KR20100134684A - Sirocco fan and air conditioner using the same - Google Patents

Abstract

Provided are a sirocco fan and an air conditioner using the same to reduce a sound generated when a predetermined amount of blowout air is supplied. In the sirocco fan 100 according to the present invention, the inlet port 2a is formed on both sides of the scroll casing 2 as an extension line of the rotation center of the fan 1, and thus, in the air passage 2c. Q [m 3 / min] is the quantity of air to receive the ventilation resistance from P [Pa], the inlet port 2a, the width of the fan 1 in the rotational axis direction is L [mm], k is an integer, and the scroll casing ( a height of 2) in the case of H = 246k [㎜], the loss factor ^{P / Q 2 (ξ) [} Pa / (㎥ / min) 2], in the range of 0.1≤k ⁴ ξ≤0.4, f ( k ⁴ ξ) = 0.34947 (k ⁴ ξ) ² -1.0554 (k ⁴ ξ) + 1.8, and 0.75f (k ⁴ ξ) ≤ L / H ≤ f (k ⁴ ξ).

Description

Sirocco fan and air conditioner using it {SIROCCO FAN AND AIR CONDITIONER USING THE SAME}

The present invention relates to a sirocco fan and an air conditioner using the same, and more particularly, to a sirocco fan and an air conditioner using the same to reduce noise generated.

Conventionally, there exists a sirocco fan which has a cylindrical shape and is a multi-centrifugal fan capable of blowing a wide strip of wind in the air-conditioning target area. This sirocco fan is often used for an indoor unit, a dehumidifier, an air purifier, etc. constituting an air conditioner. Such a sirocco fan is generally configured by arranging a plurality of elongated wing plates on a circumference and accommodating a fan having a cylindrical shape as a whole in a scroll casing provided with a suction port and a blowout port. The sirocco fan is configured to receive air therein from the inlet port and blow the air taken in from the outlet side to the air conditioning target area.

As such, a plurality of multi-centrifugal fan units connected to each other along a same axis of rotation with a space therebetween and a casing accommodating the plurality of connected multi-centrifugal fan units are provided, and the casing includes the plurality of multi-centrifugal fans. A blower flow path is formed for blowing air discharged from the unit to the outside, and the blower flow path is a multi-flow fan whose common flow path is continuous with respect to the plurality of multi-centrifugal fan units. , Patent Document 1).

Patent document 1: Unexamined-Japanese-Patent No. 11-324984 (the 5th page, 7-8 degrees)

In the conventional multi-wing fan, when the loss factor of the operating point is small and the operating point is on the open side of the surging region, there is a problem that the width of the fan is shorter and the noise generated at a predetermined amount of air increases. That is, in such a sirocco fan, when supplying a predetermined amount of blowout air volume to the air conditioning target station, the sound generated from the fan becomes loud, and it becomes a noise and is transmitted to the air conditioning target station, which may cause discomfort to the user. In addition, if the predetermined noise level is lowered, the amount of blown air blown out from the sirocco fan decreases, and if the amount of blown air blown out is increased, the noise level is increased, and it is difficult to achieve a proper balance between the amount of blown air and generation of sound. In addition, when the fan width is short and the loss factor is small, there is a problem that the fan diameter must be unnecessarily increased in order to reduce the noise. Moreover, when using such a sirocco fan for an air conditioner, if the fan width is short, and if there is a heat exchanger on the downstream side of the fan, the speed distribution in the width direction of the heat exchanger is uneven, and the heat transfer performance of the heat exchanger is deteriorated, There is also a problem that power consumption increases. Another problem is that the relationship between the loss factor and the fan width is unclear.

This invention is made | formed in order to solve the said problem, and an object of this invention is to provide the sirocco fan and the air conditioner using the same which reduced the sound which generate | occur | produces when supplying predetermined amount of blowing air volume.

A sirocco fan according to the present invention includes a scroll casing having an intake port for receiving air, a blowout port for blowing air, and an air path from the intake port to the blowout port, and accommodated in the scroll casing and rotationally driven, thereby allowing the intake port to rotate. And a bell mouse attached to the suction port of the scroll casing, the suction port being on an extension line of the rotation center of the fan, on both sides of the scroll casing. In the air flow path, the airflow resistance in the air path is P [Pa], the amount of air taken in by the suction port is Q [m 3 / min], and the width in the direction of the rotational axis of the fan is L [mm], k. When the height of the scroll casing is H = 246 k [mm] and P / Q ² is the loss factor ξ [Pa / (m 3 / min) ² ], the value is 0.1 ≦ k ⁴ ξ ≦ 0.4. In the range, f (k ⁴ ξ) = 0 .34947 (k ⁴ ξ) ² -1.0554 (k ⁴ ξ) + 1.8, and 0.75f (k ⁴ ξ) ≤ L / H ≤ f (k ⁴ ξ).

A sirocco fan according to the present invention includes a scroll casing having an intake port for receiving air, a blowout port for blowing air, and an air path from the intake port to the blowout port, and accommodated in the scroll casing and rotationally driven, thereby allowing the intake port to rotate. And a bell mouse attached to the suction port of the scroll casing, wherein the suction port is on an extension line of the rotational center of the fan, and has one side of the scroll casing. In the air flow path, the airflow resistance in the air path is P [Pa], the amount of air to be taken in by the suction port is Q [m 3 / min], and the width in the direction of the rotational axis of the fan is L [mm], k. When 0.1 is an integer and the height of the scroll casing is H = 246 k [mm] and P / Q ² is the loss factor ξ [Pa / (m 3 / min) ² ], 0.1 ≦ k ⁴ ξ ≦ 0.4 In the range of g (k ⁴ ξ) = 1 .39788 (k ⁴ ξ) is characterized in that in a ² -2.1108 (k ⁴ ξ) to +1.8, and ^{1.5g (k 4 ξ) ≤L /} H≤2g (k 4 ξ).

Moreover, the air conditioner which concerns on this invention was characterized by using the sirocco fan mentioned above.

According to the sirocco fan according to the present invention, since the fan width is determined only on the basis of a predetermined formula such that the operating point of the fan is within a predetermined range, it is possible to balance the amount of air blown out with the noise, so that a predetermined amount of blown out It is possible to effectively reduce the sound generated when supplying.

1 is a perspective perspective view showing the inside of a sirocco fan according to an embodiment of the present invention.
Figure 2 is a perspective view showing the overall shape of the fan.
3 is a sectional view showing a schematic longitudinal section configuration of a sirocco fan.
4 is a graph showing PQ characteristics and Ks-Q characteristics of a sirocco fan.
5 is a graph showing the relationship between L ₀ / H ₀ and a loss factor (ξ ₀ ) of a sirocco fan.
6 is a graph showing PQ characteristics and Ks-Q characteristics of a sirocco fan when passing through operating point A;
7 is a graph showing the relationship between the air volume between the blades of each fan blade and the position of the blade.
8 is a schematic cross-sectional view showing a longitudinal section configuration of a bell mouse.
Fig. 9 is a perspective view of the sirocco fan showing the region α of the bell mouse.
Fig. 10 is an enlarged view of the region α showing the rms value of the static pressure variation on the wall surface of the region α without a step;
Fig. 11 is an enlarged view of the region α showing the rms value of the static pressure fluctuation on the wall surface of the stepped region α.
12 is a longitudinal sectional view showing a schematic cross-sectional configuration of a sirocco fan.
Fig. 13 is a perspective perspective view of the sirocco fan as shown in perspective.
14 is a graph showing PQ characteristics of a sirocco fan when passing through operating point B. FIG.
Fig. 15 is a plan view showing a schematic overall configuration of an indoor unit suspended from a ceiling mounted with a sirocco fan.
Fig. 16 is a sectional view showing the vertical cross section of the indoor unit suspended from the ceiling.
Fig. 17 is a table showing noise values in an indoor unit suspended from the ceiling.
FIG. 18 is a schematic configuration diagram showing a schematic configuration of an air conditioner according to Embodiment 2 of the present invention. FIG.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described based on drawing.

Embodiment 1

1 is a perspective perspective view showing the inside of the sirocco fan 100 according to Embodiment 1 of the present invention. 2 is a perspective view showing the overall shape of the fan 1. 3 is a schematic longitudinal cross-sectional view illustrating a cross-sectional configuration of the sirocco fan 100. Based on FIGS. 1-3, the whole structure of the sirocco fan 100 is demonstrated. This sirocco fan 100 is used for an indoor unit, a dehumidifier, an air cleaner, etc. which constitute an air conditioner such as an air conditioner or a dehumidifier. In addition, including the FIG. 1, in the following drawings, the relationship of the magnitude | size of each structural member may differ from an actual thing.

As shown in FIG. 1, the sirocco fan 100 arrange | positions several elongate blade boards (blades) on the circumference, and accommodates the fan 1 and the fan 1 which become cylindrical shape as a whole. And a bell mouth (3) attached to both sides of the scroll casing (2) on the scroll casing (2) forming an air path therein and on an extension line of the rotation center of the fan (hereinafter only referred to as a rotation axis). It consists of). The fan 1 has a center of rotation, rotates, sucks in air, and blows out the air. The scroll casing 2 includes an inlet port 2a having an opening formed on a rotating shaft, an outlet port 2b for blowing air received from the inlet port 2a toward the target area, and a rotational circumferential direction of the fan 1. It is formed in the scroll casing shape (curve shape), and is comprised by the air path 2c which communicates the suction port 2a and the blowout port 2b.

The bell mouth 3 has an opening and is attached to the inlet port 2a of the scroll casing 2, and the air received from the inlet port 2a is concentrated and accelerated to be supplied to the fan 1. . The fan 1 may be configured such that the fan diameter D is, for example, φ192 mm, the width dimension L is, for example, 150 to 400 mm, and the number of vanes is 40, for example. The scroll casing 2 may be configured such that the scroll casing height H is 246 mm. In addition, the shape of the bell mouth 3 is not specifically limited, For example, what is necessary is just to determine according to the length of the fan diameter D. As shown in FIG.

4 is a graph showing PQ characteristics and Ks-Q characteristics of the sirocco fan 100. Based on FIG. 4, PQ characteristic and Ks-Q characteristic of the sirocco fan 100 are demonstrated. Here, P represents static pressure [Pa], Q represents air volume [m 3 / min], and Ks represents non-noise [dB], respectively. In addition, non-noise (Ks) is, was derived on the basis of the expression _{Ks = SPL-10 · log 10} (P · Q 2 .5). In addition, SPL represents the noise level and is generated from the sirocco fan 100 at a position about 1 m away from the center of the bell mouse 3 attached to the suction port 2a of the scroll casing 2 along the rotation axis. The noise measured value is used. In addition, black circles indicate PQ characteristics and solid white circles indicate Ks-Q characteristics. 1 to 3 indicate operating points.

The P-Q characteristic shows the relationship between the positive pressure P (left vertical axis) which is ventilation resistance, and the air volume Q (horizontal axis) in the state which made the rotation speed of the fan 1 constant. As indicated by the black circled marks in FIG. 4, the smaller the static pressure, the easier the wind flows in the air path 2c, and the larger the positive pressure, the more difficult the wind flows in the air path 2c. That is, at the operating point 3, the air volume is easy to be obtained, and at the operating point 1, the air volume is difficult to be obtained. Therefore, the smaller the static pressure, the larger the air volume, and the larger the static pressure, the smaller the air volume. In addition, in the following description, the low wind volume side while being fixed pressure is called the finishing side (left upper side of a graph), and the high wind volume side while being low static pressure is called an open side (lower side of a graph).

However, as shown in FIG. 4, even if the air volume becomes small, the area | region in which static pressure becomes small exists locally. This area is called a surging area (broken line encirclement shown in Fig. 4). In such surging region, the flow of air in the air passage 2c tends to be unstable. In other words, the surging region is a region that is likely to cause abnormal sound due to unstable air flow. In addition, the non-noise Ks (right vertical axis) becomes large when the airflow quantity Q increases, as shown by the white circle | round | yen circle display of FIG. This non-noise Ks is a noise value which considered the static pressure P and the air volume Q.

5 is a graph showing the relationship between L ₀ / H ₀ and the loss factor ξ of the sirocco fan 100. Also on the basis of 5, a description will be given of the relationship between the sirocco fan L ₀ / H ₀ and the loss factor (ξ ₀₎ (100). 5, the scroll casing height H ₀ is fixed at 246 mm, the fan width dimension L ₀ is changed to 150 to 500 mm, and the loss factor ξ ₀ = P ₀ / Q ₀ ² [Pa / (M ₃ / min) ² ], the relationship between L ₀ / H ₀ and the loss factor (ξ ₀ ) is shown using the width dimension L ₀ at which the specific noise Ks becomes the minimum. In FIG. 5, the vertical axis represents L ₀ / H ₀ , and the horizontal axis represents the loss coefficient ξ ₀ , respectively.

Loss coefficient ξ ₀ = P ₀ / Q ₀ ² indicates that, on the PQ characteristics shown in FIG. 4, the larger the loss coefficient ξ ₀ , the more the finish side, and the smaller the loss coefficient ξ ₀ , the open side. . In addition, a loss factor is a value calculated | required by the position of the operating point P and Q mentioned later. In addition, L ₀ / H ₀ is, indicates the ratio of the case in which the fixed scroll casing height (H ₀₎ and the change in the width (L _0). It can be seen from this FIG. 5 that the width dimension L ₀ at which the non-noise Ks becomes the minimum is changed by the loss factor ξ ₀ . In other words, the smaller the loss coefficient ξ ₀ is, the longer the width dimension L ₀ at which the non-noise Ks becomes minimum. Therefore, from Fig. 5, when the loss coefficient ξ is in the range of 0.1 ≦ ξ ≦ 0.4, f (ξ ₀ ) = 0.34947ξ ₀ ² -1.0554ξ ₀ +1.8, and L ₀ / H ₀ = f When (ξ ₀ ), the non-noise Ks is minimum. In addition, f (ξ ₀ ) = 0.34947ξ ₀ ² -1.0554ξ ₀ +1.8 is an equation calculated from the graph shown in FIG. 5.

Next, the reason why the specific noise Ks changes is explained by the loss factor ξ ₀ and the width dimension L ₀ .

FIG. 6 is a graph showing PQ characteristics and Ks-Q characteristics of the sirocco fan 100 when the width dimension L ₀ is 230 or 300 mm and passes through the operating point A. FIG. In addition, the black circled circle indicates the PQ characteristics when the width dimension L is 230 mm, and the white circle circle indicates the PQ characteristic when the width dimension L ₀ is 300 mm. the Ks-Q characteristic of the case displays a width dimension (L ₀₎ to 230㎜, it shows a Ks-Q characteristic of the case lie one to the white triangle mark width (L ₀₎ to 300㎜ respectively. The operating point described here is determined by the design air flow rate of the unit and the design static pressure (ventilation resistance of the heat exchanger, air flow resistance of the unit, air flow resistance of the air duct of the duct, ventilation resistance by a filter, etc.).

In the case where the width dimension L ₀ is set to 230 mm and 300 mm, when the PQ characteristic passing through the operating point A is compared, the longer the 300 mm width dimension L ₀ is, the surging region is the PQ characteristic. It turns out that it moves to the lower right (open side) of a graph, and is approaching operating point A. From the PQ characteristic and the Ks-Q characteristic shown in FIG. 6, it can be seen that the operating point at which the non-noise Ks is minimum is in the vicinity of the surging region. However, if the operating point is in the surging region or near the surging region, the flow becomes unstable, back suction, abnormal sound occurs, or time fluctuation of the air volume increases. Therefore, when forming a stable flow reliably, it is necessary to make an operating point open rather than a surging area.

That is, for a certain operating point P and Q, when the volume of the fan is increased, the surging region moves to the lower right in the P-Q characteristic diagram. At this time, the farther away the operating point is from the surging area to the open side (that is, the lower right side of the P-Q characteristic diagram), the more likely the abnormal sound is to occur. This is because the static pressure fluctuations increase in the region of the casing (2b1 shown in FIG. 3) and the short distance to the fan of the bell mouse. In the present invention, by increasing the volume of the fan with respect to the predetermined operating point and moving the surging region, the operating point and the surging region are approached as much as possible to reduce the noise generated.

Here, in order to increase the volume of the fan, it is considered that the fan diameter is increased or the fan width is increased. However, when the fan diameter is increased, the unit height becomes unnecessarily large. According to the present invention, the fan height can be made larger than before, and the relationship between the operating point and the surging area can be optimized, thereby reducing the installation constraints of the unit and reducing noise. You can get units.

FIG. 7 is a graph showing the relationship between the air volume between the blades for each blade plate of the fan 1 and the position of the blade plate. Based on FIG. 7, the relationship between the air volume between the blade | wings of every blade board of the fan 1 which comprises the sirocco fan 100, and the position of a blade board is demonstrated. In this FIG. 7, the vertical axis | shaft has shown the air volume (m <3> / min) between each wing | blade, and the horizontal axis | shaft has shown the position of a blade | plate respectively. In addition, in FIG. 7, the black circled circle shows the relationship between the air volume between the blades per wing sheet at the operating point 1, and the position of the wing plate. The relationship between the air volume between the wing | blade and the position of a wing plate shows the relationship between the air volume between a wing | blade for every one wing plate in the operating point 3, and the position of a wing plate, respectively.

In addition, in FIG. 7, the air volume between the blades of each of the blade | wing boards of the fan 1 shown to a vertical axis | shaft is a case where the wind is a flow from the inner peripheral side to the outer peripheral side of a wing (wing plate), The case where the wind is a flow from the outer peripheral side of the wing to the inner peripheral side is shown as negative. In addition, in FIG. 7, the position of the wing plate shown on the horizontal axis is represented by the hour hand of a clock. That is, the position of a wing plate is substituted and represented by the position of the minute hand of the clock from 0: 0 to 12: 0. In addition, it is assumed that the operating points 1 to 3 shown in FIG. 7 represent the same operating points as the operating points 1 to 3 shown in FIG. 4.

As shown in FIG. 7, it turns out that when the position of a wing plate is near 10:30, the air volume between wings is larger as the open side, and it becomes smaller as a finishing side. In addition, it turns out that a remarkable difference does not appear in the area | region other than 9: 30-11: 30 between air volume. If the air volume between the wings is Qi (i = 1 to 40 when the number of blade plates is 40), the expression (expression (expression ( 1) and formula (2) hold.

Formula (1) SPL∝Σ10log ₁₀ Qi ⁶

Formula (2) W∝ΣQi ³

Therefore, the more uniform the distribution of the air volume Qi between the blades, the smaller the noise value SPL and the fan input value W are. That is, in the case of the operating point 1 close to the surging region as shown in FIG. 4, since the distribution of the air volume Qi between the wings is uniform, the non-noise Ks is minimized. Here, as described above, inversely, the closer the operating point is to the surging region, that is, the closer to L ₀ / H ₀ = f (ξ ₀ ), the smaller the non-noise Ks is, but L ₀ / H ₀ = f When (ξ ₀ ) is exceeded, the operating point is included in the surging region, and conversely, the non-noise Ks deteriorates. On the other hand, when the operating point is farther away from the surging area, the farther away the casing (2b1 shown in Fig. 3) and the shorter distance from the fan of the bell mouse, the static pressure fluctuation increases, so that abnormal noise is generated. Easier

So, 0 <n≤1, L ₀ / H ₀ = n × f (ξ ₀ ), in a case where the loss factor is small (the air volume is large and the ventilation resistance is small), that is, in the range of 0.1 ≦ ξ ₀ ≤ 0.4 The minimum n at which no abnormal sound occurs was found to be n = 0.75. Therefore, in a condition where the loss factor is small (large air volume and small ventilation resistance), that is, in a range of 0.1≤ξ ₀ ≤ 0.4, 0.75f (ξ ₀ ) ≤ L ₀ / H ₀ ≤f (ξ ₀ ) The non-noise Ks is small, and it can be said that the flow which does not generate an abnormal noise can be formed.

In the above description, the case where the casing height H ₀ = 246 mm has been described, but the case where the dimensions of the casing height are generalized will be described. Let k be an integer and let H = kH ₀ , L = kL ₀ , and D = kD ₀ . When the dimension changes, the following formulas (formula (3) and formula (4)) hold for P and Q according to similar rules. Here, N is rotation speed.

Equation (3) P = P ₀ (D / D ₀ ) ² (N / N ₀ ) ²

Equation (4) Q = Q ₀ (D / D ₀ ) ³ (N / N ₀ )

From equations (3) and (4), if N / N ₀ is eliminated and summed up, equation (5) holds.

Equation (5) P ₀ / Q ₀ ² = P / Q ² (D / D ₀ ) ⁴

If ξ = P / Q ² and D = kD ₀ are substituted into this equation (5), equation (6) holds.

Equation (6) ξ ₀ = k ⁴ ξ

Using equation (6) and H = kH ₀ , L = kL ₀ ,

0.1≤ξ ₀ ≤ 0.4, 0.1≤k ⁴ ξ≤0.4

0.75f as _{(ξ 0) ≤L 0 / H} 0 ≤f (ξ 0) ^{is, 0.75f (k 4 ξ) ≤L} / H≤f (k 4 ξ), can be generalized.

That is, when the fan 1 is used in an air conditioner provided with a heat exchanger downstream of the fan, in a condition where the loss factor is small (a large amount of air and a small ventilation resistance), the fan width is increased to increase the noise. Since the velocity distribution in the width direction of the heat exchanger is uniformly close, it is finished without unnecessarily increasing the power consumption of the compressor.

Next, the case where the sirocco fan 100 is a piece suction type | mold is demonstrated.

What is necessary is just to replace L / 2 mentioned above by L / 2, and Q / 2 by Q / 2. And when g (ξ) = f {P / (Q / 2) ² }, g (k ⁴ ξ) = 1.39788 (k ⁴ ξ) ² -2.1108 (k ⁴ ξ) +1.8, and 1.5g ( k ⁴ ξ) ≤ L / H ≤ 2 g (k ⁴ ξ). That is, by a sirocco fan 100 at a range of In this case, end-suction ^{type, 0.1≤k 4 ξ≤0.4, 1.5g (k} 4 ξ) ≤L / H≤2g (k 4 ξ), non-noise (Ks) This small and abnormal unit can be formed.

In the above description, the case of the sirocco fan 100 alone is explained. However, the operation point when the sirocco fan 100 is mounted in a unit such as an air conditioner, a dehumidifier, or an air purifier is similarly determined. Can be. In such a case, the rotation speed N _{1 of the} unit and the air volume Q ₁ of the unit are obtained, and the rotation speed N ₁ and the air volume Q ₁ are used from the PQ characteristics of the sirocco fan 100 alone. It is good to calculate the static pressure P ₁ . In the case where m fans are mounted in the unit, the loss coefficient may be obtained by setting the air volume of one fan to Q ₁ / m and the static pressure to P ₁ .

As is apparent from the above description, the sirocco fan 100 is positive (兩) when the suction type, in the range of ^{0.1≤k 4 ξ≤0.4, 0.75f (k 4} ξ) (k 4 ξ) ≤L / H≤f By this, the non-noise Ks is small and a stable flow can be formed. In addition, when the sirocco fan 100 is a single-suction type, in the range of 0.1≤k ⁴ ξ≤0.4, by setting 1.5g (k ⁴ ξ) ≤ L / H ≤ 2g (k ⁴ ξ), the specific noise (Ks) ) Is small and can form a stable flow.

8 is a schematic cross-sectional view showing the longitudinal cross-sectional structure of the bell mouse 3. 9 is a perspective view of the sirocco fan 100 showing the region α of the bell mouse 3. FIG. 10 is an enlarged view of the region α showing the rms value of the static pressure variation on the wall surface of the region α without a step. FIG. 11 is an enlarged view of a region α showing the rms value of the static pressure variation on the wall surface of the stepped region α. 8 to 11, the bell mouse 3 attached to the sirocco fan 100 has the bell mouse 3 attached to form a step on the side of the scroll casing 2, and the scroll casing. It demonstrates, comparing the thing which attached the bell mouse 3 so that a step may not be formed in the side surface of (2).

In the longitudinal cross-sectional configuration of the bell mouse 3 shown in FIG. 8, the disadvantages (disadvantages in the minimum opening of the bell mouse 3) on the side of the sirocco fan 100 are point A and point A '(bell Point B and point symmetry with respect to the center of the mouse 3) and the other disadvantage (disadvantage of the maximum opening of the bell mouse 3) is point B and point B '(center of the bell mouse 3). A point symmetrical with point B), a straight line drawn in the direction of the fan 1 from the point B and the side of the scroll casing 2, and a straight line drawn in the direction of the fan 1 from the point C, point B ' And the intersection point of the scroll casing 2 side surface with the point C ', the line segment AA', and the rotation line extension line of the fan 1 as point O.

That is, the bell mouse 3 is attached so that a step is formed on the side of the scroll casing 2 when BC> 0, and the bell mouse 3 is attached so that the step is not formed on the side of the scroll casing 2 when BC = 0. Attached. In addition, it demonstrates that the rms value of static pressure fluctuations other than 5 [mm] and the area (alpha) of BC when BC> 0 is almost 0 [Pa]. In FIGS. 9 to 11, as shown in FIG. 8, the static pressure fluctuations in forming a step on the side surface of the scroll casing 2 by the bell mouse 3 attachment method, and in not forming a step, are shown in FIG. 8. This compares and represents the static pressure fluctuations.

The definition formula of the rms value of the static pressure fluctuation is shown below.

(7) p _s (t) = p _s + p _s ' = (t)

(8) rms value = {(Σp _s ' (t) ² ) / N} ^0.5

Here, p _s is the time average value, p _s' (t) shows the fluctuation of the static pressure.

The larger the rms value of the static pressure fluctuation on the wall surface, the greater the noise generated on the wall surface. It can be seen from FIG. 10 and FIG. 11 that the static pressure fluctuation when the step is formed on the side surface of the scroll casing 2 is smaller than the static pressure fluctuation when the step is not formed. Therefore, the step formed on the side surface of the scroll casing 2 can reduce the noise generated.

12 is a longitudinal sectional view showing a schematic cross-sectional configuration of the sirocco fan 100. 13 is a perspective perspective view of the sirocco fan 100 as viewed through it. Based on FIG. 12 and FIG. 13, the area | region where the rms value of the static pressure fluctuation in the sirocco fan 100 is large is demonstrated. In FIG. 12, the portion closest to the outer circumferential portion of the fan 1 is formed in the curved portion from the air passage 2c to the blowout opening 2b of the scroll casing 2 constituting the sirocco fan 100. It is shown as (4).

In FIG. 13, the point D, the bell mouse (the point where the distance from the fan 1 becomes the minimum on the intersection between the plane passing through the point A, the point O, and the point A 'shown in FIG. The point closest to the point D of 3) is located at the point E and the point O about 65 ° in the semi-rotation direction of the fan (1) from point E. Point G located at 40 ° in the half rotation direction of (1) with point G and point O as the center, and point F at point 40 in the rotation direction of fan 1 from point F. The point located at 180 degrees from the rotation direction of the fan 1 is shown as the point I. FIG.

In the case where the region was defined as described above, it was found that the region having a large rms value of the static pressure fluctuation in the sirocco fan 100 was the region of the schematic arc HFG connecting the points H, the points F, and the points G. Therefore, when the length of line segment BC in arc HFG is X and the length of line segment BC in rough arc HIG (circular arc connecting point H, point I and point G) is Y, L / H≤f (ξ) or In the range of L / H? G (ξ), the bell mouse 3 with X > Y &gt; 0 can reduce the rms value of the static pressure fluctuation and reduce the noise.

As shown in Figs. 10 and 11, when no step is formed on the side surface of the scroll casing 2, the rms value of the static pressure fluctuation in the region of the circular arc HFG is 7 Pa at maximum, but the side surface of the scroll casing 2 is In the case where a step is formed in the rms value, the rms value of the static pressure variation in the region of the arc HFG is at most 1 Pa or less. That is, by forming the step on the side of the scroll casing 2, the noise which makes the bell mouse 3 the sound source is reduced. This reason is considered to be because the distance from the fan 1 is enlarged only by the step formation, that is, by the length of the line segment BC, and the static pressure fluctuation caused by the rotation of the fan 1 is suppressed. .

14 is a graph showing P-Q characteristics of the sirocco fan 100 when passing through the operating point B. FIG. Based on FIG. 14, the PQ characteristic at the time of passing the operating point B of the sirocco fan 100 which provided the step | step in the side of the scroll casing 2, and the sirocco which did not form the step | step in the side of the scroll casing 2 The PQ characteristic when passing through the operating point B of the fan 100 is demonstrated. In Fig. 14, black colored circles indicate the PQ characteristics of the sirocco fan 100, which does not form a step on the side of the scroll casing 2, while white hollow marks form a step on the side of the scroll casing 2. The PQ characteristic of the fan 100 is shown, respectively. In addition, in FIG. 14, the vertical axis | shaft has shown the positive pressure P [Pa], and the horizontal axis | shaft has shown the air volume Q Q [m <3> / min].

As shown in FIG. 14, a surging area | region is compared in the sirocco fan 100 which formed the step in the side of the scroll casing 2, and the sirocco fan 100 which did not form the step in the side of the scroll casing 2. As shown in FIG. Then, it can be seen that the former side is on the open side. When the sirocco fan 100 having a step formed on the side of the scroll casing 2 is mounted in a unit such as an air conditioner, a dehumidifier, or an air purifier, the width dimension of the sirocco fan 100 is limited by the unit size constraint. There is a thing that can not be long. That is, since the width is short, when the operating point is on the open side of the surging region where the non-noise is minimum, the surging region can approach the operating point, which is effective for low noise.

FIG. 15: is a top view which shows schematic outline structure of the indoor unit 110 which hangs on the ceiling in which the sirocco fan 100 was mounted. FIG. 16: is sectional drawing which shows the longitudinal cross-sectional structure of the indoor unit 110 which hangs to a ceiling. Based on FIG. 15 and FIG. 16, the static pressure fluctuation | variation in the case where the sirocco fan 100 which provided the step | step on the side surface of the scroll casing 2 in the indoor unit 110 which hangs on a ceiling is mounted is demonstrated. In addition, in FIG. 15, the case where two sirocco fans 100 are mounted and the suction space 5 is formed in each width direction side surface is shown. 16, the flow of air is shown by the arrow.

When the sirocco fan 100 having a step formed on the side of the scroll casing 2 is mounted on the indoor unit 110 to be suspended from the ceiling, the suction step 5 decreases by the step by the step formed, and the noise It may be a factor to increase the. From the above description, the region where the rms value of the static pressure fluctuation is large is the arc HFG, and in other regions, the influence of the rms value of the static pressure fluctuation with the distance from the fan 1 is small. Therefore, when the sirocco fan 100 having a step formed in the arc HFG region is mounted on the indoor unit 110 to be suspended from the ceiling, the step can be located downstream of the suction port 2a, thereby reducing the reduction of the suction space 5. It can be made small.

FIG. 17 is a table showing noise values in the indoor unit 110 that is suspended from the ceiling. Based on FIG. 17, the noise level generated from the indoor unit 110 that hangs on the ceiling mounted with the sirocco fan 100 having a step formed on the side of the scroll casing 2, and does not form a step on the side of the scroll casing 2. A noise level generated from the indoor unit 110 that is suspended from the ceiling on which the non-sirocco fan 100 is mounted will be described. In addition, it is assumed that a step is formed in the region of the arc HFG. In addition, the noise value in the case where blow-out air volume was 16 m <3> / min is shown, respectively.

As shown in Fig. 17, when the blow-out air flow rate was set to 16 m 3 / min, the noise level when the step was formed in the arc HFG region was 42.4 [dB], and the step was not formed in the arc HFG region. It was found that the noise value at the was 44.0 [dB]. In this way, the noise level can be reduced by forming a step in the region of the arc HFG. As mentioned above, by providing a step | step in the area | region of circular arc HFG, reduction of the suction space 5 can be suppressed and a noise value can be made small.

Embodiment 2:

FIG. 18: is a schematic block diagram which shows schematic structure of the air conditioner 150 which concerns on Embodiment 2 of this invention. Based on FIG. 18, the structure of the air conditioner 150 is demonstrated. This air conditioner 150 is equipped with the sirocco fan 100 according to the first embodiment. This sirocco fan 100 is installed in an indoor unit (indoor unit) constituting the air conditioner 150 in the vicinity of the heat exchanger. In addition, in this Embodiment 2, it demonstrates centering around difference with Embodiment 1 mentioned above, and attaches | subjects the same code | symbol to the same part as Embodiment 1, and abbreviate | omits description.

This air conditioner 150 is comprised by connecting the compressor 151, the condensation heat exchanger 152, the fastening apparatus 153, and the evaporation heat exchanger 154 one by one by refrigerant piping. Among these, the indoor unit in which the condensation heat exchanger 152 or the evaporation heat exchanger 154 is provided is provided with the sirocco fan 100 which concerns on Embodiment 1. That is, the sirocco fan 100 is provided near the condensation heat exchanger 152 or the evaporation heat exchanger 154 installed in the indoor unit, and supplies air to the condensation heat exchanger 152 or the evaporation heat exchanger 154. Has the ability to

The compressor 151 sucks in the refrigerant flowing through the refrigerant pipe, compresses the refrigerant, and brings it into a high temperature and high pressure state. The condensation heat exchanger 152 performs heat exchange between air and a refrigerant, and condenses and liquefies the refrigerant. The tightening device 153 expands the refrigerant under reduced pressure. The evaporation heat exchanger 154 performs heat exchange between air and a refrigerant, and evaporates and vaporizes the refrigerant. The indoor unit in which the condensation heat exchanger 152 or the evaporation heat exchanger 154 constituting the air conditioner 150 is installed is mounted to the room by mounting the sirocco fan 100 according to the first embodiment. Noise can be reduced.

Here, the operation of the air conditioner 150 will be briefly described. The arrow shown in FIG. 18 has shown the flow direction of a refrigerant | coolant. The refrigerant gas compressed by the compressor 151 to become high temperature and high pressure flows into the condensation heat exchanger 152. In this condensation heat exchanger (152), the refrigerant is condensed by heat exchange with air to form a low-temperature or high-pressure liquid refrigerant or a gas-liquid abnormal refrigerant. The refrigerant flowing out of the condensation heat exchanger 152 is then depressurized by the tightening device 153 and becomes a low temperature / low pressure liquid refrigerant or a gas-liquid abnormal refrigerant and flows into the evaporation heat exchanger 154. In the evaporation heat exchanger (154), the refrigerant exchanges heat with air to evaporate, becomes a refrigerant gas of high temperature and low pressure, and is again sucked into the compressor (151). In the heating operation, the condensation heat exchanger 152 is mounted in the indoor unit, and in the cooling operation, the evaporation heat exchanger 154 is mounted in the indoor unit.

When the loss factor is small and the fan width is long, the heat transfer area of the heat exchanger can be used more effectively than when the speed distribution in the width direction of the heat exchanger is close to uniform, the fan width is short, and the speed distribution is uneven. . For this reason, the temperature difference between the air and the refrigerant required for obtaining the predetermined air conditioning capacity is small, the compressor input is small, and the noise is low. When the loss factor is small, the noise can be reduced by increasing the fan width without increasing the fan diameter. In addition, in the air conditioner provided with a plurality of fans having a short fan width, by replacing the fan with a long fan width, even if the number of fans is reduced, the noise level of the air conditioner at a predetermined operating point can be reduced. In addition, the speed distribution in the width direction of the heat exchanger can be close to uniform.

1: fan 2: scroll casing
2a: inlet 2b: outlet
2b1: tongue 2c: cooker
3: bell mouse 4: tongue
5: suction space 100: sirocco fan
110: suspended indoor unit 150: air conditioner
151: compressor 152: condensation heat exchanger
153: tightening device 154: evaporative heat exchanger

Claims (5)

A scroll casing having a suction port for receiving air, a blowout port for blowing air, and an air path from the suction port to the blowout port;
A fan accommodated in the scroll casing and driven to rotate to receive air from the suction port and blow air from the blowout port;
A bell mouse attached to the suction port of the scroll casing,
The suction port is formed on both sides of the scroll casing as an extension line of the rotation center of the fan.
The air flow resistance in the air path is P [Pa], the amount of air to be taken in by the suction port is Q [m 3 / min], the width in the direction of the rotation axis of the fan is L [mm], k is an integer, and the scroll When the height of the casing is H = 246 k [mm] and P / Q ² is the loss factor ξ [Pa / (m 3 / min) ² ],
In the range of ⁴ 0.1≤k ξ≤0.4,
f (k ⁴ ξ) = 0.34947 (k ⁴ ξ) ² -1.0554 (k ⁴ ξ) + 1.8, and 0.75f (k ⁴ ξ) ≤ L / H ≤ f (k ⁴ ξ) Sirocco fan. The method of claim 1,
In the curved part from the air passage of the scroll casing to the blowout port, the part closest to the outer peripheral part of the fan is a tongue.
In the longitudinal section of the bell mouse,
The disadvantages in the minimum opening of the bell mouse point A,
Point A 'which becomes point A and point symmetry with respect to the center of the bell mouse,
Point B, the disadvantage in the maximum opening of the bell mouse
Point B 'which is point symmetric with point B with respect to the center of the bell mouse,
The point C, the intersection of the straight line drawn in the direction of the fan and the scroll casing side from the point B,
From the point B ', the intersection point between the straight line drawn in the direction of the fan and the side surface of the scroll casing is the point C',
The point O, the intersection of the line segment AA 'and the rotation axis extension line of the fan,
In the intersection between the plane passing through the point A, the point O and the point A 'and the tongue, the distance between the fan and the fan is minimized.
Point E, the point closest to point D of the bell mouse,
Point F, which is located at 65 ° in the semi-rotating direction of the fan from the point E, centering on the point O,
Point G, which is located in the semi-rotating direction of the fan at 40 ° from the point F with respect to the point O,
Point H, which is located in the rotational direction of the fan 40 ° from the point F with respect to the point O,
Point I, located at 180 ° from the point F, in the rotational direction of the fan with respect to the point O,
The length of the line segment BC in the schematic arc HFG which connected the said point H, the said point F, and the said point G is X,
When the length of the line segment BC in the schematic arc HIG which connected the said point H, the said point I, and the said point G was made into Y,
In the range of L / H≤f (k ⁴ ξ),
A sirocco fan, wherein X> Y≥0. A scroll casing having a suction port for receiving air, a blowout port for blowing air, and an air path from the suction port to the blowout port;
A fan accommodated in the scroll casing and driven to rotate to receive air from the suction port and blow air from the blowout port;
A bell mouse attached to the suction port of the scroll casing,
The suction port is formed on one side of the scroll casing as an extension line of the rotation center of the fan.
The air flow resistance in the air path is P [Pa], the amount of air to be taken in by the suction port is Q [m 3 / min], the width in the direction of the rotation axis of the fan is L [mm], k is an integer, and the scroll When the height of the casing is H = 246 k [mm] and P / Q ² is the loss factor ξ [Pa / (m 3 / min) ² ],
In the range of ⁴ 0.1≤k ξ≤0.4,
^{g (k 4 ξ) = 1.39788} (k 4 ξ) , characterized in that a ² -2.1108 (k ⁴ ξ) to +1.8, and ^{1.5g (k 4 ξ) ≤L /} H≤2g (k 4 ξ) Sirocco fan. The method of claim 3,
In the curved part from the air passage of the scroll casing to the outlet, the part closest to the outer peripheral part of the fan is a tongue.
In the longitudinal section of the bell mouse,
The disadvantages in the minimum opening of the bell mouse point A,
Point A 'which becomes point A and point symmetry with respect to the center of the bell mouse,
Point B, the disadvantage in the maximum opening of the bell mouse
Point B 'which is point symmetric with point B with respect to the center of the bell mouse,
The point C, the intersection of the straight line drawn in the direction of the fan and the scroll casing side from the point B,
From the point B ', the intersection point between the straight line drawn in the direction of the fan and the side surface of the scroll casing is the point C',
The point O, the intersection of the line segment AA 'and the rotation axis extension line of the fan,
In the intersection between the plane passing through the point A, the point O and the point A 'and the tongue, the distance between the fan and the fan is minimized.
Point E, the point closest to point D of the bell mouse,
Point F, which is located at 65 ° in the semi-rotating direction of the fan from the point E, centering on the point O,
Point G, which is located in the semi-rotating direction of the fan at 40 ° from the point F with respect to the point O,
Point H, which is located in the rotational direction of the fan 40 ° from the point F with respect to the point O,
Point I, located at 180 ° from the point F, in the rotational direction of the fan with respect to the point O,
The length of the line segment BC in the schematic arc HFG which connected the said point H, the said point F, and the said point G is X,
When the length of the line segment BC in the schematic arc HIG which connected the said point H, the said point I, and the said point G was made into Y,
In the range of L / H≤g (k ⁴ ξ),
A sirocco fan, wherein X> Y≥0. An air conditioning apparatus using the sirocco fan according to any one of claims 1 to 4.

Images