WO2019142466A1 - Air conditioner - Google Patents

Abstract

Provided is an air conditioner in which air blowing noise generated when a discharge air flow strikes fins is reduced without a significant increase in air flow resistance. This air conditioner is provided with: an indoor heat exchanger (18) disposed surrounding the outer periphery of a turbo fan (17); and a plurality of flow conditioning plates (32) mounted on the inner peripheral side of the indoor heat exchanger (18). The indoor heat exchanger (18) has: a plurality of flat surface sections arranged along a flat plane perpendicular to a radial direction at a closest position (P1) which is closest to the turbo fan (17); and a plurality of curved surface sections which connect the plurality of flat surface sections. First flat surface sections (18A) have mounted thereon: a first flow conditioning plate (32A) located at a first predetermined position on the upstream side of the closest position (P1) in the rotational direction (Rd) of the turbo fan (17); and a second flow conditioning plate (32B) located at a second predetermined position on the downstream side of the closest position (P1) in the rotational direction (Rd) of the turbo fan (17), the first and second flow conditioning plates (32A, 32B) being arranged adjacent to each other.

Description

Air conditioner

The present invention relates to an air conditioner provided with a plurality of straightening vanes mounted on the inner circumferential side of a heat exchanger.

BACKGROUND Conventionally, a ceiling-embedded air conditioner in which a finned tube type heat exchanger is provided around a centrifugal fan is known (see, for example, Patent Document 1).
The air conditioner disclosed in Patent Document 1 has three air guide plates disposed at the centers of the inner sides of the four sides of the square heat exchanger. The air guide plate is formed in a curved surface shape which is inclined in the direction opposite to the rotation direction of the centrifugal fan and bulges inward. In the air conditioner of Patent Document 1, the blowing air is generated by colliding with the fins by causing the blowing air to flow into the narrow space of the three baffle plates and changing the direction of the blowing air to the direction of the fins. Reduce noise.

JP 2001-99436 A

However, the air conditioner of patent document 1 arrange | positions three sheets of wind guide boards in the center inside the four sides of a square shaped heat exchanger, respectively. The air guide plate is formed in a curved shape which is inclined in the direction opposite to the rotation direction of the centrifugal fan and bulges inward. Therefore, the ventilation resistance is greatly increased by arranging the baffle plate.

This invention is made in view of such a situation, Comprising: The air conditioner which can reduce the ventilation noise which a blowout wind collides with a fin and generates without raising ventilation resistance greatly is provided. The purpose is to

In order to solve the said subject, the air conditioner of this invention employ | adopts the following means.
An air conditioner according to an aspect of the present invention includes a fan that allows air flowing in along an axial direction of a rotation shaft to flow out radially in a direction intersecting the axial direction, and is disposed to surround the outer periphery of the fan A heat exchanger having a heat transfer pipe and a plurality of fins attached to the heat transfer pipe, and attached to the inner peripheral side of the heat exchanger and extending along an axis parallel to the rotation axis toward the rotation axis A plurality of straightening plates projecting in a straight line, the heat exchanger being provided with a plurality of flat portions disposed along a plane orthogonal to the radial direction at the closest position to the fan; A plurality of curved surface portions connecting the flat surface portions, and at least one of the plurality of flat surface portions is disposed at a first predetermined position upstream of the closest position in the rotational direction of the fan; 1 of the rectifier plate And the second straightening vane is attached to a second predetermined position downstream of the closest position in the rotation direction of the fan, and the first straightening vane and the second straightening vane are adjacent to each other. Will be placed.

According to the air conditioner pertaining to one aspect of the present invention, at least one of the plurality of flat portions of the heat exchanger is a first predetermined upstream side of the rotational direction of the fan than the closest position with the fan. A first baffle is mounted in position. Therefore, the velocity component in the rotational direction of the blowing air decreases due to the turbulent flow generated by the first current plate before reaching the closest position, and the blowing noise is generated due to the blowing wind colliding with the fins at the closest position. Decreases.
According to the air conditioner pertaining to one aspect of the present invention, at least one of the plurality of flat portions of the heat exchanger is a second predetermined side downstream of the closest position with the fan in the rotational direction of the fan. A second baffle is mounted in position. Therefore, it is suppressed that the velocity component in the rotational direction of the blowing air rises again on the downstream side of the rotational direction of the fan from the closest position, and the blowing noise generated by the blowing air colliding with the fins is reduced.

According to the air conditioner pertaining to an aspect of the present invention, the flow straightening plate extends along an axis parallel to the rotation axis of the fan and has a shape projecting linearly toward the rotation axis. The air flow resistance is reduced as compared to the case where it is formed in a curved shape that bulges inward by inclining in the direction opposite to the direction. Since the first straightening vane and the second straightening vane are disposed on the upstream side and the downstream side in the rotational direction of the fan with the closest position therebetween, the three straightening vanes including the closest position are disposed. Ventilation resistance is reduced compared to the case of
As described above, according to the air conditioner according to one aspect of the present invention, it is possible to reduce the blowing noise generated due to the blowing wind colliding with the fins without largely increasing the ventilation resistance.

In the air conditioner according to one aspect of the present invention, the first predetermined position includes the radial direction passing through the closest position of the flat portion and the radial direction passing through the tip of the first straightening vane. It may be a position where the angle to be formed is in the range of 3 degrees or more and 7 degrees or less. More preferably, the position may be 5 degrees.
By doing this, it is possible to appropriately reduce the velocity component in the rotational direction of the blowing wind at the closest position.

In the air conditioner according to one aspect of the present invention, the second predetermined position may be the radial direction passing through the closest position of the flat portion and the radial direction passing through the tip of the second straightening vane. It may be a position where the angle to be formed is in the range of 15 degrees or more and 20 degrees or less.
By doing this, it is possible to appropriately suppress that the velocity component in the rotational direction of the blow-off air rises again on the downstream side of the rotational direction of the fan than the closest position.

In the air conditioner according to one aspect of the present invention, the radial direction of the fan and the heat exchanger at the closest position of the flat portion to which the first straightening vane and the second straightening vane are attached When the distance is L and the length of the first current plate projecting toward the rotation axis is l, L / l ≧ 3.5 and l ≧ 7 mm may be satisfied.
Raising the draft resistance by the first rectifying plate by setting the radial distance L between the fan and the heat exchanger to be 3.5 times or more of the length l projecting toward the rotating shaft of the first rectifying plate Can be sufficiently suppressed. By setting l to 7 mm or more, it is possible to appropriately generate turbulence with the first straightening vane and to reduce the velocity component in the rotational direction of the blowout wind at the closest position.

ADVANTAGE OF THE INVENTION According to this invention, the air conditioner which can reduce the ventilation noise which a blowing wind collides with a fin and generate | occur | produces, without raising a ventilation resistance large can be provided.

It is a perspective view of the air conditioner concerning one embodiment of the present invention. It is a longitudinal cross-sectional view of the indoor unit of the air conditioner shown in FIG. It is the figure which looked at the fan and indoor heat exchanger which are shown in FIG. 2 from the opening side. It is the elements on larger scale of the indoor heat exchanger and the baffle plate shown in FIG. It is the elements on larger scale near the nearest position of the 1st plane part shown in FIG. It is a graph which shows the sound pressure level of the noise generated by an indoor unit.

Below, one Embodiment of the air conditioner 1 which concerns on this invention is described with reference to drawings.
FIG. 1 shows a perspective view of a ceiling-embedded air conditioner 1 according to the present embodiment, and FIG. 2 shows a longitudinal sectional view thereof. Here, an example of the ceiling-embedded air conditioner 1 in which one indoor unit 3 is connected to the outdoor unit 2 is shown.

In the air conditioner 1, the indoor unit 3 is hung and installed on a ceiling or the like in a room, and is connected to the outdoor unit 2 installed outdoors via the refrigerant pipe 4 and the electric wiring 5. The outdoor unit 2 is provided with equipment such as a refrigerant compressor 6, an outdoor heat exchanger 7, an outdoor fan 8, a control box 9, and a four-way switching valve (not shown). The outdoor unit 2 constitutes a refrigeration cycle together with an indoor heat exchanger 18 described later provided on the indoor unit 3 side, and has an adjusting function of the refrigerant supplied to the indoor unit 3.

The indoor unit 3 includes a cabinet 10 whose lower portion is opened, and a substantially square ceiling panel 11 attached to the lower part of the cabinet 10. A bell mouth 13 forming an air suction port 12 and a drain pan 14 are installed at a lower part in the cabinet 10, and an air passage 15 is formed by a part of the drain pan 14. At the center of the top plate of the cabinet 10, a turbofan 17 rotationally driven by a fan motor 16 is installed, and an indoor heat exchanger formed in a rectangular shape so as to surround the outer periphery of the turbofan 17. The reference numeral 18 is fixedly installed on the top plate side via a bracket (not shown).

Inside the cabinet 10, indoor air is introduced to the turbo fan 17 via the bell mouth 13 forming the air suction port 12, and air radially boosted by the turbo fan 17 is drawn to surround the outer periphery thereof. An air flow passage 19 is formed to flow through the disposed indoor heat exchanger 18 to the air passage 15 formed by the inner surface of the cabinet 10 and the outer peripheral surface of the drain pan 14.

A rectangular air outlet 20 for blowing conditioned air along the four sides of the square-shaped ceiling panel 11 is provided to communicate with the air passage 15, and for drawing room air into the central portion. An opening 21 is provided. As shown in FIG. 1, a suction grille 23 provided with an air filter 22 and the like is provided in the opening 21 so as to be able to move up and down via a wire 24 and the like. At each air outlet 20, a wind direction adjusting louver 25 for adjusting the wind direction of the conditioned air blown out from the air outlet 20 is installed so as to be separately swingable.

The turbo fan 17 has a main plate 27 provided with a hub 26 for fixing the rotation shaft 16A of the fan motor 16 at its central portion, and a shroud for forming a fluid flow path 28 opposed to the main plate 27. A plurality of blades 30 disposed between the shroud 29 and the main plate 27 are configured. The turbo fan 17 is disposed such that the shroud 29 side is opposed to the air suction port 12 of the bell mouth 13 and a part of the bell mouth 13 is overlapped with the inner periphery of the shroud 29. A recirculation passage 31 is formed, which circulates a portion along the back surface of the bell mouth 13 from the gap between the overlap portion of the bell mouth 13 and the shroud 29 to the inner surface 29 A of the shroud 29.

The turbo fan 17 is a fan that rotates around the rotation shaft 16A of the fan motor 16, and discharges the air flowing in along the axial direction of the rotation shaft 16A in the radial direction intersecting the axial direction of the rotation shaft 16A. The axial direction of the rotation shaft 16A coincides with the vertical direction, and the radial direction intersecting the axial direction coincides with the horizontal direction.

Here, the indoor heat exchanger 18 will be described with reference to FIG. FIG. 3 is a view of the turbo fan 17 and the indoor heat exchanger 18 shown in FIG.
As shown in FIG. 3, the indoor heat exchanger 18 is disposed to surround the outer periphery of the turbo fan 17 and has a heat transfer pipe 18 a and a plurality of fins 18 b attached to the heat transfer pipe 18 a. As shown in FIG. 3, the indoor heat exchanger 18 includes a first flat portion 18A, a second flat portion 18B, a third flat portion 18C, a fourth flat portion 18D, a fifth flat portion 18E, and a first curved portion 18F. , A second curved surface portion 18G, a third curved surface portion 18H, and a fourth curved surface portion 18I.

The first flat portion 18A is a portion disposed along a plane orthogonal to the radial direction at the closest position P1 to the blade 30 of the turbo fan 17. The second flat portion 18B is a portion disposed along a plane orthogonal to the radial direction at the closest position P2 to the blade 30 of the turbo fan 17. The third flat portion 18C is a portion disposed along a plane orthogonal to the radial direction at the closest position P3 to the blade 30 of the turbo fan 17. The fourth flat portion 18D is a portion disposed along a plane orthogonal to the radial direction at the closest position P3 to the blade 30 of the turbo fan 17. The fifth flat portion 18E is a portion disposed along a plane orthogonal to the radial direction at the closest position P5 to the blade 30 of the turbo fan 17.

The first curved surface portion 18F is a portion connecting the first flat surface portion 18A and the second flat surface portion 18B, and the second curved surface portion 18G is a portion connecting the second flat surface portion 18B and the third flat surface portion 18C, The third curved surface portion 18H is a portion connecting the third flat surface portion 18C and the fourth flat surface portion 18D, and the fourth curved surface portion 18I is a portion connecting the fourth flat surface portion 18D and the fifth flat surface portion 18E.

Next, with reference to FIGS. 2 to 5, the plurality of flow straightening plates 32 mounted on the inner peripheral side of the indoor heat exchanger 18 will be described. FIG. 4 is a partially enlarged view of the indoor heat exchanger 18 and the straightening vane 32 shown in FIG. FIG. 5 is a partially enlarged view of the vicinity of the closest position P1 of the first plane portion 18A of FIG.
As shown in FIG. 2, on the inner peripheral side of the indoor heat exchanger 18, a straightening vane 32 extending along an axis X1 parallel to the rotation axis 16A, and a straightening vane extending along an axis X2 parallel to the rotation axis 16A 32 and are attached.

As shown in FIG. 3, the two flow straightening plates 32 are attached to the inner peripheral side of the first flat portion 18A, and the two flow straightening plates 32 are attached to the inner peripheral side of the second flat portion 18B. The two flow straightening plates 32 are attached to the inner peripheral side of the third flat portion 18C. One straightening vane 32 is attached to the inner circumferential side of the fourth flat portion 18D, and one straightening vane 32 is attached to the inner circumferential side of the fifth flat portion 18E.

As shown in FIG. 4, the straightening vane 32 includes a base portion 32 a disposed along a plane orthogonal to the radial direction of the turbo fan 17, and a plate portion 32 b linearly projecting from the base portion 32 a toward the rotation shaft 16 A A pair of holding portions 32c that project in the opposite direction of the plate portion 32b from the base portion 32a, and a support portion 32d that protrudes in the opposite direction of the plate portion 32b from the base portion 32a. The straightening vane 32 is attached to the indoor heat exchanger 18 by holding the heat transfer pipe 18 a by the pair of holding parts 32 c in a state where the support part 32 d is supported by the heat transfer pipe 18 a.

As shown in FIG. 4, in a state in which the flow straightening plate 32 is attached to the indoor heat exchanger 18, the upper end of the base 32 a of the flow straightening plate 32 coincides with the upper end of the fin 18 b of the indoor heat exchanger 18. With such a positional relationship, the operator can easily align the baffle plate 32 with the indoor heat exchanger 18 by aligning the upper end of the base 32 a of the baffle plate 32 with the upper end of the fin 18 b. Can be attached to

As shown in FIG. 5, the first flat portion 18A is mounted in a state where the straightening vane 32A (first straightening vane) and the straightening vane 32B (second straightening vane) are disposed adjacent to each other. There is. The straightening vane 32A is attached to a first predetermined position on the upstream side of the rotational direction Rd of the turbo fan 17. In the first predetermined position, an angle θ1 formed by a radial direction passing the closest position P1 of the first flat surface portion 18A and a radial direction passing the tip of the straightening vane 32A is in the range of 3 degrees to 7 degrees. Position. More preferably, the first predetermined position is a position where θ1 is 5 degrees. By doing this, it is possible to appropriately reduce the speed component of the rotational direction Rd of the blow-off air from the turbo fan 17 at the closest position P1.

The straightening vane 32B is attached to a second predetermined position on the downstream side of the rotational direction Rd of the turbo fan 17. In the second predetermined position, an angle θ2 formed by a radial direction passing through the closest position P1 of the first flat portion 18A and a radial direction passing through the tip of the straightening vane 32B is in the range of 15 ° to 20 °. Position. By doing this, it is possible to appropriately suppress that the speed component of the rotational direction Rd of the blow-off air rises again on the downstream side of the rotational direction Rd of the turbo fan 17 with respect to the closest position P1.

In FIG. 5, the distance L is the radial distance between the turbofan 17 and the indoor heat exchanger 18 at the closest position P1 of the first flat portion 18A to which the straightening vanes 32A and the straightening vanes 32B are attached. The distance l is a length projecting toward the rotation shaft 16A of the straightening vane 32A and the straightening vane 32B. In the present embodiment, the distance L and the distance l satisfy the relationships of the following equations (1) and (2).
L / l ≧ 3.5 (1)
l 7 7 mm (2)
Formula (1) is a condition for suppressing the rise of the draft resistance by the straightening vane 32A. The equation (2) is a condition for reducing the velocity component of the rotational direction Rd of the blowing air of the turbo fan 17 at the closest position P1.

Although the two flow straightening plates 32 attached to the first flat surface portion 18A have been described above, the two flow straightening plates 32 attached to the second flat surface portion 18B are also two flow straightening flow plates 32 attached to the first flat surface portion 18A. It becomes the same arrangement as. The two flow straightening plates 32 attached to the third flat surface portion 18C also have the same arrangement as the two flow straightening flow plates 32 attached to the first flat surface portion 18A.

Two straightening vanes 32 are attached to each of the first flat portion 18A, the second flat portion 18B, and the third flat portion 18C, while one each of the fourth flat portion 18D and the fifth flat portion 18E is attached. The current plate 32 is attached. This is because the lengths of the fourth flat portion 18D and the fifth flat portion 18E are shorter than those of the first flat portion 18A, the second flat portion 18B, and the third flat portion 18C, and the blowout wind at the closest positions P4 and P5 is This is because the velocity component in the rotational direction Rd is small.

Next, the sound pressure level of the noise generated by the indoor unit 3 of the air conditioner 1 of the present embodiment and a comparative example thereof will be described. FIG. 6 is a graph showing the sound pressure level of noise generated in the indoor unit 3 of the present embodiment. In FIG. 6, solid lines indicate sound pressure levels when a plurality of rectifying plates 32 are disposed on the inner peripheral side of the indoor heat exchanger 18 as shown in FIG. 3 of this embodiment, and broken lines indicate a plurality of The sound pressure level in the case where all of the rectifying plates 32 are not arranged is shown. FIG. 6 shows the relationship between the 1/3 octave band center frequency (Hz) and the sound pressure level (dB).

As shown in the experimental result of FIG. 6, in the air conditioner 1 of the present embodiment, the sound pressure level in the high frequency region (2 kHz to 4 kHz) that is easily recognized as noise is lower than that in the comparative example. This is because the current plate 32 is attached to the first predetermined position on the upstream side of the rotational direction Rd of the turbo fan 17 with respect to the closest positions P1, P2, and P3. It is considered that the cause is the decrease due to the turbulent flow generated in the straightening vane 32 before reaching the closest position P1, P2, P3.

Since the straightening vane 32 is attached at a second predetermined position on the downstream side of the rotational direction Rd of the turbo fan 17 with respect to the closest positions P1, P2 and P3 with the turbo fan 17, from the nearest positions P1, P2 and P3 It is considered that this is because the speed component of the rotational direction Rd of the blowing air is suppressed to rise again on the downstream side of the rotational direction Rd of the turbo fan 17.

The operation and effect of the air conditioner 1 of the present embodiment described above will be described.
According to the air conditioner 1 of the present embodiment, the closest position P1 to the blade 30 of the turbo fan 17 is on the first flat portion 18A, the second flat portion 18B, and the third flat portion 18C of the indoor heat exchanger 18. , P2, and P3, the current plate 32 is attached to a first predetermined position on the upstream side of the rotational direction Rd of the turbo fan 17. Therefore, the velocity component in the rotational direction Rd of the blowing air decreases due to the turbulent flow generated by the rectifying plate 32 before reaching the closest positions P1, P2 and P3, and the blowing wind is generated at the closest positions P1, P2 and P3. The blowing noise generated by collision with the fins 18 b is reduced.

The first predetermined position is a radial direction passing the closest position P1 (P2, P3) of the first flat surface portion 18A (the second flat surface portion 18B, the third flat surface portion 18C) and a radial direction passing the tip of the rectifying plate 32A. This is a position where the angle θ1 formed by と is in the range of 3 degrees to 7 degrees. More preferably, the position is 5 degrees.

According to the air conditioner 1 of the present embodiment, the closest position P1 to the blade 30 of the turbo fan 17 is on the first flat portion 18A, the second flat portion 18B, and the third flat portion 18C of the indoor heat exchanger 18. , P2, and P3, the current plate 32 is attached to a second predetermined position on the downstream side of the rotational direction Rd of the turbo fan 17. Therefore, it is suppressed that the speed component of the rotational direction Rd of the blowing air rises again downstream of the rotational direction Rd of the turbo fan 17 with respect to the closest position P1, P2, P3, and the blowing air collides with the fin 18b. The blowing noise generated is reduced.

The second predetermined position is a radial direction passing the closest position P1 (P2, P3) of the first flat surface portion 18A (the second flat surface portion 18B, the third flat surface portion 18C) and a radial direction passing the tip of the rectifying plate 32B. This is a position where the angle θ2 formed by と is in the range of not less than 15 degrees and not more than 20 degrees.

According to the air conditioner 1 of the present embodiment, the straightening vane 32 extends along the axes X1 and X2 parallel to the rotation shaft 16A of the turbo fan 17 and protrudes linearly toward the rotation shaft 16A. Therefore, the ventilation resistance is reduced as compared with the case where the turbo fan 17 is formed in a curved shape which is inclined in the direction opposite to the rotational direction Rd of the turbo fan 17 and bulges inward. Since the two straightening vanes 32 are disposed on the upstream side and the downstream side of the rotational direction Rd of the turbo fan 17 with the closest positions P1, P2 and P3 interposed therebetween, the closest positions P1, P2 and P3 are included. The air flow resistance is reduced compared to the case where three straightening vanes are arranged.
As described above, according to the air conditioner 1 of the present embodiment, it is possible to reduce the blowing noise generated due to the blowing wind colliding with the fins 18 b without largely increasing the ventilation resistance.

In the air conditioner 1 of the present embodiment, the turbo at the closest position P1 (P2, P3) of the first flat portion 18A (the second flat portion 18B, the third flat portion 18C) to which the straightening vane 32A and the straightening vane 32B are attached. Assuming that the distance between the fan 17 and the indoor heat exchanger 18 in the radial direction is L, and the length of the straightening plate 32A projecting toward the rotation shaft 16A is l, L / l ≧ 3.5 and l ≧ 7 mm. Fulfill.

The distance L between the turbo fan 17 and the indoor heat exchanger 18 in the radial direction is 3.5 times or more of the length l of the straightening plate 32A and the straightening plate 32B protruding toward the rotation shaft 16A. And the rise of the draft resistance by the current plate 32B can be sufficiently suppressed. By setting l to 7 mm or more, turbulent flow can be appropriately generated by the straightening vane 32A, and the velocity component of the rotational direction Rd of the blowing air at the closest position P1 (P2, P3) can be reduced.

Reference Signs List 1 air conditioner 2 outdoor unit 3 indoor unit 4 refrigerant piping 5 electric wiring 6 refrigerant compressor 7 outdoor heat exchanger 8 outdoor fan 9 control box 10 cabinet 11 ceiling panel 12 air suction port 13 bell mouth 14 drain pan 15 air passage 16 fan 16 fan Motor 16A Rotary shaft 17 Turbo fan 18 Indoor heat exchanger 18a Heat transfer tube 18b Fin 18A First flat portion 18B Second flat portion 18C Third flat portion 18D Fourth flat portion 18E Fifth flat portion 18F First curved surface portion 18G Second Curved part 18H Third curved part 18I Fourth curved part 19 Air flow passage 20 Air outlet 21 Opening 22 Air filter 23 Suction grille 24 Wire 25 Wind direction adjustment louver 26 Hub 27 Main plate 28 Fluid flow path 29 Shroud 30 Blade 31 Recirculation path 32, 32A, 32B Current plate 32a Part 32b plate portion

Claims (5)

A fan that allows air flowing in along the axial direction of the rotation axis to flow radially out of the axial direction;
A heat exchanger disposed so as to surround the outer periphery of the fan and having a heat transfer pipe and a plurality of fins attached to the heat transfer pipe;
And a plurality of straightening vanes mounted on the inner circumferential side of the heat exchanger and extending along an axis parallel to the rotation axis and linearly projecting toward the rotation axis;
The heat exchanger is
A plurality of flat portions disposed along a plane orthogonal to the radial direction at a position closest to the fan;
A plurality of curved surface portions connecting the plurality of flat surface portions;
A first straightening vane is attached to a first predetermined position on the upstream side of the rotational direction of the fan than the closest position to at least one of the plurality of flat portions, and the first straightening plate is mounted to the closest position A second straightening vane is attached to a second predetermined position on the downstream side in the rotational direction of the fan,
An air conditioner in which the first straightening vane and the second straightening vane are disposed adjacent to each other. In the first predetermined position, an angle formed by the radial direction passing through the closest position of the flat portion and the radial direction passing through the tip of the first straightening vane is in a range of 3 degrees to 7 degrees The air conditioner according to claim 1, which is a position where The first predetermined position is a position at which an angle formed by the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the first straightening plate is 5 degrees. The air conditioner according to 2. In the second predetermined position, an angle formed by the radial direction passing through the closest position of the flat surface portion and the radial direction passing through the tip of the second straightening plate is within a range of 15 degrees to 20 degrees. The air conditioner according to any one of claims 1 to 3, which is a position where The distance in the radial direction between the fan and the heat exchanger at the closest position of the flat portion to which the first straightening vane and the second straightening vane are attached is L, and the first straight straightening vane The air conditioner according to any one of claims 1 to 4, wherein L / l 3.5 3.5 and l 7 7 mm are satisfied, where l is a length projecting toward the rotation axis.

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