JPH09236276A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a sound of interference of air flowing into fins of a heat exchanger at an angle of elevation from an impeller provided in an air conditioner. SOLUTION: When a point on a plane on the blower side in the minimum gap between a fin tube type heat exchanger and an impeller is adopted as A and a point is intersection of the peripheral part of the impeller and a straight line OA connecting the axis O of rotation and the point A is adopted as P and when a point at which an end part 4a of a straightening member is fitted closely to the heat exchanger at a distance being 25 to 90% of the distance AP is adopted as B and a point at which an end part 4b of the straightening member is fitted closely to the heat exchanger is adopted as F, a straightening part formed of a straight line 4a-E obtained by a method wherein a straight line having a length being equal to or smaller than the length of a straight line 4a-4b or equal to or larger than 50% thereof the rotated by an angle β=3 to 20 deg. around the point 4a from the straight line 4a-4b connecting the upstream-side end part of the straightening member and the downstream-side end part thereof and having a length of 20 to 50% if the diameter ϕD of the impeller, and by a circular arc having a tangential line which is in contact with a straight line connecting the points E and 4b or the straight line 4a-E and of which the angle to the fin at the point F is 90 deg. toward the upstream side, is provided so that it is fitted closely to the heat exchanger at the points B and F.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the fins of a fin tube type heat exchanger in which the flow of air blown from a fan, for example, of an air blower installed in an air conditioner to a fin tube type heat exchanger. , Caused by the separation vortex in the fins of the heat exchanger, which occurs due to the inflow at an angle of attack,
The present invention relates to an air conditioner with reduced interference noise that can be heard as humul.

[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 outlet side of an impeller of a blower, and FIG. Figure,
FIG. 61 shows a horizontal sectional view taken along the line XX in FIG. In FIG. 60, inside the main body 2 embedded in the ceiling 14, the impeller 1 of the blower, the fin-tube type heat exchanger 3 standing around the impeller 1 of the blower, and the heat exchanger 3 are installed. A drain pan 5, which receives drain water flowing out from the surface of the heat exchanger, a motor 6, an electric component box 12 which houses a control board, and the like are arranged below. A decorative panel 13 is fixed to the lower part of the main body 2, a suction port 20 is formed in the vicinity of the central portion thereof, and blowout ports 10 are formed on four outer sides of the suction port 20. The main body is fixed by a main body fixing hook 21 by 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 causes room air to pass from the suction port 20 through the suction grill 7 and the filter 9 as indicated by the thick arrow.
It is guided by the bell mouth 8 and sucked into the impeller 1 of the centrifugal blower. After that, 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, is blown out into the room from the blowout port 10, and is air-conditioned.

FIG. 62 shows a heat exchanger 3 and an impeller 1 of a blower.
FIG. 5 is an enlarged view of an essential part in which the vicinity of the minimum clearance point A between and is illustrated, showing a state of the flow 50 blown out from the impeller 1 of the blower and the flow of air to the fins 3a of the heat exchanger.
As shown in the figure, on the upstream side of the minimum clearance point A of the flow 50 blown out from the impeller 1 of the blower, the flow is closer to the fin 3a direction of the heat exchanger, and as it goes downstream, the flow becomes closer to the fin 3a. The angle becomes nearly vertical, and the angle formed by the fins 3a and the inflow direction of air, that is, the angle of attack α increases. This allows
The separation vortex 24 is generated in the fin 3a, and the pressure fluctuation of the separation vortex 24 causes an interference sound between the fins 3a. Fig. 63 shows 1 / 3OCT of this conventional air conditioner.
The relation between the sound pressure level and the frequency according to the analysis result is shown. It can be seen that the interference sound is particularly large in the frequency band of 3.15 kHz in the figure.

[0004]

In the above-described 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 between the fins. Interference sound is generated. This phenomenon is due to the downsizing of the air conditioner and the increase in the outer diameter of the impeller of the blower.
It was noticeable when the heat exchanger and the impeller of the blower approached each other.
Further, at this time, there is a problem that a wind noise (NZ sound) is generated and the noise is deteriorated. The present invention is to obtain an air conditioner having no noise problem. Further, the present invention provides a highly reliable device even when the air conditioner is downsized.

[0005]

An air conditioner according to a first aspect of the present invention includes a heat exchanger having fins, and a blower having a blow-out flow that flows into the fins of the heat exchanger at an angle of attack. In the air conditioner equipped with, is provided in the vicinity of the minimum gap between the heat exchanger and the blower, is formed to be convex in the direction of the blower from the heat exchanger, the plate-shaped member that separates from the heat exchanger at this convex portion. There is a rectifying member having a ventilation opening in the plate-shaped member, and a portion extending from the minimum gap portion of the rectifying member to the upstream side and the downstream side of the air blown from the blower, and to the heat exchanger. And both ends of the rectifying member arranged in close proximity to each other.

In the air conditioner according to the second aspect of the invention, the top portion formed so as to be convex from the heat exchanger in the direction of the blower projects downstream from the minimum gap of the air blown out from the impeller of the blower. It was done.

An air conditioner according to a third aspect of the present invention is characterized in that a straight length between both ends of the flow regulating member is 20-50% of a diameter of an impeller of a blower. 1
Air conditioner described

In the air conditioner according to the fourth aspect of the present invention, the straight length between the upstream end of the rectifying member and the minimum clearance point is
It is 25-90% of the minimum gap length.

In the air conditioner according to the fifth aspect of the present invention, the tip of the convex portion formed so as to be convex from the heat exchanger toward the blower has both end portions centering on the upstream end portion of the rectifying member. The air conditioner according to claim 1, wherein the connecting straight line is provided in a range rotated by 3 to 20 degrees.

An air conditioner according to a sixth aspect of the invention has an impeller of a blower in a main body and a heat exchanger having fins on the outlet side of the impeller of the blower, and a rotary shaft of the impeller of the blower. The center is point O, the point on the blower side of the heat exchanger is the minimum clearance between the heat exchanger and the impeller of the blower, and A is the outer circumference of the impeller of the blower and the rotation axis O of the blower impeller and the minimum. P is the intersection with the straight line OA connecting the gap points A, B is the point where the upstream side rectifying member end 4a of the air blown from the impeller of the blower from point A is close to the heat exchanger, and B is the downstream side. End 4 of rectifying member
When b is a point close to the heat exchanger, and F is a straight line 4a-4b connecting the end of the upstream rectifying member and the end of the downstream rectifying member of the air blown from the impeller of the blower of the rectifying member. , A straight line 4a-E having an arbitrary length rotated about the point 4a by an arbitrary angle β ° and a straight line or a straight line 4a- connecting the points E and 4b.
An arcuate shape E-4 which is in contact with E at a point E and has a tangent line with the fin of the heat exchanger at a point F of 90 ° or less on the upstream side.
The baffle member formed by b is connected to the point B on the heat exchanger,
It is arranged in F so as to be close to the heat exchanger.

In the air conditioner according to the seventh aspect of the invention, the length connecting the end of the air flow regulating member on the upstream side to the end of the air blown from the impeller is 20 with the diameter φD of the impeller of the blower. ~
From the straight line 4a-4b which is 50%, the straight line 4a-E obtained by rotating the straight line 4a-4b which is the length of the straight line 4a-4b and 50% or more around the point 4a by an arbitrary angle β ° and the points E, 4b. A straight line or a straight line 4a-E that connects the above and a circular arc E-4b that has a tangent to the fin of the heat exchanger at the point F at an upstream side of 90 ° or less. It is arranged so that points B and F on the exchanger are close to the heat exchanger.

In the air conditioner pertaining to the eighth aspect of the present invention, the point B where the end 4a of the upstream rectifying member of the air blown from the impeller of the blower from point A comes into close contact with the heat exchanger, and the downstream side When the point where the end portion 4b of the rectifying member is in close contact with the heat exchanger is F, the end portion of the rectifying member on the upstream side and the end portion on the downstream side of the air blown from the impeller of the blower of the rectifying member are connected. From a straight line 4a-4b whose length is 20 to 50% of the diameter φD of the impeller of the blower, rotate a straight line that is less than the length of the straight line 4a-4b and 50% or more around the point 4a by an arbitrary angle β °. The straight line 4a-E and the straight line connecting the points E, 4b or the straight line 4a-E in contact with the straight line 4a-E, and the arc E having a tangent line of which the angle with the fin of the heat exchanger is 90 ° or less on the upstream side at the point F −
4b, and a rectifying member formed by 4b is arranged at points B and F on the heat exchanger so as to be close to the heat exchanger.

In the air conditioner according to the ninth aspect of the invention, from the straight line 4a-4b connecting the end portion of the upstream side rectifying member and the end portion of the downstream side of the air blown from the impeller of the blower of the rectifying member, A straight line 4a-E of an arbitrary length rotated about the point 4a by an angle β ° = 3 to 20 ° and a straight line or a straight line 4a-E connecting the points E and 4b are in contact with each other at the point E and heat at the point F. A rectifying member formed by an arcuate E-4b having a tangent line of 90 ° or less on the upstream side with the fins of the exchanger is provided so that points B and F on the heat exchanger are close to the heat exchanger. It is arranged in.

In the air conditioner according to the tenth aspect of the present invention, the length of the air blown out from the impeller of the blower of the air flow regulating member is such that the length connecting the upstream end of the air flow regulating member and the downstream end of the air blower impeller of the air blower. From the straight line 4a-4b which is 20 to 50% of the diameter φD of
% Of a straight line 4a-E rotated by an angle β ° = 3 to 20 ° and a straight line connecting the points E and 4b or a straight line 4a-E and at a point F of the heat exchanger Arc E with a tangent of 90 ° or less on the upstream side with the fin
-4b, and the rectifying member formed by -4b is arranged at points B and F on the heat exchanger so as to be close to the heat exchanger.

In the air conditioner according to the eleventh aspect of the invention, a mesh member is used as a rectifying member provided near the minimum gap between the heat exchanger and the blower, and the wire diameter is 1 to 2 times the fin pitch of the heat exchanger and The aperture ratio is 20 to 40%.

In the air conditioner according to the twelfth aspect of the invention, a rectifying member provided in the vicinity of the minimum gap between the heat exchanger and the blower uses a perforated plate material, and the hole diameter is 0.3 of the fin pitch of the heat exchanger. .About.2 times and the aperture ratio = 25 to 40%.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION

First Embodiment 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 an embodiment of the air conditioner according to the first invention. In the figure,
Inside the main body 2 buried in the ceiling 14, an impeller 1 of a centrifugal blower, which is a blower, a fin-tube heat exchanger 3 standing upright around the impeller 1 of the centrifugal blower, and a mesh-like rectifying member 4 Below the heat exchanger, a drain pan 5 for receiving drain water flowing from the surface of the heat exchanger, a motor 6,
An electric component box 12 and the like that accommodates the control board are arranged.
A decorative panel 13 is fixed to the lower portion of the main body 2, and a suction port 20 is formed near the center of the decorative panel 13.
Air outlets 10 are formed on the four outer sides of 0. The main body is fixed by a main body fixing hook 21 by a main body fixing bolt 18 and a fixing nut 19 suspended from the attic. During operation, by the impeller 1 of the blower driven by the motor 6, the indoor air is guided from the suction port 20 through the suction grill 7 and the filter 9 to the bell mouth 8 as shown by the thick arrow, and is directed to the impeller 1 of the blower. Be sucked. After that, the air blown out from the impeller 1 of the blower passes through the heat exchanger 3 in which the refrigerant circulates,
After being heated or cooled, it is blown into the room from the outlet 10 and is air-conditioned.

FIG. 2 is a sectional view taken along a plane orthogonal to the rotation axis of the impeller 1 of the blower shown in FIG. 16
Is a drain pump used to drain the drain water collected in the drain pan to the outside, 17 is a header for distributing the refrigerant to each copper pipe in the height direction of the heat exchanger, and 15 is a pipe for connecting with an outdoor unit. Show. Further, 23 is the rotation direction of the impeller 1 of the blower, point A is the minimum clearance between the heat exchanger 3 and the impeller 1 of the blower, and 4 is the minimum clearance A between the impeller 1 of the blower and the heat exchanger 3. Further, the rectifying member formed so as to be convex from the heat exchanger 3 toward the impeller of the blower, and 4a are
From the minimum clearance point A of the flow regulating member 4, the impeller 1 of the blower
The upstream end surfaces 4b of the air blown out from the air flow guides 4b indicate the downstream end surfaces of the air blown out from the impeller of the blower from the minimum clearance point A of the rectifying member 4, and the rectifying member 4 is heated at these two points. Proximity to, for example, close contact with the exchanger.

FIG. 3 is a perspective view of the vicinity of the minimum clearance point A between the heat exchanger 3 and the impeller 1 of the blower in FIGS. 1 and 2 as seen from the blower side. Near the minimum gap A between the impeller 1 of the blower and the heat exchanger 3, the hanger-shaped end portion 4a of the straightening member 4 of the straightening member 4 is formed so as to be convex from the heat exchanger 3 toward the blower, At 4b, it is hung and fixed on the copper pipe 22 of the heat exchanger 3 and is in close contact with the heat exchanger 3. FIG. 4 is a view showing only the flow regulating member 4 of FIG. 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 the main part of FIG.

In the air conditioner thus constructed, as shown in FIG. 5, the air 5 blown out from the impeller 1 of the blower from the minimum clearance point A between the impeller 1 of the blower and the heat exchanger 3.
Since the ends 4a and 4b of the rectifying members on the upstream side and the downstream side of 0 are in close contact with the heat exchanger 3 and there is a space between the heat exchanger 3 and the rectifying member 4, they are blown out from the impeller 1 of the blower. The heat-exchanger fins 3a and the vertical component 50x of the flow 50 are decelerated by the rectifying member 4, are deflected in the direction of the heat-exchanger fins 3a, and pass, while the flow 50b that has not passed the rectifying member 4 is rectified. Due to the Kounder effect in the member 4, the heat is deflected in the direction of the fins 3a of the heat exchanger.
Pass through. As a result, from the separation vortex 24 due to the blowing flow 50 flowing into the fin 3a of the heat exchanger when there is no flow straightening member in FIG. 62 at an angle of attack, and the minimum clearance point A of the flow straightening member 4 in FIG. As in the case where 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 forms an angle of attack with the fins 3a of the heat exchanger. Blow off the impeller 1 of the blower, as in the case where the separation vortex 24 caused by the presence of the rectifying member 4 and the end 4b of the rectifying member 4 on the downstream side of the minimum clearance point A are not in close contact with the heat exchanger 3. Since the generated flow 50 passes through the flow straightening member 4 and the pressure of the discharge vortex 25 generated near the end 4b of the flow straightening member 4 on the downstream side of the minimum gap point A is lower than the surroundings, the direction of the discharge vortex 25 is increased. The flow induces the fins 3 of the heat exchanger. Since the separation vortex 24 having an angle of attack can be eliminated, and at the same time, the interference noise between the fins 3a of the heat exchanger, which is induced by the pressure fluctuation of the separation vortex 24, can be eliminated. Can be reduced.

FIG. 8 shows the same blow-out air volume of the main body,
It shows the relationship between the sound pressure level and the frequency based on the 1/3 octave analysis result. The one of the present invention shown by the broken line is 2 to 5 kH compared with the one without the rectifying member shown by the solid line.
z noise is significantly reduced. In the above description, the rectifying member 4 is described as being in close contact with the heat exchanger.
This close contact means that it is desirable that the flow regulating member is present on the line where the upper end faces of the fins of the heat exchanger are lined up, and the end portion of the flow regulating member may be in contact with the fin or between the fins. Furthermore, even if there is no end of the rectifying member on the line where the upper end faces of the fins are lined up, and there is a gap of about the thickness of the rectifying member, for example, there is an effect of suppressing abnormal noise. Need not be the same.
The point is that the ends should be as close to the fin array as necessary to suppress abnormal noise. In addition, this top portion formed to be convex in the direction of the blower from the heat exchanger has been described as having a configuration in which it projects downstream from the minimum gap of air blown from the impeller of the blower, but if the rotation direction is either It can be said that the point E may be provided on the line OA if the air conditioner has a structure that can occur. The rectifying member 4 can be manufactured from 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 the rectifying member is installed at a place where the flow of wind is strong, annoying noise can be reduced.

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

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 invention of the air conditioner 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 a blower, is point O, the minimum gap between the fin-tube heat exchanger 3 and the impeller 1 of the blower is point A, the outer peripheral portion of the impeller 1 of the blower and the impeller of the blower. The intersection point of the rotary shaft O of No. 1 and the straight line OA connecting the minimum clearance point A is P, and the end portion 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.
Let B be the point of close contact with the heat exchanger 3 and F be the point of contact of the downstream side rectifying member 4b with the heat exchanger 3.
A straight line 4a connecting the end portion of the upstream side rectifying member and the end portion of the downstream side of the air blown from the impeller of the blower of the rectifying member.
-4b, a straight line 4a-E having an arbitrary length rotated about the point 4a by an arbitrary angle β ° and a straight line E-4 connecting the points E and 4b
The rectification | straightening member 4 formed by b is shown. This straightening member 4
Are closely attached to 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 the copper pipe of FIG.

In the air conditioner thus constructed, as shown in FIG. 11, the upstream side of the air 50 blown out from the impeller 1 of the blower from the minimum clearance point A between the impeller 1 of the blower and the heat exchanger 3, Since the ends 4a, 4b of the downstream side rectifying member are in close contact with the heat exchanger 3 and there is a space between the heat exchanger 3 and the rectifying member 4, the flow 50 blown out from the impeller 1 of the blower 50
Fins 3a of the heat exchanger and the vertical component 50x are decelerated by the straight line 4a-E of the rectifying member 4, are deflected in the direction of the fins 3a of the heat exchanger, and pass through the rectifying member 4.
The flow 50b that has not passed through is deflected toward the fins 3a of the heat exchanger by the Counder effect on the straight line E-F on the downstream side of the flow straightening member 4 and passes through the heat exchanger 3. As a result, the separation vortex 24 due to the blow-out flow 50 flowing into the fin 3a of the heat exchanger when there is no rectifying member in FIG.
Since the interference noise between the fins 3a of the heat exchanger, which is induced by the pressure fluctuation of 4, can be eliminated, the offensive 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 1/3 octave analysis result for the same blow-out air volume of the main body. The one of the present invention shown by the broken line has a noise of 2 to 5 kHz significantly reduced as compared with the one without the rectifying member shown by the solid line.

It should be noted that the straight line 4a-E portion of the straightening member 4 is matched with the fact that a substantially straight plate material is used, and if a convex or concave arc shape is used, the wind flow follows this straightening plate. Therefore, a straight line is acceptable as long as the wind does not flow.

Fourth Embodiment 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 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 point O, the minimum gap between the fin-tube heat exchanger 3 and the impeller 1 of the blower is point A, the outer peripheral portion of the impeller 1 of the blower and the impeller of the blower. The intersection point of the rotary shaft O of No. 1 and the straight line OA connecting the minimum clearance point A is P, and the end portion 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.
Let B be the point of close contact with the heat exchanger 3 and F be the point of contact of the downstream side rectifying member 4b with the heat exchanger 3.
A straight line 4a-4b connecting the end of the rectifying member upstream and the end of the rectifying member upstream from the minimum clearance point A between the heat exchanger of the air blown from the impeller of the blower of the rectifying member and the impeller of the blower.
From the top, the angle γ between the straight line 4a-E of 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 is on the upstream side. The rectification | straightening member 4 formed by the circular arc E-4b which has a tangent of 90 degrees or less is shown. 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, the third embodiment of the invention will be described. 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 the first embodiment of the invention in an example of another 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 point O,
The minimum gap between the fin-tube type heat exchanger 3 and the impeller 1 of the blower is a point A, and the straight line OA connecting the outer peripheral portion of the impeller 1 of the blower and the rotation axis O of the impeller 1 of the blower and the minimum gap point A. The intersection point is P, the point 4a where the end portion 4a of the upstream side rectifying member of the air 50 blown out from the impeller 1 of the blower comes into close contact with the heat exchanger 3 from the point A, and the end portion 4b of the downstream side rectifying member 4b. Where F is the point of contact with the heat exchanger 3, on the straight line 4a-4b connecting the end of the upstream rectifying member and the end of the downstream rectifying member of the air blown from the impeller of the blower of the rectifying member. From
Straight line 4 of arbitrary length rotated by an arbitrary angle β ° around point 4a
The straightening member 4 formed by the 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 drawing, 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 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 from the impeller 1 of the blower from the minimum clearance point A between the impeller 1 of the blower and the heat exchanger 3, Since the ends 4a, 4b of the downstream side rectifying member are in close contact with the heat exchanger 3 and there is a space between the heat exchanger 3 and the rectifying member 4, the flow 50 blown out from the impeller 1 of the blower 50
Fins 3a of the heat exchanger and the vertical component 50x are decelerated by the straight line 4a-E of the rectifying member 4, are deflected in the direction of the fins 3a of the heat exchanger, and pass through the rectifying member 4.
The flow 50b that has not passed through is passed through the heat exchanger 3 by being deflected toward the fins 3a of the heat exchanger by the Counder effect in the straight line E-F on the downstream side of the flow straightening member 4. This eliminates the separation vortex 24 due to the blow-out flow 50 flowing into the fin 3a of the heat exchanger without the rectifying member shown in FIG. 62 at an angle of attack, and at the same time induces the pressure fluctuation of the separation vortex 24. Since interference noise between the fins 3a of the heat exchanger can be eliminated, it is possible to reduce annoying noise generated from the main body. FIG. 15 shows the relationship between the sound pressure level and the frequency according to the 1/3 octave analysis result in the same blowing air volume of the main body. The one of the present invention shown by the broken line has a noise of 2 to 5 kHz significantly reduced as compared with the one without the rectifying member shown by the solid line.

However, when determining the shape of the straightening member in the air conditioner thus constructed, the straightening member 4 is used.
If the length of the straight line 4a-4b connecting the end 4a of the rectifying member on the upstream side of the minimum clearance point A of the air 50 blown out from the impeller 1 of the blower and the end 4b of the downstream side is too short, it is effective. Disappears, and even if it is too long, it will not have any further effect,
On the contrary, as shown in FIG. 16, there is a pressure loss of the flow 50 blown out from the impeller 1 of the blower. A straight line 4a-connecting the upstream end 4a and the downstream end 4b of the rectifying member 4 with respect to the air 50 blown out from the impeller of the blower.
The straight line 4a-E rotated from the point 4a about the point 4a by an arbitrary angle β ° is too long to cause 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 sound at the fins 3a of the heat exchanger is lost. Therefore, there is an optimum range.

In FIG. 17, the ratio L / D between the length L of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the flow straightening member 4 and the diameter φD of the impeller of the blower is changed. When
It is a frequency band of occurrence of interference noise between the fins 3a of the heat exchanger in the 1/3 OCT analysis result of the noise value of FIG.
-Sound pressure level noise reduction amount without and with rectifying member 4 in the 3.15 kHz band showing the highest value among sound pressure levels in the ~ 5 kHz band ΔSPL 3.15k (marked x in the figure)
And the noise value O. A. The comparison ΔSPLOA (circle in the figure) is shown. ΔSPL 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 line portion 4a-E of the straightening member 4 and the length L of the straight line 4a-4b is changed. 1/3
Of the sound pressure level in the 2 to 5 kHz band, which is the frequency band in which the interference noise occurs between the fins 3a of the heat exchanger in the OCT analysis result, the rectifying member 4 in the 3.15 kHz band showing the highest numerical value is provided. Noise reduction of sound pressure level △
SPL 3.15k (marked with X in the figure) and noise value O.S. A. The comparison ΔSPLOA (circle in the figure) is shown. LM / in the figure
ΔSPL 3.15k at L = 0 is the value when there is no rectifying member. As can be seen from the figure, the ratio L / D of the length of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the rectifying member 4 to the diameter φD of the impeller 1 of the blower L / D = 20
And the length of the straight line 4a-E is between 50% and 50%.
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 noise 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 invention of the air conditioner in another example of the 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 point O, the minimum gap between the fin-tube heat exchanger 3 and the impeller 1 of the blower is point A, the outer peripheral portion of the impeller 1 of the blower and the impeller of the blower. The intersection 4 of the rotary shaft O of No. 1 and the straight line OA connecting the minimum clearance point A is P, and 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 the heat exchanger 3 Let B be the point of close contact with the heat exchanger 3 and F be the point of contact of the downstream side rectifying member 4b with the heat exchanger 3, and the heat of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4 Minimum clearance point A between the exchanger 3 and the impeller 1 of the blower
From a straight line 4a-4b connecting the end 4a of the rectifying member on the upstream side and the end 4b on the downstream side, an arbitrary angle β around the point 4a
Straight line 4a-E and straight line 4a-E of arbitrary length rotated by
Arc E- which is tangent to the point E and has a tangent line whose angle γ with the fin 3a of the heat exchanger at the point F is 90 ° or less on the upstream side.
4b shows the flow regulating 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 configured as described above, the fifth embodiment of the invention will be described. The same effect can be obtained. However, when determining the shape of the rectifying member 4 in the air conditioner thus configured, the rectifying member 4 of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4 upstream of the minimum gap point A. If the length of the straight line 4a-4b connecting the end 4a of the No. 4 and the end 4b on the downstream side is too short, as shown in FIG.
Separation vortices 24 are generated in the fins 3a of the heat exchanger on the upstream side, the effect disappears, and even if it is too long, no further effect occurs. As shown in FIG. 21, the flow 50 blown out from the impeller 1 of the blower 50 And the noise level deteriorates. Further, from the straight line 4a-4b connecting the end 4a of the upstream rectifying member and the end 4b of the downstream rectifying member of the air 50 blown out from the impeller of the blower of the rectifying member 4, an arbitrary angle around the point 4a. 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 too short, causing interference noise at the fins 3a of the heat exchanger. The effect disappears. Therefore, there is an optimum range.

In FIG. 22, the ratio L / D between the length L of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the rectifying member 4 and the diameter φD of the impeller of the blower is changed. When
Of the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which interference noise occurs between the heat exchanger fins 3a in the 1/3 OCT analysis result of the noise value as shown in FIG. 15, in the 3.15 kHz band showing the highest value. Noise reduction amount of sound pressure level with and without rectifying member 4 of ΔSPL 3.15k (× in the figure
Mark) and noise value O. A. Comparison of △ SPLOA (○ in the figure
Mark). 23 is a 1 / 3OCT corresponding to FIG. 17 when the ratio LM / L between the length LM of the upstream straight line portion 4a-E of the straightening member 4 and the length L of the straight line 4a-4b is changed. The sound pressure level without and with the rectifying member 4 in the 3.15 kHZ band, which has the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band of interference noise generated between the fins 3a of the heat exchanger in the analysis results. Noise reduction amount △
SPL 3.15k (marked with X in the figure) and noise value O.S. A. The comparison ΔSPLOA (circle in the figure) is shown. LM / in the figure
ΔSPL 3.15k at L = 0 is the value when there is no rectifying member. As can be seen from the figure, the ratio L / D of the length of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the rectifying member 4 to the diameter φD of the impeller 1 of the blower L / D = 20
And the length of the straight line 4a-E is between 50% and 50%.
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 noise can be obtained.

Embodiment 7 of the Invention FIG. 24 is a partially enlarged view of a main portion corresponding to FIG. 5 of the first embodiment of the invention of the air conditioner in the example of the other 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 point O, the minimum gap between the fin-tube heat exchanger 3 and the impeller 1 of the blower is point A, the outer peripheral portion of the impeller 1 of the blower and the impeller of the blower. The intersection 4 of the rotary shaft O of No. 1 and the straight line OA connecting the minimum clearance point A is P, and 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 the heat exchanger 3 Let B be the point of close contact with the heat exchanger 3 and F be the point of contact of the downstream side rectifying member with the heat exchanger 3, and rectify the air blown from the impeller of the blower of the rectifying member on the upstream side. Straight line 4a- connecting the end of the member and the end on the downstream side
A straight line E-4b connecting a straight line 4a-E of arbitrary length rotated from the point 4a by an arbitrary angle β around the point 4a and points E and 4b.
The rectification | straightening member 4 formed by this is shown. The rectifying member 4 is disposed in close contact with the heat exchanger 3 at points B and F. Further, in the figure, the center of the rotation axis of the blower is indicated by point O, the direction of rotation of the blower is indicated by 23, the aluminum fins 3a of the heat exchanger 3 and the copper pipe 22 of the heat exchanger 3 are indicated. In the air conditioner thus configured, as shown in FIG. 24, the impeller 1 of the blower and the heat exchanger 3
Of the air 50 blown from the impeller 1 of the blower from the minimum gap point A of
Is in close contact with 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 fins 3a of the heat exchanger and passes through,
The flow 50b that has not passed through the flow regulating member 4 is
Due to the Counder effect on the straight line E-F on the downstream side of the heat exchanger 3, it is deflected toward the fins 3a of the heat exchanger and passes through the heat exchanger 3. This eliminates the separation vortex 24 due to the blow-out flow 50 flowing into the fin 3a of the heat exchanger without the rectifying member shown in FIG. 62 at an angle of attack, and at the same time induces the pressure fluctuation of the separation vortex 24. Since interference noise between the fins 3a of the heat exchanger can be eliminated, it is possible to reduce annoying noise generated from the main body. FIG. 25 shows the relationship between the sound pressure level and the frequency based on the 1/3 octave analysis result in the same blowing air volume of the main body. The one of the present invention shown by the broken line has a noise of 2 to 5 kHz significantly reduced as compared with the one 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 On the upstream side, pressure loss occurs and the interference sound cannot be reduced at point A.

Further, a straight line 4a connecting the end portion 4a of the rectifying member upstream of the minimum gap point A of the air 50 blown out from the impeller 1 of the blower of the rectifying member 4 and the end portion 4b of the downstream side thereof.
If the length of -4b is too short, the effect is lost, and if it is too long, the effect is not produced any more, and conversely, there is a pressure loss of the flow 50 blown out from the impeller 1 of the blower. Then, the air 5 blown out from the impeller of the blower of the rectifying member 4
0 on a straight line 4a-4b connecting the end 4a of the rectifying member on the upstream side and the end 4b on the downstream side, an arbitrary angle β around the point 4a.
The length of the straight line 4a-E rotated is too long, resulting in a pressure loss of the flow 50 blown out from the impeller 1 of the blower, resulting in worsening of noise, and being too short, it is effective for interference noise at the fin 3a of the heat exchanger. Disappears. Therefore, AB that determines the position of point B
Line 4a-4b connecting the upstream and downstream ends of the rectifying member
There is an optimum range for the distance and the length of the straightening member straight portion 4a-E. 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 when the ratio AB / AP of the length AB to the minimum gap length AP of the impeller 1 of the blower and the heat exchanger is changed. Of the sound pressure level in the 2 to 5 kHz band, which is the frequency band of the interference noise generated between the heat exchanger fins 3a in the 1/3 OCT analysis result of the noise value in FIG. Noise reduction amount ΔSPL 3.15k (x mark in the figure) at sound pressure level with and without member 4, noise value O. A noise reduction amount ΔSPLO. A (
It is indicated by a circle in the figure). △ SPL3 in ● in the figure.
15k is a value when there is no rectifying member.

In FIG. 27, the ratio L / D between the length L of the straight line 4a-4b connecting the upstream end 4a and the downstream end 4b of the rectifying member 4 and the diameter φD of the impeller of the blower is changed. When
It is a frequency band of interference noise generated between the fins 3a of the heat exchanger in the 1/3 OCT analysis result of the noise value of FIG.
-Sound pressure level noise reduction amount without and with rectifying member 4 in the 3.15 kHz band showing the highest value among sound pressure levels in the ~ 5 kHz band ΔSPL 3.15k (marked x in the figure)
And the noise value O. A. The comparison ΔSPLOA (circle in the figure) is shown. ΔSPL 3.15 at L / D = 0 in the figure
k is a value when there is no rectifying member. Also, FIG.
Between the fins 3a of the heat exchanger in the 1 / 3OCT analysis result when the ratio LM / L of the length LM of the upstream straight line portion 4a-E of the straightening member 4 and the length L of the straight line 4a-4b is changed. 3.15 kHz showing the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which interference noise is generated
The noise reduction amount ΔSPL 3.15k (marked with X in the figure) at the sound pressure level with and without the rectifying member 4 in the band, and the noise value O.
A. The comparison ΔSPLOA (circle in the figure) is shown. In the figure, ΔSPL 3.15k at LM / L = 0 is the value when there is no rectifying member. As can be seen from the figure, the upstream end of the flow regulating member is 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 flow regulating member 4 is located upstream of the minimum gap. 4 connecting the end part 4b on the downstream side with
Ratio L between the length of a-4b and the diameter φD of the impeller 1 of the blower
If the length of the straight line 4a-E is less than or equal to the length of the straight line 4a-4b and is 50% or more between / D = 20 to 50%,
It is possible to obtain an air conditioner in which interference noise between the fins 3a of the heat exchanger can be reduced without deteriorating the noise value, and which does not cause an offensive sound.

Embodiment 8 of the Invention FIG. 29 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the invention in the air conditioner according to the present invention. The rotation shaft center of the impeller 1 of the blower is a point O, the minimum gap between the fin tube type heat exchanger 3 and the impeller 1 of the blower is a point A, the outer peripheral portion of the impeller 1 of the blower and the rotation shaft of the impeller 1 of the blower. The intersection point of O and the straight line OA connecting the minimum gap point A is P, and the end portion 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.
Let B be the point of close contact with the heat exchanger 3 and F be the point of contact of the downstream side rectifying member 4b with the heat exchanger 3.
A straight line 4a connecting the end portion of the upstream side rectifying member and the end portion of the downstream side of the air blown from the impeller of the blower of the rectifying member.
-4b, a straight line 4a-E having an arbitrary length rotated about the point 4a by an arbitrary angle β ° and a straight line E-4 connecting the points E and 4b
The rectification | straightening member 4 formed by b is shown. This straightening member 4
Are closely attached to 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 the copper pipe of FIG.

In the air conditioner thus constructed, as shown in FIG. 29, the upstream side of the air 50 blown out from the impeller 1 of the blower from the minimum clearance point A between the impeller 1 of the blower and the heat exchanger 3, Since the ends 4a, 4b of the downstream side rectifying member are in close contact with the heat exchanger 3 and there is a space between the heat exchanger 3 and the rectifying member 4, the flow 50 blown out from the impeller 1 of the blower 50
Fins 3a of the heat exchanger and the vertical component 50x are decelerated by the straight line 4a-E of the rectifying member 4, are deflected in the direction of the fins 3a of the heat exchanger, and pass through the rectifying member 4.
The flow 50b that has not passed through is deflected toward the fins 3a of the heat exchanger by the Counder effect on the straight line E-F on the downstream side of the flow straightening member 4 and passes through the heat exchanger 3. As a result, the separation vortex 24 due to the blow-out flow 50 flowing into the fin 3a of the heat exchanger when there is no rectifying member in FIG.
Since the interference noise between the fins 3a of the heat exchanger, which is induced by the pressure fluctuation of 4, can be eliminated, the offensive noise generated from the main body can be reduced. FIG. 30 shows the relationship between the sound pressure level and the frequency according to the 1/3 octave analysis result in the same blowing air volume of the main body. The one of the present invention shown by the broken line has a noise of 2 to 5 kHz significantly reduced as compared with the one 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 portion 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 and the downstream of the rectifying member 4 are downstream. From the straight line 4a-4b connecting the side end 4b,
A straight line 4a-having a length equal to or shorter than the length of the straight line 4a-4b centered on the point 4a
If the angle β ° when E is rotated is too large,
1 causes a pressure loss of the blowout flow 50 of the impeller of the blower, and the flow on the surface of the rectifying member 4 gives pressure fluctuations to the impeller 1 of the blower, and the Nz sound and noise value deteriorate as shown in FIG. To do. If it is too small, there is no space between the flow straightening 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 fins 3a of the heat exchanger cannot be deflected. The separation vortex 24 is generated and an interference sound is generated. Therefore, there is an optimum range of the angle β °.

FIG. 34 shows the sound in the 2 to 5 kHz band which is the frequency band of the interference noise between the heat exchanger fins 3a in the 1/3 OCT analysis result of the noise value of FIG. 30 when the angle β is changed. Noise reduction amount of sound pressure level with and without rectifying member 4 in the 3.15 kHz band, which has the highest numerical value among pressure levels ΔSPL 3.15k (marked x in the figure)
And the noise value O. A. The comparison ΔSPLOA (circle in the figure) is shown. In the figure, ● indicates ΔSPL3.
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 harsh noise can be reduced. You can get an air conditioner that does not.

Embodiment 9 of the Invention FIG. 35 is a partially enlarged view of a main part corresponding to FIG. 5 of the first embodiment of the invention in 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 point O, and this rotation direction is 23.
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 peripheral portion of the impeller 1 of the blower and the rotation axis O of the impeller 1 of the blower, and P is an intersection with a straight line OA connecting the minimum clearance points A, and B is a point where the upstream end 4a of the rectifying member 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. Further, when the point where the end portion 4b of the rectifying member on the downstream side is in close contact with the heat exchanger 3 is F, the end portion of the rectifying member on the upstream side of the air blown from the impeller of the blower of the rectifying member and the downstream side From the straight line 4a-4b connecting the ends of the
A straight line 4a obtained by rotating a straight line having a length equal to or smaller than -4b by an angle β °.
-E and the straight line 4a-E at a point E and an angle γ with the fin 3a of the heat exchanger at a point F shows a straightening member 4 formed by an arc E-4b having a tangent line of 90 ° or less on the upstream side. . 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 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 is located on the upstream side and the downstream side. Since the ends 4a and 4b of the flow regulating member are in close contact with the heat exchanger 3 and there is a space between the heat exchanger 3 and the flow regulating member 4, the heat exchanger of the flow 50 blown out from the impeller 1 of the blower is The fins 3a and the vertical direction component 50x are decelerated by the straight line 4a-E portion of the flow straightening member 4, are deflected in the direction of the fins 3a of the heat exchanger and pass, and the flow 50b that has not passed through the flow straightening member 4 is Due to the Counder effect in the arc E-4b on the downstream side of the heat exchanger 3, the heat exchanger 3 is deflected in the direction of the fins 3a of the heat exchanger and passes through the heat exchanger 3. This eliminates the separation vortex 24 due to the blow-out flow 50 flowing into the fin 3a of the heat exchanger without the rectifying member shown in FIG. 62 at an angle of attack, 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 annoying 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 according to the 1/3 octave analysis result for the same blowing air volume of the main body. The one of the present invention shown by the broken line is 2 to 5 k compared with the one without the rectifying member shown by the solid line.
Hz noise is significantly reduced. However, in the air conditioner configured as described above, when determining the shape of the rectifying member 4, the end portion 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 and the downstream of the rectifying member 4 are downstream. 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 about the point 4a from the straight line 4a-4b connecting the end portions 4b on the side is too large, the impeller 1 of the blower 1 Of the blowout flow 50 of the blower, and the flow on the surface of the flow straightening member 4 causes a pressure fluctuation in the impeller 1 of the blower.
Sound and noise levels deteriorate. If it is too small, a space cannot be formed between the flow straightening 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 separation vortex 24 is generated in the fin 3a of the heat exchanger. , Interfering sound is generated. Therefore, there is an optimum range of the angle β °. FIG. 37 shows the result of FIG. 35 when the angle β ° is changed.
2 to 5 kH, which is the frequency band of interference noise between the heat exchanger fins 3a in the 1/3 OCT analysis result of the noise value of
3.15kH, which has the highest sound pressure level in the z band
A noise reduction amount ΔSPL of 3.15 k (X mark in the figure) at the sound pressure level with and without the rectifying member 4 in the z band, and a noise value O.S.
A. The comparison ΔSPLOA (circle in the figure) is shown. In the figure, ● indicates the value of ΔSPL 3.15k at β ° = 0 without a rectifying member. As can be seen from the figure, β ° =
If it is between 3 and 20 °, an 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 an offensive sound can be obtained.

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 invention in 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 point O, and this rotation direction is 2
3, the minimum gap between the fin tube 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 peripheral portion of the impeller 1 of the blower and the rotation axis O of the impeller 1 of the blower And P is the intersection of the straight line OA connecting the minimum clearance point A, and 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. B, where F is the point where the end 4b of the downstream rectifying member is in close contact with the heat exchanger 3, and F is the end of the rectifying member upstream of the air blown from the impeller of the blower of the rectifying member. From the straight line 4a-4b connecting the ends on the downstream side, a straight line 4a-E and a straight line 4a-E which are obtained by rotating a straight line having a length equal to or less than the length of the straight line 4a-4b about the point 4a are contacted at the point E. And an arc having a tangent line whose angle γ with the fin 3a of the heat exchanger is 90 ° or less on the upstream side at the point F 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, as shown in FIG. 38, the impeller 1 of the blower and the heat exchanger 3
Of the air 50 blown from the impeller 1 of the blower from the minimum gap point A of
Is in close contact with 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 fins 3a of the heat exchanger and passes through,
The flow 50b that has not passed through the flow regulating member 4 is
By the Counder effect in the arc E-4b on the downstream side of
It is deflected in the direction of the fins 3 a of the heat exchanger and passes through the heat exchanger 3. As a result, the separation vortex 24 due to the blow-out flow 50 flowing into the fin 3a of the heat exchanger without the rectifying member of FIG. 62 at an angle of attack can be eliminated, and at the same time,
Since the interference noise between the fins 3a of the heat exchanger, which is induced by the pressure fluctuation of the separation vortex 24, can be eliminated, the annoying 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 according to the 1/3 OCT analysis result in the case where the same blowing air volume of the main body. The one of the present invention shown by the broken line is 2 to 5 kH compared with the one without the rectifying member shown by the solid line.
z noise is significantly 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 at the fin 3a of the heat exchanger on the upstream side 24 is formed. Occurs, the effect disappears, even if it is too long, it will not produce any further effect,
A pressure loss occurs in the flow 50 blown out from the impeller 1 of the blower, and the noise value deteriorates. 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
The pressure loss becomes 0 and the noise is deteriorated, or the noise is too short to be effective for the interference sound at the fins 3a of the heat exchanger. Also the angle β
If the angle is too large, a pressure loss of the blowout flow 50 of the impeller of the blower is caused, and the flow on the surface of the rectifying member 4 causes a pressure fluctuation in the impeller 1 of the blower, which deteriorates the Nz sound and noise value. If it is too small, there is no space between the flow straightening 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 are not able to be deflected.
The separation vortex 24 at a occurs and an interference sound is generated. Further, if the point B where the end 4a of the upstream rectifying member 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, pressure loss occurs, resulting in point A. In the above, the interference sound cannot be reduced completely. Therefore, each optimum range exists. FIG. 40 shows the upstream end 4 a of the flow regulating member 4.
And the ratio L / D between the length L of the straight line 4a-4b connecting the downstream end 4b and the diameter φD of the impeller of the blower is changed, the heat exchanger 1/3 OCT analysis result of the noise value 2 to 5 which is a frequency band of interference noise generated between the fins 3a
3.15, which has the highest sound pressure level in the kHz band
Noise reduction amount ΔSPL 3.15k (X mark in the figure) of sound pressure level with and without rectifying member 4 in the kHz band, and noise value O. A. The comparison ΔSPLOA (circle in the figure) is shown. In the figure, ΔSPL 3.15k at L / D = 0 is the value when there is no rectifying member. 41 shows the length LM of the upstream straight portion 4a-E of the straightening member 4 and the straight line 4a-.
1 / 3O when the ratio LM / L with the length L of 4b is changed
The sound pressure without and with the rectifying member 4 in the 3.15 kHz band, which has 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 generated between the fins 3a of the heat exchanger in the CT analysis result. Level noise reduction ΔSPL
3.15k (X mark in the figure) and noise value O. A. Comparison of ΔS
It is indicated by PLOA (circle in the figure). In the figure, ΔSPL 3.15k at L / D = 0 is the value when there is no rectifying member.

FIG. 42 shows a frequency band of occurrence of interference noise between the heat exchanger fins 3a in the result of 1/3 OCT analysis of noise value when the angle β ° is changed from 2 to 5k.
3.15k, which has the highest sound pressure level in the Hz band
Hz noise reduction amount ΔSPL 3.15k (X mark in the figure) at the sound pressure level with and without the rectifying member 4, and the noise value O. A. The comparison ΔSPLOA (circle in the figure) is shown. In the figure, ● indicates the value of ΔSPL 3.15k at β ° = 0 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 when the ratio AB / AP of the length AB to the minimum gap length AP of the impeller 1 of the blower and the heat exchanger is changed. Of the noise level of Fig. 39
The sound pressure without and with the rectifying member 4 in the 3.15 kHz band, which has the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band of interference noise generated between the heat exchanger fins 3a in the / 3OCT analysis result. Level noise reduction △ SP
L3.15k (marked x in the figure), noise level reduction amount SPL
O. It is indicated by A (circle in the figure). △ S in the figure
PL 3.15k = 0 is the value when there is no rectifying member.
As can be seen from the figure, the length of the straight line 4a-4b is 20 to 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 25 to 90% of the minimum clearance distance AP between the impeller of the blower and the heat exchanger, upstream of the blowout flow of the impeller of the blower from the minimum clearance point A. With the distance between them, an 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 with no offensive noise can be obtained.

Eleventh Embodiment of the Invention FIG. 44 shows the impeller 1 and the heat exchanger 3 of the blower in the air conditioner according to the present invention.
An example of a rectifying member made of a net-like member disposed near the minimum gap point A of FIG. As shown in the figure, rust-proof wires made of stainless steel, zinc, etc. are laminated or knitted in a grid pattern. Further, FIG. 45 shows the material of the braided mesh member unlike FIG. Since the flow straightening 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 flow straightening member 50a in the direction perpendicular to the fins 3a of the heat exchanger. And is deflected in the direction of the fins 3a of the heat exchanger. As a result, as shown in FIG. 47, the fins 3 of the heat exchanger are
The interference noise generated in a can be reduced. However, if the wire diameter of the rectifying member is too large, as shown in the 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 jizz is generated. On the contrary, if the wire diameter is too small, the flow straightening member 4 has no strength and the flow blows out from the impeller 1 of the blower. Further, the opening ratio of the rectifying member (=
If the (total area with the opening / total area without the opening) is too large, the interference sound cannot be completely eliminated, and if it is too small, the rectifying member causes pressure loss of the blowout flow 50 of the impeller of the blower. Therefore, there is an optimum range for the wire diameter and the aperture ratio of the rectifying member.

FIG. 50 shows the wire diameter φdM of the mesh-shaped rectifying member 4.
2 is the frequency band of the interference noise generated between the fins 3a of the heat exchanger in the result of 1/3 OCT analysis when
Highest numerical value among sound pressure levels in the ~ 5 kHz band 3.
The noise reduction amount of the sound pressure level with and without the rectifying member 4 in the 15 kHz band ΔSPL3.15k (marked by X in the figure) and the interference sound in the 2 kHz band of FIG. 50 are compared by ΔSPL2k (marked by ○ in the figure). Shows. FIG. 51 shows the fins 3 of the heat exchanger in the 1/3 OCT analysis result when the aperture ratio T is changed.
The noise reduction amount of the sound pressure level ΔSPL 3.15k with and without the rectifying member 4 in the 3.15 kHz band, which has the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band of interference noise between a. (X mark in the figure) and noise value O. A.
The comparison ΔSPLOA (circle in the figure) is shown. 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 aperture ratio is 20 to 40%, the noise value is reduced and the fins 3a of the heat exchanger are It is possible to obtain an air conditioner that can reduce the interference noise in the air and does not produce an offensive sound.

Embodiment 12 of the Invention FIG. 52 shows the impeller 1 and the heat exchanger 3 of the blower in the air conditioner according to the present invention.
Another embodiment of the rectifying member made of a mesh member disposed near the minimum clearance point A of FIG. As shown, straight line 4a-E
Even if the pitch of the net is different, the wire diameter φdM and the aperture ratio T of the surface are in the range φdM = 1 to 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 clearance 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 resinous. With such a rectifying member 4, as shown in FIG.
4, the flow 5 blown out from the impeller 1 of the blower
The flow 50x perpendicular to the heat-exchanger fins 3a of 0 is decelerated and deflected toward the heat-exchanger fins 3a. Thereby, as shown in FIG. 55, the interference noise in the 2 to 5 kHz band generated in the fin 3a of the heat exchanger can be reduced. However, if the hole diameter φdt of the perforated plate material is too large, as shown in the enlarged view between the heat exchanger 3 and the rectifying member 4 in FIG. 56, the jet 27 generated by the holes causes the fins of the heat exchanger in the 2 kHz band. Interference noise is generated from 3a. Also, if the opening ratio (= (total area with opening / total area without opening) of this rectifying member is too large, the interference sound cannot be eliminated, and if it is too small, the impeller of the blower blows out by the rectifying member. There is a pressure drop in stream 50, so there is an optimum range.

FIG. 57 shows the fin pitch F.F. of the heat exchanger 3.
P to hole diameter φdt F. 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 of the interference noise generated between the fins 3a of the heat exchanger in the 1/3 OCT analysis result in FIG. Noise reduction amount of sound pressure level with and without rectifying member 4 in the 15 kHz band ΔSPL 3.15k (marked x in the figure)
And comparison of interference sound of 2 kHz band in FIG. 55 ΔSPL2k
(Marked with ▲ in the figure), noise level O. A. Comparison ΔSPLOA (○ in the figure). FIG. 58 shows fins 3 of the heat exchanger in the 1/3 OCT analysis result when the aperture ratio T is changed.
The noise reduction amount ΔSPL of the sound pressure level without and with the rectifying member 4 in the 3.15 kHz band, which has the highest numerical value among the sound pressure levels in the 2 to 5 kHz band, which is the frequency band in which interference noise occurs between a and (Middle x mark) and noise value O. A. Comparison of ΔS
It is indicated by PLOA (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%,
It is possible to obtain an air conditioner that reduces the noise value, reduces the interference noise between the fins 3a of the heat exchanger, and does not produce a jarring sound.

Fourteenth Embodiment of the Invention FIG. 59 shows another embodiment of the rectifying member made of a perforated plate material disposed near the minimum clearance point A between the impeller 1 of the blower and the heat exchanger 3 in the air conditioner according to the present invention. In the figure, for the rectifying member using the perforated member, even if the hole diameters are not all the same,
Embodiment 13 of the invention. The fin pitch of the heat exchanger F. If the aperture ratio is in the range of 0.3 to 2 times P and the range is 25 to 40%, the noise value can be reduced and the interference noise between the fins 3a of the heat exchanger can be reduced.
In addition, an air conditioner with no harsh sound can be obtained.

[0052]

According to the first aspect of the present invention, the rectifying member provided in the vicinity of the minimum gap between the heat exchanger and the blower allows the blowout flow from the blower to flow into the fins of the heat exchanger at an angle of attack. It is possible to obtain an air conditioner that reduces the generated interference noise and does not produce offensive noise.

According to the second aspect of the invention, 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 to the fins of the heat exchanger and the air is blown to the heat exchanger. However, it is possible to obtain an air conditioner that reduces interference noise that occurs due to an inflow with an angle of attack, and that produces no harsh sound.

According to the third 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 fins of the heat exchanger can be effectively flowed at an angle of attack. It is possible to obtain an air conditioner that reduces the generated interference noise and does not produce offensive noise.

According to the fourth aspect of the present invention, the rectifying member can be optimally arranged, and the interference noise caused by the inflow to the fins of the heat exchanger at an angle of attack can be effectively generated without drastically changing the air volume and the air pressure. It is possible to obtain an air conditioner that reduces noise and does not produce offensive sounds.

According to the fifth aspect of the present invention, it is possible to obtain an efficient air conditioner that does not cause a jarring sound, without significantly increasing the wind pressure and without causing a sudden change.

According to the sixth invention, the wind noise of the blower (NZ
The air blown from the impeller of the blower installed in the air passage in the air conditioner to the heat exchanger flows into the fins of the heat exchanger at an angle of attack without increasing noise. It is possible to obtain an air conditioner that reduces the interference noise that is caused by doing so and does not produce an offensive sound.

According to the seventh invention, the air conditioner can be downsized by providing the rectifying member at the optimum position, and the interference noise at the fin of the heat exchanger caused by the inflow at an angle of attack can be reduced. It is possible to obtain an air conditioner that does not produce offensive sounds.

According to the eighth aspect of the present invention, by providing the rectifying member at the optimum position, the air conditioner can be downsized, and the interference noise at the fin of the heat exchanger caused by the inflow at an angle of attack can be reduced. It is possible to obtain an air conditioner that does not produce offensive sounds.

According to the ninth aspect of the present invention, it is possible to obtain an air conditioner that does not produce annoying noise by reducing the interference noise at the fins of the heat exchanger without increasing the wind pressure in the downsized air conditioner.

According to the tenth aspect of the present invention, the air conditioner can be downsized by providing the rectifying member at the optimum position, and the interference noise in the fins of the heat exchanger can be efficiently reduced, and the air conditioning without the harsh sound. You can get the opportunity.

According to the eleventh aspect of the present invention, it is possible to obtain an air conditioner which has a simple structure, reduces interference noise at the fins of the heat exchanger, and produces no harsh sound.

According to the twelfth aspect of the invention, it is possible to effectively reduce the interference noise at the fins of the heat exchanger and obtain an air conditioner that does not produce a jarring noise.

[Brief description of drawings]

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

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

FIG. 3 is a perspective view of the vicinity of a minimum clearance point between the heat exchanger and the impeller of the blower in FIGS. 1 and 2 as viewed from the blower side.

FIG. 4 is a view showing only the rectifying member of FIG.

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

FIG. 6 is an explanatory diagram showing the flow when the end 4a on the upstream side of the blowout flow of the impeller of the blower is not in close contact with the heat exchanger with respect to the minimum gap of the rectifying member.

FIG. 7 is an explanatory view showing the flow when the end portion 4b on the downstream side of the blowout flow of the impeller of the blower is not in close contact with the heat exchanger with respect to the minimum gap of the flow regulating member.

FIG. 8 is a diagram showing the relationship between the sound pressure level and the frequency according to the 1 / 3OCT analysis result in 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 in an example of a second embodiment of the air conditioner according to the present invention.

FIG. 10 is a cross-sectional view taken along a plane orthogonal to the rotation axis of the impeller of the blower of the air conditioner of FIG. 9.

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 according to the 1/3 OCT analysis result in the same blown air volume of the main body in the air conditioner according to the present invention.

FIG. 13 is a partially enlarged view of the essential parts of the air conditioner in the example of the fourth embodiment of the air conditioner according to the present invention.

FIG. 14 is a partially enlarged view of the essential parts of the air conditioner in the example of the 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 according to the 1 / 3OCT analysis result in the same blown air volume of the main body in the air conditioner according to the present invention.

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

FIG. 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 air flow regulating member of the air conditioner according to the present invention to the diameter φD of the impeller of the blower. Which shows the largest value for the noise reduction amount SPL 3.15k in the 3.15 kHz band and the noise value O. The figure which showed the reduction amount (DELTA) SPLOA of A.

FIG. 18 is a length L of the upstream straight portion 4a-E of the straightening member.
2. The largest numerical value is shown for the ratio LM / L between M and the length L of the straight line 4a-4b connecting the upstream and downstream ends of the rectifying member.
Noise reduction amount ΔSPL 3.15k and noise value O.S. The figure which showed the reduction amount (DELTA) SPLOA of A.

FIG. 19 is a partially enlarged view of the essential parts of the example of the sixth embodiment of the air-conditioning apparatus according to the present invention.

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

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

FIG. 22 is a straight line 4a-connecting the upstream end 4a and the downstream end 4b of the rectifying member in the air conditioner according to the present invention.
Ratio of length L of 4b to diameter φD of fan impeller of blower L /
The noise reduction amount ΔSPL 3.15k and the noise value O.S. A
Showing the relationship between the amount of reduction ΔSPLOA

FIG. 23 is a length L of the upstream straight portion 4a-E of the straightening member.
A straight line 4a-4 connecting M and the upstream and downstream ends of the rectifying member
Noise reduction amount in the 3.15 kHz band of 1/3 OCT analysis with respect to the ratio LM / L with the length L of b ΔSPL 3.15k
And noise value O. A. Reduction amount ΔSPLO. The figure which showed the relationship with A.

FIG. 24 is a partially enlarged view of a main part of an air conditioner according to an embodiment of the fourth invention, the part corresponding to FIG.

FIG. 25 is a diagram showing an example of the seventh embodiment of the air conditioner according to the present invention, in which 1 /
The figure which showed the relationship between the sound pressure level and frequency by 3OCT analysis result.

FIG. 26 shows a ratio of a distance AB between a point B close to the heat exchanger at the upstream end 4a of the rectifying member and a minimum clearance point A to a minimum clearance distance AP between the impeller of the blower and the heat exchanger. 3.15 kHz with 1/3 OCT analysis for AB / AP
Noise reduction amount ΔSPL 3.15k and noise value O.S. A. Reduction amount ΔSPLO. 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 rectifying member in the air conditioner according to the present invention.
Ratio of length L of 4b to diameter φD of fan impeller of blower L /
The noise reduction amount ΔSPL 3.15k and the noise value O.S. A
FIG. 6 is a diagram showing the relationship of the reduction amount ΔSPLOA of FIG.

FIG. 28 is a length L of the upstream straight portion 4a-E of the straightening member.
2. The largest numerical value is shown for the ratio LM / L between M and the length L of the straight line 4a-4b connecting the upstream and downstream ends of the rectifying member.
Noise reduction amount ΔSPL 3.15k and noise value O.S. The figure which showed the reduction amount (DELTA) SPLOA of A.

FIG. 29 is a partially enlarged view of the essential parts of the air conditioner in the example of the 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 according to the 1 / 3OCT analysis result in the same blowing air volume of the main body in the air conditioner according to the present invention.

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

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

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

FIG. 34 is a noise reduction amount Δ in the 3.15 kHz band showing the largest numerical 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 value O.S. Reduction amount of A △ SPL
The figure which showed the relationship of OA.

FIG. 35 is a partially enlarged view of the essential parts of the air conditioner in the example of the 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 according to the 1 / 3OCT analysis result in the same blow-out air volume of the main body in the air conditioner according to the present invention.

FIG. 37 shows the upstream straight end portion 4a-E of the straightening member from the upstream end portion 4a-4b of the straightening member to the upstream end portion 4a.
1 / 3O against the angle β ° when rotating around a
Noise reduction amount in 3.15 kHz band of CT analysis ΔSPL
3.15k and noise value O. A. Reduction amount ΔSPLO.
The figure which showed the relationship with A.

FIG. 38 is a partially enlarged view of the essential parts of the air conditioner in the example of the 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 according to the 1 / 3OCT analysis result in the same blowing air volume of the main body in the air conditioner according to the present invention.

FIG. 40 is a straight line 4a-connecting the upstream end 4a and the downstream end 4b of the rectifying member in the air conditioner according to the present invention.
Ratio of length L of 4b to diameter φD of fan impeller of blower L /
The noise reduction amount ΔSPL 3.15k and the noise value O.S. A
FIG. 6 is a diagram showing the relationship of the reduction amount ΔSPLOA of FIG.

FIG. 41 is a length L of the upstream straight portion 4a-E of the rectifying member.
A straight line 4a-4 connecting M and the upstream and downstream ends of the rectifying member
Noise reduction amount in the 3.15 kHz band of 1/3 OCT analysis with respect to the ratio LM / L with the length L of b ΔSPL 3.15k
And noise value O. A. Reduction amount ΔSPLO. The figure which showed the relationship with A.

FIG. 42 is a noise reduction amount Δ in the 3.15 kHz band showing the largest numerical 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 value O.S. Reduction amount of A △ SPL
The figure which showed the relationship of OA.

FIG. 43 shows a ratio of a distance AB between a point B close to the heat exchanger at the upstream end 4a of the rectifying member and a minimum gap point A to a minimum gap distance AP between the impeller of the blower and the heat exchanger. 3.15 kHz with 1/3 OCT analysis for AB / AP
Noise reduction amount ΔSPL 3.15k and noise value O.S. A. Reduction amount ΔSPLO. The figure which showed the relationship with A.

FIG. 44 is a view showing an example of a rectifying member arranged 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 arranged 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 according to the 1 / 3OCT analysis result for the same blown air volume of the main body in the air conditioner according to the present invention.

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.

FIG. 50 is a fin pitch F.F. of a heat exchanger of a rectifying member in the air conditioner according to the present invention. P and ratio of wire diameter φdM of rectifying member F.P. Noise reduction amount in the 3.15 kHz band showing the largest value for P / φdM ΔSPL3.1
The figure which showed the relationship of noise reduction amount (triangle | delta) SPL2k in 5K and 2kHz band.

FIG. 51 shows the largest numerical value with respect to the aperture ratio T of the rectifying member in the air conditioner according to the present invention.
Noise reduction amount ΔSPL 3.15k and noise value O.V. A. Showing the relationship between the noise reduction amount ΔSPLOA of FIG.

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

FIG. 53 is a diagram showing an example of a rectifying member using a perforated plate member arranged in the thirteenth embodiment of the air-conditioning apparatus according to the present invention.

54 is a partially enlarged view of a main part in the vicinity of the minimum gap between the impeller and the heat exchanger of the blower using the flow regulating member of FIG. 53 of the air conditioner according to the present invention.

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

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

FIG. 57 is a diagram showing a flow regulating member using a perforated member in the air conditioner according to the present invention, wherein the fin pitch F. Ratio of P to hole diameter φdt of perforated member F.P. P / φd
The figure which showed the relationship of the noise reduction amount (DELTA) SPL3.15k in 3.15kHz band which shows the largest numerical value with respect to t, and the noise reduction amount (DELTA) SPL2k in 2kHz band.

FIG. 58 shows the largest numerical value with respect to the opening ratio T of the rectifying member in the air conditioner according to the present invention.
Noise reduction amount ΔSPL 3.15k and noise value O.V. A. Showing the relationship between the noise reduction amount ΔSPLOA of FIG.

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

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

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

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

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

[Explanation of symbols]

1 blower impeller, 2 main body, 3 fin-tube heat exchanger, 3a aluminum fin of fin-tube heat exchanger, 4 rectifying member, 4a End of the rectifying member on the upstream side of the flow blown from the blower, 4b Impeller 1 of the blower
And the end 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 drain pan, 6 motor, 7 suction grill, 8 bell mouth, 9
Filter, 10 air outlet, 11 wind deflector vane, 12 electrical component 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 main body suction port, 21 main body fixing hook, 22 copper pipe, 23 rotational direction of impeller of blower, 24 separation vortex generated by fin 3a of heat exchanger, 25 minimum of impeller of blower and heat exchanger of rectifying member 4 End 4b on the downstream side of the gap
Ejection vortex that occurs in the vicinity, 26 Wake vortex of wire of rectifying member,
27 Jet generated in the hole of the flow regulating member, 50 Air blown from the impeller of the blower

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Manabu Asahina 2-6-2 Otemachi, Chiyoda-ku, Tokyo Sanryo Electric Engineering Co., Ltd.

Claims (12)

[Claims] 1. An air conditioner comprising a heat exchanger provided with fins and a blower having a blow-off flow that flows into the fins of the heat exchanger at an angle of attack, wherein the heat exchanger and the blower are combined. It is a plate-like member that is provided near the minimum gap and is formed so as to project from the heat exchanger in the direction of the blower, and is separated from the heat exchanger by the projecting portion, and the plate-like member has a ventilation port. A rectifying member and a part extending from the minimum gap portion of the rectifying member to the upstream side and the downstream side of the air blown from the blower, and both ends of the rectifying member arranged in proximity to the heat exchanger. And an air conditioner 2. The top portion formed so as to project from the heat exchanger in the direction of the blower projects downstream from the minimum gap of the air blown from the impeller of the blower. Air conditioner described 3. The air conditioner according to claim 1, wherein the straight length between the both ends of the flow regulating member is 20-50% of the diameter of the impeller of the blower. 4. The air conditioner according to claim 1, wherein the straight length between the upstream end of the flow regulating member and the minimum gap point is 25-90% of the minimum gap length. 5. The upper end of the convex portion formed so as to be convex from the heat exchanger toward the blower is rotated by 3-20 degrees about a straight line connecting both end portions with the upstream end portion of the rectifying member as the center. The air conditioner according to claim 1, wherein the air conditioner is provided in a range. 6. An air conditioner having a fan impeller of a blower and a heat exchanger having fins on the outlet side of the impeller of the blower in the main body, wherein the center of the rotation axis of the impeller of the blower is point O,
The minimum clearance between the heat exchanger and the impeller of the blower is A on the blower side surface of the heat exchanger, A is the outer peripheral part of the impeller of the blower, the rotation axis O of the impeller of the blower, and the minimum clearance point A. P is the point of intersection with the straight line OA connecting points B, B is the point where the upstream side rectifying member end 4a of the air blown from the impeller of the blower from point A is close to the heat exchanger, and B is the downstream rectifying member. End 4b
Where F is the point close to the heat exchanger, from the straight line 4a-4b connecting the end of the upstream side rectifying member and the end of the downstream side of the air blown from the impeller of the blower of the rectifying member. , A straight line 4a-E having an arbitrary length rotated about the point 4a by an arbitrary angle β °, and a straight line connecting the points E and 4b or a straight line 4a-E at the point E and at the point F of the heat exchanger. A straightening member formed by an arcuate shape E-4b having a tangent line of 90 ° or less on the upstream side with the fins is disposed so as to be close to the heat exchanger at points B and F on the heat exchanger. An air conditioner characterized by 7. A straight line 4a-4b in which the length connecting the end of the air flow regulating member on the upstream side and the end of the air blown from the impeller is 20 to 50% of the diameter φD of the impeller of the blower. From above, a straight line 4a obtained by rotating a straight line that is equal to or less than the length of the straight line 4a-4b and 50% or more around the point 4a by an arbitrary angle β °.
-E and an arcuate shape E-4b which is in contact with a straight line connecting the points E and 4b or a straight line 4a-E and which has a tangent line whose angle to the fin of the heat exchanger is 90 ° or less on the upstream side at the point F, 7. The air conditioner according to claim 6, wherein the formed rectifying member is arranged at points B and F on the heat exchanger so as to be close to the heat exchanger. 8. The minimum clearance distance AP between the impeller of the blower and the heat exchanger is located upstream of the minimum clearance point A where the end portion 4a of the rectifying member on the upstream side of the air blown from the impeller of the blower from the point A is upstream of the minimum clearance point A. Let B be the point of close contact with the heat exchanger at a distance of 25 to 90%, and F be the point of contact of the end 4b of the downstream rectifying member with the heat exchanger. The length connecting the upstream end of the air flow rectifying member and the downstream end of the air blown from the fan is 20 when the impeller diameter of the blower is φD.
From the straight line 4a-4b, which is ˜50%, a straight line 4a-E obtained by rotating a straight line 4a-4b having a length equal to or less than the length of the straight line 4a-4b around the point 4a and at least 50%, and a point E, A straight line connecting 4b or a straight line 4a-E and an arc E-4b having a tangent line with the fin of the heat exchanger at a point F having an angle of 90 ° or less on the upstream side; 7. The air conditioner according to claim 6, wherein points B and F on the heat exchanger are arranged close to the heat exchanger. 9. An angle β ° = centered at a point 4a from a straight line 4a-4b connecting the end of the upstream side rectifying member and the end of the downstream side rectifying member of the air blown out from the impeller of the blower of the rectifying member. Three
The straight line 4a-E of an arbitrary length rotated by -20 ° and the straight line connecting the points E and 4b or the straight line 4a-E are in contact with each other at the point E, and at the point F, the angle with the fin of the heat exchanger is on the upstream side. A rectifying member formed by an arcuate E-4b having a tangent line of 90 ° or less is disposed at points B and F on the heat exchanger so as to be close to the heat exchanger. Item 6
Or the air conditioner described in 7 or 8. 10. The length of the air blown out from the impeller of the blower of the flow regulating member, which connects the end of the flow regulating member on the upstream side and the end on the downstream side, is 20 to 50% of the diameter φD of the impeller of the blower. From a straight line 4a-4b, a straight line 4a-
A straight line 4a-E obtained by rotating a straight line having a length not more than 4b and not less than 50% and an angle β = 3 to 20 °, and a point E,
The straightening member formed by an arcuate E-4b which is in contact with a straight line connecting 4b or a straight line 4a-E and has an angle with the fin of the heat exchanger at the point F of 90 ° or less on the upstream side. The air conditioner according to claim 6, 7 or 8 or 9, wherein the points B and F on the device are arranged so as to be close to the heat exchanger. 11. A rectifying member provided in the vicinity of the minimum gap between the heat exchanger and the blower is a mesh member, and 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 claim 1, wherein 12. A perforated plate member is used as a rectifying member provided in the vicinity of the minimum gap between the heat exchanger and the blower, and the hole diameter is 0.3 to 2 times the fin pitch of the heat exchanger and the aperture ratio = 25.
It is -40%, The air conditioner of Claim 1-10 characterized by the above-mentioned.