a cross-sectional view showing a modified example of the resistor of the blower according to Embodiment 1 of the present invention.

FIG. 7 is a cross-sectional view showing a modified example of the resistor of the blower according to Embodiment 1 of the present invention.

FIG. 8 is a cross-sectional view illustrating a blower according to a second embodiment of the present invention.

9 is a graph showing measured values of the rotational speed constant definitive air volume when changing the ratio of the distance S ₁ between the resistor and the stabilizer relative to the diameter D of the impeller in embodiment 2 of the present invention.

FIG. 10 shows a diameter D of an impeller in Embodiment 2 of the present invention.
6 is a graph showing actual measured values of noise at the same air volume when the ratio of the distance S ₁ between the resistor and the stabilizer to the resistance is changed.

FIG. 11 is a cross-sectional view illustrating a blower according to a third embodiment of the present invention.

FIG. 12 shows a diameter D of an impeller in Embodiment 3 of the present invention.
Is a graph showing measured values of the rotational speed constant definitive air amount when the ratio of the projected length S ₂ of the resistor is changed for.

FIG. 13 shows a diameter D of an impeller in Embodiment 3 of the present invention.
Is a graph showing measured values of the noise in the same air amount when the ratio of the projected length S ₂ of the resistor is changed for.

FIG. 14 is a cross-sectional view illustrating a blower according to a fourth embodiment of the present invention.

FIG. 15 shows a diameter D of an impeller in Embodiment 4 of the present invention.
Is a graph showing the measured values of the volume of air at a constant rotational speed of the impeller when the ratio of the distance S ₃ between the resistor and the impeller was varied for.

FIG. 16 shows a diameter D of an impeller in Embodiment 4 of the present invention.
7 is a graph showing actual measured values of noise at the same air volume when the ratio of the distance S ₃ between the resistor and the impeller to the resistance is changed.

FIG. 17 is a cross-sectional view illustrating a blower according to Embodiment 5 of the present invention.

FIG. 18 shows a diameter D of an impeller according to the fifth embodiment of the present invention.
Is a graph showing the measured values of the volume of air at a constant rotational speed of the impeller when the ratio of the projected length S ₄ of the resistor is changed for.

FIG. 19 shows the diameter D of the impeller in the fifth embodiment of the present invention.
Is a graph showing measured values of the noise in the same air amount when the ratio of the projected length S ₄ of the resistor is changed for.

FIG. 20 is a cross-sectional view illustrating a blower according to a sixth embodiment of the present invention.

FIG. 21 is a graph showing actual measured values of airflow at a constant rotation speed of an impeller when the number of resistors is changed according to Embodiment 6 of the present invention.

FIG. 22 is a graph showing actually measured values of noise at the same airflow when the number of resistors is changed in Embodiment 6 of the present invention.

FIG. 23 is a cross-sectional view illustrating a blower according to a seventh embodiment of the present invention.

FIG. 24 is a cross-sectional view showing a modification of the position of the heat exchanger of the blower according to Embodiment 7 of the present invention.

FIG. 25 is a cross-sectional view showing a modification of the position of the heat exchanger of the blower according to Embodiment 7 of the present invention.

FIG. 26 is a cross-sectional view showing a modification of the position of the heat exchanger of the blower according to Embodiment 7 of the present invention.

FIG. 27 is a cross-sectional view showing a blower according to Embodiment 8 of the present invention.

FIG. 28 is a perspective view showing a state in which a resistor in Embodiment 8 of the present invention is fixed to a mounting member.

FIG. 29 is a transverse sectional view showing a blower according to Embodiment 9 of the present invention.

FIG. 30 is a perspective view showing a state in which a resistor in a ninth embodiment of the present invention is supported by a stabilizer.

FIG. 31 is a cross-sectional view showing a blower according to Embodiment 10 of the present invention.

FIG. 32 is a perspective view showing a state in which a resistor in Embodiment 10 of the present invention is fixed to a mounting member.

FIG. 33 is a perspective view showing a main part of a blower according to Embodiment 11 of the present invention.

FIG. 34 is a cross-sectional view showing a blower according to Embodiment 11 of the present invention.

FIG. 35 is an enlarged perspective view showing a resistor according to Embodiment 11 of the present invention.

FIG. 36 is a cross-sectional view illustrating streamlines in a general blower using a conventional once-through fan.

FIG. 37 is a cross-sectional view showing a configuration of a main part of a blower using a cross-flow fan according to a conventional example.

[Explanation of symbols]

1 impeller, 2 stabilizer, 2a tip of stabilizer viewed from suction side, 3 rear guider, 3a tip of rear guider viewed from suction side, 4, 4a, 4b, 4c suction port, 5 outlets, 6, 6a, 6b, 6c resistor, 7
Cross-sectional center of gravity of resistor, rotating shaft of 8 impeller, 11 nozzle, 12 casing cover, 13 rotating blade, 14,
14a, 14b, 14c heat exchanger, 16 resistor mounting member, 17 holes, 18 side plate of blower, 100
Circulation flow, 100a leak flow, 100b swirl flow in the impeller, 101 flow-through flow.

Continuation of the front page (56) References Japanese Utility Model Sho-56-66088 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04D 17/04 F04D 29/28

Claims (7)

(57) [Claims] 1. A blower using a cross-flow fan having an impeller, a stabilizer positioned close to and opposed to the impeller, and a rear guider forming a flow path, wherein a cross section perpendicular to a rotation axis of the impeller is provided. The suction shaft is provided on the suction side with respect to a straight line connecting the rotating shaft of the impeller and the tip of the stabilizer as viewed from the suction side of the once-through fan, and suctions the space between the impeller and the stabilizer from the discharge side of the once-through fan. A resistor that returns the leakage flow flowing to the side into the impeller , and
The impeller and the switch are placed between the resistor and the stabilizer.
Communication between the stabilizer and the suction side of the once-through fan
An air blower characterized by having a gap to be formed. 2. On a section perpendicular to the rotation axis of the impeller, assuming that the length between the closest positions of the resistor and the stabilizer is S ₁ and the diameter of the impeller is D, S ₁ / D is 0.0
The blower according to claim 1, wherein the blower is set to 5 or more and 0.50 or less. 3. The projected length of the resistor on a section perpendicular to the axis of rotation of the impeller and a straight line passing through the center of gravity of the cross section of the resistor and the axis of rotation of the impeller is S ₂ , and the diameter of the impeller is To D
That the blowing device according to claim 1, characterized in that as large as 0.30 or less than 0 to S ₂ / D. 4. The length between the closest position between the resistor and the impeller on a section perpendicular to the rotation axis of the impeller is S ₃ ,
2. The blower according to claim 1, wherein S ₃ / D is 0.02 or more and 0.15 or less, where D is the diameter of the impeller. 5. A resistor perpendicular to a straight line passing through a cross-section center of gravity of the resistor and a rotation axis of the impeller on a cross section perpendicular to the rotation axis of the impeller and a straight line passing through the cross-section center of gravity of the resistor. Is the projected length of S ₄ and the diameter of the impeller is D,
2. The blower according to claim 1, wherein S ₄ / D is greater than 0 and less than or equal to 0.10. 6. The blower according to claim 1, wherein a plurality of resistors are provided along the impeller. 7. The blower according to claim 1, wherein a heat exchanger is provided on the suction side or the blowout side of the once-through fan.