JP2011052673A - Sirocco fan and indoor unit of air conditioner using this sirocco fan - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To easily secure an air passage and reduce fan noise. <P>SOLUTION: The sirocco fan is provided with a scroll-type fan casing 2 having a bell mouth 7 used as a suction port and a tongue part 6 used as the starting point of a whirlpool and a multi-aerofoil centrifugal type fan 1. The fan casing 2 is formed so that the fan casing width Lc of the area part from 0 to θ degrees (80≤θ≤180) in the reverse rotating direction of the fan relative to the tongue part 6 becomes larger than the fan casing width Ld of the area part which is greater than θ degrees and 360 degrees or less in the reverse rotating direction of the fan. Then the bell mouth 7 is formed in a straight semi-cylindrical shape that at least the part close to the fan of the section corresponding to the area part of the bell mouth 7 which is 0 to θ degrees has an inner diameter nearly equal to the inner diameter of the fan. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a sirocco fan that can suppress noise and an indoor unit of an air conditioner using the sirocco fan.

  Conventionally, in a sirocco fan having a bell mouth as a suction port and a scroll type fan casing having a tongue as a spiral start point and a multi-blade centrifugal fan, the fan casing extends over substantially the entire area in the fan rotation direction. It is known that the air passage in the fan casing is enlarged by enlarging the width so as to improve the blowing performance and reduce the operating noise (see, for example, Patent Document 1).

Japanese Patent No. 1523823 (FIGS. 1, 2, and 3)

  By the way, when such a sirocco fan is installed in an indoor unit of an air conditioner, to some extent, the suction space of the fan, that is, the suction of the fan casing of the sirocco fan installed in the outer shell suction port and the outer shell of the indoor unit It is necessary to secure a space formed between the mouth (see the suction space 14 in FIG. 9). However, since the indoor unit has dimensional constraints, the outer shell width, that is, the suction space cannot be increased. For this reason, it is necessary to shorten the width on the fan casing side. However, in the case where the width of the fan casing is increased over the substantially entire area in the fan rotation direction as described above, the condition becomes more severe, and the suction space Cannot be increased, which has been a factor in increasing fan noise.

  The technical problem of the present invention is to make it easy to secure an air passage and to reduce fan noise.

  The air conditioner according to the present invention has the following configuration. That is, in a sirocco fan having a scroll mouth fan casing having a bell mouth serving as a suction port and a tongue serving as a spiral start point, and a multi-blade centrifugal fan, the fan casing rotates counterclockwise with respect to the tongue. The fan casing width of the region portion of 0 to θ ° (80 ≦ θ ≦ 180) in the direction is longer than the fan casing width of the region portion exceeding θ and 360 ° in the counter-rotating direction of the fan. The mouse is formed in a straight semi-cylindrical shape in which at least the vicinity of the fan corresponding to the 0 to θ ° region has an inner diameter substantially equal to the inner diameter of the fan.

According to the sirocco fan of the present invention, the fan casing width in the region of 0 to θ ° (80 ≦ θ ≦ 180) in the fan counter-rotation direction with reference to the tongue portion exceeds θ in the fan counter-rotation direction and is 360 °. Since it is formed longer than the fan casing width of the region up to, aerodynamic performance close to that when the entire fan casing width is increased can be obtained. And when such a sirocco fan is mounted in an indoor unit of an air conditioner, the fan casing width in the region portion exceeding θ and up to 360 ° is short, so the suction space can be increased, and the inside of the fan casing Both the air passage and the suction space can be expanded at the same time, and the fan noise of the air conditioner can be made smaller than when the entire fan casing width is increased.
Furthermore, when the fan casing is constituted by a part of 0 to 180 ° in the counter-rotating direction from the tongue and a part of 180 to 360 °, the part of 180 to 360 ° and the fan are not changed, If the fan casing width is changed so as to increase only the part at 0 to 180 °, the fan noise of the air conditioner can be reduced, and the cost required for the part change can be reduced.

It is the front sectional view and side sectional view showing the schematic structure of the sirocco fan concerning Embodiment 1 of the present invention. It is a perspective view which shows schematic structure of the fan casing of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the PQ characteristic of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the Ks-Q characteristic of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the PQ and Ks-Q characteristic of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the PQ and Ks-Q characteristic of the sirocco fan which concerns on Embodiment 1 of this invention. It is a schematic diagram which shows the trajectory line of the sirocco fan which concerns on Embodiment 1 of this invention. It is front sectional drawing which shows schematic structure of the comparative example of a sirocco fan. It is the cross-sectional view and side sectional view which show schematic structure of the ceiling-suspended type indoor unit of the air conditioner using the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the PQ characteristic of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the Ks-Q characteristic of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the noise value of the sirocco fan which concerns on Embodiment 1 of this invention. It is a graph which shows the PQ characteristic of the sirocco fan which concerns on Embodiment 2 of this invention. It is a graph which shows the Ks-Q characteristic of the sirocco fan which concerns on Embodiment 2 of this invention. It is a figure which shows the speed distribution in the blower outlet of the sirocco fan which concerns on Embodiment 2 of this invention. It is a front cross section which shows schematic structure of the sirocco fan which concerns on Embodiment 3 of this invention.

Embodiment 1 FIG.
The present invention will be described below with reference to illustrated embodiments.
FIG. 1 is a front sectional view and a side sectional view showing a schematic configuration of a double suction type sirocco fan according to Embodiment 1 of the present invention. FIG. 2 is a perspective view showing a schematic configuration of the fan casing of the sirocco fan according to Embodiment 1 of the present invention.

  The sirocco fan of the present embodiment includes a scroll-type fan casing 2 having a bell mouth 7 serving as a suction port 10 and a tongue 6 serving as a spiral start point, as shown in FIGS. And.

  The fan 1 has a main plate 3 having a fan boss 11 mounted on a motor shaft, that is, a fan shaft 12. A plurality of blades extending in the axial direction are attached to the outer edge portions of both end faces of the main plate 3 at substantially equal intervals, and the extending ends of these blades are attached to the ring-shaped side plates 4 and 4. Yes.

  The fan casing width Lc in the region of 0 to θ ° (80 ≦ θ ≦ 180) in the fan counter-rotating direction with reference to the tongue 6 serving as the spiral start point of the fan casing, and over 360 ° in the fan counter-rotating direction. The fan casing width Ld in the region up to is generally in a relationship of Lc = Ld. However, in the fan casing 2 of the present embodiment, as shown in FIGS. 1 and 2, the fan casing widths Lc and Ld are in a relationship of Lc> Ld.

  The bell mouth 7 is integrally formed continuously from the side surface 5 of the fan casing 2, and a portion corresponding to the region of 0 to θ ° has a straight half-cylinder shape having an inner diameter substantially equal to the inner diameter of the fan 1. Is formed.

  Next, the operation of the sirocco fan of the present embodiment will be described with further details of this. The fan boss 11 and the motor shaft, that is, the fan shaft 12 are connected by screws or the like, and the fan 1 is rotated by the rotation of the fan motor.

The PQ and Ks-Q characteristics of the fan alone are shown in FIGS. Here, P is a static pressure [Pa], Q is an air volume [m ³ / min], Ks is a specific noise [dB], SPL is a noise value,
Ks = SPL- ₁₀ log ₁₀ (P · Q ^2.5 ).

  Further, the fan unit characteristic is a characteristic in a state where there is no wall surface near the suction port. All the rotation speeds are the same, and the noise value SPL is a value measured at a position 1 m away from the center of the bell mouth 7 on the rotation axis. The sirocco fan is a double suction type, the fan diameter D is φ140 mm, the fan width Lf is 190 mm, the number of blades is 40, the longer fan casing width Lc is 280 mm, the shorter fan casing width Ld is 220 mm, the fan casing height The length H is 210 mm, and the distance X between the fan 1 and the bell mouth 7 is 5 mm.

  The PQ characteristic represents the relationship between the static pressure P, which is the ventilation resistance, and the air volume Q, with the fan speed being constant. The smaller the draft resistance, the easier the wind will flow, and the greater the draft resistance, the more difficult the wind will flow. Therefore, the smaller the static pressure, the larger the air volume, and the larger the static pressure, the smaller the air volume. Hereinafter, the low air volume and high static pressure side in FIG. 3 will be referred to as the cutoff side (upper left side of the graph), and the high air volume and low static pressure side will be referred to as the open side (lower right side of the graph).

  Table 1 below shows the conditions of Cases 1 to 3 shown in FIGS. In Cases 1 to 3, the cross-sectional shapes of the fan 1 and the fan casing 2 are the same, and the fan casing width Lc is different.

As is apparent from FIGS. 3 and 4 and Table 1, in Cases 1 and 2, Case 2 with a longer fan casing width Lc has a gentler slope on the open side. When the gradient is gentle, the change in the specific noise Ks is small when the operating point changes, which is effective for low noise. The reason for this will be described with reference to FIG. Considering the PQ and Ks-Q characteristics with a steep and gentle slope, both pass through the operating point A, and an operating point B having a larger static pressure and air volume than the operating point A is considered.
When the rotational speed N is changed, the PQ and Ks-Q characteristics change as shown in the following equation.
P = P ₀ (N / N ₀ ) ²
Q = Q ₀ (N / N ₀ )
Ks = SPL ₀ −10 log ₁₀ (N / N ₀ ) ⁶ −10 log ₁₀ (P · Q ^2.5 )

  FIG. 6 shows PQ and Ks-Q characteristics when the rotation speed is changed so that PQ passing through the operating point A has a steep and gentle slope and passes through the operating point B. FIG. As described above, the PQ and Ks-Q characteristics having gentle slopes have a smaller difference between the specific noise at the operating point B and the minimum specific noise, and suppress an increase in noise when the operating point changes. Can do.

  In Cases 2 and 3, the P-Q and Ks-Q characteristics almost coincide. This means that the fan casing width Ld is irrelevant to noise suppression, and noise suppression depends on the fan casing width Lc.

  Next, the reason why Cases 2 and 3 are lower in noise than Case 1 will be described. FIG. 7 is a trajectory line from Case 2 between blade A at a position of about 90 ° in the fan rotation direction from tongue 6. Although the sirocco fan in FIG. 7 is a double suction type, for ease of viewing, the fan 1 and the fan casing 2 are divided into two equal parts in the axial direction, and only half of them are shown. In FIG. 7, the flow flowing out from the inter-blade A at a position of about 90 ° in the fan rotation direction from the tongue portion 6 is partially along the wall surface of the spiral fan casing 2 as shown by the trajectory line A. Goes to the side of the fan casing side surface 5, from there to the area near the fan casing side surface 5 of the air outlet 9, and blows out of the fan through the air outlet 9. The reason why the specific noise is smaller in Case 2 than in Case 1 is that the space between the side plate 4 of the fan 1 and the side surface 5 of the fan casing is larger in Case 2, and the flow that flows out from the blade A is Along the wall surface of the scroll portion 6 in the direction of the fan casing side surface 5, the flow path of the air blown out from the region near the fan casing side surface 5 of the air outlet 9 is widened. This is because it has been reduced and it has become easier to flow.

  Further, the reason why the PQ and Ks-Q characteristics substantially coincide with each other in Cases 2 and 3 is that the flow flowing out from the interblade A is 180 to 360 ° in the fan counter-rotating direction, as is apparent from the trajectory line in FIG. This is because the width of the fan casing in the region from 180 to 360 ° does not affect the specific noise.

  In FIG. 1, the inner diameter of the straight semi-cylindrical portion corresponding to the straight portion 8 of the bell mouth, that is, the region of 0 to θ ° in the fan counter-rotation direction is made equal to the inner diameter of the blade. The fan casing widths Lc and Ld are equal, and a linear portion 8 is provided starting from the outer diameter side (large diameter side) of approximately ¼ circle as seen in the section along the axis of the bell mouth 7 having a normal shape as shown in FIG. In this case, even if the fan casing width Lc is set to 280 mm, which is the same as that of Case 3, the PQ characteristics substantially coincide with those of Case 1, the minimum specific noise is increased, and the effect of increasing the fan casing width Lc cannot be obtained. This is because the wall surface of the region B in FIG.

FIG. 9 is a plan view and a side view showing a schematic configuration of a ceiling-suspended indoor unit of an air conditioner using the sirocco fan according to the present embodiment. Table 2 below shows the results of measuring the noise level when the above-mentioned Case 1 to 3 sirocco fans are mounted on the ceiling-suspended indoor unit of FIG. 9 and the air flow rate of the ceiling-suspended indoor unit is 16 m ³ / min. It is shown.

  As is clear from Table 2, Case 3 has the lowest noise. This is because, as shown in FIG. 9, Case 3 is smaller than Case 2 in the region C near the indoor unit suction port 13, because the fan casing width is shorter, the suction space 14 is larger, and the ventilation resistance is reduced.

  That is, Cases 2 and 3 have substantially the same characteristics as a single fan, but when mounted on a ceiling-suspended indoor unit, Case 3 that can increase the suction space near the indoor unit suction port 13 may reduce noise. it can.

  Next, the case where the angle θ of the region in the fan counter-rotating direction with respect to the tongue 6 (FIG. 2) is changed in the range of 0 to 180 ° will be described. The PQ and Ks-Q characteristics of the single fan are shown in FIGS. The larger the angle θ, the closer to the above-mentioned Case 3 characteristic, and the smaller the angle θ, the closer to the Case 1 characteristic.

  FIG. 12 shows a noise value when a sirocco fan in which the angle θ is changed in the range of 0 to 180 ° is mounted on a ceiling-mounted indoor unit. When the angle θ is in the range of 0 to 54 °, the noise value increases as the angle θ increases. Considering the trajectory line A shown in FIG. 7, the fan casing width is long on the downstream side near the blowout port, but the fan casing width remains short on the upstream side near the blowout port. Because of the small effect.

  When the angle θ is in the range of 54 to 180 °, the noise value decreases as the angle θ increases. This is because the area where the fan casing width in the vicinity of the air outlet becomes longer is widened, so that the suction space of the ceiling-suspended indoor unit is reduced in the range of 0 to 180 °, but the ventilation resistance of the trajectory line A is small. It is because it became. Further, the angle θ = 0 ° is equal to the noise value when the angle θ = 80 °.

  When the angle θ is greater than 180 °, the effect of reducing the airflow resistance of the trajectory line A is lost, and only the suction space of the ceiling-suspended indoor unit is reduced, so that the noise value increases. Therefore, when the angle θ is 80 to 180 °, the noise value of the ceiling-suspended indoor unit can be reduced. Thus, by using the sirocco fan according to the present embodiment for an indoor unit of an air conditioner, an indoor unit with low noise and low vibration can be obtained.

Embodiment 2. FIG.
Next, the fan width Lf shown in FIG. 1 is fixed to 190 mm, the shorter fan casing width Ld is fixed to 220 mm, and the distance X between the fan 1 and the bell mouth 7 is fixed to 5 mm. A case where the longer fan casing width Lc is changed by changing the length will be described.

  First, the case where the angle θ is 180 ° will be described. The PQ and Ks-Q characteristics of the single fan are shown in FIGS. In the range of Lc / Lf ≦ 1.25, the longer the Lc, the gentler the slopes of PQ and Ks-Q on the open side, so that the noise is reduced even if the operating point changes. This is due to the effect of reducing the draft resistance of the trajectory line A.

  On the other hand, in the range of Lc / Lf> 1.25, the longer the Lc, the steeper the slopes of PQ and Ks-Q on the open side, so that the noise and input when the operating point changes increases. . FIG. 15 is a diagram showing a velocity component perpendicular to the air outlet 9, that is, a velocity component effective for the air volume, and a white portion indicates a backflow region. Thus, if Lc is too long, reverse suction occurs on the side plate side of the air outlet 9, and the rotational speed must be increased by the amount of the reversely sucked air.

  When the angle θ is changed by 10 ° in the range of 80 to 180 °, in any case, when Lc / Lf ≦ 1.25, the gradient of PQ and Ks-Q increases as Lc increases. When Lc / Lf> 1.25, the slopes of PQ and Ks-Q become steeper as Lc becomes longer.

  When a sirocco fan with Lc / Lf ≦ 1.25 is mounted on an indoor unit, for example, a ceiling-suspended indoor unit, there is a restriction on the outer shell width of the ceiling-suspended indoor unit. Although Lc / Lf = 1.25 with the gradual slope of −Q and Ks−Q is not necessarily effective in reducing fan noise, Lc should be as much as possible within the range of Lc / Lf ≦ 1.25. It is better to make it longer.

  As described above, by mounting the sirocco fan having Lc / Lf ≦ 1.25 in the indoor unit, fan noise of the ceiling-mounted indoor unit or the like can be reduced.

Embodiment 3 FIG.
In the first and second embodiments described above, the cross-sectional shape of the bell mouth 7 on the side plate 5 located on the upper side in the range of 0 to θ ° in the fan counter-rotating direction as shown in FIG. Although the case has been described, here, the cross-sectional shape of the bell mouth on the side plate 5 located on the upper side is formed at a right angle as shown in FIG.

  Table 3 shows a case where a sirocco fan with an angle θ of 180 ° and a bell mouth cross-section of approximately ¼ circle is mounted on a ceiling-suspended indoor unit, and a sirocco fan with a bell mouth cross-section of a right angle. The noise level when mounted on a suspended indoor unit is shown.

  As is clear from Table 3, the noise value is reduced when the cross-sectional shape of the bell mouth 7 on the side plate 5 located above is set to a right angle. This is because the air path is wider at right angles and the draft resistance of the trajectory line A becomes smaller.

  Therefore, in the range of 0 to θ °, the noise value can be reduced by making the cross-sectional shape of the bell mouth 7 a right angle.

  1 fan, 2 fan casing, 3 main plate, 4 side plate, 5 side surface of fan casing, 6 tongue, 7 bell mouth, 8 bell mouth straight portion, 9 air outlet, 10 air inlet, 11 fan boss, 12 fan shaft, 13 indoor unit inlet, 14 inlet space.

Claims (4)

In a sirocco fan comprising a scroll type fan casing having a bell mouth serving as a suction port and a tongue serving as a spiral start point, and a multi-bladed centrifugal fan,
The fan casing has a region where the fan casing width in the region of 0 to θ ° (80 ≦ θ ≦ 180) in the counterclockwise direction of the fan exceeds θ in the counterclockwise direction of the fan and exceeds 360 ° with respect to the tongue. It is formed longer than the fan casing width of the part,
The bell mouth has a sirocco shape in which at least the vicinity of the fan corresponding to the 0 to θ ° region is formed in a straight semi-cylinder shape having an inner diameter substantially equal to the inner diameter of the fan. fan.   2. The sirocco fan according to claim 1, wherein Lc / Lf ≦ 1.25, where Lc is a fan casing width of the region of 0 to θ ° of the fan casing and Lf is a fan width.   The bell mouth is integrally formed continuously from the side surface of the fan casing, and a transition portion from the side surface of the fan casing to the bell mouth in the region of the 0 to θ ° is substantially perpendicular to the cross section. The sirocco fan according to claim 1, wherein the sirocco fan is configured.   The indoor unit of the air conditioner using the sirocco fan in any one of Claims 1 thru | or 3.

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