JP3138632B2 - Air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a fin tube type heat exchanger in which the flow of air blown from, for example, an impeller to a fin tube type heat exchanger of a blower arranged in an air passage in an air conditioner is applied to a fin of the fin tube type heat exchanger. Caused by separation vortices in the fins of the heat exchanger resulting from entering at an angle of attack,
TECHNICAL FIELD The present invention relates to an air conditioner in which interference sound heard as hurul is reduced.

[0002]

2. Description of the Related Art FIGS. 60 and 61 are views showing a typical conventional air conditioner as an example of an air conditioner in which a heat exchanger is arranged on the blowout side of an impeller of a blower. FIG. Figure,
FIG. 61 is a horizontal cross-sectional view when cut along the XX plane in FIG. In FIG. 60, inside a main body 2 buried in a ceiling 14, an impeller 1 of a blower, a fin tube type heat exchanger 3 erected around the impeller 1 of the blower, and a heat exchanger 3 are provided. A drain pan 5 for receiving drain water flowing out from the surface of the heat exchanger, a motor 6, an electric component box 12 containing a control board, and the like are provided below. A decorative panel 13 is fixed to a lower portion of the main body 2, and a suction port 20 is formed in the vicinity of a central portion thereof, and blowout ports 10 are formed on four sides outside the suction port 20. Further, the main body is suspended and fixed by a main body fixing hook 21 and a main body fixing bolt 18 and a fixing nut 19 suspended from the attic. During operation, the impeller 1 of the centrifugal blower driven by the motor 6 allows room air to pass through the suction grille 7 and the filter 9 from the suction port 20, as indicated by the thick arrow.
It is guided by the bell mouth 8 and is sucked into the impeller 1 of the centrifugal blower. Thereafter, the air blown out from the impeller 1 of the centrifugal blower is heated or cooled by passing through the heat exchanger 3 in which the refrigerant circulates, blows out from the blowout port 10 into the room, and is air-conditioned.

FIG. 62 shows a heat exchanger 3 and an impeller 1 of a blower.
FIG. 4 is an enlarged view of a main part in which the vicinity of a minimum gap point A is enlarged, showing a state of a flow 50 blown out from an impeller 1 of a blower and a flow of air to a fin 3a of a heat exchanger.
As shown in the drawing, on the upstream side of the minimum gap point A of the flow 50 blown out from the impeller 1 of the blower, the flow is closer to the fins 3a of the heat exchanger, and the further downstream, the more the flow is toward the fins 3a. Therefore, the angle between the fin 3a and the inflow direction of the air, that is, the angle of attack α increases. This allows
Separation vortices 24 are generated in the fins 3a, and interference noise between the fins 3a is generated due to pressure fluctuation of the separation vortices 24. FIG. 63 shows 1/3 OCT of this conventional air conditioner.
The relationship between the sound pressure level and the frequency based on the analysis result is shown. In the figure, it can be seen that the interference sound is particularly large in the 3.15 kHz frequency band.

[0004]

In the above-mentioned conventional air conditioner, the flow blown out from the impeller of the blower flows into the fins of the heat exchanger at an angle of attack, so that a separation vortex is generated and the fins are separated between the fins. Interference noise is generated. This phenomenon is particularly caused by downsizing of air conditioners and increase of outer diameter of impeller of blower.
It was noticeable when the heat exchanger and blower impeller approached.
Further, at this time, there is a problem that a wind noise (NZ sound) is also generated and noise is deteriorated. An object of the present invention is to obtain an air conditioner having no problem in noise. The present invention also provides a highly reliable device even when the size of the air conditioner is reduced.

[0005]

An air conditioner according to a first aspect of the present invention includes a heat exchanger provided with fins, and a blower having a blowout flow which flows into the fins of the heat exchanger at an angle of attack. In the air conditioner provided with, in the vicinity of the minimum gap between the heat exchanger and the blower, is formed so as to be convex in the direction of the blower from the heat exchanger, plate-shaped away from the heat exchanger at this convex portion A rectifying member having a ventilation opening in the plate-shaped member, and the rectifying member is provided with a heat exchange portion extending from the vicinity of the minimum gap to the upstream side and the downstream side of the air blown from the blower. It has ends on both sides which are arranged in close contact with the container.

[0006] In the air conditioner according to the second aspect of the invention, the top portion of the rectifying member formed so as to protrude from the heat exchanger in the direction of the blower is protruded downstream from the minimum gap, and both sides of the rectifying member. The end portion is closely attached to the heat exchanger with a gap at most about the thickness of the rectifying member. Also,
In the air conditioner according to the third invention, the rectifying member is configured such that the rectifying member is a top portion of the convex portion, a member that approaches the blower from one end to the top portion, and a member that goes from the top portion to the other end. And a member moving away from the blower.

An air conditioner according to a fourth aspect of the present invention is the air conditioner wherein the straight length between both ends of the flow regulating member is 20 to 50% of the diameter of the impeller of the blower.

An air conditioner according to a fifth aspect of the present invention is the air conditioner, wherein the minimum gap between the upstream end of the flow regulating member, the heat exchanger, and the blower is a point on the surface of the heat exchanger on the blower side. Is 25 to 90% of the minimum gap length.

[0009] In the air conditioner according to the sixth invention, the upper end of the convex portion formed so as to protrude from the heat exchanger in the direction of the blower has both ends around the upstream end of the rectifying member. The connecting straight line is provided in a range rotated by 3 to 20 degrees.

[0010] An air conditioner according to a seventh aspect of the present invention is an air conditioner having an impeller of a blower and a heat exchanger provided with fins on an outlet side of the impeller of the blower in a main body of the air conditioner. A point O is at the center of the rotation axis, A is a point on the surface of the heat exchanger on the side of the fan at the minimum gap between the heat exchanger and the impeller of the blower, and the rotation axis of the outer periphery of the impeller of the blower and the impeller of the blower. The intersection point between O and the straight line OA connecting the minimum gap point A is P, and the point at which the end 4a of the rectifying member on the upstream side of the air blown out from the point A from the impeller of the blower comes into close contact with the heat exchanger is B. When the point at which the end 4b of the downstream rectifying member is in close contact with the heat exchanger is F, the end of the upstream rectifying member and the downstream side of the air blown out from the impeller of the blower of the rectifying member are referred to as F. From the straight line 4a-4b connecting the ends, rotate at an arbitrary angle β ° about the point 4a. A linear 4a-E of any length;
Formed by a straight line connecting the points E and 4b or a straight line 4a-E at a point E and an arc-shaped E-4b having a tangent line with the fin of the heat exchanger at a point F at an angle of 90 ° or less upstream at a point F. The rectifying member is disposed at points B and F on the heat exchanger so as to be in close contact with the heat exchanger.

An air conditioner according to an eighth aspect of the present invention is the air conditioner, wherein the length connecting the end of the upstream rectifying member and the end of the downstream of the air blown out from the impeller is two times the diameter φD of the impeller of the blower.
A straight line 4a-E obtained by rotating a straight line having a length equal to or less than the length of the straight line 4a-4b and equal to or more than 50% around the point 4a from the straight line 4a-4b which is 0 to 50% by an arbitrary angle β °, and a point E , 4b
A straight line or a straight line 4a-E, and an arc-shaped E-4b having a tangent line with the fin of the heat exchanger at the point F at an angle of 90 ° or less at the point F on the upstream side. The heat exchanger is disposed at points B and F on the exchanger so as to be in close contact with the heat exchanger.

The air conditioner according to the ninth invention is characterized in that point A
The end 4a of the rectifying member on the upstream side of the air blown out from the impeller of the blower is located upstream of the minimum gap point A at 25 to 90 of the minimum gap distance AP between the impeller of the blower and the heat exchanger.
%, And the point at which the end 4b of the downstream rectifying member comes into close contact with the heat exchanger is F, and the point of the rectifying member blown out from the impeller of the blower is B. From the straight line 4a-4b whose length connecting the end of the air upstream rectifying member and the downstream end is 20 to 50% of the diameter φD of the impeller of the blower, a straight line 4a- A straight line 4a-E obtained by rotating a straight line having a length of 4b or less and 50% or more by an arbitrary angle β °, and a straight line or a straight line 4a-E connecting the points E and 4b and the point F of the heat exchanger Arc-shaped E- having an angle with the fin of 90 ° or less on the upstream side
4b, the rectifying member formed by this is disposed at points B and F on the heat exchanger so as to be in close contact with the heat exchanger.

An air conditioner according to a tenth aspect of the present invention is the air conditioner, wherein straight lines 4a-4b connecting the end of the upstream rectifying member and the downstream end of the air blown out from the impeller of the blower of the rectifying member.
From above, a point E contacts a straight line 4a-E of an arbitrary length rotated by an angle β ° = 3 to 20 ° around the point 4a and a straight line or a straight line 4a-E connecting the points E and 4b, and In F, an arc-shaped E-4b having a tangent of 90 ° or less on the upstream side with respect to the fin of the heat exchanger, and a rectifying member formed by the heat exchanger at points B and F on the heat exchanger. It is arranged so as to be in close contact.

[0014]

An air conditioner according to an eleventh aspect of the present invention uses a net-like member as a rectifying member provided near the minimum gap between the heat exchanger and the blower, and has a wire diameter of 1 to 2 of the heat exchanger fin pitch.
It is doubled and the aperture ratio is 20 to 40%.

The air conditioner according to the twelfth aspect uses a perforated plate material for a rectifying member provided near the minimum gap between the heat exchanger and the blower, and the diameter of the hole is 0.3 mm of the fin pitch of the heat exchanger. ２2 times and the aperture ratio = 25-40%. An air conditioner according to a thirteenth invention is an air conditioner comprising: a heat exchanger provided with a plurality of fins; and a blower having a blowout flow which flows into the fins of the heat exchanger at an angle of attack. In the above, the plurality of fins are provided across the plurality of fins on the upstream side of the minimum gap between the heat exchanger and the blower, and the plurality of fins are provided on the downstream side, and the flow of the flow blown out from the blower is provided. Among them, a rectifying member having a ventilation port for decelerating a vertical component with the fin is provided. In the air conditioner according to the fourteenth aspect, the rectifying member may include: a member that approaches the blower from one end to the minimum gap portion with the minimum gap portion as a boundary; And a member moving away from the blower as it goes to the section. Further, an air conditioner according to a fifteenth invention includes a main body for housing a heat exchanger and a blower, and a decorative panel provided at a lower portion of the main body, and only one pair on both sides of the blower so as to sandwich the blower. Of the decorative panel, and the heat exchanger is arranged between the blower and the outlet.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1 of the Invention Hereinafter, an example of an embodiment will be described with reference to the drawings. FIG. 1 is a sectional view of an air conditioner in one embodiment of the air conditioner according to the first invention. In the figure,
Inside a main body 2 buried in a ceiling 14, an impeller 1 of a centrifugal blower as a blower, a fin tube type heat exchanger 3 erected around the impeller 1 of the centrifugal blower, a net-like rectifying member 4 , A drain pan 5, a motor 6, which receives drain water flowing out of the heat exchanger surface, below the heat exchanger.
An electric component box 12 containing a control board is provided.
A decorative panel 13 is fixed to a lower portion of the main body 2, and a suction port 20 is formed near the center thereof.
Outlets 10 are formed on the four sides outside the zero. Further, the main body is suspended and fixed by a main body fixing hook 21 and a main body fixing bolt 18 and a fixing nut 19 suspended from the attic. During operation, room air is guided by the bell mouth 8 through the suction grille 7 and the filter 9 through the suction grille 7 and the filter 9 by the impeller 1 of the blower driven by the motor 6 to the impeller 1 of the blower. Inhaled. Thereafter, the air blown out from the impeller 1 of the blower passes through the heat exchanger 3 in which the refrigerant is circulating,
The air is heated or cooled and blown out from the outlet 10 into the room to be air-conditioned.

FIG. 2 is a sectional view taken along a plane perpendicular to the rotation axis of the impeller 1 of the blower of FIG. 16
Is a drain pump used for draining drain water collected in a drain pan to the outside, 17 is a header for distributing a refrigerant to each copper pipe in a height direction of the heat exchanger, and 15 is a pipe for connecting to an outdoor unit. Show. 23 is the rotation direction of the impeller 1 of the blower, point A is the minimum gap between the heat exchanger 3 and the impeller 1 of the blower, 4 is the vicinity of the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3. A rectifying member formed so as to be convex from the heat exchanger 3 in the direction of the impeller of the blower;
From the minimum clearance point A of the rectifying member 4, the impeller 1 of the blower
The upstream end face 4b of the air blown out from the air blower indicates the downstream end face of the air blown out from the impeller of the blower from the minimum gap point A of the rectifying member 4, and the rectifying member 4 heats the heat at these two points. Close to, for example, close to the exchanger.

FIG. 3 is a perspective view of the vicinity of the minimum gap point A between the heat exchanger 3 and the impeller 1 of the blower in FIGS. In the vicinity of the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3, the end 4a of the hanger-shaped rectifying member of the rectifying member 4 formed so as to protrude from the heat exchanger 3 toward the fan. At 4b, it is hung and fixed on the copper pipe 22 of the heat exchanger 3, and is closely attached to the heat exchanger 3. FIG. 4 is a diagram in which only the rectifying member 4 of FIG. 3 is taken out. 4a, 4 in the figure
b shows the end of the rectifying member 4 when the rectifying member 4 is brought into close contact with the heat exchanger 3. FIG. 5 is a partially enlarged view of a main part of FIG.

In the air conditioner thus configured, as shown in FIG. 5, the air 5 blown out from the impeller 1 of the blower from the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3.
Since the ends 4a and 4b of the rectifying member on the upstream side and the downstream side of the rectifier 0 are in close contact with the heat exchanger 3 and there is a space between the rectifying member 4 and the heat exchanger 3, the air is blown out from the impeller 1 of the blower. The fins 3a of the heat exchanger 50 and the vertical component 50x of the flow 50 are decelerated by the rectifying member 4 and deflected in the direction of the fins 3a of the heat exchanger. Due to the Cander effect of the member 4, the heat exchanger 3 is deflected in the direction of the fin 3a of the heat exchanger.
Pass through. Thereby, the separation vortex 24 caused by the blowout flow 50 flowing at an angle of attack into the fins 3a of the heat exchanger when there is no rectifying member in FIG. 62 or the minimum gap point A of the rectifying member 4 in FIG. As when the upstream end 4a is not in close contact with the heat exchanger 3, the flow 50 blown out from the impeller 1 of the blower does not pass through the rectifying member 4 and has an angle of attack with the fin 3a of the heat exchanger. 7 and blows out the impeller 1 of the blower as when the end 4b of the rectifying member 4 on the downstream side of the minimum gap point A is not in close contact with the heat exchanger 3. After the flow 50 passes through the flow regulating member 4, the pressure of the discharge vortex 25 generated near the end 4 b downstream of the minimum gap point A of the flow rectification member 4 is lower than the surrounding pressure. By the flow being induced, the heat exchanger fins 3 At the same time, the interference noise between the fins 3a of the heat exchanger caused by the pressure fluctuation of the separation vortex 24 can be eliminated. Can be reduced.

FIG. 8 is a graph showing the flow rate of air blown from the main body.
The relationship between the sound pressure level and the frequency based on the result of the 1/3 octave analysis is shown. The device of the present invention shown by the broken line is 2 to 5 kHz higher than that without the rectifying member shown by the solid line.
The noise of z is greatly reduced. In the above description, the configuration in which the rectifying member 4 is in close contact with the heat exchanger has been described.
This close contact means that it is desirable that the rectifying member exists on a line where the upper end surfaces of the fins of the heat exchanger are arranged. The end of the rectifying member may be in contact with the fins or may be between the fins. Furthermore, the end of the rectifying member does not exist on the line on which the upper end surfaces of the fins are arranged, and even if there is a gap, for example, about the thickness of the rectifying member, there is an effect of suppressing abnormal sound. Need not be identical.
In short, it is only necessary to bring the end portion close to the fin row as necessary to suppress the abnormal sound. Also described is a configuration in which the top portion formed so as to be convex in the direction of the blower from the heat exchanger projects downstream from the minimum gap of the air blown out from the impeller of the blower, but if the rotation direction is either In an air conditioner having a possible structure, it can be said that the point E may be provided on the line OA. The rectifying member 4 can be made of a resin, a metal member, or the like. Further, the width of the rectifying member does not necessarily have to be the same as the width of the heat exchanger, and if it is installed in a location where the flow of wind is strong, harsh noise can be reduced.

Embodiment 2 of the Invention FIG. 9 is a diagram corresponding to FIG. 1 of the first embodiment of the air conditioner according to another embodiment of the present invention. Corresponding symbols indicate the same. FIG. 10 is a diagram corresponding to FIG. 2 of the first embodiment of the air conditioner according to another embodiment of the first invention. Corresponding symbols indicate the same. 9 and 1
Even if the heat exchanger 3 is linear as in 0, by arranging the rectifying member 4 near the minimum gap, the same effect as in the first embodiment can be obtained.

Embodiment 3 of the Invention FIG. 11 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the air conditioner in another example of the air conditioner according to the present invention. The point O is at the center of the rotation axis of the impeller 1 of the centrifugal blower which is a blower, the point A is the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, the outer periphery of the impeller 1 of the blower and the impeller of the blower The intersection point of the rotation axis O and the straight line OA connecting the minimum gap point A is P, and the end 4a of the rectifying member on the upstream side of the air 50 blown out from the point A from the impeller 1 of the blower.
Let B be the point at which the end comes into contact with the heat exchanger 3, and F be the point at which the end 4b of the downstream rectifying member comes into contact with the heat exchanger 3.
Straight line 4a connecting the end of the upstream rectifying member and the downstream end of the air blown out from the impeller of the blower of the rectifying member.
-4b, a straight line E-4 connecting the straight line 4a-E of an arbitrary length rotated by an arbitrary angle β ° about the point 4a to the points E and 4b.
b shows the rectifying member 4 formed by b. This rectifying member 4
Are disposed in close contact with the heat exchanger 3 at points B and F. In the figure, the center of the rotation axis of the blower is point O, the rotation direction of the blower is 23, the aluminum fins of the heat exchanger 3 are 3a, and the heat exchanger 3 is
22 shows a copper pipe of the present invention.

In the air conditioner constructed as described above, as shown in FIG. 11, the upstream side of the air 50 blown out from the impeller 1 of the blower from the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3. Since the ends 4a and 4b of the downstream rectifying member are in close contact with the heat exchanger 3 and there is a space between the rectifying member 4 and the heat exchanger 3, the flow 50 blown out from the impeller 1 of the blower is provided.
The fin 3a of the heat exchanger and the vertical component 50x are decelerated by the straight line 4a-E portion of the rectifying member 4 and deflected in the direction of the fin 3a of the heat exchanger.
Is deflected in the direction of the fins 3a of the heat exchanger due to the Coander effect at the straight line EF downstream of the rectifying member 4, and passes through the heat exchanger 3. This eliminates the separation vortex 24 caused by the blowing flow 50 flowing at an angle of attack to the fins 3a of the heat exchanger without the rectifying member in FIG.
Since the interference noise between the fins 3a of the heat exchanger caused by the pressure fluctuation of 4 can be eliminated, the unpleasant noise generated from the main body can be reduced. FIG. 12 shows the relationship between the sound pressure level and the frequency based on the result of the 1/3 octave analysis at the same blowing air volume of the main body. In the case of the present invention shown by the broken line, the noise at 2 to 5 kHz is significantly reduced as compared with the case without the rectifying member shown by the solid line.

The straight line 4a-E of the rectifying member 4 matches with the fact that a substantially linear plate material is used. If a convex or concave arc shape is used, the flow of the wind will follow the rectifying plate. Therefore, it is sufficient that the air flow is linear as long as the wind does not flow.

Embodiment 4 of the Invention FIG. 13 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the air conditioner in another example of the air conditioner according to the present invention. The point O is at the center of the rotation axis of the impeller 1 of the centrifugal blower which is a blower, the point A is the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, the outer periphery of the impeller 1 of the blower and the impeller of the blower The intersection point of the rotation axis O and the straight line OA connecting the minimum gap point A is P, and the end 4a of the rectifying member on the upstream side of the air 50 blown out from the point A from the impeller 1 of the blower.
Let B be the point at which the end comes into contact with the heat exchanger 3, and F be the point at which the end 4b of the downstream rectifying member comes into contact with the heat exchanger 3.
A straight line 4a-4b connecting the end of the rectifying member upstream of the minimum gap point A between the heat exchanger for the air blown out from the impeller of the blower of the rectifying member and the impeller of the blower and the end on the downstream side.
From above, the angle γ between the straight line 4a-E of an arbitrary length rotated by β ° about the point 4a and the straight line 4a-E at the point E and the fin 3a of the heat exchanger at the point F at the point F is on the upstream side. The rectifying member 4 formed by an arc E-4b having a tangent of 90 ° or less is shown. The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F. Embodiment 3 of the air conditioner configured as described above. The same effect can be obtained.

Embodiment 5 of the Invention FIG. 14 is a partially enlarged view of a main part corresponding to FIG. 5 of Embodiment 1 of the invention in another example of the air conditioner according to the present invention. The center of the rotation axis of the impeller 1 of the centrifugal blower which is the blower is a point O,
A point A represents the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, and a straight line OA connecting the outer peripheral portion of the impeller 1 of the blower, the rotation axis O of the impeller 1 of the blower, and the minimum gap point A. The intersection point is P, the end 4a of the upstream rectifying member of the air 50 blown out from the point A from the impeller 1 of the blower is B at the point where the end 4a of the rectifying member is in close contact with the heat exchanger 3, and the end 4b of the rectifying member on the downstream side. Let F be the point at which the airflow comes into close contact with the heat exchanger 3, on a straight line 4a-4b connecting the end of the upstream rectifying member and the downstream end of the air blown out from the impeller of the blower of the rectifying member. From
An arbitrary-length straight line 4 rotated by an arbitrary angle β ° about the point 4a
The rectifying member 4 formed by a straight line E-4b connecting aE and points E and 4b is shown. The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F. In the figure, the center of the rotation axis of the blower is point O, the rotation direction of the blower is 23, the aluminum fin of the heat exchanger 3 is 3a, and the copper pipe of the heat exchanger 3 is 22.
Is shown.

In the air conditioner configured as described above, as shown in FIG. 14, the upstream side of the air 50 blown out from the impeller 1 of the blower from the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3. Since the ends 4a and 4b of the downstream rectifying member are in close contact with the heat exchanger 3 and there is a space between the rectifying member 4 and the heat exchanger 3, the flow 50 blown out from the impeller 1 of the blower is provided.
The fin 3a of the heat exchanger and the vertical component 50x are decelerated by the straight line 4a-E portion of the rectifying member 4 and deflected in the direction of the fin 3a of the heat exchanger.
Is deflected in the direction of the fins 3 a of the heat exchanger by the Cander effect at EF, which is a straight line on the downstream side of the rectifying member 4, and passes through the heat exchanger 3. This eliminates the separation vortex 24 caused by the blowing flow 50 flowing at an angle of attack with respect to the fin 3a of the heat exchanger without the rectifying member in FIG. 62, and at the same time, induces the pressure fluctuation of the separation vortex 24. Since the interference noise between the fins 3a of the heat exchanger can be eliminated, the harsh noise generated from the main body can be reduced. FIG. 15 shows the relationship between the sound pressure level and the frequency based on the result of the 1/3 octave analysis at the same blowing air volume of the main body. In the case of the present invention shown by the broken line, the noise at 2 to 5 kHz is significantly reduced as compared with the case without the rectifying member shown by the solid line.

However, when determining the shape of the rectifying member in the air conditioner thus configured, the rectifying member 4
If the length of the straight line 4a-4b connecting the end 4a of the rectifying member upstream of the minimum gap point A and the end 4b of the downstream of the minimum gap point A of the air 50 blown from the impeller 1 of the blower is too short, the effect is obtained. Is lost, even if it is too long, the effect will not come out anymore,
Conversely, as shown in FIG. 16, the pressure loss of the flow 50 blown out from the impeller 1 of the blower is obtained. Further, a straight line 4a- connecting the end 4a of the upstream rectifying member and the downstream end 4b of the air 50 blown out from the impeller of the blower of the rectifying member 4 is provided.
4b, the length of the straight line 4a-E rotated by an arbitrary angle β ° about the point 4a is too long, resulting in a pressure loss of the flow 50 blown out from the impeller 1 of the blower, resulting in noise deterioration or too short. The effect on the interference noise at the fins 3a of the heat exchanger is lost. Therefore, there is an optimum range.

FIG. 17 shows the ratio L / D of the length L of a straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the flow regulating member 4 to the diameter φD of the impeller of the blower. Sometimes,
The frequency band 2 where the interference noise occurs between the fins 3a of the heat exchanger in the 1/3 OCT analysis result of the noise value in FIG.
Among the sound pressure levels in the ~ 5 kHz band, there is a rectifying member 4 in the 3.15 kHz band, which indicates the highest numerical value, and the noise reduction amount of the sound pressure level without and without SPL 3.15 k (marked in the figure)
And the noise value O. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). △ SPL 3.15 at L / D = 0 in the figure
k is a value when there is no rectifying member.

FIG. 18 corresponds to FIG. 17 when the ratio LM / L of the length LM of the upstream straight portion 4a-E of the straightening member 4 to the length L of the straight line 4a-4b is changed. 1/3
Of the sound pressure levels in the 2 to 5 kHz band, which is the frequency band of the interference noise between the fins 3 a of the heat exchanger in the OCT analysis results, the rectifying member 4 in the 3.15 kHz band showing the highest numerical value was used. Noise reduction of sound pressure level △
SPL 3.15k (x mark in the figure) and noise value O. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). LM /
△ SPL 3.15k at L = 0 is a value when there is no rectifying member. As can be seen from the figure, the ratio L / D = 20 between the length of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the flow regulating member 4 to the diameter φD of the impeller 1 of the blower.
５０50% and the length of the straight line 4a-E is
If the length is −4b or less and 50% or more, the interference noise between the fins 3a of the heat exchanger can be reduced without deteriorating the noise value, and an air conditioner without harsh sound can be obtained.

Embodiment 6 of the Invention FIG. 19 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the air conditioner in another example of the air conditioner according to the present invention. The point O is at the center of the rotation axis of the impeller 1 of the centrifugal blower which is a blower, the point A is the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, the outer periphery of the impeller 1 of the blower and the impeller of the blower The point of intersection of the rotation axis O of the first rotation axis O and the straight line OA connecting the minimum clearance point A is P, and the end 4 a of the rectifying member on the upstream side of the air 50 blown out from the point A from the impeller 1 of the blower is connected to the heat exchanger 3. When the point at which the end 4b of the downstream rectifying member comes into close contact with the heat exchanger 3 is F, the heat of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4 is referred to as F. Minimum gap point A between the exchanger 3 and the impeller 1 of the blower
From the straight line 4a-4b connecting the end 4a of the more upstream rectifying member and the end 4b on the downstream side, an arbitrary angle β around the point 4a
A straight line 4a-E rotated by an arbitrary length and a straight line 4a-E
At the point E and the angle γ with the fin 3a of the heat exchanger at the point F has a tangent line of 90 ° or less on the upstream side.
4B shows a rectifying member 4 formed by 4b. The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F.

In the air conditioner thus configured, Embodiment 5 of the present invention will be described. The same effect can be obtained. However, when determining the shape of the rectifying member 4 in the air conditioner configured as described above, the rectifying member on the upstream side of the minimum gap point A of the air 50 blown from the impeller 1 of the blower of the rectifying member 4. If the length of a straight line 4a-4b connecting the end 4a and the downstream end 4b is too short, as shown in FIG.
Separation vortex 24 occurs at the fin 3a of the heat exchanger on the upstream side, and the effect is lost. If the length is too long, the effect is no longer obtained, and as shown in FIG. 21, the flow 50 blown out from the impeller 1 of the blower. Pressure loss, and the noise value deteriorates. An arbitrary angle around a point 4a from a straight line 4a-4b connecting an end 4a of the upstream rectifying member and an end 4b on the downstream side of the air 50 blown out from the impeller of the blower of the rectifying member 4. The length of the straight line 4a-E rotated by β ° is too long, resulting in pressure loss of the flow 50 blown out from the impeller 1 of the blower, resulting in noise deterioration or being too short to cause interference noise at the fins 3a of the heat exchanger. No effect. Thus, there is an optimal range.

FIG. 22 shows the ratio L / D of the length L of a straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the flow regulating member 4 to the diameter φD of the impeller of the blower. Sometimes,
Among the sound pressure levels in the 2 to 5 kHz band, which are the frequency bands of the interference noise generated between the heat exchanger fins 3a in the result of the 1/3 OCT analysis of the noise value as shown in FIG. Noise reduction amount of the sound pressure level without and with the rectifying member △ SPL 3.15k (× in the figure)
Mark) and the noise value O. A. Comparison of SPLOA (○ in the figure)
Mark). FIG. 23 shows 1/3 OCT corresponding to FIG. 17 when the ratio LM / L between the length LM of the upstream straight portion 4a-E and the length L of the straight line 4a-4b of the straightening member 4 is changed. The sound pressure level in the 3.15 kHz band, which is the highest numerical value among the sound pressure levels in the 2 to 5 kHz band which is the frequency band of the interference noise between the fins 3a of the heat exchanger in the analysis result, with and without the rectifying member 4 Noise reduction △
SPL 3.15k (x mark in the figure) and noise value O. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). LM /
△ SPL 3.15k at L = 0 is a value when there is no rectifying member. As can be seen from the figure, the ratio L / D = 20 between the length of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the flow regulating member 4 to the diameter φD of the impeller 1 of the blower.
５０50% and the length of the straight line 4a-E is
If the length is −4b or less and 50% or more, the interference noise between the fins 3a of the heat exchanger can be reduced without deteriorating the noise value, and an air conditioner without harsh sound can be obtained.

Embodiment 7 of the Invention FIG. 24 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the air conditioner in another example of the air conditioner according to the present invention. The point O is at the center of the rotation axis of the impeller 1 of the centrifugal blower which is a blower, the point A is the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, the outer periphery of the impeller 1 of the blower and the impeller of the blower The point of intersection of the rotation axis O of the first rotation axis O and the straight line OA connecting the minimum clearance point A is P, and the end 4 a of the rectifying member on the upstream side of the air 50 blown out from the point A from the impeller 1 of the blower is connected to the heat exchanger 3. When the point at which the end 4b of the downstream rectifying member comes into contact with the heat exchanger 3 is F, and the point at which the end 4b of the downstream rectifying member comes into contact with the heat exchanger 3 is F, the upstream rectifying of the air blown out from the impeller of the blower of the rectifying member. Straight line 4a- connecting the end of the member and the end on the downstream side
4b, a straight line E-4b connecting the straight lines 4a-E of any length and the points E and 4b rotated by an arbitrary angle β ° around the point 4a.
5 shows the rectifying member 4 formed by: The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F. In the figure, the center of the rotation axis of the blower is point O, the rotation direction of the blower is 23, the aluminum fin of the heat exchanger 3 is 3a, and the copper pipe of the heat exchanger 3 is 22. In the air conditioner thus configured, the impeller 1 of the blower and the heat exchanger 3 as shown in FIG.
End 4a, 4b of the rectifying member on the upstream side and downstream side of the air 50 blown out from the impeller 1 of the blower from the minimum gap point A of FIG.
Is close to the heat exchanger 3 and there is a space between the heat exchanger 3 and the rectifying member 4, so that the fins 3a of the heat exchanger and the vertical component 50 of the flow 50 blown out from the impeller 1 of the blower.
x is decelerated by the straight line 4a-E portion of the rectifying member 4, is deflected in the direction of the fin 3a of the heat exchanger, and passes therethrough.
The flow 50b that has not passed through the rectifying member 4 is
Is deflected in the direction of the fins 3 a of the heat exchanger and passes through the heat exchanger 3 by the Cone effect in the straight line EF on the downstream side of the heat exchanger. This eliminates the separation vortex 24 caused by the blowing flow 50 flowing at an angle of attack with respect to the fin 3a of the heat exchanger without the rectifying member in FIG. 62, and at the same time, induces the pressure fluctuation of the separation vortex 24. Since the interference noise between the fins 3a of the heat exchanger can be eliminated, the harsh noise generated from the main body can be reduced. FIG. 25 shows the relationship between the sound pressure level and the frequency based on the result of the 1/3 octave analysis at the same blowing air volume of the main body. In the case of the present invention shown by the broken line, the noise at 2 to 5 kHz is significantly reduced as compared with the case without the rectifying member shown by the solid line. However, in the air conditioner configured as described above, the position of the point B where the end 4a of the rectifying member on the upstream side of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4 comes into close contact with the heat exchanger is determined. If it is too upstream, pressure loss will occur, and at point A, the interference sound cannot be reduced.

A straight line 4a connecting the end 4a of the rectifying member upstream of the minimum gap point A and the downstream end 4b of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4
If the length of -4b is too short, the effect is lost, and if it is too long, the effect is no longer obtained, and conversely, the pressure loss of the flow 50 blown out from the impeller 1 of the blower is caused. The air 5 blown out from the impeller of the blower of the rectifying member 4
0 from a straight line 4a-4b connecting the end 4a of the upstream rectifying member and the end 4b on the downstream side with an arbitrary angle β centered on the point 4a.
The rotated straight line 4a-E is too long to reduce the noise due to the pressure loss of the flow 50 blown out from the impeller 1 of the blower, or to be too short to effect interference noise at the fins 3a of the heat exchanger. Disappears. Therefore, AB that determines the position of point B
Distance, straight line 4a-4b connecting the upstream and downstream ends of the rectifying member
And the length of the straightening member straight portions 4a-E have an optimum range. FIG. 26 shows a case where the length range of the distance AB between the point B and the minimum gap point A is changed by changing the ratio AB / AP of the AB length to the minimum gap length AP between the impeller 1 of the blower and the heat exchanger. 25, the rectification in the 3.15 kHz band where the numerical value is the highest among the sound pressure levels in the 2 to 5 kHz band which is the frequency band of the interference noise between the heat exchanger fins 3a in the result of the 1/3 OCT analysis of the noise value in FIG. Noise reduction of sound pressure level with and without member 4 △ SPL 3.15 k (marked with x in the figure), noise value O. A noise reduction amount SPLO. A (
This is indicated by a circle in the figure). {SPL3.
15k is a value when there is no rectifying member.

FIG. 27 shows the ratio L / D of the length L of a straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the flow regulating member 4 to the diameter φD of the impeller of the blower. Sometimes,
The frequency band 2 where the interference noise occurs between the fins 3a of the heat exchanger in the result of the 1/3 OCT analysis of the noise value in FIG.
Among the sound pressure levels in the ~ 5 kHz band, there is a rectifying member 4 in the 3.15 kHz band, which indicates the highest numerical value, and the noise reduction amount of the sound pressure level without and without SPL 3.15 k (marked in the figure)
And the noise value O. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). △ SPL 3.15 at L / D = 0 in the figure
k is a value when there is no rectifying member. Also, FIG.
1/3 OCT analysis results when the ratio LM / L between the length LM of the upstream straight portion 4a-E and the length L of the straight line 4a-4b of the straightening member 4 is changed between the fins 3a of the heat exchanger. 3.15 kHz indicating the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which the interference noise is generated.
The noise reduction amount of the sound pressure level without and with the rectifying member 4 in the band △ SPL 3.15k (marked with x in the figure) and the noise value O.
A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). In the drawing, △ SPL 3.15k at LM / L = 0 is a value when there is no rectifying member. As can be seen from the figure, the upstream end of the rectifying member is located at an upstream side of the minimum gap at 25 to 90% of the minimum gap length between the impeller of the blower and the heat exchanger, and the upstream end 4a of the rectifying member 4. Line 4 connecting the end 4b on the downstream side
a ratio L between the length of a-4b and the diameter φD of the impeller 1 of the blower
/ D = 20 to 50%, and if the length of the straight line 4a-E is less than or equal to the length of the straight line 4a-4b and 50% or more,
The interference noise between the fins 3a of the heat exchanger can be reduced without deteriorating the noise value, and an air conditioner without harsh sound can be obtained.

Embodiment 8 of the Invention FIG. 29 is a partially enlarged view of a main part corresponding to FIG. 5 of Embodiment 1 of the air conditioner according to the present invention. The point O is the center of the rotation axis of the impeller 1 of the blower, the point A is the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, and the rotation axis of the outer periphery of the impeller 1 of the blower and the impeller 1 of the blower. The point of intersection of O with the straight line OA connecting the minimum gap point A is P, and the end 4a of the rectifying member on the upstream side of the air 50 blown out from the point A from the impeller 1 of the blower.
Let B be the point at which the end comes into contact with the heat exchanger 3, and F be the point at which the end 4b of the downstream rectifying member comes into contact with the heat exchanger 3.
Straight line 4a connecting the end of the upstream rectifying member and the downstream end of the air blown out from the impeller of the blower of the rectifying member.
-4b, a straight line E-4 connecting the straight line 4a-E of an arbitrary length rotated by an arbitrary angle β ° about the point 4a to the points E and 4b.
b shows the rectifying member 4 formed by b. This rectifying member 4
Are disposed in close contact with the heat exchanger 3 at points B and F. In the figure, the center of the rotation axis of the blower is point O, the rotation direction of the blower is 23, the aluminum fins of the heat exchanger 3 are 3a, and the heat exchanger 3 is
22 shows a copper pipe of the present invention.

In the air conditioner thus configured, as shown in FIG. 29, the upstream side of the air 50 blown out from the impeller 1 of the blower from the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3. Since the ends 4a and 4b of the downstream rectifying member are in close contact with the heat exchanger 3 and there is a space between the rectifying member 4 and the heat exchanger 3, the flow 50 blown out from the impeller 1 of the blower is provided.
The fin 3a of the heat exchanger and the vertical component 50x are decelerated by the straight line 4a-E portion of the rectifying member 4 and deflected in the direction of the fin 3a of the heat exchanger.
Is deflected in the direction of the fins 3a of the heat exchanger due to the Coander effect at the straight line EF downstream of the rectifying member 4, and passes through the heat exchanger 3. This eliminates the separation vortex 24 caused by the blowing flow 50 flowing at an angle of attack to the fins 3a of the heat exchanger without the rectifying member in FIG.
Since the interference noise between the fins 3a of the heat exchanger caused by the pressure fluctuation of 4 can be eliminated, the unpleasant noise generated from the main body can be reduced. FIG. 30 shows the relationship between the sound pressure level and the frequency based on the result of the 1/3 octave analysis at the same blowing air volume of the main body. In the case of the present invention shown by the broken line, the noise at 2 to 5 kHz is significantly reduced as compared with the case without the rectifying member shown by the solid line. However, in the air conditioner configured as described above, when determining the shape of the rectifying member 4, the end 4a of the rectifying member on the upstream side of the air 50 blown from the impeller 1 of the blower of the rectifying member 4 and the downstream side. From the straight line 4a-4b connecting the side end portions 4b,
A straight line 4a- having a length equal to or less than the length of the straight line 4a-4b around the point 4a.
If the angle β ° when rotating E is too large, FIG.
As shown in FIG. 1, the pressure loss of the blowout flow 50 of the impeller of the blower causes a pressure loss, and the flow on the surface of the rectifying member 4 gives pressure fluctuation to the impeller 1 of the blower, and the Nz sound and the noise value deteriorate as shown in FIG. I do. If it is too small, there is no space between the rectifying member 4 and the heat exchanger 3 as shown in FIG. 33, so that the flow 50 blown out from the impeller 1 of the blower cannot be deflected and the fin 3a of the heat exchanger Separation vortices 24 are generated, and interference noise is generated. Therefore, there is an optimum range of the angle β °.

FIG. 34 shows the sound in the frequency band of 2 to 5 kHz which is the frequency band in which the interference noise between the heat exchanger fins 3a is obtained in the result of the 1/3 OCT analysis of the noise value in FIG. 30 when the angle β ° is changed. Among the pressure levels, there is a rectifying member 4 in the 3.15 kHz band where the numerical value is the highest, and the noise reduction amount of the sound pressure level without and without SPL 3.15 k (marked in the figure)
And the noise value O. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). In the figure, ● represents {SPL3.
15k is a value when there is no rectifying member. As can be seen from the figure, if β ° = 3 to 20 °, the interference noise between the fins 3a of the heat exchanger can be reduced without deteriorating the Nz sound and the noise value, and the noise is unpleasant. Not get an air conditioner.

Embodiment 9 of the Invention FIG. 35 is a partially enlarged view of a main part corresponding to FIG. 5 of Embodiment 1 of the air conditioner according to the present invention. The center of the rotation axis of the impeller 1 of the centrifugal blower which is the blower is a point O, and the rotation direction is 23,
The point A is the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower, the copper pipe 22 of the heat exchanger 3, the outer periphery of the impeller 1 of the blower and the rotation axis O of the impeller 1 of the blower P is the intersection point with the straight line OA connecting the minimum gap point A, B is the point where the end 4a of the rectifying member on the upstream side of the air 50 blown from the impeller 1 of the blower from the point A is in close contact with the heat exchanger 3. When the point at which the end 4b of the downstream rectifying member is in close contact with the heat exchanger 3 is F, the end of the upstream rectifying member of the air blown out from the impeller of the blower of the rectifying member and the downstream side From the straight line 4a-4b connecting the ends of
-4b, a straight line 4a obtained by rotating a straight line having a length equal to or less than the length by an angle β °
The rectifying member 4 is formed by an arc E-4b having a tangent line with the fin 3a of the heat exchanger at the point F at a point E which is tangent to the straight line 4a-E at a point E and at the point F. . The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F. In the air conditioner configured as described above, as shown in FIG. 35, the upstream and downstream sides of the air 50 blown out from the impeller 1 of the blower from the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3. Since the ends 4a and 4b of the rectifying member are in close contact with the heat exchanger 3 and there is a space between the rectifying member 4 and the heat exchanger 3, the flow of the heat 50 blown out from the impeller 1 of the blower 1 The fin 3a and the vertical component 50x are decelerated by the straight line 4a-E portion of the rectifying member 4, and are deflected in the direction of the fin 3a of the heat exchanger and pass therethrough. Is deflected in the direction of the fins 3a of the heat exchanger and passes through the heat exchanger 3 by the Cander effect in the arc E-4b on the downstream side of. This eliminates the separation vortex 24 caused by the blowing flow 50 flowing at an angle of attack with respect to the fin 3a of the heat exchanger without the rectifying member in FIG. 62, and at the same time, induces the pressure fluctuation of the separation vortex 24. Since the interference noise between the fins 3a of the heat exchanger can be eliminated, the harsh noise heard from the main body 2 of the air conditioner can be reduced.

FIG. 36 shows the relationship between the sound pressure level and the frequency based on the result of the 1/3 octave analysis at the same blowing air volume of the main body. The thing of the present invention shown by the broken line is 2 to 5 k
Hz noise is greatly reduced. However, in the air conditioner configured as described above, when determining the shape of the rectifying member 4, the end 4a of the rectifying member on the upstream side of the air 50 blown from the impeller 1 of the blower of the rectifying member 4 and the downstream side. If the angle β ° when rotating the straight line 4a-E having a length equal to or less than the length of the straight line 4a-4b around the point 4a from the straight line 4a-4b connecting the side ends 4b is too large, the impeller 1 Pressure loss of the blowout flow 50 of the blower, and the flow on the surface of the rectifying member 4 gives pressure fluctuation to the impeller 1 of the blower, and Nz
The sound and noise values deteriorate. If it is too small, there is no space between the rectifying member 4 and the heat exchanger 3, so that the flow 50 blown from the impeller 1 of the blower cannot be deflected, and the separation vortex 24 occurs at the fins 3a of the heat exchanger. , Interference noise is generated. Therefore, there is an optimum range of the angle β °. FIG. 37 shows the state when the angle β ° is changed.
2 to 5 kHz, which is the frequency band in which the interference noise between the heat exchanger fins 3a in the 1/3 OCT analysis result of the noise value of
3.15 kHz, the highest numerical value among the sound pressure levels in the z band
The noise reduction amount of the sound pressure level with and without the rectifying member 4 in the z-band △ SPL 3.15k (marked by x in the figure) and the noise value O.
A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). In the figure, ● indicates a value when β ° = 0 and △ SPL 3.15k is a value without a rectifying member. As can be seen from the figure, β ° =
When the angle is in the range of 3 to 20 °, it is possible to reduce the interference noise between the fins 3a of the heat exchanger without deteriorating the Nz sound and the noise value, and to obtain an air conditioner free of harsh sound.

Embodiment 10 of the Invention FIG. 38 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the air conditioner according to the present invention. The center of the rotation axis of the impeller 1 of the centrifugal blower, which is a blower, is a point O, and the rotation direction is 2 points.
3. The minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower is point A, the copper pipe of the heat exchanger 3 is 22, the outer periphery of the impeller 1 of the blower and the rotation axis O of the impeller 1 of the blower. P is the intersection of the straight line OA connecting the minimum gap point A with the end point 4a of the rectifying member on the upstream side of the air 50 blown from the impeller 1 of the blower from the point A. B, when the point at which the end 4b of the downstream rectifying member is in close contact with the heat exchanger 3 is F, the end of the upstream rectifying member of the air blown out from the impeller of the blower of the rectifying member is referred to as F. From a straight line 4a-4b connecting the downstream ends, a straight line having a length equal to or less than the length of the straight line 4a-4b centered on the point 4a is rotated by an angle β ° at a point E to the straight line 4a-E and the straight line 4a-E. And an arc having an angle γ with the fin 3a of the heat exchanger at the point F of 90 ° or less on the upstream side. Shows the straightening member 4 which is formed by -4b. The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F. In the air conditioner thus configured, the impeller 1 of the blower and the heat exchanger 3 as shown in FIG.
End 4a, 4b of the rectifying member on the upstream side and downstream side of the air 50 blown out from the impeller 1 of the blower from the minimum gap point A of FIG.
Is close to the heat exchanger 3 and there is a space between the heat exchanger 3 and the rectifying member 4, so that the fins 3a of the heat exchanger and the vertical component 50 of the flow 50 blown out from the impeller 1 of the blower.
x is decelerated by the straight line 4a-E portion of the rectifying member 4, is deflected in the direction of the fin 3a of the heat exchanger, and passes therethrough.
The flow 50b that has not passed through the rectifying member 4 is
Effect on the downstream arc E-4b by
It is deflected in the direction of the fins 3 a of the heat exchanger and passes through the heat exchanger 3. This eliminates the separation vortex 24 caused by the blowing flow 50 flowing at an angle of attack to the fins 3a of the heat exchanger without the rectifying member in FIG.
Since the interference noise between the fins 3a of the heat exchanger induced by the pressure fluctuation of the separation vortex 24 can be eliminated, the unpleasant noise heard from the main body 2 of the air conditioner can be reduced.

FIG. 39 shows the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis at the same blowing air volume of the main body. The device of the present invention shown by the broken line is 2 to 5 kHz higher than that without the rectifying member shown by the solid line.
The noise of z is greatly reduced. However, in the air conditioner configured as described above, if the length of the straight line 4a-4b when determining the shape of the rectifying member 4 is too short, the separation vortex 24 in the fin 3a of the heat exchanger on the upstream side. Occurs, the effect is lost, even if it is too long, the effect will not be obtained anymore,
The pressure loss of the flow 50 blown out from the impeller 1 of the blower results in a reduction in noise value. And the flow 5 blown out from the impeller 1 of the blower because the length of the straight line 4a-E is too long.
A pressure loss of 0 causes noise deterioration, and the noise is too short, so that there is no effect on interference noise at the fins 3a of the heat exchanger. And the angle β
If the angle is too large, pressure loss of the blowout flow 50 of the impeller of the blower will be caused, and the flow on the surface of the rectifying member 4 will give pressure fluctuations to the impeller 1 of the blower, and the Nz sound and noise value will deteriorate. If it is too small, there will be no space between the rectifying member 4 and the heat exchanger 3, so that the flow 50 blown out from the impeller 1 of the blower cannot be deflected, and the fins 3 of the heat exchanger will not be deflected.
Separation vortex 24 at a occurs, and an interference sound is generated. Further, if the point B at which the end 4a of the rectifying member on the upstream side of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4 comes into close contact with the heat exchanger is too upstream, a pressure loss occurs, and the point A Above, the interference sound cannot be completely reduced. Thus, each optimal range exists. FIG. 40 shows the upstream end 4 a of the flow regulating member 4.
When the ratio L / D of the length L of the straight line 4a-4b connecting the end portion 4b on the downstream side and the diameter φD of the impeller of the blower is changed, the heat exchanger in the 1/3 OCT analysis result of the noise value is changed. 2-5 which are the frequency bands in which the interference noise between the fins 3a occurs.
3.15, the highest numerical value among the sound pressure levels in the kHz band
The noise reduction amount of the sound pressure level with and without the rectifying member 4 in the kHz band △ SPL 3.15 k (marked with x in the figure) and the noise value O. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). In the drawing, △ SPL 3.15k at L / D = 0 is a value when there is no rectifying member. FIG. 41 shows the length LM of the upstream straight portion 4a-E of the straightening member 4 and the straight line 4a-E.
1 / 3O when the ratio LM / L to the length L of 4b is changed
The sound pressure level with and without the rectifying member 4 in the 3.15 kHz band, which is the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band of the interference noise between the fins 3a of the heat exchanger in the CT analysis results. Level noise reduction △ SPL
3.15k (marked by x in the figure) and noise value O. A. Comparison of △ S
This is indicated by PLOA (marked with a circle in the figure). In the drawing, △ SPL 3.15k at L / D = 0 is a value when there is no rectifying member.

FIG. 42 shows a frequency band of interference noise between heat exchanger fins 3a in the result of 1/3 OCT analysis of the noise value when the angle β ° is changed.
3.15k, the highest numerical value among sound pressure levels in the Hz band
The noise reduction amount of the sound pressure level with and without the rectifying member 4 in the Hz band △ SPL 3.15k (marked with x in the figure) and the noise value O.P. A. The comparison is shown by △ SPLOA (indicated by a circle in the figure). In the figure, ● indicates a value when β ° = 0 and △ SPL 3.15k is a value without a rectifying member. FIG. 43 shows a case where the length range of the distance AB between the point B and the minimum gap point A is changed by changing the ratio AB / AP of the AB length to the minimum gap length AP between the impeller 1 of the blower and the heat exchanger. Of the noise value of FIG.
The sound pressure level with and without the rectifying member 4 in the 3.15 kHz band where the numerical value is the highest among the sound pressure levels in the 2 to 5 kHz band which is the frequency band of the interference noise between the heat exchanger fins 3a in the / 3 OCT analysis result Level noise reduction △ SP
L 3.15k (x mark in the figure), noise value reduction amount 低 減 SPL
O. This is indicated by A (indicated by a circle in the figure). △ S in ● in the figure
PL 3.15k = 0 is a value when there is no rectifying member.
As can be seen, the length of the straight line 4a-4b is 20-50% of the diameter of the impeller of the blower, the length of the straight line 4a-E is 50% to 100% of the straight line 4a-4b, and the angle β ° is Between 3 ° and 20 °, and the position of the point B is upstream of the minimum gap point A with respect to the blowout flow of the impeller of the blower, and is 25 to 90% of the minimum gap distance AP between the impeller of the blower and the heat exchanger. As long as the distance is between, the interference noise between the fins 3a of the heat exchanger can be reduced without deteriorating the Nz sound and the noise value, and an air conditioner without harsh sound can be obtained.

Embodiment 11 of the Invention FIG. 44 shows an impeller 1 and a heat exchanger 3 of a blower in the air conditioner according to the present invention.
1 shows an embodiment of a rectifying member made of a net-like member disposed near the minimum gap point A of FIG. As shown in the figure, stainless steel, zinc, or other rust-preventive wires are stuck or woven in a grid pattern. FIG. 45 shows the material of the braided net-like member different from FIG. Since the rectifying member 4 is such a structure, as shown in FIG. 46, the flow 50 blown out from the impeller 1 of the blower is decelerated by the fin 3a of the heat exchanger and the flow 50x in the vertical direction by the rectifying member. At the same time, it is deflected in the direction of the fins 3a of the heat exchanger. As a result, as shown in FIG.
The interference noise occurring at a can be reduced. However, if the wire diameter of the rectifying member is too large, as shown in an enlarged view between the heat exchanger and the rectifying member 4 in FIG.
As described above, the sound around 2 kHz increases, and an interference sound such as a jig is generated. Conversely, if the wire diameter is too small, the rectifying member 4 has no strength and follows the flow blown out from the impeller 1 of the blower. In addition, the aperture ratio of the rectifying member (=
If (the total area without the opening / the total area without the opening) is too large, the interference sound cannot be completely eliminated, and if it is too small, the pressure loss of the blowout flow 50 of the impeller of the blower due to the rectifying member. Therefore, there is an optimum range in the wire diameter and the aperture ratio of the rectifying member.

FIG. 50 shows a wire diameter φdM of the net-shaped rectifying member 4.
Is the frequency band in which the interference noise between the fins 3a of the heat exchanger in the 1/3 OCT analysis result when
2. The highest numerical value among the sound pressure levels in the band of 5 to 5 kHz.
Noise reduction of sound pressure level with and without the rectifying member 4 in the 15 kHz band △ SPL 3.15 k (x mark in the figure) and comparison of interference sound in the 2 kHz band in Fig. 50 △ SPL2k (○ mark in the figure) Is shown. FIG. 51 shows the fins 3 of the heat exchanger in the 1/3 OCT analysis result when the aperture ratio T was changed.
The rectifying member 4 in the 3.15 kHz band, which is the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which the interference noise occurs between "a" and "no noise reduction in the sound pressure level without SPL 3.15 k" (X in the figure) and the noise value O. A.
The comparison is shown by △ SPLOA (indicated by a circle in the figure). FIG.
As can be seen from 0 and 51, if the wire diameter φdM is 1 to 2 times the fin pitch of the heat exchanger and the opening ratio is 20 to 40%, the noise value is reduced, and the distance between the fins 3a of the heat exchanger is reduced. Therefore, it is possible to obtain an air conditioner that can reduce interference noise at the same time and does not generate harsh sound.

Embodiment 12 of the Invention FIG. 52 shows an impeller 1 and a heat exchanger 3 of a blower in the air conditioner according to the present invention.
Another embodiment of the rectifying member made of a net-like member disposed near the minimum gap point A is shown. As shown, straight lines 4a-E
In the plane of the above, the wire diameter φdM and the aperture ratio T are in the range φdM = 1-2 times the fin pitch, T
= 20 to 40%, the same effect can be obtained.

Embodiment 13 of the Invention FIG. 53 shows an embodiment of a rectifying member made of a perforated plate material disposed near the minimum gap point A between the impeller 1 of the blower and the heat exchanger 3 in the air conditioner according to the present invention. It is made of sheet metal or resin. With such a rectifying member 4, FIG.
4, the flow 5 blown out from the impeller 1 of the blower
The zeros are deflected in the direction of the heat exchanger fins 3a while the flow 50x in the vertical direction with the heat exchanger fins 3a is decelerated. As a result, as shown in FIG. 55, interference noise in the 2 to 5 kHz band generated in the fins 3a of the heat exchanger can be reduced. However, if the hole diameter φdt of the perforated plate is too large, the fins of the heat exchanger in the 2 kHz band are generated by the jet 27 generated by the holes as shown in the enlarged view between the heat exchanger 3 and the rectifying member 4 in FIG. Interference noise is generated from 3a. Also, if the opening ratio (= (total area with openings / total area without openings)) of this rectifying member is too large, the interference noise cannot be completely eliminated, and if it is too small, the rectifying member blows out the impeller of the blower. There will be a pressure drop in stream 50. Therefore, there is an optimal range.

FIG. 57 shows the fin pitch of the heat exchanger 3.
F. Ratio between P and hole diameter φdt. When P / φdt is changed, the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which the interference noise occurs between the fins 3 a of the heat exchanger in the result of the 1/3 OCT analysis in FIG. Noise reduction of sound pressure level with and without rectifying member 4 in 15 kHz band △ SPL 3.15 k (x mark in the figure)
And comparison of interference sound in 2 kHz band in FIG. 55５５SPL2k
(▲ in the figure), the noise value O. A. △ SPLOA (○ in the figure). FIG. 58 shows fins 3 of the heat exchanger in the 1/3 OCT analysis result when the aperture ratio T was changed.
Among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which the interference noise occurs between “a” and “3. Medium x mark) and noise level O. A. Comparison of △ S
This is indicated by PLOA (indicated by a circle in the figure). As can be seen from FIGS. 57 and 58, if the hole diameter φdt is 0.3 to 2 times the fin pitch of the heat exchanger and the aperture ratio is 25 to 40%,
The noise value can be reduced, the interference noise between the fins 3a of the heat exchanger can be reduced, and an air conditioner without harsh sound can be obtained.

Embodiment 14 of the Invention FIG. 59 shows another embodiment of the rectifying member made of a perforated plate material disposed near the minimum gap point A between the impeller 1 and the heat exchanger 3 of the blower in the air conditioner according to the present invention. In the figure, for the rectifying member using the holed member, even if all the hole diameters are not equal,
Embodiment 13 of the Invention The fin pitch of the heat exchanger in the range of the hole diameter of F. If the aperture ratio is in the range of 0.3 to 2 times P and the aperture ratio is 25 to 40% of the above range, the noise value can be reduced, and the interference noise between the fins 3a of the heat exchanger can be reduced.
And an air conditioner without harsh sound is obtained.

[0052]

According to the first aspect of the present invention, the air flow from the blower flows into the fins of the heat exchanger at an angle of attack by the rectifying member provided near the minimum gap between the heat exchanger and the blower. The resulting interference noise can be reduced, and an air conditioner without harsh sound can be obtained.

According to the second and third aspects of the invention, in particular, the blowout flow from the blower having a large angle of attack with respect to the fins of the heat exchanger on the downstream side from the minimum gap efficiently flows through the fins of the heat exchanger and exchanges heat. It is possible to reduce interference noise caused by the air blown into the vessel at an angle of attack, and to obtain an air conditioner without harsh sound.

According to the fourth aspect of the present invention, the rectifying member can be optimally arranged so as to cover the area where the interference noise is generated, and the rectifying member effectively flows into the fins of the heat exchanger at an angle of attack. Interference noise can be reduced, and an air conditioner without harsh sound can be obtained.

According to the fifth aspect of the present invention, it is possible to optimally arrange the rectifying member, and to reduce interference noise caused by flowing into the fins of the heat exchanger at an angle of attack effectively without suddenly changing the air volume and the air pressure. It is possible to obtain an air conditioner with reduced noise and no harsh sound.

According to the sixth aspect of the present invention, it is possible to obtain an air conditioner that is efficient and does not generate harsh sound without greatly increasing the wind pressure and without abrupt fluctuation.

According to the seventh invention, the wind noise of the blower (NZ
The air blown from the impeller of the blower installed in the air path inside the air conditioner to the heat exchanger at an angle of attack into the fin of the heat exchanger without increasing the noise) and deteriorating the noise value Therefore, it is possible to obtain an air conditioner that does not generate harsh sound by reducing interference noise generated due to noise.

According to the eighth aspect of the present invention, by providing the rectifying member at the optimum position, the air conditioner can be miniaturized, and interference noise at the fins of the heat exchanger generated due to inflow at an angle of attack can be reduced. An air conditioner without harsh sound can be obtained.

According to the ninth aspect of the present invention, by providing the rectifying member at the optimum position, the air conditioner can be reduced in size, and interference noise at the fins of the heat exchanger generated due to inflow at an angle of attack can be reduced. An air conditioner without harsh sound can be obtained.

According to the tenth aspect, for a miniaturized air conditioner, interference noise at the fins of the heat exchanger can be reduced without increasing wind pressure, and an air conditioner without harsh sound can be obtained.

[0061]

According to the eleventh aspect, it is possible to obtain an air conditioner which has a simple structure, reduces interference noise at the fins of the heat exchanger, and does not cause harsh sound.

According to the twelfth aspect, it is possible to effectively reduce the interference noise at the fins of the heat exchanger and obtain an air conditioner free from harsh sounds.

[Brief description of the drawings]

FIG. 1 is a sectional view of an air conditioner according to a first embodiment of the air conditioner according to the present invention.

FIG. 2 is a cross-sectional view of the air conditioner of FIG. 1 cut along a plane orthogonal to a rotation axis of an impeller of the blower.

FIG. 3 is a perspective view of the vicinity of a minimum gap point between the heat exchanger and the impeller of the blower in FIGS.

FIG. 4 is a diagram showing only a rectifying member of FIG. 3;

FIG. 5 is a partially enlarged view of a main part of FIG. 2;

FIG. 6 is an explanatory view showing the flow when the upstream end 4a of the blowout flow of the impeller of the blower from the minimum gap of the straightening member is not in close contact with the heat exchanger.

FIG. 7 is an explanatory diagram showing a flow state when the downstream end 4b of the blowout flow of the impeller of the blower from the minimum gap of the rectifying member is not in close contact with the heat exchanger.

FIG. 8 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis at the same blowing air volume of the main body in the air conditioner according to the present invention.

FIG. 9 is a cross-sectional view of an air conditioner according to a second embodiment of the air conditioner according to the present invention.

10 is a cross-sectional view taken along a plane orthogonal to the rotation axis of the impeller of the air conditioner blower of FIG.

FIG. 11 is a partially enlarged view of a main part corresponding to FIG. 5 in an example of the third embodiment of the air conditioner according to the present invention.

FIG. 12 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

FIG. 13 is a partially enlarged view of a main part of an air conditioner according to a fourth embodiment of the air conditioner according to the present invention.

FIG. 14 is a partially enlarged view of a main part of an air conditioner according to a fifth embodiment of the air conditioner according to the present invention.

FIG. 15 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

FIG. 16 is a partially enlarged view of a main part of the air conditioner according to the present invention.

17 is a ratio L / φD of the length L of a straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the straightening member of the air conditioner according to the present invention to the diameter φD of the impeller of the blower. The noise reduction amount in the 3.15 kHz band showing the largest value with respect to SPL 3.15 k and the noise value O. The figure which showed the relationship of the reduction amount of A * SPLOA.

FIG. 18 shows a length L of the upstream straight portion 4a-E of the rectifying member.
2. The largest numerical value with respect to the ratio LM / L between M and the length L of the straight line 4a-4b connecting the upstream and downstream ends of the straightening member.
Noise reduction in the 15 kHz band 帯 域 SPL 3.15 k and noise value O. The figure which showed the relationship of the reduction amount of A * SPLOA.

FIG. 19 is a partially enlarged view of a main part in an example of the sixth embodiment of the air conditioner according to the present invention.

FIG. 20 is a partially enlarged view of a main part showing a flow state when the length of a straight line 4a-4b connecting the upstream end portion and the downstream end portion of the straightening member is too short.

FIG. 21 is a partially enlarged view of a main part showing a flow state when the length of a straight line 4a-4b connecting the upstream end and the downstream end of the straightening member is too long.

FIG. 22 is a straight line 4a- connecting the upstream end 4a and the downstream end 4b of the straightening member in the air conditioner according to the present invention.
4b and the ratio L / L of the length L of the fan to the diameter φD of the impeller of the blower.
The noise reduction amount △ SPL 3.15k in the 3.15 kHz band showing the largest value for φD and the noise value O.D. A
Showing the relationship between the reduction amount of the △ SPLOA

FIG. 23 shows the length L of the upstream straight portion 4a-E of the straightening member.
Straight line 4a-4 connecting M and the upstream and downstream ends of the flow regulating member
Noise reduction in the 3.15 kHz band of the 1/3 OCT analysis with respect to the ratio LM / L to the length L of bｂSPL 3.15 k
And noise level O. A. Reduction amount of SPLO. The figure which showed the relationship with A.

FIG. 24 is a partially enlarged view of a main part corresponding to FIG. 5 of the air conditioner in one embodiment of the air conditioner according to the fourth invention;

FIG. 25 shows an example of the seventh embodiment of the air conditioner according to the present invention, wherein 1/100 of the same blowout air volume of the main body is provided.
The figure which showed the relationship between the sound pressure level and frequency based on the 3OCT analysis result.

FIG. 26 shows the ratio of the distance AB between the point B of the upstream end 4a of the rectifying member and the minimum gap point A to the heat exchanger with respect to the minimum gap distance AP between the impeller of the blower and the heat exchanger. 3.15 kHz of 1/3 OCT analysis for AB / AP
Noise reduction in the band △ SPL 3.15k and noise value O. A. Reduction amount of SPLO. The figure which showed the relationship with A.

FIG. 27 is a straight line 4a- connecting the upstream end 4a and the downstream end 4b of the straightening member in the air conditioner according to the present invention.
4b and the ratio L / L of the length L of the fan to the diameter φD of the impeller of the blower.
The noise reduction amount △ SPL 3.15k in the 3.15 kHz band showing the largest value for φD and the noise value O.D. A
FIG. 7 is a diagram showing a relationship between a reduction amount △ SPLOA of FIG.

FIG. 28: Length L of the upstream straight portion 4a-E of the rectifying member
2. The largest numerical value with respect to the ratio LM / L between M and the length L of the straight line 4a-4b connecting the upstream and downstream ends of the straightening member.
Noise reduction in the 15 kHz band 帯 域 SPL 3.15 k and noise value O. The figure which showed the relationship of the reduction amount of A * SPLOA.

FIG. 29 is a partially enlarged view of a main part of an air conditioner according to an eighth embodiment of the air conditioner according to the present invention.

FIG. 30 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

FIG. 31 is a partially enlarged view of a main part showing a flow state when the rotation angle β ° is too large.

FIG. 32 is a diagram showing the relationship between the frequency and the sound pressure level when the rotation angle β ° is too large.

FIG. 33 is a partially enlarged view of a main part showing a flow state when the rotation angle β ° is too small.

FIG. 34 shows a noise reduction amount in a 3.15 kHz band, which indicates the largest value with respect to the rotation angle β ° of the upstream straight portion 4a-E of the rectifying member in the air conditioner according to the present invention.
SPL 3.15k and noise level O.S. A reduction amountＡSPL
The figure which showed the relationship of OA.

FIG. 35 is a partially enlarged view of a main part of an air conditioner according to a ninth embodiment of the air conditioner according to the present invention.

FIG. 36 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

37. The upstream straight portion 4a-E of the straightening member is moved from the upstream and downstream ends 4a-4b of the straightening member to the upstream end portion 4a.
1/3 O with respect to the angle β ° when rotating about a
Noise reduction in 3.15 kHz band of CT analysis △ SPL
3.15k and noise level O. A. Reduction amount of SPLO.
The figure which showed the relationship with A.

FIG. 38 is a partially enlarged view of a main part of an air conditioner according to a tenth embodiment of the air conditioner according to the present invention.

FIG. 39 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

FIG. 40 is a straight line 4a- connecting the upstream end 4a and the downstream end 4b of the straightening member in the air conditioner according to the present invention.
4b and the ratio L / L of the length L of the fan to the diameter φD of the impeller of the blower.
The noise reduction amount △ SPL 3.15k in the 3.15 kHz band showing the largest value for φD and the noise value O.D. A
FIG. 7 is a diagram showing a relationship between a reduction amount △ SPLOA of FIG.

FIG. 41: Length L of the upstream straight portion 4a-E of the rectifying member
Straight line 4a-4 connecting M and the upstream and downstream ends of the flow regulating member
Noise reduction in the 3.15 kHz band of the 1/3 OCT analysis with respect to the ratio LM / L to the length L of bｂSPL 3.15 k
And noise level O. A. Reduction amount of SPLO. The figure which showed the relationship with A.

FIG. 42 shows a noise reduction amount in a 3.15 kHz band indicating the largest value with respect to the rotation angle β ° of the upstream straight portion 4a-E of the rectifying member in the air conditioner according to the present invention.
SPL 3.15k and noise level O.S. A reduction amountＡSPL
The figure which showed the relationship of OA.

FIG. 43 shows the ratio of the distance AB between the point B of the upstream end 4a of the rectifying member and the minimum gap point A to the heat exchanger with respect to the minimum gap distance AP between the impeller of the blower and the heat exchanger. 3.15 kHz of 1/3 OCT analysis for AB / AP
Noise reduction in band 帯 域 SPL 3.15k and noise level O. A. Reduction amount of SPLO. The figure which showed the relationship with A.

FIG. 44 is a view showing an example of a rectifying member provided in the air conditioner in the example of the eleventh embodiment of the air conditioner according to the present invention.

FIG. 45 is a view showing another example of the rectifying member provided in the air conditioner in the air conditioner according to the present invention.

FIG. 46 is a partially enlarged view of a main part of the air conditioner in the air conditioner according to the present invention.

FIG. 47 is a diagram showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

FIG. 48 is an enlarged view between the heat exchanger and the rectifying member when the wire diameter of the rectifying member is too large.

FIG. 49 shows a noise spectrum when the wire diameter of the rectifying member is too large.

50 is a fin pitch of a heat exchanger of a rectifying member in an air conditioner according to the present invention; FIG. P and the ratio of the wire diameter φdM of the rectifying member. Noise reduction in 3.15 kHz band showing the largest value for P / φdM △ SPL3.1
The figure which showed the relationship of the noise reduction amount △ SPL2k in 5K and 2kHz band.

FIG. 51 shows the largest numerical value with respect to the aperture ratio T of the flow regulating member in the air conditioner according to the present invention.
Noise reduction in the kHz band △ SPL 3.15k and noise value O.K. A. FIG. 7 is a diagram showing a relationship between noise reduction amounts △ SPLOA of FIG.

FIG. 52 is a view showing an example of another embodiment of the net-like rectifying member provided in the air conditioner according to the present invention.

FIG. 53 is a view showing an example of a rectifying member using a perforated plate material provided in an example of the thirteenth embodiment of the air conditioner according to the present invention.

54 is a partially enlarged view of a main part near a minimum gap between the impeller of the blower and the heat exchanger by the rectifying member of FIG. 53 of the air conditioner according to the present invention.

FIG. 55 is a view showing the relationship between the sound pressure level and the frequency based on the result of the 1/3 OCT analysis in the air conditioner according to the present invention at the same blowing air volume of the main body.

FIG. 56 is an enlarged view between the rectifying member and the heat exchanger when the hole diameter of the rectifying member using the perforated member is too large.

FIG. 57 is a rectifying member using a perforated member in the air conditioner according to the present invention, wherein the fin pitch of the heat exchanger is F.F. F. Ratio between P and hole diameter φdt of perforated member. P / φd
FIG. 9 is a diagram showing a relationship between a noise reduction amount in a 3.15 kHz band △ SPL 3.15 k and a noise reduction amount in a 2 kHz band △ SPL2 k showing the largest value for t.

FIG. 58 shows the largest numerical value with respect to the aperture ratio T of the flow regulating member in the air conditioner according to the present invention.
Noise reduction in the kHz band △ SPL 3.15k and noise value O.K. A. FIG. 7 is a diagram showing a relationship between noise reduction amounts △ SPLOA of FIG.

FIG. 59 is a view showing another embodiment of the flow regulating member in the air conditioner according to the present invention.

FIG. 60 is a sectional view of a conventional air conditioner.

FIG. 61 is a cross-sectional view cut along a plane orthogonal to a rotation axis of an impeller of a blower of a conventional air conditioner.

FIG. 62 is a partially enlarged view of a main part of a conventional air conditioner.

FIG. 63 is a view showing the relationship between sound pressure level and frequency based on the result of 1/3 OCT analysis in a conventional air conditioner.

[Explanation of symbols]

Reference Signs List 1 impeller of blower, 2 main body, 3 fin tube type heat exchanger, 3a aluminum fin of fin tube heat exchanger, 4 rectifying member, 4a impeller of blower from minimum clearance between impeller 1 of blower and heat exchanger 3 End of the rectifying member on the upstream side of the flow blown out of the blower, 4b impeller 1 of the blower
Of the rectifying member downstream of the flow blown from the impeller of the blower through the minimum gap between the heat exchanger 3 and the heat exchanger 3, 5 drain pans, 6 motors, 7 suction grills, 8 bellmouths, 9
Filter, 10 main body outlet, 11 wind direction deflection vane, 12 electrical parts box, 13 decorative panel, 14 ceiling,
15 Piping, 16 Drain water drainage pump, 17 Header, 18 Body fixing bolt, 19 Body fixing nut, 2
0 body suction port, 21 body fixing hook, 22 copper pipe, 23 direction of rotation of impeller of blower, 24 separation vortex generated in fin 3a of heat exchanger, 25 minimum of impeller and heat exchanger of blower of rectifying member 4 End 4b downstream of the gap
Discharge vortex generated in the vicinity, 26 wake vortex of wire of rectifying member,
27 Jet generated in the hole of the straightening member, 50 Air blown out from impeller of blower

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Manabu Asahina 2-6-2 Otemachi, Chiyoda-ku, Tokyo Mitsubishi Electric Engineering Co., Ltd. (56) References JP 5-126351 (JP, A) JP 61-1007019 (JP, A) JP-A-2-14335 (JP, A) JP-A-5-215354 (JP, A) JP-A-4-74215 (JP, U) .Cl. ⁷ , DB name) F24F 1/00 401 F24F 1/00 306 F24F 13/08

Claims (15)

(57) [Claims] 1. An air conditioner comprising a heat exchanger provided with fins, and a blower having a blow-off flow which flows into the fins of the heat exchanger at an angle of attack. A plate-shaped member that is provided near the minimum gap and is formed so as to be convex in the direction of the blower from the heat exchanger, and is a plate-shaped member that is separated from the heat exchanger at the protruding portion, and has an air vent in the plate-shaped member. A rectifying member is provided.
The member is blown out from the blower from near the minimum gap.
Heat exchange between the upstream and downstream
An air conditioner having both ends arranged in close contact with a vessel . 2. A rectifying member that projects from the heat exchanger toward the blower.
Is formed downstream of the minimum clearance.
Side of the rectifying member,
The rectifying member was brought into close contact with the heat exchanger with a gap about the thickness of the rectifying member.
The air conditioner according to claim 1, wherein: 3. The rectifying member includes a top portion of the convex portion and one end.
Part approaching the blower from the part to the top
From the top to the other end
Having a member moving away from the blower.
The air conditioner according to claim 1 or 2. 4. The air conditioner according to claim 1, wherein the linear length between both ends of the straightening member is 20 to 50% of the diameter of the impeller of the blower. 5. The heat exchanger and the upstream end of the flow regulating member.
A point on the blower side surface of the heat exchanger at the minimum gap with the blower
The air conditioner according to claim 1, wherein a linear length from the minimum gap point is 25 to 90% of the minimum gap length. 6. The upper end of the projection formed so as to project from the heat exchanger in the direction of the blower rotates a straight line connecting both end portions around the upstream end portion of the rectifying member by 3 to 20 degrees. The air conditioner according to claim 1, wherein the air conditioner is provided in a range. 7. An air conditioner having an impeller of a blower and a heat exchanger provided with fins on an outlet side of the impeller of the blower in the main body, wherein a center of a rotation axis of the impeller of the blower is O,
The point A on the surface of the heat exchanger on the fan side at the minimum gap between the heat exchanger and the impeller of the blower, the outer peripheral portion of the impeller of the blower and the rotation axis O of the impeller of the blower and the minimum gap point A The point of intersection with the straight line OA connecting P with the straight line OA, the point where the end 4a of the upstream rectifying member of the air blown out from the point A from the impeller of the blower comes into close contact with the heat exchanger is B, and the downstream rectifying member has End 4b
Let F be the point at which the airflow comes into close contact with the heat exchanger, from above a straight line 4a-4b connecting the end of the upstream rectifying member and the downstream end of the air blown out from the impeller of the blower of the rectifying member. A straight line 4a-E of an arbitrary length rotated by an arbitrary angle β ° about the point 4a and a straight line or a straight line 4a-E connecting the points E and 4b at the point E and the point F of the heat exchanger A rectifying member formed by an arc-shaped E-4b having a tangent of 90 ° or less on the upstream side with respect to the fin is disposed at points B and F on the heat exchanger so as to be in close contact with the heat exchanger. An air conditioner characterized by: 8. A straight line 4a-4b having a length connecting an end of the upstream rectifying member and an end of the downstream side of the air blown out from the impeller is 20 to 50% of a diameter φD of the impeller of the blower. From the top, a straight line 4a obtained by rotating a straight line having a length equal to or less than 50% and equal to or less than the length of the straight line 4a-4b around the point 4a by an arbitrary angle β °.
-E and an arc-shaped E-4b having a tangent to the straight line or the straight line 4a-E connecting the points E and 4b and having an angle with the fin of the heat exchanger at the point F of 90 ° or less on the upstream side at the point F. The air conditioner according to claim 7 , wherein the formed flow regulating member is disposed at points B and F on the heat exchanger so as to be in close contact with the heat exchanger. 9. The end 4a of the rectifying member on the upstream side of the air blown from the impeller of the blower from the point A is located at the upstream side of the minimum gap point A at the minimum gap distance AP between the impeller of the blower and the heat exchanger. B is the point where the end 4b of the downstream rectifying member is in close contact with the heat exchanger, and B is the impeller of the blower of the rectifying member. The length connecting the end of the upstream rectifying member and the downstream end of the air blown out from the fan is 20 mm in diameter φD of the impeller of the blower.
A straight line 4a-E obtained by rotating a straight line having a length equal to or less than the length of the straight line 4a-4b and not less than 50% about the point 4a from the straight line 4a-4b, which is about 50%, by an arbitrary angle β °; A rectifying member formed by an arc-shaped E-4b tangent to a straight line or a straight line 4a-E connecting the fins 4b and having an angle of 90 ° or less on the upstream side with the fin of the heat exchanger at the point F. The air conditioner according to claim 7 , wherein the air conditioner is disposed at points B and F on the heat exchanger so as to be in close contact with the heat exchanger. 10. An angle β ° = about a point 4a from a straight line 4a-4b connecting an end of a rectifying member on an upstream side and an end of a downstream side of air blown from an impeller of a blower of a rectifying member.
The angle between the straight line 4a-E of an arbitrary length rotated by 3 to 20 ° and the straight line or the straight line 4a-E connecting the points E and 4b at the point E and the angle with the fin of the heat exchanger at the point F is upstream A rectifying member formed by an arc-shaped E-4b having a tangent of 90 ° or less on its side is disposed at points B and F on the heat exchanger so as to be in close contact with the heat exchanger. Claim 7
Or the air conditioner of 8 or 9 . 11. A net-like member is used as a rectifying member provided near the minimum gap between the heat exchanger and the blower, the wire diameter is 1 to 2 times the fin pitch of the heat exchanger, and the aperture ratio is 20 to 40%. The air conditioner according to any one of claims 1 to 10 , wherein: 12. A rectifying member provided near the minimum gap between the heat exchanger and the blower is made of a perforated plate, and the hole diameter is 0.3 to 2 times the fin pitch of the heat exchanger, and the opening ratio is 25.
The air conditioner according to any one of claims 1 to 10 , wherein the air conditioner is 40% to 40%. 13. A heat exchanger provided with a plurality of fins,
An air conditioner including a blower having a blowout flow that flows into the fins of the heat exchanger at an angle of attack, wherein an upstream side of a minimum gap between the heat exchanger and the blower is provided.
Straddles the plurality of fins, and
An air conditioner, comprising: a rectifying member provided across a plurality of fins and having a ventilation port for reducing a component of a flow blown from the blower in a direction perpendicular to the fins. 14. The rectifying member may be one side of the minimum gap portion.
From the end of the fan to the minimum clearance
From the minimum clearance to the other end.
A member moving away from the blower
The air conditioner according to claim 13, wherein: 15. A body for housing a heat exchanger and a blower.
And a decorative panel provided at a lower portion of the main body,
Only one pair of makeup on both sides of the blower so as to sandwich the blower
Forming an outlet for the panel, and connecting the blower with the outlet
2. The heat exchanger according to claim 1, wherein the heat exchanger is disposed between the heat exchangers.
15. The air conditioner according to 3 or 14.