JP5518104B2 - Heat exchanger, indoor unit, and outdoor unit - Google Patents

Description

  The present invention relates to a heat exchanger, and an indoor unit and an outdoor unit equipped with the heat exchanger.

  In the prior art, a device that provides a ceiling-mounted air conditioner that can accommodate both a ceiling-embedded type and a ceiling-suspended type has been proposed. As its configuration, an air conditioner that can be installed on the ceiling of an air-conditioning room, comprising a substantially rectangular box-shaped casing in which an inlet and an outlet are formed, and a turbofan whose rotation axis extends in the vertical direction A fan and four heat exchangers arranged so as to surround the outer peripheral portion of the blower fan in a plan view of the casing are provided. In this air conditioner, a blower fan composed of a turbofan whose rotation axis extends in the vertical direction is disposed in the casing, and the four heat exchangers are disposed so as to surround the outer peripheral portion of the blower fan in a plan view of the casing. Therefore, it is possible to reduce the size of the casing in the height direction. Thereby, in respond | corresponding to both the form of a ceiling embedding type and the form of a ceiling suspension type | mold, the common use of the components accommodated in a casing and a casing can be aimed at (for example, refer patent document 1).

JP 2007-147144 A (Claim 3, FIG. 25)

In the conventional technique, when a flat tube is mounted on a four-way cassette, the heat exchanger is provided with four heat exchangers arranged so as to surround the outer peripheral portion of the blower fan. In this case, the end of the heat exchanger fits in the corner, but in actual specifications, a bypass metal plate or spacer is required to prevent wind bypass from the joint of the heat exchanger. There was a problem of high costs.
In addition, when the heat exchanger is configured as an integral type, wrinkles occur on the inner fin due to the difference between the inner and outer circumferences when the corner is bent, or the outer fin is peeled off from the flat tube and the heat transfer area There is a problem that the performance is remarkably deteriorated due to a decrease in the number of particles.

  The present invention has been made in order to solve the above-described problems, and is a heat exchanger that can suppress the separation of fins due to fin deformation when the heat exchanger is bent, and can suppress performance degradation. And an indoor unit and an outdoor unit equipped with the same.

The heat exchanger according to the present invention includes a plurality of flat tubes arranged in parallel at intervals, a pair of headers respectively connecting both ends of the plurality of flat tubes, and a joint between the adjacent flat tubes is provided with a fin, a heat exchanger in which at least one portion is bent is machined in the longitudinal direction of the pair of header, the fins, the trailing edge of the tensile by pre Symbol bending deformation, the bending those which are collision Kiga formed chevron shape to absorb the amount of deformation due to tensile deformation of the fins as they are.

  Since the present invention has formed a chevron-shaped projection or notch that absorbs the amount of deformation of the fin when bent, it suppresses the separation of the fin accompanying the deformation of the fin when bending the heat exchanger. The decrease can be suppressed.

It is a figure which shows the state after the bending process of the heat exchanger which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view of the four-way cassette type indoor unit according to Embodiment 1 of the present invention. It is a figure which shows the deformation | transformation process of the bending process of the heat exchanger which concerns on Embodiment 1 of this invention. It is a figure which shows the rib and deformation | transformation state of the front edge of the fin which concerns on Embodiment 1 of this invention, or a rear edge. It is a figure explaining each part dimension of the rib which concerns on Embodiment 1 of this invention. It is a figure which shows the notch or corrugated fin which concerns on Embodiment 1 of this invention. It is a general-view figure of the top flow type outdoor unit which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
FIG. 1 is a diagram showing a state after bending of the heat exchanger according to Embodiment 1 of the present invention.
In FIG. 1, the heat exchanger 100 in the present embodiment includes a flat tube 1, fins 2, a liquid header 3, a gas header 4, a liquid inlet 5, and a gas outlet 6.
The heat exchanger 100 is mounted on, for example, an indoor unit or an outdoor unit of an air conditioner, and exchanges heat between air passing through the heat exchanger 100 and refrigerant circulating in the flat tube 1. Details of the indoor unit and the outdoor unit will be described later.

A plurality of the flat tubes 1 are arranged in parallel at intervals such that the longitudinal direction is the vertical direction (gravity direction). Between adjacent flat tubes 1, fins 2 (corrugated fins) processed into a corrugated shape made of, for example, aluminum are brazed and joined. The liquid header 3 is arranged in a horizontal direction, and a plurality of holes are formed at substantially equal intervals on a side surface in the longitudinal direction, and one end of the flat tube 1 is connected to the liquid header 3. In addition, a liquid inlet 5 through which refrigerant flows during cooling operation is provided on one side of the liquid header 3, and the other side is closed. The gas header 4 is arranged in the horizontal direction so as to face the liquid header 3, and a plurality of holes are formed at substantially equal intervals on the side surface in the longitudinal direction, and one end of the flat tube 1 is connected thereto. . A gas outlet 6 through which refrigerant flows out during cooling operation is provided on one side of the gas header 4 and the other side is closed.
In addition, although the corrugated fin is shown here as the fin 2, the present invention is not limited to this, and a plate fin configuration in which the flat tube 1 is inserted into the laminated plate-like fins, or the fin leading edge side is cut into a flat tube shape. Alternatively, a plate fin configuration in which a pipe is inserted from the lateral direction may be used.

  The liquid header 3 and the gas header 4 correspond to “a pair of headers” in the present invention.

Next, the indoor unit 200 equipped with the heat exchanger 100 will be described.
In this embodiment, a ceiling-embedded four-way cassette type indoor unit will be described as an example, but the present invention is not limited to this.

FIG. 2 is a longitudinal sectional view of the four-way cassette type indoor unit according to Embodiment 1 of the present invention.
As shown in FIG. 2, the four-way cassette type indoor unit 200 is installed in a direction in which the top is a top plate 210 a with respect to a room 217. A side plate 210b is attached around the top plate 210a, and the casing 210 is installed so as to open toward the room 217. Below the indoor unit 200, a substantially rectangular decorative panel 211 in a plan view is attached and faces the room 217. In the vicinity of the center of the decorative panel 211, there are provided a suction grill 211a serving as a suction port for air into the indoor unit 200, and a filter 212 for removing dust after passing through the suction grill 211a. In addition, on each side of the decorative panel 211, a panel outlet 211b serving as an air outlet is formed along each side of the decorative panel 211. Each panel outlet 211b includes a wind vane 213.

Further, inside the indoor unit 200, a turbo fan 201 that is a centrifugal blower having a rotation shaft arranged in a vertical direction, a bell mouth 214 that forms a suction air passage of the turbo fan 201, and the turbo fan 201 are driven to rotate. The fan motor 215 that heats up and the heat exchanger 100 that stands up to surround the downstream side of the turbo fan 201 are provided. The heat exchanger 100 is a parallel flow type heat exchanger in which the flat tubes 1 are arranged in the vertical direction as described above, and is connected to an outdoor unit (not shown) through a connection pipe to circulate refrigerant. Further, the heat exchanger 100 is formed in a substantially square shape so as to surround the turbofan 201 (see FIG. 1).
In addition, a unit suction port 210c is provided at the center of the lower surface of the indoor unit 200, and a unit air outlet 210d is provided around the unit suction port 210c. And the suction grille 211a, the unit suction inlet 210c, the unit blower outlet 210d, and the panel blower outlet 211b are connected.
In the above description, the case where the turbo fan 201 is used as the centrifugal blower has been described. However, the present invention is not limited to this. For example, a sirocco fan or a radial fan may be used.

The “unit suction port 210c” corresponds to the “suction port” in the present invention.
The “unit outlet 210d” corresponds to the “outlet” in the present invention.

As described above, the heat exchanger 100 according to the present embodiment is formed in a substantially square shape by bending three portions in the longitudinal direction (direction in which the header extends) to approximately 90 °.
Next, the bending process and the deformation of the fin 2 will be described.

FIG. 3 is a diagram showing a deformation process of the bending process of the heat exchanger according to Embodiment 1 of the present invention. Fig.3 (a) shows the heat exchanger 100 before a bending process, and FIG.3 (b) has shown the heat exchanger 100 after bending one place.
As shown in FIG. 3 (a), the bending of the heat exchanger 100 is performed by bending the white arrow portion upward while holding the upper black arrow portion with a jig or the like to perform L bending. Thereby, the bending shape shown in FIG. In the four-way cassette type indoor unit 200 on which the heat exchanger 100 according to the present embodiment is mounted, such a bending process is performed at three places to form a square shape that matches the unit form.
In such a bending process, the front edge (inner peripheral side) of the fin 2 that undergoes compressive deformation shrinks and the wall thickness increases, wrinkles approach, or the rear edge (outer peripheral side) of the fin 2 that undergoes tensile deformation extends to increase the thickness. The thickness becomes thinner. For this reason, the fin 2 may be peeled off or cut off from the flat tube 1. The heat exchanger 100 according to the present embodiment forms a chevron-shaped protrusion or notch in the fin 2 to absorb such a deformation amount of the fin.

FIG. 4 is a diagram showing a rib on the front edge or the rear edge of the fin according to Embodiment 1 of the present invention and a deformed state. 4A is a perspective view, and FIG. 4B is a top view.
As shown in FIGS. 4 (a) and 4 (b), the flat portion of the fin 2 is provided with a plurality of slits 13 formed by cutting and raising to promote heat transfer. Note that the slit 13 may be omitted.
In addition, the fin 2 in the present embodiment has a chevron shape that absorbs the deformation amount of the fin 2 when bent at the front edge that is compressively deformed by bending and the rear edge that is tensile deformed by bending. Ribs 14 (protrusions) are provided. By providing the rib 14, even when the heat exchanger 100 is bent as shown by the solid line arrow in FIG. 4B, the deformation amount of the fin 2 is absorbed by the rib 14, and the fin 2 from the flat tube 1 is absorbed. Peeling can be suppressed.

  In this embodiment, the case where the ribs 14 are provided on the front edge and the rear edge will be described. However, the present invention is not limited to this, and the front edge that is compressively deformed by bending and the tension by bending. The rib 14 may be provided on at least one of the rear edges to be deformed.

Here, details of the rib 14 will be described with reference to FIG.
FIG. 5 is a diagram for explaining dimensions of each part of the rib according to the first embodiment of the present invention.
5A shows a top view, FIG. 5B shows the AA cross section of FIG. 5A, and FIG. 5C shows the cross section of the bent portion of the fin 2. FIG.
The dimension of each part of the rib 14 is determined in consideration of the shrinkage of the front edge of the fin 2 and the extension of the rear edge depending on the bending radius of the heat exchanger 100. As for the stretched portion, the thickness of the fin 2 is small.
For example, as shown in FIG. 5A, the rib 14 is formed in an isosceles triangle shape with the front edge or the rear edge of the fin 2 as a base in a plan view.
Further, as shown in FIG. 5C, the step pitch that is the arrangement interval of the flat tubes 1 is Dp, the radius of curvature of the front edge (fin inner peripheral side) of the fin 2 that is compressed and deformed by bending is R1, and bending is performed. Let R2 be the radius of curvature of the rear edge (fin outer periphery side) of the fin 2 that undergoes tensile deformation.
At this time, the extension length of the fin 2 at the position of the outermost periphery R2 with respect to the intermediate position (= (R1 + R2) / 2) between the radii R1 and R2 without bending is as follows: It is expressed as equation (1).
π (2 × R2− (R1 + R2)) = π (R2−R1) (1)
In addition, the number N of the entire circumference of the heat transfer tubes at the intermediate position in the radial direction is expressed by Expression (2).
N = π (R1 + R2) / Dp (2)
Therefore, the length of extension of the trailing edge between the step pitches is expressed by Expression (3).
π (R2-R1) / N = (R2-R1) / (R2 + R1) × Dp (3)

Further, if the length of the isosceles side of the rib 14 is r, and the angle of the apex angle after the bending process is θ, the outermost peripheral length of the rib 14 (the length of the bottom side after the bending process) is expressed by the equation (4). It can be written as
2 × r × sin (θ / 2) (4)

And the rib 14 formed in the fin 2 which deform | transforms when bending is carried out, as shown to Formula (5), the base length at the time of expand | deploying the rib 14 until it becomes zero height is between step pitches. If it is larger than the extended length of the outermost peripheral fin, the crack of the fin 2 and the peeling from the flat tube 1 due to the influence of stress accompanying the bending of the fin 2 can be absorbed.
2 * r * sin ([theta] / 2)> (R2-R1) / (R2 + R1) * Dp (5)
Here, the unit of length in the formulas (1) to (5) is, for example, “m”.

  A plurality of such ribs 14 may be formed between the adjacent flat tubes 1. It is desirable that the smaller the bending radius, the larger the number.

In the above example, the shape of the rib 14 is defined by the length r of the isosceles side and the opening angle θ after bending, but can also be defined by the height H of the rib 14. That is, as shown in FIG. 5B, the rib 14 is formed in a triangular shape with the front edge or the rear edge as the bottom in a side view, and when the height of the triangle is H, the rib 14 is If the base length when expanded to zero satisfies Equation (6), it is possible to absorb fin cracks and peeling from the flat tube due to the stress effect associated with the bending of the fins 2.
H> (R2-R1) / (R2 + R1) × Dp (6)

  Actually, a rib shape that satisfies at least one of the equations (5) and (6) is selected.

  In the above description, the case where the chevron-shaped rib 14 that absorbs the deformation amount of the fin 2 is provided has been described, but the notch 15 may be provided. For example, as shown in FIG. 6A, when the heat exchanger 100 is bent, the notches 15 are provided so that the front edges of the fins 2 overlap each other and the rear edges of the fins 2 open to the left and right. A plurality of such cutouts 15 may be formed between adjacent flat tubes 1 when the bending radius is small.

Furthermore, when using the corrugated fin which does not provide the slit 13 as the fin 2, it is good also as a structure which uses the corrugated fin 16 which made the corrugated fin itself corrugated.
For example, as shown in FIG. 6B, a wave shape that is continuous from a leading edge that is compressively deformed by bending to a trailing edge that is tensilely deformed by bending and absorbs the deformation amount of the fin 2 when bent. Protrusions are formed. Also in such a corrugated corrugated fin 16, a plurality of corrugations may be formed between adjacent flat tubes 1 when the bending radius is small.
Further, in this corrugated corrugated fin 16, when the amplitude of the corrugated shape is set to the height H and the corrugated shape (for example, a sine wave shape) is approximated by a triangular shape, the equation (6) is satisfied as described above. If the corrugated shape is adopted, it is possible to absorb fin cracks and peeling from the flat tube due to the stress caused by the bending of the corrugated corrugated fins 16.

By the way, in the conventional circular pipe heat exchanger mounted on the four-way cassette type, the circular pipes are arranged in the horizontal direction, and it is difficult to increase the number of refrigerant branches due to the restriction on the unit height. That is, when the number of branches of the refrigerant is increased to more than the number of stages, a refrigerant take-out pipe is required in the middle of the heat exchanger in the longitudinal direction, and the longitudinal direction of the heat exchanger is shortened.
In the present embodiment, the longitudinal direction of the flat tube 1 is installed in the gravitational direction (vertical direction), and the parallel flow configuration in which the number of refrigerant branches can be increased, so that the pressure loss of the refrigerant can be kept low, particularly HFO-1234yf. When using a low-pressure refrigerant such as, high-performance air conditioners (indoor units and outdoor units) can be obtained. In addition, since the fins 2 are arranged in the horizontal direction, the ventilation resistance of the heat exchanger 100 is suppressed, and the swirling component of the blown air speed of the turbofan 7 collides with the surface of the fins 2 of the heat exchanger 100. Collision loss (wind path loss) can be reduced, and an air conditioner with a large air volume and low noise can be obtained.

As described above, in the present embodiment, the fin 2 is deformed when the fin 2 is bent into at least one of the leading edge that is compressively deformed by bending and the trailing edge that is tensilely deformed by bending. A chevron-shaped rib 14 or notch 15 is formed to absorb the amount. In addition, a corrugated corrugated fin 16 having a corrugated shape that absorbs deformation when bent is provided.
For this reason, the expansion | swelling and shrinkage | contraction of the front edge (inner peripheral side) and rear edge (outer peripheral side) fin 2 which arise when bending the heat exchanger 100 are absorbed, and peeling of the fin 2 from the flat tube 1 is absorbed. It is possible to suppress the degradation of performance even when bending is performed. Therefore, the high-performance indoor unit 200 can be provided.
Further, since the fins do not peel off, reliability such as corrosion and dust clogging is improved.

Further, in the present embodiment, the heat exchanger 100 is arranged between the turbo fan 201 of the indoor unit 200 and the unit outlet 210d so that the longitudinal direction of the flat tube 1 is the vertical direction.
For this reason, the fins 2 of the heat exchanger 100 are arranged in the horizontal direction, reducing the collision loss (ventilation resistance) on the fin surface of the swirling flow blown out from the turbo fan 201, and obtaining the effect of large air volume and low noise. It is done. Furthermore, since the number of refrigerant branches can be increased to more than the number of stages and the pressure loss of the refrigerant can be kept low, the high-performance indoor unit 200 can be provided.

Embodiment 2. FIG.
In the present embodiment, a mode in which the above-described heat exchanger 100 is mounted on the outdoor unit 300 will be described.
In this embodiment, a top flow type outdoor unit will be described as an example, but the present invention is not limited to this.

FIG. 7 is an overview of a top flow type outdoor unit according to Embodiment 2. FIG.
As shown in FIG. 7, the top flow type outdoor unit 300 includes a box-shaped housing 310, a unit suction port 308 formed by an opening on the side surface of the housing 310, and the unit suction port 308. In this way, the heat exchanger 100 arranged in the housing 310, a unit air outlet 309 formed by the opening on the top surface of the housing 310, and a fan provided so as to allow ventilation to cover the unit air outlet 309 A guard 311 and a propeller fan 312 installed inside the fan guard 311 are provided. The heat exchanger 100 is a parallel flow type heat exchanger in which the flat tubes 1 are arranged in the vertical direction as in the first embodiment. The heat exchanger 100 is connected to an indoor unit (not shown) through a connection pipe so that refrigerant is circulated. The
This outdoor unit 300 is used, for example, in a multi-building outdoor unit for buildings, and is installed on the roof of a building.
In addition, the side surface of the housing 310 forming the unit suction port 308 may be any of two, three, and four surfaces. Further, the heat exchanger 100 is appropriately arranged according to the side surface on which the unit suction port 308 is formed. For example, when the unit suction port 308 is formed on three surfaces, the heat exchanger 100 is formed in a substantially U shape by bending two portions in the longitudinal direction (direction in which the header extends) at approximately 90 °.

The “unit suction port 308” corresponds to the “suction port” in the present invention.
The “unit outlet 309” corresponds to the “air outlet” in the present invention.
Further, the “propeller fan 312” corresponds to the “blower” in the present invention.

  When the propeller fan 312 is rotated by the outdoor unit 300 configured as described above, air is sucked from the unit suction port 308 on the side surface of the casing 310 and passes through the heat exchanger 100 to become a vertical flow. The air is blown upward from a unit air outlet 309 formed at the top of the body 310. In such a top flow type configuration, the air volume at a portion close to the propeller fan 312 increases, and as a result, a wind speed (air volume) distribution is generated in the height direction of the heat exchanger 100.

In the conventional circular pipe heat exchanger, since the circular pipes are arranged in the horizontal direction, the heat exchange amount is nonuniform between the upper refrigerant path and the lower refrigerant path of the heat exchanger. For this reason, the refrigerant | coolant of an upper path exit will be in an overheated state, for example at the time of heating operation, and the non-uniform distribution which the refrigerant | coolant of a lower path exit will be in a gas-liquid two-phase state will arise.
On the other hand, since the outdoor unit 300 in the present embodiment has a parallel flow configuration in which the heat exchanger 100 is arranged in the vertical direction in the longitudinal direction of the flat tube 1, it is possible to prevent uneven distribution between refrigerant paths. In addition, since uneven distribution can be prevented, the number of refrigerant branches (number of passes) can be significantly increased as compared with the case where the flat tubes 1 are arranged in the horizontal direction. Therefore, the pressure loss of the refrigerant flowing through the heat exchanger 100 can be kept low, and a high-performance air conditioner can be obtained.

  As described above, also in the present embodiment, the expansion and contraction of the fins 2 at the front edge (inner peripheral side) and the rear edge (outer peripheral side) that occur when the heat exchanger 100 is bent are absorbed, and the flat tube Separation of the fins 2 from 1 can be suppressed, and even when bending is performed, deterioration in performance can be suppressed. Therefore, the high performance outdoor unit 300 can be provided. Further, since the fins do not peel off, reliability such as corrosion and dust clogging is improved.

  DESCRIPTION OF SYMBOLS 1 Flat tube, 2 fin, 3 liquid header, 4 gas header, 5 liquid inlet, 6 gas outlet, 7 turbofan, 13 slit, 14 rib, 15 notch, 16 wave type corrugated fin, 100 heat exchanger, 200 indoor unit , 201 turbo fan, 210 housing, 210a top plate, 210b side plate, 210c unit inlet, 210d unit outlet, 211 decorative panel, 211a inlet grille, 211b panel outlet, 212 filter, 213 wind direction vane, 214 bellmouth, 215 Fan motor, 217 rooms, 300 outdoor units, 308 unit inlet, 309 unit outlet, 310 housing, 311 fan guard, 312 propeller fan.

Claims (10)

A plurality of flat tubes arranged in parallel at intervals;
A pair of headers respectively connecting both ends of the plurality of flat tubes;
A heat exchanger comprising a fin joined between the adjacent flat tubes, wherein at least one place in the longitudinal direction of the pair of headers is bent;
The fins, the trailing edge of the tensile by pre Symbol bending deformation, heat exchange, characterized in that the amount of deformation due to tensile deformation of the fins is collision Kiga formed chevron shape to absorb when it is the bent vessel. Between adjacent said flat tubes, the heat exchanger according to claim 1, characterized in that the impact force of the chevron shape forming a plurality. At least one place in the longitudinal direction of the pair of headers is bent at approximately 90 °,
The collision caused is,
It is formed in an isosceles triangle shape with the leading edge or the trailing edge as a base in plan view, the length of the isosceles is r, and the apex angle is θ,
A step pitch which is an arrangement interval of the flat tubes in the longitudinal direction of the pair of headers is Dp,
The radius of curvature of the leading edge of the fin that is compressed and deformed by the bending process is R1,
When the radius of curvature of the trailing edge of the fin that undergoes tensile deformation by the bending process is R2,
2 × r × sin (θ / 2)> (R2−R1) / (R2 + R1) × Dp
The heat exchanger according to claim 1 or 2, wherein the following relationship is satisfied. At least one place in the longitudinal direction of the pair of headers is bent at approximately 90 °,
The protrusion is
In a side view, it is formed in a triangular shape with the front edge or the rear edge as the base, and the height of the triangle is H,
A step pitch which is an arrangement interval of the flat tubes in the longitudinal direction of the pair of headers is Dp,
The radius of curvature of the leading edge of the fin that is compressed and deformed by the bending process is R1,
When the radius of curvature of the trailing edge of the fin that undergoes tensile deformation by the bending process is R2,
H> (R2-R1) / (R2 + R1) × Dp
The heat exchanger according to claim 1 or 2, wherein the following relationship is satisfied. A plurality of flat tubes arranged in parallel at intervals;
A pair of headers respectively connecting both ends of the plurality of flat tubes;
A heat exchanger comprising a fin joined between the adjacent flat tubes, wherein at least one place in the longitudinal direction of the pair of headers is bent;
The fin is constituted by a corrugated fin,
Edge continuously after tensile deformation by the bending from the front edge to compressive deformation by the bending, the bending when being processed, the front edge of the deformation amount and the fins by the tensile deformation of the trailing edge of the fin A heat exchanger characterized in that corrugated projections are formed to absorb deformation due to compression deformation . The heat exchanger according to claim 5, wherein a plurality of the corrugated protrusions are formed between the adjacent flat tubes. At least one place in the longitudinal direction of the pair of headers is bent at approximately 90 °,
The protrusion is
Let the amplitude of the corrugated shape be H,
A step pitch which is an arrangement interval of the flat tubes in the longitudinal direction of the pair of headers is Dp,
The radius of curvature of the leading edge of the fin that is compressed and deformed by the bending process is R1,
When the radius of curvature of the trailing edge of the fin that undergoes tensile deformation by the bending process is R2,
H> (R2-R1) / (R2 + R1) × Dp
The heat exchanger according to claim 5 or 6, wherein the following relationship is satisfied. A housing having an inlet and an outlet;
A centrifugal blower that is provided at a substantially central portion of the housing, sucks air from the suction port, and blows out the air radially;
The heat exchanger according to any one of claims 1 to 7, wherein the heat exchanger is disposed between the centrifugal blower and the outlet so that a longitudinal direction of the flat tube is a vertical direction. An indoor unit characterized by that. The indoor unit according to claim 8, wherein the heat exchanger is formed in a substantially square shape and is installed so as to surround the centrifugal blower. A housing having a suction port on the side surface and a blower outlet on the upper surface;
The heat exchanger according to any one of claims 1 to 7, which is disposed in the casing so as to be along the suction port so that a longitudinal direction of the flat tube is a vertical direction.
An outdoor unit that is disposed at an upper part of the casing, and includes a blower that sucks air from the suction port and blows out the air that has passed through the heat exchanger from the blower outlet.

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