CN220871003U - Indoor heat exchanger - Google Patents

Abstract

The present disclosure provides an indoor heat exchanger having a dead water area reduction structure having versatility. The indoor heat exchanger (41) is provided with a plurality of fins (50) arranged in layers at a prescribed fin pitch, and a plurality of heat transfer tubes (60) penetrating the fins (50) and having an outer diameter of greater than 5.3 mm. In the indoor heat exchanger (41), a deflection part (53) with a top part having a height of more than 15% of a fin pitch is arranged between a first through hole (51) and a second through hole (52) which are adjacent to each other in the length direction of the fin (50), thereby generating turbulence on the air flow on the fin (50), so that dead water area behind the heat transfer tube (60) is reduced, and air supply noise is suppressed.

Description

Indoor heat exchanger

Technical Field

The present utility model relates to an indoor heat exchanger.

Background

Behind the heat transfer tubes in the air flow of the heat exchanger, a region where the movement of air is inactive, i.e., a dead water region, is created. If the dead water area increases, the air supply noise increases, and therefore, it is necessary to suppress the increase of the dead water area and reduce the noise.

Patent document 1 (japanese patent application laid-open No. 2008-180168) discloses a heat exchanger that suppresses growth of a dead water area. In this heat exchanger, the fins are corrugated, and the fin members are arranged so that the angle between the streamline of air and the wave is in the range of 10 ° to 60 °, whereby the air is caused to flow in the dead water area.

However, patent document 1 does not study a heat exchanger in which fins are not corrugated, and has a limited range of applications as a structure for reducing dead water area (hereinafter referred to as a dead water area reduction structure). Accordingly, there is a problem in providing a heat exchanger having a general dead water area reduction structure.

Patent document 1: japanese patent laid-open No. 2008-180496

Disclosure of utility model

The indoor heat exchanger of the first aspect is an indoor heat exchanger disposed upstream of a fan in a path of an air flow from a suction port to a blowout port of an air conditioning indoor unit, and includes fins and a heat transfer tube. The fins are arranged in layers at predetermined fin pitches. The heat transfer pipe penetrates through the fins and has an outer diameter greater than 5.3mm. In addition, the fin has a first hole, a second hole, and a flexure. The second hole is adjacent to the first hole in the length direction of the fin. The flexing portion flexes uniformly between the first aperture and the second aperture. The height of the top of the flexure is 15% or more of the fin pitch.

In this indoor heat exchanger, since the flexing portion is provided between the first hole and the second hole adjacent thereto in the longitudinal direction of the fin, and the flexing portion is 15% or more of the fin pitch, turbulence is generated in the air flow on the fin, and therefore, dead water behind the heat transfer tube is reduced, and blowing noise is suppressed.

Therefore, the heat exchanger in which the fins are not corrugated can be applied as a dead water area reduction structure.

The indoor heat exchanger of the second aspect is the indoor heat exchanger of the first aspect, wherein the fins further have cut-and-raised portions and slits. The cut-and-raised portion is formed by cutting up the fin in the plate thickness direction. The slit is generated by forming a cut-up portion. The height of the top of the flexure is 50% or less of the height of the cut-up.

In this indoor heat exchanger, if the deflection portion is too high, wind does not blow to the cut-and-raised portion, and therefore, by setting the dimension to 50% or less of the height of the cut-and-raised portion, wind blows to the cut-and-raised portion.

The indoor heat exchanger according to the third aspect is the indoor heat exchanger according to the second aspect, wherein the top of the bent portion and the top of the cut-and-raised portion do not overlap when the fin is viewed from a direction orthogonal to both the plate thickness direction and the longitudinal direction of the fin.

In this indoor heat exchanger, when the bent portion and the cut-up portion overlap, wind does not blow onto the cut-up portion, and therefore, by making the bent portion and the cut-up portion non-overlapping, wind blows onto the cut-up portion.

The indoor heat exchanger according to a fourth aspect is the indoor heat exchanger according to any one of the first to third aspects, wherein the height of the top of the bent portion is 30% or less of the fin pitch.

In this indoor heat exchanger, if the flexure portion is too high, wind does not blow to the cut-up portion, and therefore, by setting the height of the top portion of the flexure portion to a size of 30% or less of the fin pitch, wind blows to the cut-up portion.

The indoor heat exchanger according to a fifth aspect is the indoor heat exchanger according to any one of the first to fourth aspects, wherein the bent portion is formed by tube expansion processing for expanding the diameter of the heat transfer tube to bring the heat transfer tube into close contact with the fins. In this indoor heat exchanger, the expansion pipe and the formation of the bent portion can be performed simultaneously.

The indoor heat exchanger according to a sixth aspect is the indoor heat exchanger according to any one of the first to fifth aspects, wherein the shortest distance between the fins and the fan is in a range of 15mm to 30 mm. In this indoor heat exchanger, the dead water does not reach the fan, and thus noise is suppressed.

An indoor heat exchanger pertaining to a seventh aspect is the indoor heat exchanger pertaining to any one of the first aspect to the sixth aspect, wherein the bent portions are formed in fins close to the fan among the fins arranged in layers. In this indoor heat exchanger, the bending portion is formed at a position closest to the fan, whereby the growth of the dead water area is suppressed.

An indoor heat exchanger according to an eighth aspect is the indoor heat exchanger according to the second aspect, wherein a part of the cutout is located in a space on the back surface side of the heat transfer pipe in the air flow. In this indoor heat exchanger, wind is guided to the back surface side of the heat transfer pipe in the air flow, and the growth of dead water area is suppressed.

Drawings

Fig. 1 is a schematic configuration diagram of an air conditioner including an indoor heat exchanger according to an embodiment of the present disclosure.

Fig. 2 is a sectional view of the indoor unit.

Fig. 3 is an explanatory diagram of the arrangement of the cut-up portions of the fins.

Fig. 4 is a cross-sectional view A-A of fig. 3.

Fig. 5 is a B-B cross-sectional view of fig. 3.

Fig. 6 is an explanatory diagram showing a process of forming the flexure.

Fig. 7 is a graph showing a relationship between a compression ratio and a deflection.

Fig. 8 is a graph showing the relationship between the deflection and the dead water area length according to the pipe outer diameter.

Fig. 9 is a partial plan view of a fin according to a modification.

Description of the reference numerals

4 Indoor unit (indoor unit of air-conditioner)

41 Indoor heat exchanger

42 Indoor fan (Fan)

45F air outlet

50 Fin

51 First through hole (first hole)

52 Second through hole (second hole)

53 Flexure

54 Cut-up portion

55 Gap

60 Heat transfer tube

541 First cutting and starting part (cutting and starting part)

542 Second cut-and-raised portion (cut-and-raised portion)

543 Third cutting and starting part (cutting and starting part)

544 Fourth cutting and starting part (cutting and starting part)

545 Fifth cutting and starting part (cutting and starting part)

552 Second slit (slit)

553 Third gap (gap)

Detailed Description

(1) Schematic structure of air conditioner 1

Fig. 1 is a schematic configuration diagram of an air conditioner 1 including an indoor heat exchanger 41 according to an embodiment of the present disclosure. In fig. 1, an air conditioner 1 is connected to an outdoor unit 2 as a heat source side device and an indoor unit 4 as a use side device through refrigerant pipes, and air-conditioning a space in which the indoor unit 4 is disposed.

The air conditioner 1 includes a refrigerant circuit 10, various sensors, and a control unit 70. The refrigerant circuit 10 is configured by connecting a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an outdoor expansion valve 24, an indoor heat exchanger 41, and a gas-liquid separator 25 in this order.

The compressor 21, the four-way switching valve 22, the outdoor heat exchanger 23, the outdoor expansion valve 24, the gas-liquid separator 25, and the outdoor fan 26 are housed in the outdoor unit 2. The indoor heat exchanger 41 and the indoor fan 42 are housed in the indoor unit 4.

The four-way switching valve 22 can switch between a cooling operation cycle and a heating operation cycle. In fig. 1, the connection state during the cooling operation is shown by a solid line, and the connection state during the heating operation is shown by a broken line.

During the cooling operation, the indoor heat exchanger 41 functions as an evaporator, and the outdoor heat exchanger 23 functions as a condenser. During the heating operation, the indoor heat exchanger 41 functions as a condenser, and the outdoor heat exchanger 23 functions as an evaporator.

An indoor temperature sensor 43 is provided in the indoor unit 4. The indoor temperature sensor 43 is disposed on the side of the intake port of the indoor air, and detects the temperature (indoor temperature) of the indoor unit 4 before the indoor unit is taken in from the room and passed through the indoor heat exchanger 41.

The control unit 70 includes an outdoor control unit 72, an indoor control unit 74, a remote control 71, and a communication line 70a connecting them.

The outdoor control unit 72 controls devices disposed in the outdoor unit 2. The indoor control unit 74 controls devices disposed in the indoor unit 4. The remote controller 71 receives various setting inputs from a user and performs various display outputs.

(2) Schematic structure of indoor unit 4

Fig. 2 is a sectional view of the indoor unit 4. Unless otherwise specified, the explanation will be made with the front side being left as viewed from the front of fig. 2, the back side being right, the top side being top side, the front side being right, and the deep side being left.

The indoor unit 4 has a casing 45, an indoor heat exchanger 41, an indoor fan 42, a horizontal barrier 17, and a vertical barrier 18.

(2-1) Outer casing 45

The casing 45 houses the indoor heat exchanger 41 and the indoor fan 42 therein. The housing 45 has a front grill 45a, a top panel 45b, a back panel 45c, a blowout flow path upper panel 45d, and a blowout flow path lower panel 45e.

The front grill 45a is provided with an opening so that the indoor air is taken in from the front side of the casing 45 to the inside by being driven by the indoor fan 42. Similarly, an opening is provided in the top panel 45b so that the indoor air is taken in from the top surface side of the casing 45 to the inside by driving the indoor fan 42.

The back plate 45c covers the back side of the indoor heat exchanger 41 and the indoor fan 42 and the back side of the blowout flow path lower plate 45 e. The blowout flow path upper panel 45d extends further toward the front lower side from the vicinity of the front lower side of the indoor fan 42, and constitutes the upper surface of the blowout flow path.

The blowout flow path lower panel 45e extends downward from the vicinity of the back surface of the indoor fan 42 toward the back surface side, and then extends downward toward the front surface side, thereby forming the lower surface of the blowout flow path.

(2-2) Horizontal baffle 17

The horizontal baffle 17 can cover the air outlet 45f as the downstream end of the air outlet flow path. The horizontal baffle 17 opens the air outlet 45f during operation and adjusts the inclination angle, whereby the air-conditioning air outlet height direction can be adjusted.

(2-3) Vertical baffle 18

The vertical baffle 18 is provided upstream of the horizontal baffle 17 in the air flow path. In operation, the vertical damper 18 is angularly adjusted about an axis in a direction substantially perpendicular to the blowing direction, whereby the blowing direction of the conditioned air in the left-right direction can be adjusted.

(2-4) Indoor fan 42

The indoor fan 42 is a cross flow fan. The indoor fan 42 is rotationally driven to generate an air flow toward the indoor heat exchanger 41 via the front grill 45a, an air flow toward the indoor heat exchanger 41 via the top panel 45b, and an air flow that is sent from the air outlet 45f to the room via an air outlet channel surrounded by the air outlet channel upper panel 45d and the air outlet channel lower panel 45 e.

(2-5) Indoor Heat exchanger 41

The indoor heat exchanger 41 is arranged in an inverted V shape with both ends bent downward in side view.

The indoor heat exchanger 41 is a fin-and-tube heat exchanger, and includes a fin group 5 in which a plurality of thin fins 50 are arranged at predetermined intervals in the plate thickness direction, and a plurality of heat transfer tubes 60 penetrating the fins 50 of the fin group 5.

The indoor heat exchanger 41 is constituted by a first heat exchange portion 41a on the front side and a second heat exchange portion 41b on the rear side.

(3) Structure of fin 50 of indoor heat exchanger 41

Fig. 3 is an explanatory diagram of the arrangement of the cut-up portions 54 of the fins 50. Here, the fin 50 of the indoor heat exchanger 41, particularly the first heat exchange portion 41a, will be described as an example with reference to fig. 3. The second heat exchanging portion 41b is identical to the first heat exchanging portion 41a except for its outline and its inclined posture.

The fins 50 of the first heat exchange portion 41a have clip portions 56 penetrating the heat transfer pipe 60 in the plate thickness direction and first to fifth cut-and-raised portions (541 to 545). The fin portions of the fin 50 having the collar portion 56 and the first to fifth cut-and-raised portions (541 to 545) are arranged in two rows in the direction of the air flow F.

Of the two rows of fin portions, the upstream side fin portion in the air flow F is the first fin portion 50a, and the downstream side fin portion is the second fin portion 50b. The first fin portion 50a and the second fin portion 50b are integrally molded, but a plurality of linear holes 57 for suppressing heat conduction are provided at the boundaries of both.

(3-1) The clip portion 56

As shown in fig. 3, the clip portion 56 is a cylindrical protruding portion that protrudes in the plate thickness direction from the peripheral edges of the first through hole 51 and the second through hole 52 through which the heat transfer tube 60 passes. The clip portions 56 are arranged at predetermined intervals in the longitudinal direction of the fin 50. The clip portions 56 of the second fin portions 50b are offset by 1/2 of the predetermined interval in the longitudinal direction from the first fin portions 50 a. The predetermined interval here refers to the distance between the centers of the first through-holes 51 and the second through-holes 52.

(3-2) Cut-and-raised portion 54

The cut-and-raised portion 54 is formed by cutting up the fin 50 in the plate thickness direction. As the cut-and-raised portions 54, first to fifth cut-and-raised portions (541 to 545) are formed between the clip portions 56 adjacent in the longitudinal direction of the fin 50.

(3-2-1) First to fifth cut-and-raised portions (541 to 545) of the first fin portion 50a

The first to fifth cut-and-raised portions (541 to 545) in the first fin portion 50a are arranged in the order of the first cut-and-raised portion 541, the second cut-and-raised portion 542, and the third cut-and-raised portion 543 from the upstream side in the direction of the air flow F.

The fourth and fifth cut-and-raised portions 544 and 545 are located downstream of the third cut-and-raised portion 543 in a state of being adjacent along the longitudinal direction of the first fin portion 50 a.

However, the number and positions of the cut-up portions of the first fin portion 50a are not limited to the above configuration, and may be set according to the configuration of the fin 50.

(3-2-2) First to fifth cut-and-raised portions (541 to 545) of the second fin portion 50b

The first to fifth cut-and-raised portions (541 to 545) in the second fin portion 50b are arranged in the order of the first cut-and-raised portion 541, the second cut-and-raised portion 542, and the third cut-and-raised portion 543 from the downstream side in the direction of the air flow F.

The fourth and fifth cut-and-raised portions 544 and 545 are located upstream of the third cut-and-raised portion 543 in a state of being adjacent along the longitudinal direction of the second fin portion 50 b.

However, the number and positions of the cut-and-raised portions of the second fin portion 50b are not limited to the above configuration, and may be set according to the configuration of the fin 50.

The clip portions 56 of the second fin portion 50b are offset by 1/2 of the predetermined interval in the longitudinal direction from the first fin portion 50a, and in this relationship, the first to fifth cut-and-raised portions 541 to 545 are also offset by 1/2 of the predetermined interval in the longitudinal direction of the second fin portion 50b from the first fin portion 50 a. The predetermined interval here refers to the distance between the centers of the first through-holes 51 and the second through-holes 52.

(3-3) Gap 55

By forming the cut-and-raised portion 54, a gap through which air can pass can be formed between the surface without the cut-and-raised portion 54 and the cut-and-raised portion 54 (see fig. 4). This gap is referred to as a gap 55. In the art, the cut-and-raised portion 54 and the gap are sometimes referred to as a slit, but here, only the gap is referred to as a slit 55.

For convenience of explanation, for example, the slit 55 formed by forming the second raised portion 542 is denoted as a second slit 552, and the slit 55 formed by forming the third raised portion 543 is denoted as a third slit 553.

(3-4) Flexure 53

Fig. 4 is a cross-sectional view A-A of fig. 3. Further, fig. 5 is a B-B sectional view of fig. 3. In fig. 4, the flexure 53 is a portion that protrudes in an arc shape between the clip portions 56.

The flexure 53 is formed in a region between the yoke portions 56 where the first to fifth cut-and-raised portions (541 to 545) are absent.

The purpose of the flexure 53 is to reduce dead water behind the heat transfer tube 60 by varying the trajectory of the air flowing over the fins 50 at the flexure 53 and causing turbulence in the air flow.

Specifically, as shown in fig. 5, the air flow F becomes a trajectory along the flexure 53 and enters the third slit 553 immediately after passing through the second slit 552, and becomes a flow different from the case where the flexure 53 is not present. Thereby, turbulence is created in the air flow.

However, if the top of the flexure 53 is high enough to overlap the top of the cutout 54, the air flow to pass through the slit 55 is blocked, and therefore, the height of the flexure 53 needs to be limited.

Therefore, the height of the top of the flexure 53 is set to a size of 50% or less of the height of the cutout 54 so that the top of the flexure 53 does not overlap with the top of the cutout 54. Here, the "height of the top of the flexure 53" refers to the dimension in the direction in which the fins 50 are arranged, and is a height from a plane connecting the center of the first through hole 51 and the center of the second through hole 52.

In the present embodiment, the height of the top of the bent portion 53 is in the range of 15% to 30% of the interval between the fins 50 of the fin group 5 arranged in layers (hereinafter referred to as "fin pitch") and is 50% or less of the height of the cut-up portion 54.

(4) Method for forming flexure 53

The flexure 53 is formed by tube expansion processing in which the diameter of the heat transfer tube 60 is enlarged to bring the heat transfer tube 60 into close contact with the fins 50.

Fig. 6 is an explanatory diagram showing a process of forming the flexure 53. In fig. 6, a pipe expansion head H having a diameter larger than the inner diameter of the heat transfer pipe 60 by a predetermined size is inserted into the heat transfer pipe 60. At this time, the outer diameter of the heat transfer tube 60 is enlarged in the R direction (radial direction), and the heat transfer tube 60 is brought into close contact with the collar portion 56 of the fin 50.

Further, the shortest distance L between the clip portions 56 adjacent in the longitudinal direction of the fin 50 is compressed from La before the expansion to Lb after the expansion, and as a result, the flexure 53 is formed. The compression ratio Cp at this time is calculated from cp= (La-Lb)/La.

Fig. 7 is a graph showing a relationship between the compression ratio Cp and the deflection D. In fig. 7, the horizontal axis represents the compression ratio Cp (%), and the vertical axis represents the deflection D (mm).

As described above, the deflection amount of the deflection portion 53 is set in the range of 15% to 30% of the fin pitch so as not to completely close the slit 55 as the air passage. For example, when the fin pitch is 1.60mm, the deflection amount of the deflection portion 53 is in the range of 0.24mm to 0.4 mm. In this case, the compression ratio Cp may be set to a range of 0.8 to 4.7%.

(5) Relation between deflection D of deflection 53 and dead water area length K

Fig. 8 is a graph showing the relationship between the deflection D and the dead water area length K according to the pipe outer diameter. In fig. 8, the horizontal axis represents deflection D (mm), and the vertical axis represents dead water area length K (mm). In addition, the outer diameters phi 5.3, phi 6.5 and phi 7.6 of the tubes represent the outer diameters of the tubes after tube expansion, and the tube expansion is respectively phi 5, phi 6 and phi 7.

When the dead water area K becomes longer, the dead water area interferes with the indoor fan 42 to generate noise. Therefore, at the portion where the indoor fan 42 and the indoor heat exchanger 41 are closest, it is necessary to prevent the dead water from interfering with the indoor fan 42.

Specifically, the length K of the dead water region generated in the region surrounded by the ellipse E of fig. 2 needs to be smaller than the shortest distance M between the fins 50 and the indoor fan 42 in the region. In the present embodiment, the shortest distance M is 15mm. In the present embodiment, a heat transfer tube having a tube outer diameter of 7mm was used, and the tube outer diameter after expansion was 7.6mm.

As shown in fig. 8, in order to set the dead water area length K to 15mm or less of the shortest distance M in the pipe outer diameter Φ7.6, the deflection D needs to be set to 0.25mm or more.

In contrast, when the deflection D cannot be set to 0.25mm or more, the shortest distance M may be longer than 15mm, but in view of the practical applicability, the shortest distance M is preferably in the range of 15mm to 30 mm.

(6) Features (e.g. a character)

(6-1)

In the indoor heat exchanger 41, since the bent portion 53 having a height of the top portion of 15% or more of the fin pitch is provided between the first through hole 51 and the second through hole 52 adjacent to each other in the longitudinal direction of the fin 50, turbulence is generated in the air flow on the fin 50, and therefore, dead water behind the heat transfer tube 60 is reduced, and blowing noise is suppressed.

(6-2)

In the indoor heat exchanger 41, if the flexure portion 53 becomes excessively high, wind does not blow to the cut-and-raised portion 54, and therefore, by setting the height of the top portion of the flexure portion 53 to a size of 50% or less of the height of the cut-and-raised portion 54, wind blows to the cut-and-raised portion 54.

(6-3)

In the indoor heat exchanger 41, when the bent portion 53 overlaps the cut-and-raised portion 54, wind does not blow the cut-and-raised portion 54, and therefore, by making the top of the bent portion 53 not overlap the top of the cut-and-raised portion 54, wind blows the cut-and-raised portion 54.

(6-4)

In the indoor heat exchanger 41, if the flexure portion 53 becomes too high, wind does not blow to the cut-up portion 54, and therefore, by setting the height of the top portion of the flexure portion 53 to a size of 30% or less of the fin pitch, wind blows to the cut-up portion 54.

(6-5)

In the indoor heat exchanger 41, the bent portion 53 is formed by tube expansion processing in which the diameter of the heat transfer tube 60 is enlarged to bring the heat transfer tube 60 into close contact with the fins 50, and therefore, the tube expansion and the formation of the bent portion 53 can be performed simultaneously.

(6-6)

In the indoor heat exchanger 41, the shortest distance between the fins 50 and the indoor fan 42 is in the range of 15mm to 30mm.

(6-7)

In the indoor heat exchanger 41, the bent portion 53 is formed in the fin 50 adjacent to the indoor fan 42 among the fins 50 arranged in layers. Thereby, the growth of the dead water area is suppressed.

(7) Modification examples

Fig. 9 is a partial plan view of a fin 50 according to a modification. In fig. 9, a partial plan view of the fin 50 according to the above embodiment is shown in the upper stage, and a partial plan view of the fin 50 according to the present modification is shown in the lower stage.

In the above embodiment, when the first cutout 541 located on the downstream side of the air flow F is viewed from the upstream side of the air flow F, both ends of the first cutout 541 are separated by the distance G outside the downstream domain of the heat transfer pipe 60. Therefore, there is a concern that the dead water area increases due to the air passing through the section of the distance G.

In another aspect, in the modification, when the first cutout 541 located on the downstream side of the air flow F is viewed from the upstream side of the air flow F, both ends of the first cutout 541 enter the downstream domain of the heat transfer pipe 60 by a distance X. Therefore, the air is suppressed from passing through, and the air flow is guided to the back surface side of the heat transfer pipe 60, suppressing the growth of the dead water area.

While the embodiments of the present disclosure have been described above, it should be understood that various changes in form and detail may be made therein without departing from the spirit and scope of the present disclosure as set forth in the following claims.

Claims (8)

1. An indoor heat exchanger, which is disposed on the upstream side of a fan in the path of the air flow from the suction port to the blowout port of an air conditioning indoor unit, characterized in that,

The indoor heat exchanger is provided with:

a plurality of fins (50) arranged in layers at a predetermined fin pitch; and

A plurality of heat transfer tubes (60) penetrating the fins (50) and having an outer diameter greater than 5.3mm,

The fin (50) has:

A first hole (51);

A second hole (52) adjacent to the first hole (51) in the longitudinal direction of the fin (50); and

A flexing portion (53) which flexes uniformly between the first hole (51) and the second hole (52),

The height of the top of the flexure (53) is 15% or more of the fin pitch.

2. The indoor heat exchanger according to claim 1, wherein,

The fin (50) further has:

A cut-and-raised portion (54) formed by cutting up the fin (50) in the plate thickness direction; and

A slit (55) which is generated by forming the cut-up portion (54),

The height of the top of the bending part (53) is less than 50% of the height of the cutting part (54).

3. An indoor heat exchanger according to claim 2, wherein,

When the fin (50) is viewed from a direction orthogonal to both the plate thickness direction and the longitudinal direction of the fin (50), the top of the bent portion (53) and the top of the cut-and-raised portion (54) do not overlap.

4. An indoor heat exchanger according to claim 1 or 2, wherein,

The height of the top of the flexure (53) is 30% or less of the fin pitch.

5. An indoor heat exchanger according to claim 1 or 2, wherein,

The deflection section (53) is formed by tube expansion processing in which the diameter of the heat transfer tube (60) is enlarged to bring the heat transfer tube (60) into close contact with the fins (50).

6. An indoor heat exchanger according to claim 1 or 2, wherein,

The shortest distance between the fin (50) and the fan is in the range of 15 mm-30 mm.

7. An indoor heat exchanger according to claim 1 or 2, wherein,

The flexure (53) is formed in the fin (50) adjacent to the fan among the fins (50) arranged in layers.

8. An indoor heat exchanger according to claim 2, wherein,

A part of the cut-up portion (54) is located in a space on the back surface side of the heat transfer pipe (60) in the air flow.