EP4411304A1

EP4411304A1 - Heat exchanger and air-conditioning device

Info

Publication number: EP4411304A1
Application number: EP22872474.6A
Authority: EP
Inventors: Tsuyoshi Kimura; Yoshiyuki Tsuji; Yusuke MORIKITA
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2021-09-27
Filing date: 2022-06-07
Publication date: 2024-08-07
Also published as: CN117980688A; WO2023047716A1; US20240240824A1; JP2023047822A; JP7208558B1; EP4411304A4

Abstract

The disclosure provides a heat exchanger 15a including: a heat transfer tube 6 allowing a refrigerant to flow; and a fin 7 provided with a plurality of through holes 70 each allowing penetration of the heat transfer tube 6 in a thickness direction; in which the plurality of through holes 70 is aligned in a plurality of columns in a second direction crossing a first direction of air flowing from a windward side toward a leeward side, and includes first through holes 71 each penetrated by the heat transfer tube 6 and second through holes 72 not penetrated by the heat transfer tube 6, the fin 7 includes a first region A1 having the first through holes 71 aligned in the second direction, and a second region B1 having the second through holes 72 aligned in the second direction, and the second region B1 has an end or respective ends in the first direction adjacent to the first region A1, and respective ends in the second direction adjacent to the first region A1.

Description

TECHNICAL FIELD

The present disclosure relates to a heat exchanger and an air conditioner.

BACKGROUND ART

An air conditioner or an apparatus similar to the air conditioner includes a fin-and-tube heat exchanger. The heat exchanger of this type (hereinafter, simply called "heat exchanger") is produced by causing a plurality of heat transfer tubes to penetrate a plurality of fins.
There have been conventionally produced in some cases a plurality of types of heat exchangers each including a commonly shaped fin and a different number of heat transfer tubes penetrating the fin, for reduction in production cost for the heat exchangers (e.g. PATENT LITERATURE 1). For example, production of a heat exchanger including a fin having collar portions (through hole portions provided in the fin) in two columns and heat transfer tubes in two columns inserted to the fin, and a heat exchanger including an identically shaped fin and heat transfer tubes in a single column inserted to the fin achieves production of different types of heat exchangers with reduced production cost for the fins or the like. In each of the heat exchangers thus produced, the collar portions of the fin may include a region (tube removed region) not provided with the heat transfer tube.

CITATION LIST

[PATENT LITERATURE]

PATENT LITERATURE 1: Japanese Laid-Open Patent Publication No. 2015-127607

SUMMARY OF THE INVENTION

(1) The present disclosure provides a heat exchanger including: a heat transfer tube allowing a refrigerant to flow; and a fin provided with a plurality of through holes each allowing penetration of the heat transfer tube in a thickness direction; in which the plurality of through holes is aligned in a plurality of columns in a second direction crossing a first direction of air flowing from a windward side toward a leeward side, and includes first through holes each penetrated by the heat transfer tube and second through holes not penetrated by the heat transfer tube, the fin includes a first region having the first through holes aligned in the second direction, and a second region having the second through holes aligned in the second direction, and the second region has an end or respective ends in the first direction adjacent to the first region, and respective ends in the second direction adjacent to the first region.

The second region (tube removed region) includes the second through holes not penetrated by the heat transfer tube and aligned in the second direction. Air passing the second region is thus not cooled sufficiently in comparison to air passing the first region (heat transfer tube region). The present disclosure provides the second region surrounded with the first region in the first direction and the second direction, so that the first region more reliably cools air having passed (or being subject to pass) the second region. The heat exchanger can thus have more reliable dew condensation to inhibit dew condensation on a member positioned leeward of the heat exchanger.
(2) Preferably, the first through holes includes an outlet through hole penetrated by the heat transfer tube serving as a refrigerant outlet when the heat exchanger functions as an evaporator, and the outlet through hole is positioned adjacent in the first direction to the first region.
When the heat exchanger functions as an evaporator, the refrigerant flowing in the heat transfer tube serving as a refrigerant outlet is mostly (or entirely) in a gas state. Accordingly, the heat transfer tube has almost no room for heat absorption from air and refrigerant evaporation, failing to sufficiently cool passing air. The outlet through hole penetrated by the heat transfer tube is positioned adjacent in the first direction to the first region, so that the adjacent first region more reliably cools air not cooled sufficiently and having passed (or being subject to pass) the outlet through hole and the vicinity thereof. The heat exchanger can thus have more reliable dew condensation to inhibit dew condensation on a member positioned leeward of the heat exchanger.
(3) Preferably, the outlet through hole is positioned adjacent to the windward side of the first region.
If the heat transfer tube having low cooling capacity is provided windward and the heat transfer tube having high cooling capacity is provided leeward, passing air is gradually cooled to achieve higher cooling efficiency in comparison to a case of disposition in an inverted order. The outlet through hole is penetrated by the heat transfer tube having low cooling capacity, and is thus provided windward of a different first region for enhanced air cooling efficiency.
(4) Preferably, in the fin, the plurality of through holes included in a column on the windward side is disposed to be staggered with respect to the plurality of through holes included in a column on the leeward side.
The plurality of through holes disposed to be staggered allows passing air to be evenly cooled.
(5) Preferably, the fin includes a narrow portion having a smaller width than an average width in the first direction, and the plurality of through holes includes a narrow portion through hole provided closest to the narrow portion and corresponding to the first through hole.
The narrow portion is lower in cooling capacity than the remaining portion of the fin. When the narrow portion through hole provided closest to the narrow portion corresponds to the first through hole (the through hole penetrated by the heat transfer tube), air passing such a portion can be cooled more reliably.
(6) Preferably, the narrow portion is a bent portion where the fin is bent in the first direction.
(7) Preferably, the first through holes include an inlet through hole penetrated by the heat transfer tube serving as a refrigerant inlet when the heat exchanger functions as an evaporator, and the narrow portion through hole corresponds to the inlet through hole.
When the heat exchanger functions as an evaporator, the refrigerant flowing in the heat transfer tube serving as a refrigerant inlet is mostly (or entirely) in a liquid state. Accordingly, the heat transfer tube is likely to allow the refrigerant to absorb heat from air and evaporate, for preferable cooling of passing air. The inlet through hole penetrated by the heat transfer tube is provided in the narrow portion having low cooling capacity to compensate such low cooling capacity in the narrow portion. This enables more reliable cooling of air passing the narrow portion.
(8) Preferably, the narrow portion through hole is positioned adjacent in the first direction to the second region.
The narrow portion through hole corresponds to the inlet through hole, so as to preferably cool air passing the narrow portion through hole and the vicinity thereof. Accordingly, the narrow portion through hole is positioned adjacent in the first direction to the second region, so that the heat transfer tube penetrating the narrow portion through hole more reliably cools air having passed (or being subject to pass) the second region and the vicinity thereof and not cooled sufficiently.
(9) Preferably, the first through holes include an inlet through hole penetrated by the heat transfer tube serving as a refrigerant inlet when the heat exchanger functions as an evaporator, and the inlet through hole is provided in a region where air passing the heat exchanger has air flow speed higher than average air flow speed, and in a column on the leeward side.
The inlet through hole penetrated by the heat transfer tube serving as a refrigerant inlet and constituting a region most likely to be cooled is provided in the region having air flow speed higher than the average air flow speed (i.e. a region having large air flow volume) to achieve enhanced air cooling efficiency. The inlet through hole is provided in the column on the leeward side to gradually cool passing air, for further enhanced air cooling efficiency.
(10) The present disclosure provides an air conditioner including a refrigerant circuit including a compressor, a heat source heat exchanger, a decompression mechanism, and a utilization heat exchanger connected in a mentioned order, in which the utilization heat exchanger includes the heat exchanger according to any one of (1) to (9) described above.
(11) Preferably, the air conditioner according to the present disclosure further includes a control unit configured to control an opening degree of the decompression mechanism, in which the control unit controls the opening degree to cause a refrigerant flowing out of the heat transfer tube serving as a refrigerant outlet when the utilization heat exchanger functions as an evaporator to have a dryness degree equal to or more than a predetermined value.
In the air conditioner achieving such control, the refrigerant flowing out of the outlet is further reduced in liquid volume to inhibit suction, into the compressor, of the refrigerant in an excessively damp state. Meanwhile, such control lowers cooling capacity in the heat transfer tube serving as a refrigerant outlet. Accordingly, passing air may not be cooled sufficiently depending on the position of the second region. In the utilization heat exchanger included in the air conditioner according to the present disclosure, the first region and the second region are inventively disposed such that passing air is cooled sufficiently, so as to achieve an object relevant to the control described above.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a configuration diagram of an air conditioner according to an embodiment.
FIG. 2 is a functional block diagram of the air conditioner according to the embodiment.
FIG. 3 is a pattern view depicting an internal structure of an indoor unit according to the embodiment.
FIG. 4 is a pattern view of a heat exchanger according to the embodiment.
FIG. 5 is a pattern view of another heat exchanger according to the embodiment.
FIG. 6 is a pattern view of a heat exchanger according to a comparative example and peripheral structures thereof.
FIG. 7 is a pattern view depicting an internal structure of an indoor unit according to a modification example.
FIG. 8 is a pattern view of a heat exchanger according to another modification example.

DETAILED DESCRIPTION

[Technical problem]

In a case where a heat exchanger functions as an evaporator, air moisture is typically condensed on a fin to remove moisture from air passing the heat exchanger. This inhibits dew condensation on a member (e.g. a fan) positioned leeward of the heat exchanger.
However, moisture may not be sufficiently removed from air passing the heat exchanger in a case where the heat exchanger includes a tube removed region. Air passing the tube removed region is not cooled sufficiently in comparison to air passing a region (heat transfer tube region) provided with a heat transfer tube. Accordingly, moisture is not sufficiently removed from air having mainly passed the tube removed region and almost having failed to pass the heat transfer tube region, and dew condensation may be caused on a member positioned leeward.
It is an object of the present disclosure to inhibit dew condensation on a member positioned leeward of a heat exchanger.
Embodiments of the present disclosure will be described hereinafter with reference to the accompanying drawings.

[Embodiments]

[Configuration of air conditioner 1]

FIG. 1 is a schematic configuration diagram of the air conditioner 1 according to an embodiment.
FIG. 2 is a functional block diagram of the air conditioner 1 according to the embodiment.

The air conditioner 1 will be described below in terms of its configuration with reference to FIG. 1 and FIG. 2.
The air conditioner 1 has a function of cooling and heating air in a room R1. The air conditioner 1 includes an indoor unit 2 located in the room R1, an outdoor unit 3 located outdoors, a refrigerant circuit 4 provided with a refrigerant circulating therein, and a control unit 5. Examples of the refrigerant include R32. The room R1 should not be particularly limited in terms of its use, and examples thereof can include a human living space (e.g. a house, a store, an office, or a factory), a warehouse storing food materials, and a space equipped with machinery and tools (e.g. a server).
The refrigerant circuit 4 includes a compressor 11, a switching mechanism 12, a heat source heat exchanger 13, a decompression mechanism 14, a utilization heat exchanger 15, and an accumulator 16. In a case where the heat source heat exchanger 13 in the refrigerant circuit 4 functions as a condenser (i.e. in a case where the air conditioner 1 executes cooling operation), the respective devices 11 to 16 are connected such that the refrigerant discharged from the compressor 11 flows in the switching mechanism 12, the heat source heat exchanger 13, the decompression mechanism 14, the utilization heat exchanger 15, the switching mechanism 12, and the accumulator 16 in the mentioned order to return to the compressor 11.
The control unit 5 includes an indoor control unit 5a and an outdoor control unit 5b connected to each other via a communication line. As depicted in FIG. 2, the indoor control unit 5a includes a processor 52a and a memory 53a. When the processor 52a executes arithmetic processing and control in various manners in accordance with a program in the memory 53a, the indoor control unit 5a controls respective parts included in the indoor unit 2. The outdoor control unit 5b includes a processor 52b and a memory 53b. When the processor 52b executes arithmetic processing and control in various manners in accordance with a program in the memory 53b, the outdoor control unit 5b controls respective parts included in the outdoor unit 3.
The outdoor unit 3 includes a case 31 provided with an intake port (not depicted) and an exhaust air port (not depicted). The case 31 accommodates the compressor 11, the switching mechanism 12, the heat source heat exchanger 13, and the accumulator 16 in the refrigerant circuit 4. The case 31 further accommodates the outdoor control unit 5b and an outdoor fan 32.
The compressor 11 is exemplarily of a variable capacity type, and has a rotation frequency controlled by an inverter in accordance with a behavior command from the control unit 5.
The switching mechanism 12 is configured to switch a flow direction of the refrigerant in the refrigerant circuit 4, and is exemplarily constituted by a four-way switching valve. The switching mechanism 12 is controlled by the control unit 5 so as to be switched between a first connection state (solid lines in FIG. 1) where the refrigerant discharged from the compressor 11 is sent to the heat source heat exchanger 13 and a second connection state (broken lines in FIG. 1) where the refrigerant discharged from the compressor 11 is sent to the utilization heat exchanger 15.
The heat source heat exchanger 13 is exemplarily of a cross-fin tube type.
The accumulator 16 is configured to separate the refrigerant into a gas refrigerant and a liquid refrigerant in order to protect the compressor 11.
Examples of the outdoor fan 32 include a propeller fan. When the outdoor fan 32 operates, outdoor air is sucked via the intake port (not depicted) of the case 31, and air having exchanged heat with the refrigerant in the heat source heat exchanger 13 is discharged to an outdoor space via the exhaust air port (not depicted) of the case 31.
The indoor unit 2 includes a case 21 provided with intake ports 26a and 26b (FIG. 3) and a blow-out port 26c (FIG. 3). The case 21 accommodates the decompression mechanism 14 and the utilization heat exchanger 15 in the refrigerant circuit 4. The case 21 further accommodates the indoor control unit 5a and an indoor fan 22.
The decompression mechanism 14 is exemplarily constituted by an electromagnetic valve (expansion valve), and controls pressure and a flow rate of the refrigerant flowing in the refrigerant circuit 4. The decompression mechanism 14 may be accommodated in the case 31 of the outdoor unit 3. The utilization heat exchanger 15 is exemplarily of a cross-fin tube type.
Examples of the indoor fan 22 include a cross-flow fan. When the indoor fan 22 operates, air in the room R1 is sucked via the intake ports 26a and 26b of the case 21, and conditioned air having exchanged heat with the refrigerant in the utilization heat exchanger 15 is supplied into the room R1 via the blow-out port 26c of the case 21.
The indoor unit 2 is provided with a remote control unit 51 (hereinafter, called a "remote controller 51"). The remote controller 51 is located in the room R1 in a state of being communicable wiredly or wirelessly with the indoor control unit 5a, and transmits a control signal to the indoor control unit 5a in accordance with user operation.

[Regarding operating mode]

The control unit 5 causes the air conditioner 1 to execute cooling operation or heating operation in accordance with a command received by the remote controller 51. During cooling operation, the control unit 5 brings the switching mechanism 12 into the first connection state (the solid lines in FIG. 1). The control unit 5 operates the compressor 11 in this state to achieves a refrigeration cycle in which the heat source heat exchanger 13 functions as a condenser and the utilization heat exchanger 15 functions as an evaporator.
In this cycle, the compressor 11 discharges a high-pressure refrigerant that passes the switching mechanism 12, enters the heat source heat exchanger 13, and exchanges heat with outdoor air to be condensed. The refrigerant thus condensed is decompressed while passing the decompression mechanism 14, and then enters the utilization heat exchanger 15 to exchange heat with air in the room R1 and be evaporated. The indoor fan 22 causes conditioned air cooled by the refrigerant to blow into the room R1. The refrigerant having exited the utilization heat exchanger 15 passes the switching mechanism 12 and enters the accumulator 16, to be separated into gas and liquid and be then sucked into the compressor 11.
The control unit 5 controls an opening degree of the decompression mechanism 14 during cooling operation. More specifically, when the utilization heat exchanger 15 functions as an evaporator, the control unit 5 controls the opening degree of the decompression mechanism 14 such that the refrigerant flowing out of a heat transfer tube 6 to be described later and serve as an outlet of the refrigerant in the utilization heat exchanger 15 has a dryness degree that is equal to or more than a predetermined value (e.g. equal to or more than 95%).
The control unit 5 controls the dryness degree to further reduce liquid volume of the refrigerant flowing out of the outlet of the utilization heat exchanger 15 toward the outdoor unit 3, so as to inhibit suction, into the compressor 11, of the refrigerant in an excessively damp state. Meanwhile, such control lowers cooling capacity in the heat transfer tube 6 serving as a refrigerant outlet. Accordingly, air passing the utilization heat exchanger 15 may not be cooled sufficiently depending on a position of a tube removed region (a second region B1, B2, or B3) to be described later. In the air conditioner 1 according to the present disclosure, a heat transfer tube region (a first region A1, A2, or A3) to be described later and the tube removed region (the second region B1, B2, or B3) are inventively disposed such that air passing the utilization heat exchanger 15 is cooled sufficiently, so as to achieve an object relevant to the control described above.
During heating operation, the control unit 5 brings the switching mechanism 12 into the second connection state (the broken lines in FIG. 1). The control unit 5 operates the compressor 11 in this state to achieves a refrigeration cycle in which the heat source heat exchanger 13 functions as an evaporator and the utilization heat exchanger 15 functions as a condenser.
In this cycle, the compressor 11 discharges a high-pressure refrigerant that passes the switching mechanism 12, enters the utilization heat exchanger 15, and exchanges heat with air in the room R1 to be condensed. The indoor fan 22 causes conditioned air heated by the refrigerant to blow into the room R1. The refrigerant thus condensed is decompressed while passing the decompression mechanism 14, and then enters the heat source heat exchanger 13 to exchange heat with outdoor air and be evaporated. The refrigerant having exited the heat source heat exchanger 13 passes the switching mechanism 12 and enters the accumulator 16, to be separated into gas and liquid and be then sucked into the compressor 11.

[Internal structure of indoor unit 2]

FIG. 3 is a pattern view depicting an internal structure of the indoor unit 2 according to the embodiment. FIG. 3 includes hatched portions depicted as sections. The indoor unit 2 according to the present embodiment is of a wall mounted type, and is located on an upper portion of a side wall of the room R1 or the like.
In the following description, an indoor end of the side wall provided with the indoor unit 2 will correspond to a "front end" of the indoor unit 2, and an end opposite to the front end will correspond to a "rear end" of the indoor unit 2, where appropriate. A left end in FIG. 3 corresponds to the "front end" and a right end in FIG. 3 corresponds to the "rear end". Furthermore, a perpendicularly upper end corresponds to an "upper end" of the indoor unit 2, and also corresponds to an upper end in FIG. 3. A perpendicularly lower end corresponds to a "lower end" of the indoor unit 2, and also corresponds to a lower end in FIG. 3. A direction orthogonal to an anteroposterior direction and a vertical direction corresponds to a transverse direction. A "right end" of the indoor unit 2 corresponds to a far end of a sheet of FIG. 3, and a "left end" of the indoor unit 2 corresponds to a near end of the sheet of FIG. 3.
The utilization heat exchanger 15 includes a heat exchanger 15a located in front of the indoor fan 22, and a heat exchanger 15b located behind the indoor fan 22.
The case 21 includes a front panel 21a, a top panel 21b, a back panel 21c, a first accommodation panel 21d, a second accommodation panel 21e, and a flow path bottom plate 21f. The front panel 21a is a plate-shaped member covering front ends of the utilization heat exchanger 15 and the indoor fan 22. The front panel 21a is provided with a front intake port 26a.
The top panel 21b is a plate-shaped member covering upper ends of the utilization heat exchanger 15 and the indoor fan 22. The top panel 21b is equipped with a grill 23 that is provided with the top intake port 26b. Each of the front intake port 26a and the top intake port 26b may also be called an "intake port". The back panel 21c is a plate-shaped member covering rear ends of the utilization heat exchanger 15 and the indoor fan 22.
The first accommodation panel 21d is a plate-shaped member accommodating the heat exchanger 15a from below. The first accommodation panel 21d and the heat exchanger 15a interpose a drain pan 24a. The drain pan 24a is a gutter-shaped member configured to collect condensate generated in the heat exchanger 15a.
The second accommodation panel 21e is a plate-shaped member accommodating the heat exchanger 15b from below. The second accommodation panel 21e and the heat exchanger 15b interpose a drain pan 24b. The drain pan 24b is a gutter-shaped member configured to collect condensate generated in the heat exchanger 15b.
The flow path bottom plate 21f is a plate-shaped member extending obliquely forward and downward from behind the indoor fan 22. A lower surface of the first accommodation panel 21d an upper surface of the flow path bottom plate 21f form a flow path of air blowing out of the indoor fan 22. The flow path has an outlet serving as the blow-out port 26c of the case 21.
The case 21 is provided with a flap 25. The flap 25 is adjusted in terms of its inclination angle to shut off or open the blow-out port 26c. The inclination angle of the flap 25 also leads to adjustment of a blow-out direction of conditioned air. FIG. 3 exemplarily depicts the indoor unit 2 including two flaps 25, although the indoor unit 2 should not be limited in terms of the number of the flaps 25.
In a state where the blow-out port 26c is opened, the indoor fan 22 rotates to exemplarily generate air flows F1 to F4. The air flow F1 flows out of the front intake port 26a, passes the heat exchanger 15a, and flows toward the indoor fan 22. The air flow F2 flows out of the top intake port 26b, passes the heat exchanger 15a, and flows toward the indoor fan 22. The air flow F3 flows out of the top intake port 26b, passes the heat exchanger 15b, and flows toward the indoor fan 22. The air flow F4 flows out of the indoor fan 22, passes the blow-out port 26c, and is sent indoors.

[Configuration of heat exchanger 15a]

FIG. 4 is an enlarged pattern view of the heat exchanger 15a depicted in FIG. 3. The heat exchanger 15a is of a so-called fin-and-tube type, and includes a heat transfer tube 6 and a fin 7. The heat transfer tube 6 is a metal pipe allowing the refrigerant to flow therethrough. The fin 7 is a plate-shaped member having a thickness direction matching the transverse direction, and is exemplarily made of an aluminum metal plate. There is provided a plurality of fins 7 stacked in the transverse direction at predetermined pitches.
In the following description, a direction of air flowing from a windward side to a leeward side will be called a "first direction". Furthermore, a direction crossing the first direction will be called a "second direction". The second direction is more specifically orthogonal to the first direction. The first direction is dependent on an air flow direction, so that each of the fins 7 may have regions different in first direction. For example, in a region of the fin 7 where the air flow F1 flows in, the first direction corresponds to a direction from front to behind (from left to right in FIG. 4). Furthermore, in a region of the fin 7 where the air flow F2 flows in, the first direction corresponds to an obliquely backward and downward direction from front (obliquely rightward and downward from left in FIG. 4).
The fin 7 has a narrow portion 7a having a smaller width than an average width in the first direction. The narrow portion 7a is provided in a vertically center portion of the fin 7. In the fin 7, a region below the narrow portion 7a will be called a fin lower portion P1, and a region above the narrow portion 7a will be called a fin upper portion P2. The narrow portion 7a is a bent portion where the fin 7 is bent in the first direction. The fin upper portion P2 is inclined leeward from the fin lower portion P1.
The fin lower portion P1 has a center line L1 in the first direction, and the center line L1 extends substantially along the vertical direction. The center line L1 extends in a direction that matches a longitudinal direction of the fin lower portion P1 and corresponds to the second direction in the fin lower portion P1. The fin upper portion P2 has a center line L2 in the first direction, and the center line L2 extends obliquely downward and forward from above. The center line L2 extends in a direction that matches a longitudinal direction of the fin upper portion P2 and corresponds to the second direction in the fin upper portion P2.
The fin 7 is provided with a plurality of through holes 70 allowing penetration by the heat transfer tube 6. FIG. 4 exemplarily depicts the fin 7 provided with 16 through holes 70, although the through holes 70 should not be particularly limited in terms of the number. The fin 7 has an inner circumferential portion provided with the plurality of through holes 70, and the inner circumferential portion may be provided with a collar fixing the heat transfer tube 6 penetrating the through hole 70.
The plurality of through holes 70 forms a plurality of columns in the second direction. FIG. 4 exemplarily depicts the plurality of through holes 70 aligned in two columns, namely, in a windward column and a leeward column each constituted by eight through holes. The plurality of through holes 70 included in the windward column is disposed to be staggered with respect to the plurality of through holes 70 included in the leeward column. The through holes disposed in this manner allows air passing the heat exchanger 15a to be evenly cooled.
More specifically, the plurality of through holes 70 included in the windward column has centers not overlapped in the first direction with centers of the plurality of through holes 70 included in the leeward column. As exemplarily depicted in FIG. 4, a virtual line C1, which passes a center of an appropriate one of the through holes 70 in the windward column and extends in the first direction, passes between two through holes 70 and 70 included in the leeward column (more specifically, a midpoint of a line segment connecting centers of the two through holes 70 and 70). A virtual line C2, which passes an appropriate one of the through holes 70 in the leeward column and extends in the first direction, passes between two through holes 70 and 70 included in the windward column. In this manner, the through holes 70 in the windward column and the leeward column are alternately disposed.
The plurality of through holes 70 includes a first through hole 71 penetrated by the heat transfer tube 6 and a second through hole 72 not penetrated by any heat transfer tube 6. FIG. 4 exemplifies a case where eight through holes 70 included in the fin lower portion P1 each correspond to the first through hole 71. Eight through holes 70 included in the fin upper portion P2 include six first through holes 71 and two second through holes 72.
The fin 7 includes the first region A1 where a plurality of first through holes 71 is aligned in the second direction, and the second region B1 where a plurality of (two exemplarily depicted in FIG. 4) second through holes 72 is aligned in the second direction. FIG. 4 exemplarily depicts four regions A11 to A14 each corresponding to the first region A1.
The region A11 is located in a windward upper portion of the fin upper portion P2 and includes two aligned first through holes 71. The region A12 is located in a leeward portion of the fin upper portion P2 and includes four aligned first through holes 71. The region A13 is located in a windward portion of the fin lower portion P1 and includes four aligned first through holes 71. The region A14 is located in a leeward portion of the fin lower portion P1 and includes four aligned first through holes 71.
The second region B1 has an opened windward side and is surrounded with the first region A1. More specifically, the second region B1 has a leeward side adjacent to the first region A1 (the region A12) and respective ends in the second direction adjacent to the first region A1 (the regions A11 and A13).

[Configuration of heat exchanger 15b]

FIG. 5 is an enlarged pattern view of the heat exchanger 15b depicted in FIG. 3. The heat exchanger 15b includes portions that are configured similarly to the heat exchanger 15a, are denoted by identical reference signs, and will not be described repeatedly.
The heat exchanger 15b includes a heat transfer tube 6 and a fin 7. The fin 7 in the heat exchanger 15b has a center line L3 in the first direction, and the center line L3 extends in the second direction. The fin 7 is provided with the plurality of through holes 70. FIG. 5 exemplarily depicts the plurality of through holes 70 aligned in two columns, namely, in a windward column and a leeward column each constituted by six through holes.
The plurality of through holes 70 in the heat exchanger 15b includes a first through hole 71 and a second through hole 72. FIG. 5 exemplifies a case where six through holes 70 included in the windward column each correspond to the first through hole 71. Furthermore, in the leeward column, two upper and two lower through holes 70 each correspond to the first through hole 71, and two central through holes 70 each correspond to the second through hole 72.
The fin 7 of the heat exchanger 15b includes the first region A2 where a plurality of first through holes 71 is aligned in the second direction, and the second region B2 where a plurality of second through holes 72 is aligned in the second direction. FIG. 5 exemplarily depicts three regions A21 to A23 each corresponding to the first region A2.
The region A21 is located in a leeward upper portion of the fin 7 and includes two aligned first through holes 71. The region A22 is located in a leeward lower portion of the fin 7 and includes two aligned first through holes 71. The region A23 is located in a windward portion of the fin 7 and includes six aligned first through holes 71.
The second region B2 has an opened leeward side and is surrounded with the first region A2. More specifically, the second region B2 has a windward side adjacent to the first region A2 (the region A23) and respective ends in the second direction adjacent to the first region A2 (the regions A21 and A22).

[Comparative example and its problem]

FIG. 6 is a pattern view of a heat exchanger 15c according to a comparative example and peripheral structures thereof. The heat exchanger 15c exemplifies a case different from the heat exchanger 15b (FIG. 5) in terms of disposition of the first through holes 71 and the second through holes 72. FIG. 6 depicts configurations that are similar to those according to the embodiment, are denoted by identical reference signs, and will not be described repeatedly. The object to be achieved by the present disclosure will be described in more detail with reference to FIG. 6.
For production of different types of heat exchangers with reduced production cost of the fin 7 or the like, there may be produced a heat exchanger including the fin 7 having all through holes 70 each penetrated by the heat transfer tube 6 and a heat exchanger including the fin 7 shaped identically and having a plurality of through holes 70 some of which is penetrated by heat transfer tube 6 and remaining ones of the through holes 70 are not penetrated by heat transfer tube 6. The heat exchanger 15c according to the comparative example includes a reduced number of heat transfer tubes 6 penetrating the through holes 70 in order to reduce production cost (such a process of reducing the number will be called tube removal). The fin 7 according to the comparative example thus includes first regions A91 and A92 (i.e. heat transfer tube regions), and a second region B9 (i.e. tube removed region).
In a case where the heat exchanger 15c functions as an evaporator, air moisture is typically condensed on the fin 7 to remove moisture from air passing the heat exchanger 15c. The moisture condensed on the fin 7 is collected on the drain pan 24b. This allows to dry air flowing leeward from the heat exchanger 15c so as to inhibit dew condensation on a member (e.g. the indoor fan 22) positioned leeward of the heat exchanger 15c.
However, moisture may not be sufficiently removed from air passing the heat exchanger 15c in a case where the heat exchanger 15c includes the second region B9. Air passing the second region B9 is not cooled sufficiently in comparison to air passing the first region A91 or A92 provided with the heat transfer tube 6. Accordingly, moisture is not sufficiently removed from air having mainly passed the second region B9 and almost having failed to pass the first region A91 or A92, and relatively wet air flowing leeward may cause dew condensation on a member positioned leeward.
According to the comparative example, the first region A91 is disposed leeward of the second region B9. In such a configuration, an air flow F91 linearly passing across width of the fin 7 passes the second region B9 and then passes the first region A91 so as to achieve removal of moisture from the air flow F91. The air flow F91 is called a "laminar flow", a "main flow", or the like, and passes from the intake port 26b toward the indoor fan 22 linearly and stably (i.e. in a relatively short distance). The "first direction" according to the present disclosure indicates such a direction of the main flow.
Meanwhile, the fin 7 has a lower end that has a slow air flow due to the second accommodation panel 21e and the drain pan 24b and is likely to cause turning air. As indicated in FIG. 6, the lower end of the fin 7 may thus have an air flow F92 passing from the intake port 26b toward the indoor fan 22 while largely detouring around the lower end of the fin 7. The air flow F92 is called a "turbulent flow", a "bypass flow", or the like, and passes obliquely with respect to the air flow F91 (in the first direction).
FIG. 6 exemplifies a case where the air flow F92 passes the second region B9 at the lower end of the fin 7 and then reaching the indoor fan 22 while almost failing to pass the first region A91. Accordingly, moisture cannot be sufficiently removed from the air flow F92. In such a case where the second region B9 is provided at an end (upper end or lower end) in the second direction of the fin 7, the air flow F92 flowing obliquely with respect to the main flow cannot have sufficient moisture removal, and moisture contained in the air flow F92 may cause dew condensation on a member positioned leeward of the heat exchanger 15c.

[Characteristics of

heat exchangers

15a and 15b]

Refer to FIG. 4 and FIG. 5. In the heat exchanger 15a or 15b, the second region B1 or B2 (tube removed region) is surrounded with the first region A1 or A2 (heat transfer tube region) with the windward side or the leeward side being opened. That is, the first region A1 or A2 is positioned adjacent to the respective ends (an upper end and a lower end) in the second direction of the second region B 1 or B2, and the first region A1 or A2 is positioned also windward or leeward of the second region B1 or B2.
Such a configuration allows the first region A1 or A2 to more reliably cool air having passed (or being subject to pass) the second region B1 or B2. The heat exchanger 15a or 15b can thus have more reliable dew condensation to sufficiently dry air flowing leeward from the heat exchanger 15a or 15b, for inhibition of dew condensation on a member positioned leeward of the heat exchanger 15a or 15b.
More specifically, the first region A1 or A2 adjacent in the first direction to the second region B1 or B2 has respective ends in the second direction positioned outside respective ends in the second direction of the second region B1 or B2. As exemplarily depicted in FIG. 4, the first region A1 (the region A12 or A14) provided adjacent to a leeward side of the second region B1 has an upper end in the second direction positioned above an upper end in the second direction of the second region B 1, and the first region A1 (the region A12 or A14) provided adjacent to the leeward side of the second region B1 has a lower end in the second direction positioned below a lower end in the second direction of the second region B1.
In such a configuration, even in a case where air obliquely passes the second region B1 or B2, air having passed (or being subject to pass) the second region B1 or B2 more reliably passes the first region A1 or A2 because the first region A1 or A2 longer in the second direction than the second region B1 or B2 covers the second region B1 or B2. Such obliquely passing air can thus be cooled more reliably, to inhibit dew condensation on a member positioned leeward of the heat exchanger 15a or 15b.
The heat exchangers 15a and 15b will be described in terms of more characteristics with reference to FIG. 4 and FIG. 5. The first through holes 71 include an outlet through hole 73 and an inlet through hole 75. The outlet through hole 73 corresponds to the first through hole 71 penetrated by the heat transfer tube 6 serving as a refrigerant outlet when the heat exchanger 15a or 15b functions as an evaporator. In each of FIG. 4 and FIG. 5, the outlet through hole 73 is denoted by an arrowhead sign (black point mark).
The outlet through hole 73 is positioned adjacent in the first direction to the first region A1 or A2. When the heat exchanger 15a or 15b functions as an evaporator, the refrigerant flowing in the heat transfer tube 6 serving as a refrigerant outlet is mostly (or entirely) in a gas state. Accordingly, the heat transfer tube 6 serving as a refrigerant outlet has almost no room for heat absorption from air and refrigerant evaporation, failing to sufficiently cool passing air.
The present embodiment provides the outlet through hole 73 positioned adjacent in the first direction to the first region A1 or A2, so that the adjacent first region A1 or A2 more reliably cools air not cooled sufficiently and having passed (or being subject to pass) the outlet through hole 73 and the vicinity thereof. The heat exchanger 15a or 15b can thus have more reliable dew condensation to inhibit dew condensation on a member positioned leeward of the heat exchanger 15a or 15b.
Specifically as depicted in FIG. 4, the outlet through hole 73 in the region A11 is disposed adjacent to a windward side of the region A12, and the outlet through hole 73 in the region A13 is disposed adjacent to a windward side of the region A14. If the heat transfer tube 6 having low cooling capacity is provided windward and the heat transfer tube 6 having high cooling capacity (the heat transfer tube 6 other than the heat transfer tube 6 serving as a refrigerant outlet) is provided leeward, passing air is gradually cooled to achieve higher cooling efficiency in comparison to a case of disposition in an inverted order. The outlet through hole 73 is penetrated by the heat transfer tube 6 having low cooling capacity, and is thus provided windward of a different one of the first regions A1 for enhanced air cooling efficiency.
The inlet through hole 75 corresponds to the first through hole 71 penetrated by the heat transfer tube 6 serving as a refrigerant inlet when the heat exchanger 15a or 15b functions as an evaporator. In each of FIG. 4 and FIG. 5, the inlet through hole 75 is denoted by an arrow feather sign ("X" mark).
In each of the region A12 (FIG. 4) and the region A21 (FIG. 5), the inlet through hole 75 is provided in a region having air flow speed of air passing the heat exchanger 15a or 15b higher than average air flow speed, and in the leeward column. FIG. 4 depicts, as a region D1, a region mainly receiving the air flow F1 or F2 and having air flow speed higher than the average air flow speed. FIG. 4 further depicts, as a region D2, a region having a flow blocked by the first accommodation panel 21d or the like and air flow speed lower than the average air flow speed. As depicted in FIG, 4, the inlet through hole 75 in the region A12 is included in the region D1.
When the heat exchanger 15a or 15b functions as an evaporator, the refrigerant flowing in the heat transfer tube 6 serving as a refrigerant inlet is mostly (or entirely) in a liquid state. Accordingly, the heat transfer tube 6 serving as a refrigerant inlet is likely to allow the refrigerant to absorb heat from air and evaporate, for preferable cooling of passing air. The inlet through hole 75 thus corresponds to a region most likely to be cooled when the heat exchanger 15a or 15b functions as an evaporator. The inlet through hole 75 is provided in the region having air flow speed higher than the average air flow speed (i.e. a region having large air flow volume) to achieve enhanced air cooling efficiency. The inlet through hole 75 is provided in the leeward column to gradually cool passing air, for further enhanced air cooling efficiency.
Moreover, the inlet through hole 75 is positioned adjacent in the first direction or the second direction to the second region B1 or B2, so as to more reliably cool air passing the second through hole 72 and the vicinity thereof. FIG. 4 exemplifies the inlet through hole 75 included in the region A12 is adjacent to the second region B1 in the first direction. FIG. 5 exemplifies the inlet through hole 75 included in the region A21 is adjacent to the second region B2 in the second direction.
As depicted in FIG. 4, the plurality of through holes 70 includes a narrow portion through hole 74 that is provided closest to the narrow portion 7a and corresponds to the first through hole 71. The narrow portion 7a has narrow width and is thus lower in cooling capacity than the remaining portion of the fin 7. When the narrow portion through hole 74 provided closest to the narrow portion 7a corresponds to the first through hole 71 (the through hole 70 penetrated by the heat transfer tube 6), air passing such a portion can be cooled more reliably.
Furthermore, the narrow portion through hole 74 corresponds to the inlet through hole 75 as depicted in FIG. 4. As described above, the inlet through hole 75 corresponds to the region most likely to be cooled when the heat exchanger 15a or 15b functions as an evaporator. The inlet through hole 75 is provided in the narrow portion 7a having low cooling capacity to compensate such low cooling capacity in the narrow portion 7a. This enables more reliable cooling of air passing the narrow portion 7a.
The narrow portion through hole 74 is positioned adjacent to the leeward side of the second region B1. The narrow portion through hole 74 corresponds to the inlet through hole 75, so as to preferably cool air passing the narrow portion through hole 74 and the vicinity thereof. Accordingly, the narrow portion through hole 74 is positioned adjacent to the leeward side of the second region B1, so that the heat transfer tube 6 penetrating the narrow portion through hole 74 more reliably cools air having passed the second region B1 and the vicinity thereof and not cooled sufficiently.
FIG. 4 depicts the narrow portion through hole 74 positioned leeward of the second region B1. The narrow portion through hole 74 may alternatively be positioned windward of the second region B1. That is, the narrow portion through hole 74 corresponding to the inlet through hole 75 has only to be positioned adjacent to the second region B1 in the first direction.

[Modification examples]

The present disclosure should not be limited to the embodiment described above, and can be modified variously. In the following modification examples, components configured similarly to the components according to the above embodiment will be denoted by identical reference signs and will not be described repeatedly where appropriate.

[Indoor unit according to modification example]

FIG. 7 is a pattern view depicting an internal structure of an indoor unit 2a according to a modification example. The indoor unit 2a is of a ceiling embedded type, and is embedded in a ceiling of the room R1 (FIG. 1) or the like. The indoor unit according to the present disclosure should not be limited in terms of a locating manner in the room R1, and may correspond to the indoor unit 2 of the wall mounted type as in FIG. 3, the indoor unit 2a of the ceiling embedded type as in FIG. 7, or an indoor unit (not depicted) of a ceiling pendent type or a floorstanding type.
The indoor unit 2a includes the case 21, and the indoor fan 22 and a heat exchanger 15d accommodated in the case 21. The heat exchanger 15d functions as the utilization heat exchanger 15 in the air conditioner 1 (FIG. 1). An air flow F5 blowing out of the indoor fan 22 passes the heat exchanger 15d.
The heat exchanger 15d includes the heat transfer tube 6 and a fin 7b. The fin 7b is provided with through holes 70 in three columns with respect to the first direction in which the air flow F5 passes. That is, the through holes 70 are provided in the three columns in the second direction crossing the first direction (a direction crossing the air flow F5). The through holes 70 in the fin 7b should not be limited in terms of the number of columns, and may alternatively be provided in the three columns with respect to the first direction, or in four or more columns with respect to the first direction.
The plurality of through holes 70 includes a first through hole 71 penetrated by the heat transfer tube 6 and a second through hole 72 not penetrated by any heat transfer tube 6. That is, the heat transfer tubes 6 are removed from some of the plurality of through holes 70. In the fin 7b, ten through holes 70 positioned in the most windward column each correspond to the first through hole 71, whereas ten through holes 70 positioned in the most leeward column each correspond to the second through hole 72. Furthermore, in ten through holes 70 positioned in the middle column in the first direction, four through holes from an upper end each correspond to the first through hole 71, next two through holes each correspond to the second through hole 72, subsequent two through holes each correspond to the first through hole 71, and remaining two through holes each correspond to the second through hole 72.
As depicted in FIG. 7, the second region B3 including the second through holes 72 aligned in the second direction is surrounded with the first region A3 including the first through holes 71 aligned in the second direction. More specifically, the second region B3 has a windward side adjacent to the first region A3 (a region A32) and respective ends in the second direction adjacent to the first region A3 (regions A31 and A33). Such a configuration allows the first region A3 to more reliably cool air being subject to pass the second region B3.

[Heat exchanger according to modification example]

FIG. 8 is a pattern view of a heat exchanger 15e according to a modification example. The heat exchanger 15e is according to a further modification example of the heat exchanger 15d (FIG. 7) according to the modification example. The heat exchanger 15e includes the heat transfer tube 6 and a fin 7c. The fin 7c is provided with through holes 70 in three columns with respect to the first direction in which the air flow F5 passes.
The plurality of through holes 70 includes the first through hole 71 and the second through hole 72. In the fin 7c, sixteen through holes 70 positioned in the most windward column each correspond to the first through hole 71. In sixteen through holes 70 positioned in the middle column in the first direction, two through holes from an upper end each correspond to the first through hole 71, next three through holes each correspond to the second through hole 72, subsequent two through holes each correspond to the first through hole 71, following two through holes each correspond to the second through hole 72, and remaining seven through holes each correspond to the first through hole 71. In sixteen through holes 70 positioned in the most leeward column, two through holes from an upper end each correspond to the first through hole 71, next three through holes each correspond to the second through hole 72, subsequent five through holes each correspond to the first through hole 71, following four through holes each correspond to the second through hole 72, and remaining two through holes each correspond to the first through hole 71.
The fin 7c includes a first region A4 where a plurality of first through holes 71 is aligned in the second direction, and a second region B4 where a plurality of second through holes 72 is aligned in the second direction. FIG. 8 exemplarily depicts six regions A41 to A46 each corresponding to the first region A4, and three regions B41 to B43 each corresponding to the second region B4.
As depicted in FIG. 8, the second region B4 is surrounded with the first region A4. FIG. 8 depicts various variations where the second region B4 is surrounded with the first region A4. For example, the region B41 has an opened leeward side, a windward side adjacent to the region A42, and respective ends in the second direction adjacent to the regions A41 and A43.
Even in such a case where there is provided the second region B4 (the region B41) having two columns with respect to the first direction, the second region B4 has the respective ends in the second direction adjacent to the regions A41 and A43 having two columns so as to be surrounded therewith, to allow the first region A4 to more reliably cool air being subject to pass the second region B4.
The region B42 has a windward side adjacent to the region A42, a leeward side adjacent to the region A44, and respective ends in the second direction adjacent to the regions A43 and A45. The region B42 has respective ends in the first direction and respective ends in the second direction surrounded with the first region A4, so as to more reliably cool air passing the second region B4.
The region B43 has an opened leeward side, a windward side adjacent to the region A45, and respective ends in the second direction adjacent to the regions A44 and A46. In particular, the first region A4 having two columns corresponding to the regions A42 and A45 is positioned windward of the region B43, so as to more reliably cool air passing in the first direction.

[Others]

At least parts of the embodiments and the modification examples described above may be appropriately combined together.

[Functional effects of embodiments]

(1) The embodiment provides the heat exchanger 15a, 15b, 15d, 15e including: the heat transfer tube 6 allowing the refrigerant to flow; and the fin 7, 7b, 7c provided with the plurality of through holes 70 each allowing penetration of the heat transfer tube 6 in the thickness direction; in which the plurality of through holes 70 is aligned in the plurality of columns in the second direction crossing the first direction of air flowing from the windward side toward the leeward side, and includes first through holes 71 each penetrated by the heat transfer tube 6 and second through holes 72 not penetrated by the heat transfer tube 6, the fin 7 includes the first region A1, A2, A3, A4 having the first through holes 71 aligned in the second direction, and the second region B1, B2, B3, B4 having the second through holes 72 aligned in the second direction, and the second region B1, B2, B3, B4 has the end or respective ends in the first direction adjacent to the first region A1, A2, A3, A4, and respective ends in the second direction adjacent to the first region A1, A2, A3, A4.

The second regions B1, B2, B3, and B4 (the tube removed regions) includes the second through holes 72 not penetrated by the heat transfer tubes 6 and aligned in the second direction. Air passing the second region B1, B2, B3, or B4 is thus not cooled sufficiently in comparison to air passing the first region A1, A2, A3, or A4 (the heat transfer tube region). The present disclosure provides the second regions B1, B2, B3, and B4 surrounded with the first regions A1, A2, A3, and A4 in the first direction and the second direction, so that the first region A1, A2, A3, or A4 more reliably cools air having passed (or being subject to pass) the second region B1, B2, B3, or B4. The heat exchanger 15a, 15b, 15d, or 15e can thus have more reliable dew condensation to inhibit dew condensation on a member positioned leeward of the heat exchanger 15a, 15b, 15d, or 15e.
(2) According to the embodiment, the first through holes 71 includes the outlet through hole 73 penetrated by the heat transfer tube 6 serving as the refrigerant outlet when the heat exchanger 15a, 15b functions as the evaporator, and the outlet through hole 73 is positioned adjacent in the first direction to the first region A1, A2.
When the heat exchanger 15a or 15b functions as an evaporator, the refrigerant flowing in the heat transfer tube 6 serving as a refrigerant outlet is mostly (or entirely) in a gas state. Accordingly, the heat transfer tube 6 has almost no room for heat absorption from air and refrigerant evaporation, failing to sufficiently cool passing air. The outlet through hole 73 penetrated by the heat transfer tube 6 is positioned adjacent in the first direction to the first region A1 or A2, so that the adjacent first region A1 or A2 more reliably cools air not cooled sufficiently and having passed (or being subject to pass) the outlet through hole 73 and the vicinity thereof. The heat exchanger 15a or 15b can thus have more reliable dew condensation to inhibit dew condensation on a member positioned leeward of the heat exchanger 15a or 15b.
(3) According to the embodiment, the outlet through hole 73 is positioned adjacent to the windward side of the first region A1.
If the heat transfer tube 6 having low cooling capacity is provided windward and the heat transfer tube 6 having high cooling capacity is provided leeward, passing air is gradually cooled to achieve higher cooling efficiency in comparison to a case of disposition in an inverted order. The outlet through hole 73 is penetrated by the heat transfer tube 6 having low cooling capacity, and is thus provided windward of a different one of the first regions A1 for enhanced air cooling efficiency.
(4) In the fin 7 according to the embodiment, the plurality of through holes 70 included in the column on the windward side is disposed to be staggered with respect to the plurality of through holes 70 included in the column on the leeward side.
The plurality of through holes 70 disposed to be staggered allows passing air to be evenly cooled.
(5) According to the embodiment, the fin 7 includes the narrow portion 7a having the smaller width than the average width in the first direction, and the plurality of through holes 70 includes the narrow portion through hole 74 provided closest to the narrow portion 7a and corresponding to the first through hole 71.
The narrow portion 7a is lower in cooling capacity than the remaining portion of the fin 7. When the narrow portion through hole 74 provided closest to the narrow portion 7a corresponds to the first through hole 71 (the through hole 70 penetrated by the heat transfer tube 6), air passing such a portion can be cooled more reliably.
(6) According to the embodiment, the narrow portion 7a is the bent portion where the fin 7 is bent in the first direction.
(7) According to the embodiment, the first through holes 71 include the inlet through hole 75 penetrated by the heat transfer tube 6 serving as the refrigerant inlet when the heat exchanger 15a functions as the evaporator, and the narrow portion through hole 74 corresponds to the inlet through hole 75.
When the heat exchanger 15a functions as an evaporator, the refrigerant flowing in the heat transfer tube 6 serving as a refrigerant inlet is mostly (or entirely) in a liquid state. Accordingly, the heat transfer tube 6 is likely to allow the refrigerant to absorb heat from air and evaporate, for preferable cooling of passing air. The inlet through hole 75 penetrated by the heat transfer tube 6 is provided in the narrow portion 7a having low cooling capacity to compensate such low cooling capacity in the narrow portion 7a. This enables more reliable cooling of air passing the narrow portion 7a.
(8) According to the embodiment, the narrow portion through hole 74 is positioned adjacent in the first direction to the second region B1.
The narrow portion through hole 74 corresponds to the inlet through hole 75, so as to preferably cool air passing the narrow portion through hole 74 and the vicinity thereof. Accordingly, the narrow portion through hole 74 is positioned adjacent in the first direction to the second region B1, so that the heat transfer tube 6 penetrating the narrow portion through hole 74 more reliably cools air having passed (or being subject to pass) the second region B1 and the vicinity thereof and not cooled sufficiently.
(9) According to the embodiment, the first through holes 71 include the inlet through hole 75 penetrated by the heat transfer tube 6 serving as the refrigerant inlet when the heat exchanger 15a functions as the evaporator, and the inlet through hole 75 is provided in the region where air passing the heat exchanger 15 has air flow speed higher than average air flow speed, and in the column on the leeward side.
The inlet through hole 75 penetrated by the heat transfer tube 6 serving as a refrigerant inlet and constituting a region most likely to be cooled is provided in the region having air flow speed higher than the average air flow speed (i.e. a region having large air flow volume) to achieve enhanced air cooling efficiency. The inlet through hole 75 is provided in the column on the leeward side to gradually cool passing air, for further enhanced air cooling efficiency.
(10) The embodiment provides the air conditioner 1 including the refrigerant circuit 4 including the compressor 11, the heat source heat exchanger 13, the decompression mechanism 14, and the utilization heat exchanger 15 connected in the mentioned order, in which the utilization heat exchanger 15 includes the heat exchanger 15a, 15b, 15d, 15e according to any one of claims 1 to 9.
(11) The air conditioner 1 according to the embodiment further includes the control unit 5 configured to control the opening degree of the decompression mechanism 14, in which the control unit 5 controls the opening degree to cause the refrigerant flowing out of the heat transfer tube 6 serving as the refrigerant outlet when the utilization heat exchanger 15 functions as the evaporator to have the dryness degree equal to or more than the predetermined value.
In the air conditioner 1 achieving such control, the refrigerant flowing out of the outlet is further reduced in liquid volume to inhibit suction, into the compressor 11, of the refrigerant in an excessively damp state. Meanwhile, such control lowers cooling capacity in the heat transfer tube 6 serving as a refrigerant outlet. Accordingly, passing air may not be cooled sufficiently depending on the position of the second region B 1, B2, B3, or B4. In the utilization heat exchanger 15 included in the air conditioner 1 according to the present disclosure, the first region A1, A2, A3, or A4 and the second region B1, B2, B3, or B4 are inventively disposed such that passing air is cooled sufficiently, so as to achieve an object relevant to the control described above.

[Supplementary note]

The embodiments have been described above. Various modifications to modes and details should be available without departing from the object and the scope of the claims.

REFERENCE SIGNS LIST

1: air conditioner
11: compressor
12: switching mechanism
13: heat source heat exchanger
14: decompression mechanism
15: utilization 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: case
21a: front panel
21b: top panel
21c: back panel
21d: first accommodation panel
21e: second accommodation panel
21f: flow path bottom plate
22: indoor fan
23: grill
24a: drain pan
24b: drain pan
25: flap
26a: front intake port
26b: top intake port
26c: blow-out port
3: outdoor unit
31: case
32: outdoor fan
4: refrigerant circuit
5: control unit
5a: indoor control unit
5b: outdoor control unit
51: remote control unit (remote controller)
52a: processor
52b: processor
53a: memory
53b: memory
6: heat transfer tube
7: fin
7b: fin
7c: fin
7a: narrow portion
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 portion
P2: fin upper portion
L1: center line
L2: center line
L3: center line
C1: virtual line
C2: virtual line
D1: region
D2: region
A1: first region
A2: first region
A3: first region
A4: first region
A91: first region
A92: first region
B1: second region
B2: second region
B3: second region
B4: second region
B9: second region
A11: region
A12: region
A13: region
A14: region
A21: region
A22: region
A23: region
A31: region
A32: region
A33: region
A41: region
A42: region
A43: region
A44: region
A45: region
A46: region
B41: region
B42: region
B43: region
F1: air flow
F2: air flow
F3: air flow
F4: air flow
F5: air flow
F91: air flow
F92: air flow

Claims

A heat exchanger (15a, 15b, 15d, 15e) comprising:
a heat transfer tube (6) allowing a refrigerant to flow; and

a fin (7, 7b, 7c) provided with a plurality of through holes (70) each allowing penetration of the heat transfer tube (6) in a thickness direction, wherein

the plurality of through holes (70)
is aligned in a plurality of columns in a second direction crossing a first direction of air flowing from a windward side toward a leeward side, and

includes first through holes (71) each penetrated by the heat transfer tube (6) and second through holes (72) not penetrated by the heat transfer tube (6),

the fin (7) includes
a first region (A1, A2, A3, A4) having the first through holes (71) aligned in the second direction, and

a second region (B1, B2, B3, B4) having the second through holes (72) aligned in the second direction, and

the second region (B1, B2, B3, B4) has an end or respective ends in the first direction adjacent to the first region (A1, A2, A3, A4), and respective ends in the second direction adjacent to the first region (A1, A2, A3, A4).
The heat exchanger (15a, 15b) according to claim 1, wherein
the first through holes (71) includes an outlet through hole (73) penetrated by the heat transfer tube (6) serving as a refrigerant outlet when the heat exchanger (15a, 15b) functions as an evaporator, and

the outlet through hole (73) is positioned adjacent in the first direction to the first region (A1, A2).
The heat exchanger (15a) according to claim 2, wherein the outlet through hole (73) is positioned adjacent to the windward side of the first region (A1).
The heat exchanger (15a, 15b, 15d, 15e) according to any one of claims 1 to 3,
wherein in the fin (7), the plurality of through holes (70) included in a column on the windward side is disposed to be staggered with respect to the plurality of through holes (70) included in a column on the leeward side.
The heat exchanger (15a) according to any one of claims 1 to 4, wherein
the fin (7) includes a narrow portion (7a) having a smaller width than an average width in the first direction, and

the plurality of through holes (70) includes a narrow portion through hole (74) provided closest to the narrow portion (7a) and corresponding to the first through hole (71).
The heat exchanger (15a) according to claim 5, wherein the narrow portion (7a) is a bent portion where the fin (7) is bent in the first direction.
The heat exchanger (15a) according to claim 5 or 6, wherein
the first through holes (71) include an inlet through hole (75) penetrated by the heat transfer tube (6) serving as a refrigerant inlet when the heat exchanger (15) functions as an evaporator, and

the narrow portion through hole (74) corresponds to the inlet through hole (75).
The heat exchanger (15a) according to claim 7, wherein the narrow portion through hole (74) is positioned adjacent in the first direction to the second region (B1).
The heat exchanger (15a) according to any one of claims 1 to 8, wherein
the first through holes (71) include an inlet through hole (75) penetrated by the heat transfer tube (6) serving as a refrigerant inlet when the heat exchanger (15a) functions as an evaporator, and

the inlet through hole (75) is provided in a region (D1) where air passing the heat exchanger (15a) has air flow speed higher than average air flow speed, and in a column on the leeward side.
An air conditioner (1) comprising a refrigerant circuit (4) including a compressor (11), a heat source heat exchanger (13), a decompression mechanism (14), and a utilization heat exchanger (15) connected in a mentioned order, wherein
the utilization heat exchanger (15) includes the heat exchanger (15a, 15b, 15d, 15e) according to any one of claims 1 to 9.
The air conditioner (1) according to claim 10, further comprising a control unit (5) configured to control an opening degree of the decompression mechanism (14), wherein
the control unit (5) controls the opening degree to cause a refrigerant flowing out of the heat transfer tube (6) serving as a refrigerant outlet when the utilization heat exchanger (15) functions as an evaporator to have a dryness degree equal to or more than a predetermined value.