JP2013096601A - Air conditioning indoor unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning indoor unit capable of suppressing NZ noise with pressure fluctuation generated when a blade of a turbo fan passes through a non-uniform pressure field of corners.SOLUTION: This air conditioning indoor unit includes a casing 21, the turbo fan, and an indoor heat exchanger. The casing 21 has a storage space defined by a sidewall 21b and an upper wall 21a, and also has a bell mouth for allowing the air to flow into the storage space, and an outlet opening for discharging the heat-exchanged air. The indoor heat exchanger is disposed at an outer peripheral side of the turbo fan, and implements heating or cooling by exchanging heat of the air distributed from the turbo fan. A sidewall 21b of the casing 21 is formed into the rectangular shape while surrounding the indoor heat exchanger so that it has four corners 21d, 21e, and at least one corner 21e is buried in an inclined body 29 as a pressure change absorbing member.

Description

  The present invention relates to an indoor unit for air conditioning in which a main casing is embedded in a ceiling surface.

As shown in FIG. 12, the conventional indoor unit 100 for air conditioning has a turbofan 103 driven by a motor 102 arranged in the housing space S in the casing 101 at the center, and heats or cools the air around it. The indoor heat exchanger 104 is disposed, and includes a suction port 105 that sucks indoor air, a bell mouth 106 that guides the sucked air to the turbo fan 103, and a blower outlet 107 that discharges the heat-exchanged air. .
The indoor air flows into the casing 101 through the suction port 105, is guided to the turbo fan 103 driven by the motor 102 through the bell mouth 106, is pressurized by the turbo fan 103, and passes through the indoor heat exchanger 104. Then, it is heated or cooled, adjusted to a desired temperature, and then returned to the room through the outlet 107. In addition, the white arrow in a figure has shown the flow of air.

In this indoor unit 100 for air conditioning, it is known that NZ sound (N: number of rotations, Z: number of blades) having a frequency which is a product of the number of blades and the number of rotations of the turbo fan 103 and an integral multiple thereof is generated.
As a technique for suppressing NZ sounds, for example, an air conditioner described in Patent Document 1 is known. In this air conditioner, a centrifugal fan is provided in a box-shaped unit body, and a heat exchanger is provided so as to surround the outer periphery of the centrifugal fan. In Patent Document 1, a rectifying plate that rectifies the flow of wind from a centrifugal fan is provided on the inner surface of the heat exchanger, and either one of the ends of the rectifying plate in the vertical direction is centrifuged more than the other end. It is arranged so as to be located downstream of the fan in the blowing direction.

Japanese Patent Application Laid-Open No. 2003-267938

Although the technique disclosed in Patent Document 1 has a certain effect of suppressing the NZ sound, the cause of the NZ sound is ambiguous, including those in which the cause of the NZ sound is not clear, so it is not easy to eradicate the NZ sound. Absent.
The present invention has been made based on such a problem, and an object of the present invention is to provide a new air-conditioning indoor unit capable of suppressing a NZ sound in response to the cause of a new NZ sound. .

  The casing 101, which is generally constituted by a rectangular casing, has a turbo outlet 103 that rotates due to the air outlet 107 being cut off at the corners or being blocked by the piping space of the indoor heat exchanger 104. It is a unique point that is discontinuous with respect to the circumferential direction of the impeller. The inventors of the present invention are one of the causes of the generation of NZ sound, and pressure fluctuations having a frequency of NZ sound generated by the blades 22a passing through the non-uniform pressure field at the corners cause the blower outlet 107 to generate pressure. It was confirmed that the noise was harsh in the room. In the method of suppressing NZ sound that can be known so far, including Patent Document 1, the effect of suppressing NZ sound accompanying pressure fluctuation generated at the corner is not obtained. On the other hand, the present inventor can suppress the NZ sound due to the factor by providing a member at the corner portion for relaxing the surrounding pressure change for the blade 22a due to the passage of the blade 22a through the non-uniform pressure field. The present invention provides an air conditioning indoor unit according to the present invention which will be described below.

The indoor unit for air conditioning of the present invention includes a casing, a fan, and a heat exchanger.
The casing has a housing space defined by an upper wall and a side wall, and has a suction port through which air flows into the housing space and a blowout port through which heat-exchanged air is discharged.
A fan is arrange | positioned in the accommodation space of a casing, and pressure | voltage-rises and sends out the air inhaled from the suction inlet.
The heat exchanger is arranged on the outer peripheral side of the fan, and heats or cools the air sent by the fan by exchanging heat.
The indoor unit for air conditioning according to the present invention has four corners by forming the side wall of the casing into a rectangle so as to surround the heat exchanger, and a pressure change mitigation member is provided at least at one corner. It is characterized by that.

The pressure change mitigating member in the present invention includes at least two forms of a first form and a second form.
The pressure change alleviating member according to the first embodiment is composed of an inclined body that fills corners. In this inclined body, the area of the surface facing the heat exchanger decreases as the distance from the upper wall increases.
In the first embodiment, the degree of pressure change for the blades generated at the corners is reduced by gradually changing the angle of the corners (hereinafter referred to as the step of the corners) where the direction of the sidewall changes at a right angle or a corner close thereto. Relax, that is, reduce. Moreover, the area of the surface facing the heat exchanger is reduced as the distance from the upper wall increases, so that the inclined body does not block the air outlet and suppresses the generation of NZ noise without increasing pressure loss. To do.

The pressure change mitigating member according to the second embodiment is provided on the rear side in the rotation direction of the fan with respect to the corner portion, and includes one or a plurality of standing walls that protrude from the side wall toward the heat exchanger.
A 2nd form suppresses generation | occurrence | production of a NZ sound by interrupting | blocking the pressure fluctuation which generate | occur | produced when the blade | wing passed the nonuniform pressure field of a corner | angular part toward a blower outlet from a corner | angular part.

The standing wall according to the second form can incline the surface facing the heat exchanger. Then, the timing at which the pressure wave applied from the fan reaches the inclined surface of the standing wall is shifted, so that the pressure wave can be prevented from being amplified.
Further, the standing wall according to the second form can incline the surface facing the corner. If it does so, since the timing which the pressure wave reflected in the corner | angular part reaches | attains the said inclined surface of a standing wall will shift | deviate, it can suppress that a pressure wave amplifies.

  According to the air conditioning indoor unit of the present invention, the pressure change mitigating member is provided in at least one corner, thereby smoothing the non-uniform pressure field in the corner and mitigating the pressure change for the blades. Sound can be suppressed.

It is a figure which shows the structure of the ceiling embedded type air conditioner in this Embodiment. It is a perspective view which shows the casing in 1st Embodiment, and shows the state actually embedded in a ceiling, and upside down. It is an enlarged plan view which shows one corner | angular part vicinity of the indoor unit for air conditioning in 1st Embodiment. It is the expansion side view which showed one corner | angular part vicinity of the casing in 1st Embodiment, and was seen from the accommodation space side of the casing. It is the perspective view which reversed the upper and lower states and the state actually embedded in the ceiling which shows the modification of the casing in 1st Embodiment. The casing in 2nd Embodiment is shown, and it is the perspective view which reversed the state actually embedded in the ceiling, and up and down. Regarding the modification of the casing in the second embodiment, (a) shows an enlarged perspective view of the main part, (b) is a graph showing the effect of the modification, and (c) is an example of adding pressure waves of the same phase It is a graph to show. It is the perspective view which reversed the upper and lower sides in the state where it is actually embedded in the ceiling, showing the other modification of the casing in a 2nd embodiment. It is a principal part expansion perspective view which shows the modification of the casing in 2nd Embodiment shown in FIG. It is a principal part expansion perspective view which shows the modification of the casing in 2nd Embodiment shown in FIG. It is a graph which shows the effect of NZ sound reduction by embodiment, (a) shows the effect by 1st Embodiment, (b) shows the effect by 2nd Embodiment. It is a longitudinal cross-sectional view which shows the general structural example of a ceiling embedded type air conditioner.

[First Embodiment]
Hereinafter, a first embodiment of the present invention shown in FIGS. 1 to 5 will be described in detail.
As shown in FIG. 1, the ceiling-embedded air conditioner 10 includes an air conditioning indoor unit 11, an air conditioning outdoor unit 12, and a refrigerant pipe 13 as main elements. Although not shown, the outdoor unit 12 for air conditioning is an outdoor unit that compresses the refrigerant, an outdoor heat exchanger that exchanges heat between the refrigerant and outdoor air, and an outdoor heat exchanger that blows outdoor air to the outdoor heat exchanger. And a fan. The refrigerant pipe 13 is connected between the air conditioning indoor unit 11 and the air conditioning outdoor unit 12 so that the refrigerant can circulate between them.

  As shown in FIGS. 1 to 4, the air conditioning indoor unit 11 includes a casing 21, a motor (not shown) disposed in the accommodation space S of the casing 21, a turbo fan 22 rotated by the motor, A suction port 23 through which indoor air flows into the casing 21, a bell mouth 24 that guides air from the suction port 23 to the turbo fan 22, an indoor heat exchanger 25 that heats or cools the air, and an indoor heat exchanger 25 An air outlet 26 that allows air exchanged in the process of passing through to flow out of the casing 21 into the room is provided as a main element.

As shown in FIG. 2, the casing 21 has a box shape with one end opened, and is embedded above the ceiling of the room. The casing 21 accommodates the motor, the turbo fan 22, the bell mouth 24, the indoor heat exchanger 25, and the like described above in the accommodation space S defined by the upper wall 21a and the side wall 21b.
The casing 21 has an upper wall 21a and a side wall 21b. The side wall 21b rises substantially perpendicular to the upper wall 21a. The upper wall 21a and the side wall 21b are preferably composed of, for example, a strength structure portion made of an iron plate disposed outside and a heat insulation portion made of a foam material or the like fixed inside the strength structure portion. In addition, the inner peripheral surface side of the upper wall 21a may be called the top surface 21a for convenience.

  The motor is fixed to the approximate center of the top surface 21a in the planar direction, and the turbo fan 22 is fixed to the main shaft extending in the substantially vertical direction. As is well known, the turbo fan 22 includes a main plate fixed to the main shaft of the motor, and a shroud facing downward with respect to the main plate, and a circumferential direction is provided between the main plate and the shroud. A plurality of blades 22a to be fixed are arranged.

  The casing 21 has an opening at the bottom (upper in FIG. 2), and a ceiling cover 27 is attached to the opening so as to be substantially horizontal with the ceiling. The ceiling cover 27 has an opening at the center, and four air outlets 26 are formed in the ceiling cover 27 outside the opening. A lattice-shaped suction grill 28 is fixed to the opening of the ceiling cover 27.

  The bell mouth 24 is fixed to the upper part of the ceiling cover 27 and is disposed above the suction grill 28 and below the turbo fan 22. Further, the bell mouth 24 includes a portion for accommodating an electronic device for controlling a motor or a louver (not shown) provided in the air outlet 26 on an upper surface portion.

  As is well known, the indoor heat exchanger 25 is configured such that a plurality of heat transfer tubes penetrate through a plurality of fins stacked with a predetermined gap. In this embodiment, the indoor heat exchanger 25 has a shape of the casing 21. Together, it forms a rectangle. As shown in FIG. 3, the indoor heat exchanger 25 is disposed outside the turbo fan 22 and inside the side wall 21b of the casing 21, and is fixed to the lower surface of the top surface 21a.

Here, the side wall 21b of the casing 21 has a rectangular shape in plan view. The side wall 21b includes four straight portions 21c and corner portions 21d and 21e that connect the four straight portions 21c.
As shown in FIG. 3, the partition plate 42 is fixed so that the end of the indoor heat exchanger 25 enters the inside of the corner 21 e of the casing 21, so that the storage portion 43 is partitioned, and this storage The end portion of the refrigerant pipe 13 that supplies and discharges the refrigerant (heat exchange medium) to the heat transfer tube of the indoor heat exchanger 25 is accommodated in the portion 43.

  In the air conditioning indoor unit 11 described above, when the turbo fan 22 rotates, the indoor air flows into the casing 21 from the suction port 23 and is pressurized through the turbo fan 22, and then is supplied to the indoor heat exchanger 25. It reaches. Here, the pressurized air flows in the space between the turbo fan 22 and the indoor heat exchanger 25 in the circumferential direction, and after undergoing heat exchange with the refrigerant flowing inside when passing through the indoor heat exchanger 25, the side wall 21b. Then, the air is supplied into the room from each outlet 26. The turbo fan 22 rotates counterclockwise.

However, when the pressure is increased by the rotation of the turbo fan 22, the outlet 26 connected to the side wall 21b is cut off at the corners 21d and 21e, and in particular, the partition plate 42 is installed close to the turbo fan 22 inside the corner 21e. Therefore, the air pressure tends to be high. The non-uniform air pressure field becomes a cause of NZ noise.
Therefore, in the indoor unit 11 for air conditioning, the pressure change that moderates the pressure change for the air blades 22a in the circumferential direction of the turbo fan 22 discharge side in the space between the turbo fan 22 and the side wall 21b via the indoor heat exchanger 25. A relaxation member is provided. In the present embodiment, the corner 21 e of the casing 21 is filled with the inclined body 29 as the pressure change mitigating member. The inclined body 29 is disposed between the indoor heat exchanger 25 and the side wall 21b. In addition, although the corner | angular part 21e is demonstrated here, it cannot be overemphasized that the inclined body 29 can be provided in the other corner | angular part 21d.

As shown in FIGS. 2 to 4, the inclined body 29 has a triangular pyramid shape and includes an inclined surface 29 a facing the indoor heat exchanger 25. The inclined surface 29a has a base 29b (the base of the triangle) in contact with the upper wall (top surface) 21a, and the area decreases as the distance from the upper wall 21a increases. In this example, the vertex 29c facing the bottom side is close to the lower end edge of the side wall 21b.
By providing the above inclined body 29, the step of the corner portion 21e becomes gentle, and the change in pressure for the blade 22a generated in the circumferential direction of the turbo fan 22 discharge side from the partition plate 42 to the straight portion 21c of the casing 21 is alleviated. That is, it can be made smaller.

  In the air conditioning indoor unit 11, indoor air flows into the casing 21 from the suction port 23 by the action of the turbo fan 22 that is rotationally driven by a motor. The air flowing in from the suction port 23 is guided to the inside of the turbo fan 22 by the bell mouth 24 and is pressurized. That is, energy is given to the air that has passed through the plurality of blades 22a.

  The air whose energy is increased by being pressurized by the turbo fan 22 reaches the indoor heat exchanger 25. The air passes through the indoor heat exchanger 25 while swirling a space formed along the circumferential direction between the turbo fan 22 and the indoor heat exchanger 25, where the indoor heat exchanger 25 Exchange heat with the refrigerant inside. The air that has passed through the indoor heat exchanger 25 flows outward along the fins of the indoor heat exchanger 25, further changes the flow direction in the vertical direction along the side wall 21b, and is supplied into the room from the outlet 26. . At this time, since the inclined body 29 can reduce the pressure change for the air blades 22a on the discharge side of the turbo fan 22, generation of NZ noise is suppressed. Further, since the air outlet 26 is located on the apex 29c side of the triangular inclined surface 29a, it is possible to suppress the generation of NZ sound without blocking the air outlet 26 and increasing the pressure loss. An example of this effect is shown in FIG. 11 (a), and it was confirmed by experiments that the third-order NZ sound can be reduced.

In the above embodiment, the inclined body 29 is provided at the corner portion 21e, but the location is not limited to this. For example, the inclined body 29 can be selectively provided on any one or all of the other three corners 21d.
Further, the form of the inclined body 29 is not limited to this, and the present invention can widely adopt a form in which the pressure change for the blades 22a generated by making the step of the corner portion gentle is reduced.

  Furthermore, although the example provided with four blower outlets 26 is shown in the above embodiment, this invention is applicable to the indoor unit for air conditioning provided with two blower outlets. As is well known, in this unit, two air outlets each set to be longer are arranged in parallel at a predetermined interval. FIG. 5 shows a casing 121 suitable for this. This casing 121 is provided with inclined bodies 129 at all four corners 121d. In this inclined body 129, the inclined surface 129a facing the indoor heat exchanger 25 has an indefinite shape, but in any case, the inclined body 29 (inclined surface 29a) is smaller in area as it moves away from the top surface 121 side. ).

In the first embodiment described above, the example in which the inclined body 29 is in contact with the side wall 21b is shown, but even if there is a gap between the side wall 21b and the inclined body 29, the effect of the inclined body 29 can be obtained. it can. However, the effect of the inclined body 29 is greater when the slope 29 is in contact with the side wall 21b.
In addition, the surface of the inclined body 29 facing the indoor heat exchanger 25 is not limited to a flat surface, and even if it is a curved surface, the effect can be obtained.
Further, the specifications of the inclined body 29, for example, the overhanging dimensions from the corners 21d and 21e on the top surface 21a side, the vertical dimension of the inclined body 29, and the degree of inclination of the inclined surface are the air conditioning room in which the inclined body 29 is provided. What is necessary is just to determine suitably according to the unit 11. FIG.

[Second Embodiment]
Hereinafter, a second embodiment according to the present invention will be described. In the second embodiment, the configuration of the ceiling-embedded air conditioner 10 is the same as that of the first embodiment except for the casing 221, and therefore, the casing 221 will be mainly described below. Moreover, about the same structure as the casing 21 of 1st Embodiment, the code | symbol same as 1st Embodiment is attached | subjected.
As shown in FIG. 6, the casing 221 includes a standing wall 229 behind the corner portion 21 e in the rotational direction (counterclockwise) of the turbofan 22. The standing wall 229 is in contact with the side wall 21b and the top surface 21a, and projects from the side wall 21b toward the inside of the casing 221 facing the indoor heat exchanger 25. The standing wall 229 extends from the top surface 21a downward to a predetermined position. The standing wall 229 includes a side surface 229a facing the inside of the casing 221, and a pair of side surfaces 229b and 229c that connect the side surface 229a and the side wall 21b. The side walls 229b and 229c face the corners 21d and 21e. Further, the side wall 229a and the side walls 229b and 229c are orthogonal to each other. The side surface 229a is inclined with respect to the side wall 21b.

In the second embodiment, as shown in FIG. 6, it is observed that the pressure fluctuation that becomes a sound wave generated by the blade 22 a of the turbofan 22 passing through the pressure nonuniform field at the corner portion propagates and expands to the outlet 26. The wall 229 can be blocked to reduce the NZ sound.
According to the study of the present inventor, by suppressing the occurrence of an acoustic vibration mode in which the four corners that coincide with the frequency of the higher-order NZ sound at a certain rotational speed of the turbo fan 22 are antinodes, The amplification of the next NZ sound can be suppressed. An example of the experiment is shown in FIG.

  Although the side wall 229a of the standing wall 229 is inclined, the pressure wave is amplified by shifting the timing at which the pressure wave W1 reaching from the turbo fan 22 collides with the side surface 229a of the standing wall 229 in the height direction of the standing wall 229. Can be suppressed. Moreover, it can suppress that the standing wall 229 becomes resistance of the flow of the air to the blower outlet 26. FIG.

In the above example, the side surface 229a facing the inside of the casing 21 is an inclined surface. However, as shown in FIG. 7A, the side surface 229b facing the corner portion 21e can be an inclined surface. By doing so, the following effects are produced.
The distance from the corner portion 21e of the side surface 229b is different between the distal end L1 and the proximal end L2. Therefore, it is possible to suppress the pressure wave W2 from being amplified because the timing at which the pressure wave that is reflected by the corner portion 21e of the casing 21 collides with the standing wall 229 is shifted depending on the position in the height direction.
Further, since the distance that the pressure wave W2 travels between the corner portion 21e and the standing wall 229 is different, it is possible to avoid the phase being shifted and the pressure wave W2 from being amplified. This is shown in FIG. 7 (b). That is, the phases of the pressure waves W2 at the positions A, B, and C from the base end side of the side surface 229a are shifted as shown in FIG. 7B. The pressure wave as a whole from the base end to the tip end of the side surface 229b ("the whole" in the figure) is the sum of the pressure waves W2 at the positions A, B, and C. Since the phase is shifted, it is smaller than that obtained by adding the pressure waves of the same phase shown in FIG.

As shown in FIG. 8, two (plural) standing walls 229 can be provided for one corner 21e.
Various forms can be adopted also when two standing walls 229 are provided.
For example, as shown in FIG. 9, two standing walls 230 and 231 are provided. The standing wall 230 is disposed near the corner 21e, and the standing wall 231 is disposed farther from the corner 21e than the standing wall 230. The distance L3 from the corner 21e to the standing wall 230 is different from the distance L4 from the standing wall 230 to the standing wall 231 (L3 <L4). By doing so, the pressure waves W2 reflected from the corner 21e are out of phase with each other because the distance between the corner 21e and the standing wall 230 and between the corner 21e and the standing wall 231 is different. The pressure wave W2 can be prevented from being amplified. Note that the pressure wave W2 reflected by the corner 21e is blocked by the standing wall 230, but is diffracted to pass between the corner 21e and the standing wall 231. Further, the pressure wave W2 is also transferred between the standing wall 230 and the standing wall 231. However, this also means that the corner 21e and the standing wall 230 and the corner 21e and the standing wall 231 are different. Since the distance to go back and forth is different, it contributes to suppressing the pressure wave W2 from being amplified.

  The form shown in FIG. 9 shows an example in which the standing wall 230 and the amount protruding inward from the side wall 21 of the standing wall 230 (hereinafter simply referred to as the protruding amount) are the same. The protruding amount of the wall 232 and the standing wall 233 can be made different. By doing so, the pressure wave reflected from the corner 21e reaches the standing wall 233 directly, so that the above-described effect can be obtained more remarkably. In the example of FIG. 10, the standing wall 233 has the side surface 233b facing the corner portion 21e as an inclined surface. Therefore, as described with reference to FIG. 7, the effect of suppressing the pressure wave from being amplified can be enjoyed. .

In the second embodiment described above, an example in which the standing wall 229 (the same applies to the standing walls 330 to 333) is in contact with the side wall 21b is shown, but even if there is a gap between the side wall 21b and the standing wall 229, The effect of the standing wall 229 can be obtained. However, the effect of the standing wall 229 is greater when the standing wall 229 is in contact with the side wall 21b.
In the second embodiment described above, the side surface 229b as the inclined surface is inclined so as to approach the side wall 21b as it is separated from the upper wall 21a, but the inclination is opposite to this, that is, the upper wall Even if it inclines so that it may become far from the side wall 21b as it leaves | separates from 21a, the effect by an inclined surface can be acquired similarly. The same applies to the side surfaces 229b and 229c facing the corner portions 21e and 21d, respectively.
Furthermore, the specifications of the standing wall 229, for example, the overhanging dimension of the standing wall 229 from the side wall 21b, the vertical dimension of the standing wall 229, and the inclination degree of the inclined surface depend on the air conditioning indoor unit 11 provided with the standing wall 229. May be determined as appropriate.
In addition to this, as long as it does not depart from the gist of the present invention, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate. For example, the ceiling-embedded air conditioner 10 is merely an example, and it goes without saying that the present invention can be applied to a modified air conditioner. In addition, it is effective to make the corners 21d and 21e or the inclined body 29 and the standing wall 129 with a plastic having sound absorbing performance in order to make the effects of the present invention more remarkable.

DESCRIPTION OF SYMBOLS 10 Ceiling embedded type air conditioner 11 Air-conditioning indoor unit 12 Air-conditioning outdoor unit 13 Refrigerant piping 21, 121, 221 Casing 21a Upper wall (top surface)
21b, 121b Side wall 21d, 21e, 121d Corner 22 Turbo fan 23 Inlet 25 Indoor heat exchanger 26 Outlet 29, 129 Inclined body 229, 230, 231, 232, 233 Standing wall 229a, 229b, 229c, 233b Side

Claims (5)

A casing having a storage space partitioned by a side wall and an upper wall, and having a suction port through which air flows into the storage space, and a blowout port for discharging heat-exchanged air;
A fan that is arranged in the housing space of the casing and pressurizes and sends out the air sucked from the suction port;
A heat exchanger that is disposed on the outer peripheral side of the fan and that heats or cools the air sent out by the fan,
The side wall of the casing is formed in a rectangular shape so as to surround the heat exchanger, thereby having four corners,
At least one corner is provided with a pressure change relaxation member,
An indoor unit for air conditioning characterized by this. The pressure change relaxation member is
It consists of an inclined body that fills the corner,
In the inclined body, the area of the surface facing the heat exchanger decreases as the area moves away from the upper wall.
The indoor unit for air conditioning of Claim 1. The pressure change relaxation member is
2. The indoor unit for air conditioning according to claim 1, wherein the indoor unit for air conditioning is provided on the rear side in the rotation direction of the fan with respect to the corner portion and is one or a plurality of standing walls extending from the side wall toward the heat exchanger. The standing wall has an inclined surface facing the heat exchanger,
The indoor unit for air conditioning of Claim 3. The standing wall has an inclined surface facing the corner,
The indoor unit for air conditioning of Claim 3 or 4.

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