WO2023047716A1

WO2023047716A1 - Heat exchanger and air-conditioning device

Info

Publication number: WO2023047716A1
Application number: PCT/JP2022/022910
Authority: WO
Inventors: 剛士木村; 良行辻; 祐介森北
Original assignee: ダイキン工業株式会社
Priority date: 2021-09-27
Filing date: 2022-06-07
Publication date: 2023-03-30
Also published as: JP2023047822A; CN117980688A; JP7208558B1

Abstract

This heat exchanger 15a comprises heat transfer piping 6 through which refrigerant can flow, and a fan 7 in which are formed a plurality of through-holes 70 through which the heat transfer piping 6 can pass in the thickness direction. The plurality of through-holes 70 include: first through-holes 71 through which the heat transfer piping 6 passes, the first through-holes 71 being formed in a plurality of rows along a second direction intersecting a first direction in which the air flows from the upwind side toward the downwind side; and second through-holes 72 through which the heat transfer pipes 6 do not pass. In the fan 7, the first through-holes 71 include first regions A1 lined up along the second direction, and the second through-holes 72 include second regions B1 lined up along the second direction. The second regions B1 are adjacent to the first regions A1 on one or both first-direction sides, and are also adjacent to the first regions A1 on both second-direction sides.

Description

heat exchangers and air conditioners

The present disclosure relates to heat exchangers and air conditioners.

Fin-and-tube heat exchangers are used in air conditioners and air conditioners. In this type of heat exchanger (hereinafter simply referred to as "heat exchanger"), a plurality of heat transfer tubes are passed through a plurality of fins during manufacturing.

Conventionally, in order to reduce the manufacturing cost of heat exchangers, there are cases where multiple types of heat exchangers are manufactured by making the fins of a common shape and varying the number of heat transfer tubes that pass through the fins (for example, patent Reference 1). For example, a heat exchanger in which two rows of heat transfer tubes are inserted into fins having two rows of collars (fin through-hole portions), and a heat exchanger in which one row of heat transfer tubes is inserted in fins of the same shape By manufacturing the fins, it is possible to manufacture different types of heat exchangers while reducing the manufacturing cost of the fins. A heat exchanger manufactured in this way may have an area (extracted tube area) in which the heat transfer tube is not provided in the collar portion of the fin.

JP 2015-127607 A

(1) A heat exchanger according to the present disclosure includes a heat transfer tube through which a refrigerant can flow, and a fin having a plurality of through holes through which the heat transfer tube can pass in a thickness direction. is formed in a plurality of rows along a second direction that intersects with a first direction in which air flows from the windward side to the leeward side, the first through holes through which the heat transfer tubes penetrate, and the heat transfer tubes through the fin includes a first region in which the first through holes are aligned along the second direction; and a second region in which the second through holes are aligned along the second direction. 2 regions, wherein the second region is adjacent to the first region on one side or both sides in the first direction, and adjacent to the first region on both sides in the second direction, heat exchange It is a vessel.

Since the second region (extraction region) is a region in which the second through holes through which the heat transfer tubes do not penetrate are arranged in the second direction, the air passing through the second region passes through the first region (heat transfer tube region). It is not cooled sufficiently compared to the air that cools it. In the present disclosure, by surrounding such a second region with the first region in the first direction and the second direction, air after passing through (or before passing) the second region is more reliably can be cooled to As a result, dew condensation can be generated more reliably in the heat exchanger, so that dew condensation on members located on the leeward side of the heat exchanger can be suppressed.

(2) Preferably, the first through-hole includes an outlet through-hole through which the heat transfer tube passes through, which serves as an outlet for refrigerant when the heat exchanger functions as an evaporator, and the outlet through-hole is It is formed at a position adjacent to the first region in the first direction.

When the heat exchanger functions as an evaporator, most (or all) of the refrigerant flowing inside is in a gaseous state in the heat transfer tube, which is the outlet of the refrigerant. Therefore, in this heat transfer tube, there is almost no room for the refrigerant to evaporate by absorbing heat from the air, and the passing air cannot be sufficiently cooled. By forming the exit through-hole through which such a heat transfer tube penetrates at a position adjacent to the first region in the first direction, after (or before passing) passing through the exit through-hole and its vicinity, Uncooled air can be cooled more reliably by the adjacent first region. As a result, dew condensation can be generated more reliably in the heat exchanger, so that dew condensation on members located on the leeward side of the heat exchanger can be suppressed.

(3) Preferably, the outlet through-hole is formed at a position adjacent to the windward side of the first region.

If heat transfer tubes with low cooling capacity are provided on the windward side and heat transfer tubes with high cooling capacity are provided on the leeward side, the passing air is gradually cooled, so the cooling efficiency is higher than in the case of arranging them in the reverse order of the above. good. Since the outlet through-hole is penetrated by a heat transfer tube having a low cooling capacity, the air cooling efficiency can be improved by providing the outlet through-hole on the windward side of the other first region.

(4) Preferably, in the fin, the plurality of through holes included in the windward row are arranged in a staggered manner with respect to the plurality of through holes included in the leeward row. ing.

By forming multiple through-holes in a staggered arrangement, it is possible to evenly cool the passing air.

(5) Preferably, the fin has a narrow portion whose width in the first direction is narrower than an average, and the narrow portion penetrating portion is formed closest to the narrow portion among the plurality of through holes. The hole is the first through hole.

The narrow part has a lower cooling capacity than other parts of the fin. By using the narrow portion through-hole formed closest to the narrow portion as the first through-hole (the through-hole through which the heat transfer tube penetrates), the air passing through such a portion is cooled more reliably. can be done.

(6) Preferably, the narrow portion is a bent portion where the fin bends in the first direction.

(7) Preferably, the first through-hole includes an inlet through-hole through which the heat transfer tube passes through which serves as an inlet for refrigerant when the heat exchanger functions as an evaporator, and the narrow through-hole is , said inlet through hole.

When the heat exchanger functions as an evaporator, most (or all) of the refrigerant flowing inside is in a liquid state in the heat transfer tube, which is the inlet of the refrigerant. Therefore, in this heat transfer tube, the refrigerant absorbs heat from the air and evaporates easily, so that the passing air can be well cooled. By forming the inlet through-holes through which the heat transfer tubes pass through in the narrow portion where the cooling capability is low, the low cooling capability in the narrow portion can be compensated for. Thereby, the air passing through the narrow portion can be cooled more reliably.

(8) Preferably, the narrow through hole is formed at a position adjacent to the second region in the first direction.

Since the narrow through-hole is an inlet through-hole, the air passing through the narrow through-hole and its vicinity can be well cooled. Therefore, by forming the narrow through hole at a position adjacent to the second region in the first direction, the air that has not been sufficiently cooled after (or before passing) the second region and its vicinity can be removed. , the cooling can be more reliably performed by the heat transfer tubes passing through the narrow through-holes.

(9) Preferably, the first through-hole includes an inlet through-hole through which the heat transfer tube passes through which serves as an inlet for refrigerant when the heat exchanger functions as an evaporator, and the inlet through-hole is It is an area where the wind speed of the air passing through the heat exchanger is higher than average and is formed in the line on the leeward side.

The cooling efficiency of the air is improved by forming the inlet through-hole, which is the area where the heat transfer tube that is the inlet of the refrigerant penetrates and is the most chilled area, in the area where the air velocity is faster than the average (that is, the area where the air volume is large). can be improved. In addition, by forming such inlet through-holes in the row on the leeward side, the passing air is gradually cooled, so that the cooling efficiency of the air can be further improved.

(10) The air conditioner of the present disclosure includes a refrigerant circuit in which a compressor, a heat source side heat exchanger, a decompression mechanism, and a user side heat exchanger are connected in this order, and the user side heat exchanger is the above (1 ) to (9), including the heat exchanger.

(11) Preferably, the air conditioner of the present disclosure further includes a control unit that controls the degree of opening of the decompression mechanism, and the control unit controls the amount of refrigerant when the utilization side heat exchanger functions as an evaporator. The degree of opening is controlled so that the dryness of the refrigerant flowing out of the heat transfer tube serving as an outlet is equal to or higher than a predetermined value.

In an air conditioner that performs such control, it is possible to suppress excessively wet refrigerant from being drawn into the compressor by reducing the amount of refrigerant flowing out of the outlet. On the other hand, if such control is performed, the cooling capacity of the heat transfer tube, which is the outlet of the refrigerant, is lowered, so depending on the position of the second region, the passing air may not be sufficiently cooled. In the user-side heat exchanger included in the air conditioner of the present disclosure, the arrangement of the first region and the second region is devised so that the passing air is sufficiently cooled, so the problem associated with the above control is solved. can do.

It is a figure which shows the structure of the air conditioning apparatus which concerns on embodiment. 1 is a functional block diagram of an air conditioner according to an embodiment; FIG. It is a schematic diagram which shows the internal structure of the indoor unit which concerns on embodiment. It is a mimetic diagram showing a heat exchanger concerning an embodiment. It is a mimetic diagram showing a heat exchanger concerning an embodiment. It is a schematic diagram which shows the heat exchanger which concerns on a comparative example, and its peripheral structure. FIG. 5 is a schematic diagram showing an internal structure of an indoor unit according to a modification; It is a mimetic diagram showing a heat exchanger concerning a modification.

[Problems to be solved by the invention]
When the heat exchanger functions as an evaporator, the moisture in the air is normally condensed on the fins to remove the moisture from the air passing through the heat exchanger. This suppresses dew condensation on a member (for example, a fan) located on the leeward side of the heat exchanger.

However, if the heat exchanger has a vented area, it may not be possible to sufficiently remove moisture from the air passing through the heat exchanger. The air passing through the unpiped area is not sufficiently cooled compared to the air passing through the area where the heat transfer tubes are provided (heat transfer tube area). For this reason, the air that has mainly passed through the unpipe region and hardly passed through the heat transfer tube region is not sufficiently dehydrated, and may cause dew condensation on members positioned on the leeward side.

The present disclosure aims to suppress dew condensation on members located on the leeward side of the heat exchanger.

Hereinafter, embodiments of the present disclosure will be described with reference to the attached drawings.

[Embodiment]
[Configuration of air conditioner 1]
FIG. 1 is a diagram schematically showing the configuration of an air conditioner 1 according to an embodiment.
FIG. 2 is a functional block diagram of the air conditioner 1 according to the embodiment.
The configuration of the air conditioner 1 will be described below with reference to FIGS. 1 and 2. FIG.

The air conditioner 1 has the function of cooling and heating the room R1. The air conditioner 1 includes an indoor unit 2 installed in a room R1, an outdoor unit 3 installed outdoors, a refrigerant circuit 4 in which a refrigerant circulates, and a controller 5. The refrigerant is, for example, R32. The use of the room R1 is not particularly limited. server) may be installed.

The refrigerant circuit 4 has a compressor 11 , a switching mechanism 12 , a heat source side heat exchanger 13 , a pressure reducing mechanism 14 , a utilization side heat exchanger 15 and an accumulator 16 . In the refrigerant circuit 4, when the heat source side heat exchanger 13 functions as a condenser (that is, when the air conditioner 1 performs cooling operation), the refrigerant discharged from the compressor 11 flows through the switching mechanism 12 and the heat source. The parts 11 to 16 are connected so that the heat flows in the order of the side heat exchanger 13 , the decompression mechanism 14 , the use side heat exchanger 15 , the switching mechanism 12 and the accumulator 16 and returns to the compressor 11 .

The control unit 5 has an indoor control unit 5a and an outdoor control unit 5b that are connected to each other by a communication line. As shown in FIG. 2, the indoor controller 5a has a processor 52a and a memory 53a. The indoor controller 5a controls each part included in the indoor unit 2 by the processor 52a performing various calculations and controls based on the programs included in the memory 53a. The outdoor controller 5b has a processor 52b and a memory 53b. The outdoor control section 5b controls each section included in the outdoor unit 3 by the processor 52b performing various calculations and controls based on the programs included in the memory 53b.

The outdoor unit 3 has a housing 31 in which a suction port (not shown) and an exhaust port (not shown) are formed. The housing 31 houses the compressor 11 , the switching mechanism 12 , the heat source side heat exchanger 13 and the accumulator 16 of the refrigerant circuit 4 . The housing 31 further accommodates the outdoor controller 5 b and the outdoor fan 32 .

The compressor 11 is, for example, a variable displacement compressor, and the rotation frequency is controlled by the inverter based on the operation command from the control unit 5.

The switching mechanism 12 is a mechanism for switching the flow direction of the refrigerant in the refrigerant circuit 4, and is, for example, a four-way switching valve. Under the control of the control unit 5, the switching mechanism 12 has a first connection state (solid line in FIG. 1) in which the refrigerant discharged from the compressor 11 is sent to the heat source side heat exchanger 13, and is sent to the heat exchanger 15 on the user side (broken line in FIG. 1).

The heat source side heat exchanger 13 is, for example, a cross-fin tube heat exchanger.
The accumulator 16 is a device that performs gas-liquid separation of the refrigerant to protect the compressor 11 .

The outdoor fan 32 is, for example, a propeller fan. When the outdoor fan 32 operates, the outdoor air is sucked from the intake port (not shown) of the housing 31, and the air after heat exchange with the refrigerant in the heat source side heat exchanger 13 is discharged from the exhaust port (not shown) of the housing 31. to the outdoor space.

The indoor unit 2 has a housing 21 in which

suction ports

26a and 26b (Fig. 3) and an air outlet 26c (Fig. 3) are formed. The housing 21 accommodates the decompression mechanism 14 and the user-side heat exchanger 15 of the refrigerant circuit 4 . The housing 21 further accommodates the indoor controller 5 a and the indoor fan 22 .

The decompression mechanism 14 is, for example, an electromagnetic valve (expansion valve) and adjusts the pressure and flow rate of the refrigerant flowing through the refrigerant circuit 4 . The decompression mechanism 14 may be housed in the housing 31 of the outdoor unit 3 . The utilization side heat exchanger 15 is, for example, a cross-fin tube type heat exchanger.

The indoor fan 22 is, for example, a cross-flow fan. When the indoor fan 22 operates, the air in the room R1 is sucked in through the

suction ports

26a and 26b of the housing 21, and the conditioned air that has exchanged heat with the refrigerant in the user-side heat exchanger 15 is discharged from the air outlet 26c of the housing 21 into the room. fed into R1.

A remote control unit 51 (hereinafter referred to as "remote control 51") is attached to the indoor unit 2. The remote controller 51 is provided in the room R1 so as to be able to communicate with the indoor controller 5a by wire or wirelessly, and transmits a control signal to the indoor controller 5a according to the user's operation.

[About driving mode]
The control unit 5 causes the air conditioner 1 to perform cooling operation or heating operation based on the instruction received by the remote controller 51 . In the cooling operation, the controller 5 sets the switching mechanism 12 to the first connection state (solid line in FIG. 1). When the control unit 5 operates the compressor 11 in this state, a refrigeration cycle is performed in which the heat source side heat exchanger 13 functions as a condenser and the utilization side heat exchanger 15 functions as an evaporator.

In this cycle, the high-pressure refrigerant discharged from the compressor 11 passes through the switching mechanism 12, enters the heat source side heat exchanger 13, exchanges heat with the outdoor air, and condenses. The condensed refrigerant is decompressed when passing through the decompression mechanism 14, then enters the utilization side heat exchanger 15, exchanges heat with the air in the room R1, and evaporates. The conditioned air cooled by the refrigerant is blown into the room R1 by the indoor fan 22 . The refrigerant exiting the user-side heat exchanger 15 passes through the switching mechanism 12, enters the accumulator 16, and is sucked into the compressor 11 after gas-liquid separation.

The control unit 5 controls the opening degree of the decompression mechanism 14 during cooling operation. More specifically, when the usage-side heat exchanger 15 functions as an evaporator, the control unit 5 controls the dryness of the refrigerant flowing out from the later-described heat transfer tubes 6 serving as the refrigerant outlet in the usage-side heat exchanger 15. is a predetermined value or more (for example, 95% or more).

Controlling the dryness by the control unit 5 reduces the amount of refrigerant flowing out from the outlet of the user-side heat exchanger 15 to the outdoor unit 3, so that the compressor 11 sucks excessively wet refrigerant. can be suppressed. On the other hand, if such control is performed, the cooling capacity of the heat transfer tube 6, which is the outlet of the refrigerant, decreases. The air passing through the exchanger 15 may not be sufficiently cooled. In the air conditioner 1 of the present disclosure, the heat transfer tube regions (first regions A1, A2, A3) and the unpipe region (second region B1) described later so that the air passing through the utilization side heat exchanger 15 is sufficiently cooled , B2, B3) are devised, the above-described problems associated with the control can be solved.

In the heating operation, the control unit 5 puts the switching mechanism 12 in the second connection state (broken line in FIG. 1). When the control unit 5 operates the compressor 11 in this state, a refrigeration cycle is performed in which the heat source side heat exchanger 13 functions as an evaporator and the utilization side heat exchanger 15 functions as a condenser.

In this cycle, the high-pressure refrigerant discharged from the compressor 11 passes through the switching mechanism 12, enters the user-side heat exchanger 15, exchanges heat with the air in the room R1, and condenses. The conditioned air heated by the refrigerant is blown into the room R1 by the indoor fan 22 . The condensed refrigerant is decompressed when passing through the decompression mechanism 14, then enters the heat source side heat exchanger 13, exchanges heat with outdoor air, and evaporates. The refrigerant exiting the heat source side heat exchanger 13 passes through the switching mechanism 12, enters the accumulator 16, and is sucked into the compressor 11 after gas-liquid separation.

[Internal structure of indoor unit 2]
FIG. 3 is a schematic diagram showing the internal structure of the indoor unit 2 according to the embodiment. In FIG. 3, the portion shown as a cross section is hatched. The indoor unit 2 of this embodiment is a wall-mounted unit, and is installed, for example, on the upper part of the side wall of the room R1.

In the following description, the side wall on which the indoor unit 2 is installed facing the room is called the "front side" of the indoor unit 2, and the side opposite to the front side is called the "rear side" of the indoor unit 2. The left side of FIG. 3 is the "front side" and the right side of FIG. 3 is the "rear side". Also, the upper side in the vertical direction is the "upper side" of the indoor unit 2, and corresponds to the upper side in FIG. The lower side in the vertical direction is the "lower side" of the indoor unit 2, and corresponds to the lower side in FIG. The direction orthogonal to the front-back direction and the up-down direction is the left-right direction, the "right side" of the indoor unit 2 corresponds to the back side of the paper surface of FIG. 3, and the "left side" of the indoor unit 2 corresponds to the front side of the paper surface of FIG. .

The usage-side heat exchanger 15 includes a heat exchanger 15a installed on the front side of the indoor fan 22 and a heat exchanger 15b installed on the rear side of the indoor fan 22.

The housing 21 includes a front plate 21a, a top plate 21b, a back plate 21c, a first accommodation plate 21d, a second accommodation plate 21e, and a channel bottom plate 21f. The front plate 21 a is a plate-like member that covers the front sides of the user-side heat exchanger 15 and the indoor fan 22 . A front suction port 26a is formed in the front plate 21a.

The top plate 21b is a plate-shaped member that covers the upper sides of the user-side heat exchanger 15 and the indoor fan 22. A grill 23 is installed on the top plate 21b, and the grill 23 is formed with an upper suction port 26b. The front suction port 26a and the upper suction port 26b are also simply referred to as "suction ports". The back plate 21 c is a plate-shaped member that covers the rear side of the utilization side heat exchanger 15 and the indoor fan 22 .

The first housing plate 21d is a plate-shaped member that houses the heat exchanger 15a from below. A drain pan 24a is provided between the first housing plate 21d and the heat exchanger 15a. The drain pan 24a is a gutter-like member for collecting dew condensation water generated in the heat exchanger 15a.

The second housing plate 21e is a plate-shaped member that houses the heat exchanger 15b from below. A drain pan 24b is provided between the second housing plate 21e and the heat exchanger 15b. The drain pan 24b is a gutter-like member for collecting dew condensation water generated in the heat exchanger 15b.

The flow path bottom plate 21f is a plate-shaped member extending from the rear side of the indoor fan 22 to the front obliquely downward side. A flow path for the air blown out from the indoor fan 22 is formed by the lower surface of the first housing plate 21d and the upper surface of the flow path bottom plate 21f. An outlet of the flow path is the outlet 26 c of the housing 21 .

A flap 25 is provided on the housing 21 . By adjusting the inclination angle of the flap 25, the outlet 26c is closed or opened. Also, the direction of blowing out the conditioned air is adjusted by the inclination angle of the flap 25 . The indoor unit 2 in FIG. 3 has two flaps 25 as an example, but the number of flaps 25 is not limited.

When the indoor fan 22 rotates with the air outlet 26c open, for example, air flows F1 to F4 are generated. The airflow F1 is a flow of air from the front suction port 26a to the indoor fan 22 through the heat exchanger 15a. The airflow F2 is a flow of air from the upper suction port 26b to the indoor fan 22 through the heat exchanger 15a. The airflow F3 is a flow of air from the upper suction port 26b to the indoor fan 22 through the heat exchanger 15b. The air flow F4 is a flow of air sent indoors from the indoor fan 22 through the outlet 26c.

[Configuration of heat exchanger 15a]
FIG. 4 is a schematic diagram showing an enlarged view of the heat exchanger 15a of FIG. The heat exchanger 15 a is a so-called fin-and-tube heat exchanger, and includes heat transfer tubes 6 and fins 7 . The heat transfer pipes 6 are metal pipes through which a refrigerant can flow. The fin 7 is a plate-shaped member whose thickness direction is the left-right direction, and is a metal plate made of aluminum, for example. A plurality of fins 7 are laminated at a predetermined pitch in the horizontal direction.

In the following description, the direction in which the air flows from the windward side to the leeward side will be referred to as the "first direction". Also, a direction intersecting with the first direction is referred to as a "second direction". The second direction is, more specifically, a direction perpendicular to the first direction. Since the first direction depends on the direction in which the air flows, the first direction may differ for each region of the fins 7 . For example, in the region of the fins 7 into which the air flow F1 flows, the direction from the front side to the rear side (from the left side to the right side in FIG. 4) is the first direction. In addition, in the region of the fins 7 into which the air flow F2 flows, the first direction is the direction from the front side to the diagonally lower rear side (from the left side to the diagonally lower right side in FIG. 4).

The fin 7 has a narrow portion 7a whose width in the first direction is narrower than the average. The narrow portion 7a is formed in the central portion of the fin 7 in the vertical direction. A region of the fin 7 below the narrow portion 7a is referred to as a fin lower portion P1, and a region above the narrow portion 7a is referred to as a fin upper portion P2. The narrow portion 7a is a bent portion where the fin 7 bends in the first direction. The fin upper portion P2 is inclined to the leeward side with respect to the fin lower portion P1.

A center line L1 in the first direction in the fin lower portion P1 extends in a direction substantially along the vertical direction. The direction of the center line L1 is the longitudinal direction of the fin lower portion P1 and corresponds to the second direction of the fin lower portion P1. A center line L2 in the first direction in the fin upper portion P2 extends in a direction inclined from the upper side to the lower side and the front side. The direction of the center line L2 is the longitudinal direction of the fin upper portion P2 and corresponds to the second direction in the fin upper portion P2.

A plurality of through holes 70 through which the heat transfer tubes 6 can pass are formed in the fins 7 in the thickness direction. Although 16 through-holes 70 are formed in the fin 7 in the example of FIG. 4, the number of through-holes 70 is not particularly limited. A collar for fixing the heat transfer tube 6 passing through the through-holes 70 may be provided on the inner peripheral portion of the fin 7 forming the plurality of through-holes 70 .

A plurality of through holes 70 are formed in a plurality of rows along the second direction. In the example of FIG. 4, the plurality of through holes 70 are formed in two rows, one on the windward side and the other on the leeward side, with eight holes each. The plurality of through holes 70 included in the row on the windward side are arranged in a zigzag manner with respect to the plurality of through holes 70 included in the row on the leeward side. By forming in this way, it is possible to evenly cool the air passing through the heat exchanger 15a.

More specifically, the centers of the plurality of through holes 70 included in the windward row are formed at positions that do not overlap the centers of the plurality of through holes 70 included in the leeward row when viewed in the first direction. ing. For example, as shown in FIG. 4, an imaginary line C1 extending in the first direction passing through the center of an arbitrary through-hole 70 on the windward side is between two through-

holes

70, 70 included in the row on the leeward side (more Specifically, it passes through the midpoint of a line segment connecting the centers of the two through

holes

70 , 70 . An imaginary line C2 extending in the first direction through the center of an arbitrary through-hole 70 on the leeward side passes between the two through-

holes

70, 70 included in the row on the windward side. In this way, the through holes 70 on the windward side and the leeward side are alternately arranged.

The plurality of through-holes 70 includes first through-holes 71 through which the heat transfer tubes 6 pass and second through-holes 72 through which the heat transfer tubes 6 do not pass. In the example of FIG. 4, all eight through-holes 70 included in the fin lower portion P1 are first through-holes 71 . Of the eight through-holes 70 included in the fin upper portion P2, six are the first through-holes 71 and two are the second through-holes 72 .

The fin 7 has a first region A1 in which a plurality of first through holes 71 are arranged along the second direction, and a plurality of (two in the example of FIG. 4) second through holes 72 are arranged in the second direction. and a second region B1 arranged side by side. In the example of FIG. 4, four areas A11 to A14 each correspond to the first area A1.

The area A11 is an area where the two first through holes 71 are arranged on the windward side of the fin upper portion P2. The area A12 is an area where the four first through holes 71 are arranged on the leeward side of the fin upper portion P2. An area A13 is an area where four first through holes 71 are arranged on the windward side of the fin lower portion P1. The area A14 is an area where the four first through holes 71 are arranged on the leeward side of the fin lower portion P1.

The second area B1 is surrounded by the first area A1 with the windward side open. More specifically, the second area B1 is adjacent to the first area A1 (area A12) on the leeward side and adjacent to the first area A1 (areas A11 and A13) on both sides in the second direction.

[Configuration of heat exchanger 15b]
FIG. 5 is a schematic diagram showing an enlarged view of the heat exchanger 15b of FIG. In the heat exchanger 15b, the same components as those of the heat exchanger 15a are denoted by the same reference numerals, and descriptions thereof are omitted.

The heat exchanger 15b includes heat transfer tubes 6 and fins 7. A center line L3 in the first direction of the fins 7 of the heat exchanger 15b extends along the second direction. A plurality of through holes 70 are formed in the fin 7 . In the example of FIG. 5, six through-holes 70 are formed in each of two rows, one on the windward side and the other on the leeward side.

The plurality of through holes 70 in the heat exchanger 15b include first through holes 71 and second through holes 72. In the example of FIG. 5, all the six through-holes 70 included in the row on the windward side are the first through-holes 71 . In the leeward row, two upper and two lower through holes 70 are first through holes 71 , and two central through holes 70 are second through holes 72 .

The fin 7 of the heat exchanger 15b has a first region A2 in which a plurality of first through holes 71 are arranged along the second direction and a second region B2 in which a plurality of second through holes 72 are arranged along the second direction. and including. In the example of FIG. 5, three areas A21 to A23 each correspond to the first area A2.

An area A21 is an area where two first through holes 71 are arranged in the upper part of the fin 7 on the leeward side. The area A22 is an area where the two first through holes 71 are aligned in the lower part of the fin 7 on the leeward side. An area A23 is an area where six first through holes 71 are arranged on the windward side of the fins 7 .

The second area B2 is surrounded by the first area A2 with the leeward side open. More specifically, the second area B2 is adjacent to the first area A2 (area A23) on the windward side and adjacent to the first area A2 (areas A21 and A22) on both sides in the second direction.

[Comparative example and its problem]
FIG. 6 is a schematic diagram showing a heat exchanger 15c and its peripheral structure according to a comparative example. The heat exchanger 15c is an example in which the arrangement of the first through-holes 71 and the second through-holes 72 is different from that of the heat exchanger 15b (FIG. 5). In FIG. 6, the same reference numerals are given to the same configurations as in the embodiment, and the description thereof will be omitted. The problem to be solved by the present disclosure will be described in more detail with reference to FIG.

For example, in order to manufacture different types of heat exchangers while reducing the manufacturing cost of the fins 7, a heat exchanger in which the heat transfer tubes 6 are passed through all the through-holes 70 included in the fins 7 may be used. A heat exchanger in which the heat transfer tubes 6 pass through some of the plurality of through holes 70 included in the shaped fins 7 and the heat transfer tubes 6 do not pass through the other part of the through holes 70 is manufactured. Sometimes. In the heat exchanger 15c of the comparative example, the number of heat transfer tubes 6 passing through the through-holes 70 is reduced in order to reduce the manufacturing cost (this process is referred to as tube removal). Therefore, the fin 7 of the comparative example has first regions A91 and A92 (that is, heat transfer tube regions) and a second region B9 (that is, extubation region).

When the heat exchanger 15c functions as an evaporator, the moisture in the air is normally condensed on the fins 7 to remove the moisture from the air passing through the heat exchanger 15c. Moisture condensed on the fins 7 is collected in the drain pan 24b. This dries the air flowing on the leeward side of the heat exchanger 15c, and suppresses the formation of dew condensation on the member (for example, the indoor fan 22) located on the leeward side of the heat exchanger 15c.

However, when the heat exchanger 15c has the second region B9, it may not be possible to sufficiently remove moisture from the air passing through the heat exchanger 15c. The air passing through the second region B9 is not sufficiently cooled compared to the air passing through the first regions A91 and A92 where the heat transfer tubes 6 are provided. For this reason, the air that has mainly passed through the second region B9 and hardly passed through the first regions A91 and A92 is not sufficiently dehydrated, and relatively moist air flows downwind, resulting in Condensation may occur on the components where it is located.

In the comparative example, the first area A91 is arranged on the leeward side of the second area B9. With such a configuration, the air flow F91 that linearly passes through the width direction of the fin 7 passes through the first region A91 after passing through the second region B9. , moisture removal can be performed. The air flow F91 described above is a flow called “laminar flow” or “main flow”, etc., and passes linearly and stably from the suction port 26b toward the indoor fan 22 (that is, in a relatively short distance). It is the flow to do. The "first direction" in the present disclosure means the flow direction of this mainstream.

On the other hand, at the lower ends of the fins 7, the flow of air is slowed down by the second accommodation plate 21e and the drain pan 24b. As a result, at the lower end of the fin 7, as shown in FIG. 6, an air flow F92 can be generated that passes through the lower end of the fin 7 from the suction port 26b so as to largely bypass the lower end of the fin 7 and is directed to the indoor fan 22. The air flow F92 is a flow called "turbulent flow" or "bypass flow" or the like, and is a flow that passes in an oblique direction with respect to the air flow F91 (first direction).

In the example of FIG. 6, the air flow F92 reaches the indoor fan 22 without passing through the first region A91 after passing through the second region B9 at the lower end of the fin 7. , water cannot be sufficiently removed. As described above, when the second region B9 is formed at the end (upper end or lower end) of the fin 7 in the second direction, it is not possible to sufficiently remove moisture from the air flow F92 that flows obliquely with respect to the main flow. Moisture contained in F92 may cause dew condensation on members located on the leeward side of the heat exchanger 15c.

[Characteristics of

heat exchangers

15a and 15b]
Please refer to FIGS. In the

heat exchangers

15a and 15b, the second regions B1 and B2 (pipe removal regions) are surrounded by the first regions A1 and A2 (heat transfer tube regions) with their windward or leeward sides open. That is, the first regions A1 and A2 are located on both sides (upper side and lower side) of the second regions B1 and B2 in the second direction, and the first regions A1 are located on the windward side or the leeward side of the second regions B1 and B2. , A2 are located.

With this configuration, the air after (or before) passing through the second areas B1 and B2 is cooled more reliably by the first areas A1 and A2. As a result, dew condensation can be generated more reliably in the

heat exchangers

15a and 15b, so that the air flowing on the leeward side of the

heat exchangers

15a and 15b can be sufficiently dried. It is possible to suppress dew condensation on the member located on the leeward side.

More specifically, both ends in the second direction of the first regions A1 and A2 adjacent to the second regions B1 and B2 in the first direction are located outside the ends of the second regions B1 and B2 in the second direction. are doing. For example, as shown in FIG. 4, the upper end in the second direction of the first region A1 (regions A12, A14) adjacent to the leeward side of the second region B1 is higher than the upper end in the second direction of the second region B1. and the lower ends in the second direction of the first regions A1 (regions A12 and A14) adjacent to the leeward side of the second regions B1 are positioned below the lower ends of the second regions B1 in the second direction. there is

With such a configuration, even if the air passes obliquely through the second regions B1 and B2, the first regions A1 and A2 that are longer than the second regions B1 and B2 in the second direction are the second regions B1. , B2, the air after (or before) passing through the second regions B1 and B2 passes through the first regions A1 and A2 more reliably. Therefore, the air passing obliquely can be cooled more reliably, and dew condensation on members located on the leeward side of the

heat exchangers

15a and 15b can be suppressed.

Further features of the

heat exchangers

15a and 15b will be described below with reference to FIGS. The first through-hole 71 includes an outlet through-hole 73 and an inlet through-hole 75 . The outlet through-hole 73 is the first through-hole 71 through which the heat transfer tube 6, which serves as an outlet for the refrigerant, penetrates when the

heat exchangers

15a and 15b function as evaporators. In FIGS. 4 and 5, the outlet through-hole 73 is indicated by an arrowhead (black dot mark).

The outlet through-hole 73 is formed at a position adjacent to the first regions A1 and A2 in the first direction. When the

heat exchangers

15a and 15b function as evaporators, most (or all) of the refrigerant flowing inside the heat transfer tube 6, which is the outlet of the refrigerant, is in a gaseous state. For this reason, the heat transfer tube 6, which is the outlet of the refrigerant, has little room for the refrigerant to evaporate by absorbing heat from the air, and the passing air cannot be sufficiently cooled.

In the present embodiment, by forming the exit through-hole 73 at a position adjacent to the first regions A1 and A2 in the first direction, after (or before passing) passing through the exit through-hole 73 and its vicinity, Uncooled air can be cooled more reliably by the adjacent first regions A1 and A2. As a result, dew condensation can be generated more reliably in the

heat exchangers

15a and 15b, so that dew condensation in members located on the leeward side of the

heat exchangers

15a and 15b can be suppressed.

Specifically, as shown in FIG. 4, the outlet through-hole 73 of the area A11 is adjacent to the windward side of the area A12, and the outlet through-hole 73 of the area A13 is adjacent to the windward side of the area A14. When the heat transfer tubes 6 with low cooling capacity are provided on the windward side and the heat transfer tubes 6 with high cooling capacity (the heat transfer tubes 6 other than the heat transfer tubes 6 serving as the outlet of the refrigerant) are provided on the leeward side, the passing air is gradually cooled. Therefore, cooling efficiency is better than in the case of arranging them in the reverse order. Since the heat transfer pipes 6 having a low cooling capacity pass through the outlet through-holes 73, the air cooling efficiency can be improved by providing the outlet through-holes 73 on the windward side of the other first area A1. .

The inlet through-hole 75 is the first through-hole 71 through which the heat transfer pipe 6 that serves as the refrigerant inlet penetrates when the

heat exchangers

15a and 15b function as evaporators. In FIGS. 4 and 5, the inlet through-hole 75 is indicated by an arrow mark (“X” mark).

In the area A12 (FIG. 4) and the area A21 (FIG. 5), the inlet through-holes 75 are formed in a row on the leeward side in an area where the wind speed of the air passing through the

heat exchangers

15a and 15b is higher than the average. It is In FIG. 4, the air flows F1 and F2 mainly flow in, and the area where the wind speed is faster than the average is shown as area D1. Also, a region D2 is illustrated as a region where the flow is blocked by the first housing plate 21d and the like and the wind speed is slower than the average. As shown in FIG. 4, the inlet through-hole 75 of area A12 is included in area D1.

When the

heat exchangers

15a and 15b function as evaporators, most (or all) of the refrigerant flowing inside is in a liquid state in the heat transfer tubes 6 serving as refrigerant inlets. Therefore, in the heat transfer tube 6 serving as the inlet of the refrigerant, the refrigerant absorbs heat from the air and evaporates easily, so that the passing air can be well cooled. Therefore, the inlet through-hole 75 is the region that is most likely to cool when the

heat exchangers

15a and 15b function as evaporators. By forming such an inlet through-hole 75 in a region where the wind speed of air is higher than the average (that is, a region with a large amount of air), the cooling efficiency of air can be improved. In addition, by forming such inlet through-holes 75 in a row on the leeward side, the passing air is gradually cooled, so that the cooling efficiency of the air can be further improved.

Furthermore, by forming the inlet through-hole 75 at a position adjacent to the second regions B1 and B2 in the first direction or the second direction, the air passing through the second through-hole 72 and its vicinity can be cooled more reliably. can be done. In the example of FIG. 4, the inlet through-hole 75 included in the area A12 is adjacent to the second area B1 in the first direction. In the example of FIG. 5, the inlet through-hole 75 included in the area A21 is adjacent to the second area B2 in the second direction.

As shown in FIG. 4 , among the plurality of through holes 70 , the narrow portion through hole 74 formed closest to the narrow portion 7 a is the first through hole 71 . Since the narrow portion 7 a has a narrow width, it has a lower cooling capacity than the other portions of the fin 7 . By using the narrow portion through-hole 74 formed closest to the narrow portion 7a as the first through-hole 71 (the through-hole 70 through which the heat transfer tube 6 penetrates), the air passing through such a portion is further reduced. can be reliably cooled.

Further, as shown in FIG. 4, the narrow through-hole 74 is the inlet through-hole 75. As described above, the inlet through-hole 75 is the region that cools most when the

heat exchangers

15a and 15b function as evaporators. By forming such an inlet through-hole 75 in the narrow portion 7a with low cooling ability, it is possible to compensate for the low cooling ability in the narrow portion 7a. Thereby, the air passing through the narrow portion 7a can be cooled more reliably.

The narrow through hole 74 is formed at a position adjacent to the leeward side of the second region B1. Since the narrow through-hole 74 is the inlet through-hole 75, the air passing through the narrow through-hole 74 and the vicinity thereof can be well cooled. Therefore, by forming the narrow portion through hole 74 at a position adjacent to the leeward side of the second region B1, the air that has not been sufficiently cooled after passing through the second region B1 and its vicinity can pass through the narrow portion. Cooling can be more reliably performed by the heat transfer tubes 6 passing through the holes 74 .

Although the narrow through-hole 74 is located on the leeward side of the second region B1 in FIG. 4, it may be located on the windward side of the second region B1. That is, the narrow through-hole 74, which is the inlet through-hole 75, may be formed at a position adjacent to the second region B1 in the first direction.

[Modification]
The present disclosure is not limited to the above embodiments, and various modifications are possible. In the following modified examples, the same reference numerals are given to the same configurations as in the above-described embodiment, and the description thereof will be omitted as appropriate.

[Modified example of indoor unit]
FIG. 7 is a schematic diagram showing the internal structure of an indoor unit 2a according to a modification. The indoor unit 2a is a ceiling-embedded unit, and is embedded in the ceiling space of the room R1 (FIG. 1), for example. The method of installing the indoor unit of the present disclosure in the room R1 is not limited, and may be a wall-mounted indoor unit 2 as shown in FIG. 3, or a ceiling-embedded indoor unit 2a as shown in FIG. Alternatively, it may be a ceiling-suspended or floor-mounted indoor unit (not shown).

The indoor unit 2a has a housing 21, and an indoor fan 22 and a heat exchanger 15d housed in the housing 21. The heat exchanger 15d functions as the user-side heat exchanger 15 of the air conditioner 1 (Fig. 1). The airflow F5 blown out from the indoor fan 22 passes through the heat exchanger 15d.

The heat exchanger 15d includes heat transfer tubes 6 and fins 7b. Three rows of through-holes 70 are formed in the fin 7b in the first direction through which the air flow F5 passes. That is, three rows of through-holes 70 are formed along a second direction that intersects the first direction (a direction that intersects with the air flow F5). The number of rows of the through-holes 70 included in the fins 7b is not limited, and may be three rows in the first direction, or may be four rows or more in the first direction.

The plurality of through-holes 70 includes first through-holes 71 through which the heat transfer tubes 6 pass and second through-holes 72 through which the heat transfer tubes 6 do not pass. That is, the heat transfer tubes 6 are removed from some of the plurality of through holes 70 . In the fin 7b, all the ten through-holes 70 located in the windward-most row are the first through-holes 71, and all the ten through-holes 70 located in the leeward-most row are the second through-holes 72. be. In addition, of the ten through holes 70 positioned in the central row in the first direction, four are the first through holes 71, two are the second through holes 72, and two are the first through holes 71 in order from the top. There are two through holes 71 and two second through holes 72 .

As shown in FIG. 7, the second area B3 in which the second through holes 72 are arranged in the second direction is surrounded by the first area A3 in which the first through holes 71 are arranged in the second direction. More specifically, the second area B3 is adjacent to the first area A3 (area A32) on the windward side, and adjacent to the first areas A3 (areas A31 and A33) on both sides in the second direction. With such a configuration, the air before passing through the second area B3 can be cooled more reliably by the first area A3.

[Modification of heat exchanger]
FIG. 8 is a schematic diagram showing a heat exchanger 15e according to a modification. The heat exchanger 15e is a further modification of the modification heat exchanger 15d (FIG. 7). The heat exchanger 15e includes heat transfer tubes 6 and fins 7c. Three rows of through-holes 70 are formed in the fin 7c in the first direction through which the air flow F5 passes.

The plurality of through holes 70 include first through holes 71 and second through holes 72 . In the fin 7 c , all the 16 through holes 70 located in the windward most row are the first through holes 71 . Of the 16 through-holes 70 positioned in the central row in the first direction, two are first through-holes 71, three are second through-holes 72, and two are first through-holes in order from the top. 71 , two of which are the second through holes 72 and seven of which are the first through holes 71 . Of the 16 through-holes 70 positioned in the row on the most leeward side, two are first through-holes 71, three are second through-holes 72, and five are first through-holes in order from the top. 71 , four of which are the second through holes 72 and two of which are the first through holes 71 .

The fin 7c includes a first area A4 in which a plurality of first through holes 71 are arranged along the second direction, and a second area B4 in which a plurality of second through holes 72 are arranged along the second direction. In the example of FIG. 8, the six areas A41 to A46 each correspond to the first area A4, and the three areas B41 to B43 each correspond to the second area B4.

As shown in FIG. 8, the second area B4 is surrounded by the first area A4. FIG. 8 shows various variations in which the second area B4 is surrounded by the first area A4. For example, the area B41 is adjacent to the area A42 on the windward side and adjacent to the areas A41 and A43 on both sides in the second direction while the leeward side is open.

Thus, even when there are two rows of second regions B4 (regions B41) in the first direction, two rows of regions A41 are arranged on both sides in the second direction so as to surround the second regions B4. , A43 adjacent to each other, the air before passing through the second area B4 can be cooled more reliably by the first area A4.

The area B42 is adjacent to the area A42 on the windward side, adjacent to the area A44 on the leeward side, and adjacent to the areas A43 and A45 on both sides in the second direction. Since the area B42 is surrounded by the first area A4 on both sides in the first direction and both sides in the second direction, it can be cooled more reliably than the air passing through the second area B4.

With the leeward side open, the area B43 is adjacent to the area A45 on the windward side and adjacent to the areas A44 and A46 on both sides in the second direction. In particular, since the first area A4 for two rows of the areas A42 and A45 is positioned on the windward side of the area B43, the air flowing in the first direction can be cooled more reliably.

[others]
At least a part of each of the embodiments and modifications described above may be arbitrarily combined with each other.

[Action and effect of the embodiment]
(1) The

heat exchangers

15a, 15b, 15d, and 15e of the embodiment include the heat transfer tubes 6 through which the refrigerant can flow, and the fins 7 formed with a plurality of through holes 70 through which the heat transfer tubes 6 can pass in the thickness direction. , 7b and 7c, and the plurality of through holes 70 are formed in a plurality of rows along a second direction that intersects with the first direction in which the air flows from the windward side to the leeward side, and the heat transfer tubes 6 pass through the through holes 70. and a second through hole 72 through which the heat transfer tube 6 does not pass. A2, A3, A4, and second regions B1, B2, B3, B4 in which the second through holes 72 are arranged along the second direction. A heat exchanger 15a adjacent to the first regions A1, A2, A3, A4 on one side or both sides in the first direction and adjacent to the first regions A1, A2, A3, A4 on both sides in the second direction. , 15b, 15d and 15e.

The second regions B1, B2, B3, and B4 (pipe removal regions) are regions in which the second through holes 72 through which the heat transfer tubes 6 do not pass are arranged in the second direction. The air passing through is not sufficiently cooled compared to the air passing through the first regions A1, A2, A3, A4 (heat transfer tube regions). In the present disclosure, such second regions B1, B2, B3, B4 are surrounded by the first regions A1, A2, A3, A4 in the first direction and the second direction, so that the second regions B1, B2, B3 , B4 can be cooled more reliably by the first regions A1, A2, A3 and A4. As a result, dew condensation can be generated more reliably in the

heat exchangers

15a, 15b, 15d, and 15e, so that dew condensation on the members located on the leeward side of the

heat exchangers

15a, 15b, 15d, and 15e can be suppressed. can.

(2) The first through-hole 71 of the embodiment includes an outlet through-hole 73 through which the heat transfer tube 6 passes through, which serves as an outlet for refrigerant when the

heat exchangers

15a and 15b function as evaporators. 73 is formed at a position adjacent to the first regions A1 and A2 in the first direction.

When the

heat exchangers

15a and 15b function as evaporators, most (or all) of the refrigerant flowing inside the heat transfer tube 6, which is the outlet of the refrigerant, is in a gaseous state. Therefore, in the heat transfer tube 6, there is almost no room for the refrigerant to evaporate by absorbing heat from the air, and the passing air cannot be sufficiently cooled. By forming the outlet through-hole 73 through which the heat transfer tube 6 penetrates at a position adjacent to the first regions A1 and A2 in the first direction, after passing through the outlet through-hole 73 and its vicinity (or The air that has not been sufficiently cooled (before cooling) can be cooled more reliably by the adjacent first regions A1 and A2. As a result, dew condensation can be generated more reliably in the

heat exchangers

15a and 15b can be suppressed.

(3) The outlet through hole 73 of the embodiment is formed at a position adjacent to the windward side of the first area A1.

If the heat transfer tubes 6 with low cooling capacity are provided on the windward side and the heat transfer tubes 6 with high cooling capacity are provided on the leeward side, the passing air is gradually cooled. Efficient. Since the heat transfer pipes 6 having a low cooling capacity pass through the outlet through-holes 73, the air cooling efficiency can be improved by providing the outlet through-holes 73 on the windward side of the other first area A1. .

(4) In the fin 7 of the embodiment, the plurality of through holes 70 included in the windward row are arranged in a staggered manner with respect to the plurality of through holes 70 included in the leeward row. ing.

By forming a plurality of through-holes 70 in a zigzag arrangement, it is possible to evenly cool the passing air.

(5) The fin 7 of the embodiment has a narrow portion 7a having a width narrower than the average in the first direction, and the narrow portion formed closest to the narrow portion 7a among the plurality of through-holes 70. The through hole 74 is the first through hole 71 .

The narrow portion 7a has a lower cooling capacity than other portions of the fin 7. By using the narrow portion through-hole 74 formed closest to the narrow portion 7a as the first through-hole 71 (the through-hole 70 through which the heat transfer tube 6 penetrates), the air passing through such a portion is further reduced. can be reliably cooled.

(6) The narrow portion 7a of the embodiment is a bent portion where the fin 7 bends in the first direction.

(7) The first through-hole 71 of the embodiment includes an inlet through-hole 75 through which the heat transfer tube 6 penetrates, which serves as an inlet for refrigerant when the heat exchanger 15a functions as an evaporator. is the inlet through-hole 75 .

When the heat exchanger 15a functions as an evaporator, most (or all) of the refrigerant flowing inside is in a liquid state in the heat transfer tube 6 serving as the refrigerant inlet. Therefore, in the heat transfer tube 6, the refrigerant absorbs heat from the air and evaporates easily, so that the passing air can be well cooled. By forming the inlet through-hole 75 through which the heat transfer tube 6 penetrates in the narrow portion 7a having low cooling ability, the low cooling ability in the narrow portion 7a can be compensated. Thereby, the air passing through the narrow portion 7a can be cooled more reliably.

(8) The narrow through hole 74 of the embodiment is formed at a position adjacent to the second region B1 in the first direction.

Since the narrow through-hole 74 is the inlet through-hole 75, the air passing through the narrow through-hole 74 and the vicinity thereof can be well cooled. Therefore, by forming the narrow through-hole 74 at a position adjacent to the second region B1 in the first direction, it is sufficiently cooled after (or before) passing through the second region B1 and its vicinity. The heat transfer tube 6 passing through the narrow portion through-hole 74 can cool the air that does not exist in the air more reliably.

(9) The first through-hole 71 of the embodiment includes an inlet through-hole 75 through which the heat transfer tube 6 passes through, which serves as an inlet for refrigerant when the heat exchanger 15a functions as an evaporator. , the wind speed of the air passing through the heat exchanger 15 is faster than the average, and is formed in the line on the leeward side.

By forming the inlet through-hole 75, which is the area where the heat transfer tube 6, which is the inlet of the refrigerant, penetrates and is most likely to be cooled, in the area where the air velocity is faster than the average (that is, the area where the air volume is large), the air is cooled. Efficiency can be improved. In addition, by forming such inlet through-holes 75 in the row on the leeward side, the passing air is gradually cooled, so that the cooling efficiency of the air can be further improved.

(10) The air conditioner 1 of the embodiment includes a refrigerant circuit 4 in which a compressor 11, a heat source side heat exchanger 13, a pressure reducing mechanism 14, and a user side heat exchanger 15 are connected in this order. 15 is an air conditioner 1 including

heat exchangers

15a, 15b, 15d, and 15e according to any one of claims 1 to 9.

(11) The air conditioner 1 of the embodiment further includes a control unit 5 that controls the opening degree of the decompression mechanism 14. The control unit 5 controls the refrigerant outlet when the utilization side heat exchanger 15 functions as an evaporator. The opening is controlled so that the dryness of the refrigerant flowing out of the heat transfer tube 6 becomes a predetermined value or more.

In the air conditioner 1 that performs such control, it is possible to suppress the intake of excessively wet refrigerant into the compressor 11 by reducing the amount of refrigerant flowing out from the outlet. On the other hand, if such control is performed, the cooling capacity of the heat transfer tube 6, which is the outlet of the refrigerant, is lowered. it may not be done. In the user-side heat exchanger 15 included in the air conditioner 1 of the present disclosure, the first areas A1, A2, A3, A4 and the second areas B1, B2, B3, B4 are arranged so that the passing air is sufficiently cooled. is devised, it is possible to solve the problems associated with the above control.

[Supplement]
Although embodiments have been described above, it will be appreciated that various changes in form and detail may be made without departing from the spirit and scope of the claims.

1: Air conditioner 11: Compressor 12: Switching mechanism 13: Heat source side heat exchanger 14: Pressure reducing mechanism 15: User side heat exchanger 15a: Heat exchanger 15b: Heat exchanger 15c : heat exchanger 15d: heat exchanger 15e: heat exchanger 16: accumulator 2: indoor unit 2a: indoor unit 21: housing 21a: front plate 21b: top plate 21c: back plate , 21d: first housing plate, 21e: second housing plate, 21f: channel bottom plate, 22: indoor fan, 23: grill, 24a: drain pan, 24b: drain pan, 25: flap, 26a: front suction port, 26b : upper suction port, 26c: outlet, 3: outdoor unit, 31: housing, 32: outdoor fan, 4: refrigerant circuit, 5: control unit, 5a: indoor control unit, 5b: outdoor control unit, 51: remote Control unit (remote control), 52a: processor, 52b: processor, 53a: memory, 53b: memory, 6: heat transfer tube, 7: fin, 7b: fin, 7c: fin, 7a: narrow part, 70: through hole, 71 : first through hole, 72: second through hole, 73: outlet through hole, 74: narrow portion through hole, 75: inlet through hole, R1: room, P1: fin lower part, P2: fin upper part, L1: center line , L2: center line, L3: center line, C1: virtual line, C2: virtual line, D1: area, D2: area, A1: first area, A2: first area, A3: first area, A4: second 1 area, A91: first area, A92: first area, B1: second area, B2: second area, B3: second area, B4: second area, B9: second area, A11: area, A12 : area, A13: area, A14: area, A21: area, A22: area, A23: area, A31: area, A32: area, A33: area, A41: area, A42: area, A43: area, A44: area , A45: area, A46: area, B41: area, B42: area, B43: area, F1: air flow, F2: air flow, F3: air flow, F4: air flow, F5: air flow, F91: air flow , F92: air flow

Claims

a heat transfer tube (6) through which a refrigerant can flow;
fins (7, 7b, 7c) formed with a plurality of through holes (70) through which the heat transfer tubes (6) can pass in the thickness direction;
with
The plurality of through holes (70) are
The air is formed in a plurality of rows along a second direction that intersects with the first direction from the windward side to the leeward side,
including a first through hole (71) through which the heat transfer tube (6) passes and a second through hole (72) through which the heat transfer tube (6) does not pass;
The fins (7) are
a first region (A1, A2, A3, A4) in which the first through holes (71) are arranged along the second direction;
second regions (B1, B2, B3, B4) in which the second through holes (72) are arranged along the second direction;
including
The second regions (B1, B2, B3, B4) are adjacent to the first regions (A1, A2, A3, A4) on one side or both sides in the first direction, and the Adjacent to the first region (A1, A2, A3, A4),
heat exchangers (15a, 15b, 15d, 15e);
The first through-hole (71) is an outlet through-hole (73) through which the heat transfer pipe (6) passes, which serves as a refrigerant outlet when the heat exchanger (15a, 15b) functions as an evaporator. including
The exit through-hole (73) is formed at a position adjacent to the first region (A1, A2) in the first direction,
A heat exchanger (15a, 15b) according to claim 1.
The outlet through hole (73) is formed at a position adjacent to the windward side of the first area (A1),
A heat exchanger (15a) according to claim 2.
In the fin (7), the plurality of through holes (70) included in the windward row are arranged in a staggered manner with respect to the plurality of through holes (70) included in the leeward row. is formed in
A heat exchanger (15a, 15b, 15d, 15e) according to any one of claims 1 to 3.
The fin (7) has a narrow portion (7a) with a narrower than average width in the first direction,
Among the plurality of through-holes (70), a narrow-portion through-hole (74) formed closest to the narrow portion (7a) is the first through-hole (71).
A heat exchanger (15a) according to any one of claims 1 to 4.
The narrow portion (7a) is a bent portion where the fin (7) bends in the first direction,
A heat exchanger (15a) according to claim 5.
The first through-hole (71) includes an inlet through-hole (75) through which the heat transfer pipe (6) passes, which serves as an inlet for refrigerant when the heat exchanger (15) functions as an evaporator,
The narrow through-hole (74) is the entrance through-hole (75),
A heat exchanger (15a) according to claim 5 or claim 6.
The narrow through hole (74) is formed at a position adjacent to the second region (B1) in the first direction,
A heat exchanger (15a) according to claim 7.
The first through-hole (71) includes an inlet through-hole (75) through which the heat transfer pipe (6) passes, which serves as an inlet for refrigerant when the heat exchanger (15a) functions as an evaporator,
The inlet through-hole (75) is formed in a region (D1) in which the wind speed of the air passing through the heat exchanger (15a) is higher than the average and in the row on the leeward side,
A heat exchanger (15a) according to any one of the preceding claims.
A refrigerant circuit (4) in which a compressor (11), a heat source side heat exchanger (13), a pressure reducing mechanism (14) and a user side heat exchanger (15) are connected in this order,
An air conditioner (1), wherein the utilization side heat exchanger (15) includes the heat exchanger (15a, 15b, 15d, 15e) according to any one of claims 1 to 9.
further comprising a control unit (5) for controlling the opening degree of the decompression mechanism (14),
The control unit (5) controls the dryness of the refrigerant flowing out from the heat transfer pipe (6), which is the refrigerant outlet when the utilization side heat exchanger (15) functions as an evaporator, to be a predetermined value or more. controlling the opening to
Air conditioner (1) according to claim 10.