WO2017208493A1

WO2017208493A1 - Air conditioner

Info

Publication number: WO2017208493A1
Application number: PCT/JP2017/002899
Authority: WO
Inventors: 智弘小松; 禎夫関谷; 佐々木　重幸; 羽生　博之; 高藤　亮一; 啓二横山
Original assignee: 日立ジョンソンコントロールズ空調株式会社
Priority date: 2016-06-03
Filing date: 2017-01-27
Publication date: 2017-12-07

Abstract

Provided is an air conditioner comprising: a housing (30) having a front-surface air suction opening (41) and a top-surface air suction opening (42); an indoor heat exchanger (10) for exchanging heat between a refrigerant and air which is sucked in from the front-surface air suction opening (41) and the top-surface air suction opening (42); and a cross-flow fan (14) by which air having been subjected to heat exchange at the indoor heat exchanger (10) is discharged from an air discharge opening (43) to the outside of the housing (30). The indoor heat exchanger (10) is provided with: a plurality of flat heat transfer pipes (103) through which the refrigerant flows; and fins (101) having formed therein cutouts (102) into which the flat heat transfer pipes (103) are inserted. The flat heat transfer pipes (103) are located inside the end surfaces (101a) of the fins (101), which are located on the side into which the flat heat transfer pipes (103) are inserted. The cutouts (102) have wide sections (102b) formed to have a greater width than the flat heat transfer pipes (103).

Description

Air conditioner

The present invention relates to an air conditioner.

As a method for improving the energy saving performance of an air conditioner, there is an improvement in the performance of a heat exchanger that constitutes the air conditioner. The heat exchanger of an air conditioner performs heat exchange between a refrigerant flowing inside and air flowing outside. For improving the performance of the heat exchanger, there are a method for improving heat transfer performance, a method for reducing flow loss of refrigerant flowing inside, and a method for reducing flow resistance of air flowing outside. In particular, in order to improve the energy saving performance of the air conditioner, it is necessary to improve the performance of the heat exchanger for indoor units from the viewpoint of dimensional constraints due to installation.

Up to now, in air conditioner heat exchangers, various devices have been devised to improve performance. By using flat heat transfer tubes as heat transfer tubes, heat transfer performance is improved and the flow of air flowing outside Methods for reducing the resistance have been considered. As an example of a heat exchanger for an air conditioner using a flat heat transfer tube, Patent Document 1 proposes a heat exchanger in which notched portions in which flat heat transfer tubes are inserted are formed in stacked fins. As a result, a drain water droplet is caused to flow down to the flat surface portion on the side where the notch portion of the fin is not formed (the side opposite to the insertion side of the flat heat transfer tube) using the influence of gravity. Improves drainage.

JP 2010-139166 A

However, in the air conditioner described in Patent Document 1, when the heat exchanger is arranged with the insertion side of the flat heat transfer tube facing the leeward side (downstream side in the air flow direction), the wind (air) of the blower fan ) Causes the drain water to detach and scatter at the end of the flat heat transfer tube, which impairs drainage.

This invention solves the said subject, and it aims at providing the air conditioner which can aim at the improvement of energy saving performance, ensuring the drainage property of drain water.

The present invention includes a housing having an air inlet and an air outlet, a heat exchanger that exchanges heat between the air sucked from the air inlet and the refrigerant, and air that has been heat-exchanged in the heat exchanger. A blower that discharges from the air outlet to the outside of the housing, and the heat exchanger is formed with a plurality of flat heat transfer tubes through which the refrigerant flows, and a cutout portion in which the flat heat transfer tubes are inserted. The flat heat transfer tube is located on the inner side of the end surface of the fin on the insertion side of the flat heat transfer tube, and the notch is formed wider than the width of the flat heat transfer tube. It has a wide part.

According to the present invention, it is possible to provide an air conditioner capable of improving energy saving performance while ensuring drainage of drain water.

It is a lineblock diagram showing the refrigerating cycle to which the air harmony machine of a 1st embodiment is applied. It is a longitudinal cross-sectional view which shows the structure of the indoor unit which concerns on 1st Embodiment. It is an expanded sectional view of the heat exchanger of FIG. It is a figure which shows the structure of the refrigerant flow path in the indoor unit which concerns on 1st Embodiment. It is a figure explaining the effect in the front upper part heat exchanger of a 1st embodiment. It is a figure explaining the effect in the front lower part heat exchanger of a 1st embodiment. The heat exchanger of the indoor unit which concerns on 2nd Embodiment is shown, (a) is a longitudinal cross-sectional view, (b) is the sectional view on the AA line of (a). It is a figure explaining the effect in the front upper part heat exchanger of a 2nd embodiment. It is a figure explaining the effect in the front lower part heat exchanger of a 2nd embodiment. The heat exchanger of the indoor unit which concerns on 3rd Embodiment is shown, (a) is a longitudinal cross-sectional view, (b) is the BB sectional view taken on the line of (a). The heat exchanger of the indoor unit which concerns on 4th Embodiment is shown, (a) is a longitudinal cross-sectional view, (b) is CC sectional view taken on the line of (a). It is a figure which shows the structure of the refrigerant flow path in the indoor unit which concerns on 5th Embodiment.

Hereinafter, an air conditioner according to an embodiment of the present invention will be described with reference to the drawings. In the following description, a home wall-mounted indoor unit will be described as an example of an air conditioner. However, the present invention can also be applied to a domestic outdoor unit, a commercial indoor unit, and an outdoor unit.

(First embodiment)
FIG. 1 is a configuration diagram illustrating a refrigeration cycle to which the air conditioner of the first embodiment is applied.
As shown in FIG. 1, in an air conditioner 100, an indoor unit (air conditioner) 1 and an outdoor unit 2 are connected by connecting

pipes

3 and 4.

The indoor unit 1 includes a first indoor heat exchanger 11 (heat exchanger), a second indoor heat exchanger 12 (heat exchanger), a first expansion device 13, and a cross-flow fan 14 (blower). It is configured. The first indoor heat exchanger 11 is connected to the connection pipe 3 via the pipe 15a. The second indoor heat exchanger 12 is connected to the connection pipe 4 via the pipe 15b. The first expansion device 13 is provided on a pipe 15 c that connects the first indoor heat exchanger 11 and the second indoor heat exchanger 12. Note that the blower is not limited to the cross-flow fan 14 and may be another type of blower such as a propeller fan.

The outdoor unit 2 includes a compressor 21, a four-way valve 22, an outdoor heat exchanger 23, a second expansion device 24, and a blower fan 25. The four-way valve 22 is connected to the discharge port of the compressor 21 via the pipe 26a, connected to the connection pipe 3 via the pipe 26b, connected to the outdoor heat exchanger 23 via the pipe 26d, and via the pipe 26e. And connected to the suction port of the compressor 21. In the four-way valve 22, the pipe 26d and the pipe 26e are connected when the pipe 26a and the pipe 26b are connected, and the pipe 26b and the pipe 26e are connected when the pipe 26a and the pipe 26d are connected. Thus, the refrigerant flow path is switched. Note that a propeller fan is usually used as the blower fan 25.

Next, the action of each element in each operation mode of heating operation, cooling operation, and reheat dehumidification operation will be described with reference to FIG. In addition, as a refrigerant | coolant, the single refrigerant | coolant of R32, R1234yf, R1234ze, R1123, or the mixed refrigerant | coolant which has them as a main component is used.

In the heating operation mode, the refrigerant flow path is switched by the four-way valve 22, and the high-pressure gaseous refrigerant compressed by the compressor 21 flows to the indoor unit 1 through the four-way valve 22 and the connection pipe 3. The refrigerant that has entered the indoor unit 1 sequentially flows through the first indoor heat exchanger 11 and the second indoor heat exchanger 12, and is condensed by dissipating heat to the indoor air to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant flows to the outdoor unit 2 through the connection pipe 4. At this time, the first diaphragm device 13 is fully opened.

The high-pressure liquid refrigerant that has entered the outdoor unit 2 is depressurized by the action of the second expansion device 24, becomes a low-temperature low-pressure gas-liquid two-phase state, flows to the outdoor heat exchanger 23, and absorbs the heat of the outdoor air. It evaporates and becomes a gaseous refrigerant. The refrigerant that has become gaseous in the outdoor heat exchanger 23 passes through the four-way valve 22 and is compressed again by the compressor 21.

In the cooling operation mode, the high-pressure gaseous refrigerant compressed by the compressor 21 is condensed by dissipating heat to the outside air by the outdoor heat exchanger 23 to become a high-pressure liquid refrigerant. The liquid refrigerant is depressurized by the action of the second expansion device 24, becomes a low-temperature low-pressure gas-liquid two-phase state, and flows to the indoor unit 1 through the connection pipe 4.

The refrigerant that has entered the indoor unit 1 sequentially flows through the second indoor heat exchanger 12 and the first indoor heat exchanger 11, and evaporates by absorbing the heat of the indoor air. The refrigerant evaporated in the indoor unit 1 returns to the outdoor unit 2 through the connection pipe 3, passes through the four-way valve 22, and is compressed again by the compressor 21. Also in the cooling operation mode, the first expansion device 13 is in a fully open state, as in the heating operation mode.

In the reheat dehumidifying operation mode, the refrigerant flow direction is the same as in the cooling operation mode. That is, the high-pressure gaseous refrigerant compressed by the compressor 21 flows to the indoor unit 1 through the outdoor heat exchanger 23, the second expansion device 24, and the connection pipe 4. The refrigerant that has entered the indoor unit 1 passes through the second indoor heat exchanger 12, passes through the first expansion device 13 and the first indoor heat exchanger 11, returns to the outdoor unit 2 through the connection pipe 3, and enters the four-way valve 22. It flows again to the compressor 21 through.

In the reheat dehumidifying operation mode, the air passing through the first indoor heat exchanger 11 is cooled and dehumidified, and the air passing through the second indoor heat exchanger 12 is heated to reduce the humidity while suppressing the change in the indoor air temperature. Lowering control is performed. In order to heat the air passing through the second indoor heat exchanger 12, the high-pressure gaseous refrigerant compressed by the compressor 21 is not condensed into the liquid refrigerant by the outdoor heat exchanger 23, and the high-temperature high-pressure gas-liquid is not condensed. It is necessary to flow to the indoor unit 1 through the connection pipe 4 while maintaining the two-phase state. For this reason, the second expansion device 24 is controlled to an open side or a fully open state as compared with the cooling operation mode. The amount of heating in the second indoor heat exchanger 12 controls the amount of heat radiated to the outside air by the outdoor heat exchanger 23 by controlling the rotational speed of the blower fan 25 in addition to the opening degree control of the second expansion device 24. To do. Although the blower fan 25 is not shown in the figure, it is used for cooling the electrical equipment that controls the compressor 21 and the blower fan 25, so that it can be stopped at a low speed or intermittently. Never do.

By the above-described control, the refrigerant that has entered the indoor unit 1 in the high-temperature and high-pressure gas-liquid two-phase state passes through the second indoor heat exchanger 12 in the second indoor heat exchanger 12 by the operation of the cross-flow fan 14. It is condensed by dissipating heat to the room air and becomes a liquid refrigerant. Thereby, the air which passes the 2nd indoor heat exchanger 12 is heated, and temperature rises. Then, the liquid refrigerant flows to the first expansion device 13. The first throttle device 13 is controlled to the closed side so as to have a flow path resistance, and the liquid refrigerant is decompressed by the action of the first throttle device 13 to be in a low-temperature and low-pressure gas-liquid two-phase state, It flows to the heat exchanger 11. The low-temperature and low-pressure gas-liquid two-phase refrigerant evaporates in the first indoor heat exchanger 11 by absorbing heat from the air passing through the first indoor heat exchanger 11 by the operation of the cross-flow fan 14. At this time, the air passing through the first indoor heat exchanger 11 is cooled and dehumidified. In this way, the air is heated in the second indoor heat exchanger 12, and the air is cooled and dehumidified in the first indoor heat exchanger 11, so that the present operation mode is dehumidified while suppressing the temperature change of the indoor air. It is possible.

FIG. 2 is a longitudinal sectional view showing the structure of the indoor unit according to the first embodiment.
As shown in FIG. 2, the indoor unit 1 includes a housing 30 having a front air inlet 41 (air inlet), an upper air inlet 42 (air inlet), and an air outlet 43. The indoor unit 1 also includes a front upper heat exchanger 201 (second indoor heat exchanger 12), a front lower heat exchanger 202 (first indoor heat exchanger 11), and a rear heat exchanger 300 (second indoor heat exchanger). 12). In addition, the indoor unit 1 includes a cross-flow fan 14 that discharges air exchanged in the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300 from the air outlet 43 to the outside of the housing 30. It is equipped with.

A front air inlet 41 is provided on the front surface of the housing 30, and an upper air inlet 42 is provided on the upper surface of the housing 30. In addition, a rectangular air filter 51 is attached to the casing 30 so as to cover the front air inlet 41 and the upper air inlet 42, and is configured to prevent dust from entering the interior of the indoor unit 1. ing.

In addition, an air outlet 43 is provided at the lower part of the housing 30, and cool air and hot air are blown out from here. Moreover, the air direction control board 52 is provided in the air blower outlet 43 of the housing | casing 30 so that opening and closing is possible. In addition, an openable / closable panel 31 is provided on the front surface of the housing 30, and the front air suction port 41 is configured together with the housing 30 by opening the panel 31.

The casing 30 has a back casing 32 and a front casing 33. The back casing 32 is located on the back side of the cross-flow fan 14, is formed continuously with the air outlet 43, and has a curved surface 32 a as an air flow path wall surface. The curved surface 32 a is disposed so that the concave surface faces forward, and is curved so as to gradually approach from the opening edge of the air outlet 43 toward the cross-flow fan 14.

Further, the back casing 32 has a back nose portion 32b (also referred to as a rear guider) that protrudes between the cross-flow fan 14 and the rear heat exchanger 300 from an upper end portion (tip portion) 32a1 of the curved surface 32a.

The front casing 33 is located in front of the cross-flow fan 14 and below the front lower heat exchanger 202, and constitutes a wall surface 33a that continues to the air outlet 43 and extends toward the cross-flow fan 14 as an air upper flow path wall surface. is doing. In addition, a front nose portion 33c (also referred to as a stabilizer or a tongue portion) that is bent into a substantially rectangular shape is integrally formed at the front end 33b of the front casing 33.

The cross-flow fan 14 is disposed so as to be sandwiched between the back nose portion 32b and the front nose portion 33c. That is, in the cross-flow fan 14, a substantially semicircular portion of the cross-flow fan 14 projects into the housing 30 from the tip 32 b 1 of the back nose portion 32 b and the tip 33 c 1 of the front nose portion 33 c.

When the cross-flow fan 14 rotates, a circulating vortex is formed at a location facing the front nose portion 33c, and room air is sucked into the housing 30 via the front air inlet 41 and the upper air inlet 42. Then, after passing through the air filter 51, the indoor heat exchanger 10, and the once-through fan 14, the air is blown out to the air outlet 43. The blowing direction of the blown air can be controlled by a wind direction control plate 52 provided at the air outlet 43.

Further, inside the housing 30, the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchange are provided in the middle of the air path from the front air inlet 41 and the upper air inlet 42 to the cross-flow fan 14. The indoor heat exchanger 10 (the 1st indoor heat exchanger 11 and the 2nd indoor heat exchanger 12) comprised with the apparatus 300 is provided.

The front upper heat exchanger 201 is configured by combining a first front upper heat exchanger 201A and a second front upper heat exchanger 201B arranged in two rows in the air flow direction. The front lower heat exchanger 202 is configured by combining the first front lower heat exchanger 202A and the second front lower heat exchanger 202B in the same manner as described above. The back heat exchanger 300 is configured by combining the first back heat exchanger 300A and the second back heat exchanger 300B in the same manner as described above.

The front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300 are each configured by a fin 101 formed in a straight line and a plurality of flat heat transfer tubes 103 inserted through the fin 101. Yes.

The front upper heat exchanger 201 is arranged so as to be inclined so that the lower side is positioned forward of the upper side. The front lower heat exchanger 202 is disposed so as to be inclined such that the upper side is positioned forward of the lower side. The rear heat exchanger 300 is disposed so as to be inclined such that the upper side is positioned forward of the lower side.

Also, the lower end surface 201a (lower end surface of the fin 101) of the first front upper heat exchanger 201A, the lower end surface 201b (lower end surface of the fin 101) of the second front upper heat exchanger 201B, and the first front lower heat exchanger. The upper end surface 202a (upper end surface of the fin 101) of 202A and the upper end surface 202b (upper end surface of the fin 101) of the second front lower heat exchanger 202B are formed horizontally (or substantially horizontal) and joined together.

Further, the upper end surface 201c (upper end surface of the fin 101) of the first front upper heat exchanger 201A, the upper end surface 201d (upper end surface of the fin 101) of the second front upper heat exchanger 201B, and the first rear heat exchanger 300A. The upper end surface 300a (the upper end surface of the fin 101) is formed horizontally (substantially horizontal) and joined so as to be a flat surface. Moreover, the end surface 201e of the long side of the second front upper heat exchanger 201B and the upper end surface 300b of the second rear heat exchanger 300B are joined to each other.

Thereby, the indoor heat exchanger 10 including the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300 has a substantially inverted V shape (substantially Λ shape) so as to surround the cross-flow fan 14. ).

By the way, in the cooling operation mode described with reference to FIG. 1, when the second indoor heat exchanger 12 and the first indoor heat exchanger 11 absorb the heat of the indoor air, the second indoor heat exchanger 12 and the first indoor heat exchanger 12 are absorbed. Water vapor in the air cooled below the dew point temperature on the surfaces of the fins 101 constituting the heat exchanger 11 may condense and condense to generate drain water. If the drain water generated in this manner stays on the surface of the fins 101 or the flat heat transfer tubes 103 in the form of droplets, the flow of air is hindered. In order to deteriorate the heat transfer performance due to the decrease, it is important to suppress the retention of drain water on the surface of the fin 101.

In the case of the reheat dehumidifying operation mode described with reference to FIG. 1, when the first indoor heat exchanger 11 absorbs the heat of the indoor air, it is cooled below the dew point temperature on the fin surface of the first indoor heat exchanger 11. The water vapor in the air is condensed and condensed to generate drain water. When the drain water generated in this manner stays on the surface of the fin 101 or the flat heat transfer tube 103 in the form of droplets, the flow of air is obstructed, so the input of the cross-flow fan 14 and the blower fan 25 is increased, and the air volume is decreased. Therefore, it is important to suppress the drain water from staying on the surface of the fin 101.

FIG. 3 is an enlarged cross-sectional view of the heat exchanger of FIG.
As shown in FIG. 3, the indoor heat exchanger 10 (front upper heat exchanger 201, front lower heat exchanger 202, rear heat exchanger 300) is, for example, a cross fin tube type, and includes fins 101 and flat transmission. The heat tube 103 (flat tube) is combined.

The fin 101 is configured by laminating a plurality of strip-like thin plates made of aluminum or aluminum alloy with a plurality of intervals. Further, the fin 101 is formed with a concave notch 102 into which the flat heat transfer tube 103 is inserted.

The notch 102 is formed by notching from one end surface 101 a of the long side of the fin 101 (insertion side) toward the other end surface 101 b (opposite to the insertion side). It is formed to extend perpendicularly (substantially perpendicular) to 101a. The notch 102 has an elongated recess 102a in which the flat heat transfer tube 103 is inserted and held, and a substantially triangular wide portion 102b that widens from the recess 102a toward the end surface 101a.

As shown in the partially exploded sectional view of FIG. 3, the flat heat transfer tube 103 is made of aluminum or aluminum alloy, and connects the opposed

flat portions

103a and 103b to one end of the flat portion 103a and one end of the flat portion 103b. A curved surface portion 103c, and a curved surface portion 103d that connects the other end of the flat surface portion 103a and the other end of the flat surface portion 103b. The flat heat transfer tube 103 is partitioned by a plurality of partitions 103s extending from the inner wall of the flat surface portion 103a to the inner wall of the flat surface portion 103b, and is partitioned into a plurality of refrigerant flow paths. Further, the flat heat transfer tube 103 has a structure in which it is thermally connected to the notch 102 of the fin 101 by brazing in the furnace. Note that the number of the partitions 103s is not limited to this embodiment, and can be changed as appropriate.

The length L in the major axis direction g of the flat heat transfer tube 103 is formed to be shorter than the width W of the fin 101. Further, the flat heat transfer tube 103 is inserted so as to form a right angle (substantially a right angle) with respect to the end surface 101 a of the fin 101. The distance along the major axis direction g from the end surface (end surface on the insertion side) 101a on the side where the notch 102 is provided to the flat heat transfer tube 103 is α, and the end surface 101b on the side opposite to the insertion side is flat from the end surface 101b. When the distance along the major axis direction g to the heat transfer tube 103 is β, the relationship is α <β. As described above, the flat heat transfer tube 103 is set at a position that enters the inside of the fin 101 from the end surface 101 a of the fin 101.

Further, the interval (shortest distance) between the adjacent flat heat transfer tubes 103 and the flat heat transfer tubes 103 is L1, and along the edge including the end surface 101a of the fin 101 between the adjacent flat heat transfer tubes 103 and the flat heat transfer tubes 103. If the distance is L2, L1 <L2. The distance L2 includes an end surface 101a, an inclined end surface 101d extending from the end surface 101a toward the end portion 103c1 of one flat heat transfer tube 103, and an inclination extending from the end surface 101a toward the end portion 103c1 of the other flat heat transfer tube 103. It is the length obtained by adding the end face 101e.

The indoor heat exchanger 10 configured in this manner is configured such that the protruding portion 101t of the fin 101 is positioned on the insertion side with respect to the end portion 103c1 of the flat heat transfer tube 103 in the long axis direction g. Thereby, on the insertion side of the fin 101, the fin 101 is formed to have a substantially wave shape along the arrangement direction of the flat heat transfer tubes 103 on the outer side in the long axis direction g than the end portion 103 c 1 of the flat heat transfer tube 103. Has been.

Further, the indoor heat exchanger 10 has an end surface 101b (between an end portion 103d1 opposite to the insertion side in the major axis direction g of the flat heat transfer tube 103 and an end surface 101b opposite to the insertion side. A flat portion 101u extending along the direction in which the flat heat transfer tubes 103 are arranged) is formed. The planar portion 101u is continuously formed from one end (upper end) in the longitudinal direction of the fin 101 to the other end (lower end).

Returning to FIG. 2, in the indoor unit 1 of the first embodiment, in order to obtain a desired capacity, the first front upper heat exchanger 201A and the second front upper heat exchanger 201B are combined, and the first front lower heat is combined. The exchanger 202A and the second front lower heat exchanger 202B are combined, and the first back heat exchanger 300A and the second back heat exchanger 300B are combined and used in a plurality of rows in the air flow direction.

Further, in the front upper heat exchanger 201, the insertion sides of the flat heat transfer tubes 103 of the fins 101 of the first front upper heat exchanger 201A and the second front upper heat exchanger 201B are directed upward with respect to the direction of gravity. Are arranged as follows. Further, in the front lower heat exchanger 202, when the insertion side of the flat heat transfer tube 103 of the fin 101 of each of the first front lower heat exchanger 202A and the second front lower heat exchanger 202B is directed downward in the gravity direction, Arranged to face upward. Moreover, in the back surface heat exchanger 300, when the insertion side of the flat heat exchanger tube 103 of each fin 101 of the 1st back surface heat exchanger 300A and the 2nd back surface heat exchanger 300B makes a gravity direction downward, it becomes back upward. Are arranged as follows.

As shown in FIG. 2, in the front upper heat exchanger 201, the flat heat transfer tube 103 of the second front upper heat exchanger 201 </ b> B is connected to the flat heat transfer tube 103 of the first front upper heat exchanger 201 </ b> A. The positions are shifted in the longitudinal direction and arranged in a staggered pattern. Further, in the back heat exchanger 300, the flat heat transfer tubes 103 of the second back heat exchanger 300B are shifted in the longitudinal direction of the fins 101 in a staggered manner with respect to the flat heat transfer tubes 103 of the first back heat exchanger 300A. Has been placed. In the front lower heat exchanger 202, the flat heat transfer tubes 103 are not arranged in a staggered manner, but the front lower heat exchanger 202 may also be arranged in a staggered manner in the same manner as described above.

FIG. 4 is a diagram illustrating a configuration of a refrigerant flow path in the indoor unit according to the first embodiment. The indoor heat exchanger 10 of the indoor unit 1 is configured with the number of flow path branches (number of passes) corresponding to the flow rate of refrigerant flowing in the pipe. In other words, the number of branches is changed according to the ability. In FIG. 4, points B, C, D, E, F, G, H, and I indicate branch points or junction points of the refrigerant flow paths.

As shown in FIG. 4, in the heating operation mode, as indicated by the solid line arrow, the refrigerant flowing from the outdoor unit 2 (see FIG. 1) flows into the indoor heat exchanger 10 from the point A in FIG. 4. The refrigerant that has flowed in is branched into four flow paths at point B and flows through the front lower heat exchanger 202. In the front lower heat exchanger 202, the branched refrigerant flows through the plurality of flat heat transfer tubes 103 of the second front lower heat exchanger 202B, and then passes through the flat heat transfer tubes 103 of the first front lower heat exchanger 202A. Streets meet at point C. The merged refrigerant flows from the point C as one flow path, passes through the first expansion device 13 and flows to the point D.

Next, the refrigerant that has passed through the first expansion device 13 is branched into three flow paths at the point D, and the second front upper heat exchanger 201B of the front upper heat exchanger 201 on the downstream side (downstream side) of the air flow. After flowing through the plurality of flat heat transfer tubes 103, they merge at point E. The refrigerant merged at point E is branched into three flow paths at point F and flows through the plurality of flat heat transfer tubes 103 of the second rear heat exchanger 300B on the leeward side of the rear heat exchanger 300, and then on the windward side. It flows through the plurality of flat heat transfer tubes 103 of the first back heat exchanger 300A and joins at the point G. The refrigerant merged at point G is directed to point H with one flow path, branched into two flow paths, and after flowing through the plurality of flat heat transfer tubes 103 of the windward first front upper heat exchanger 201A, They merge at point I and reach point J, which is the outlet of the indoor heat exchanger 10. In the cooling operation mode, the air flows from the point J contrary to the heating operation mode, and flows in the indoor heat exchanger 10 in the direction indicated by the broken line arrow in the figure.

In the reheat dehumidifying operation mode, the high-temperature and high-pressure refrigerant flowing from the outdoor unit 2 (see FIG. 1) flows into the indoor heat exchanger 10 from the point J in FIG. 4 in a gas-liquid two-phase state. While the refrigerant flows from the point J to the point D, the front upper heat exchanger 201 and the rear heat exchanger 300 are condensed and liquefied by releasing heat to the air. The high-pressure liquid refrigerant that has passed the point D is depressurized when passing through the first throttling device 13, enters a low-temperature low-pressure gas-liquid two-phase state, flows to the point C, and is branched into four flow paths. The refrigerant branched at point C cools and dehumidifies the air when flowing through the front lower heat exchanger 202 (first front lower heat exchanger 202A and second front lower heat exchanger 202B), and merges at point B. It flows to the point A that is the outlet of the indoor heat exchanger 10.

FIG. 5 is a diagram for explaining the operational effects of the front upper heat exchanger of the first embodiment. FIG. 5 shows the fin 101 and the flat heat transfer tube during the air flow and the cooling operation mode in the front upper heat exchanger 201 in the indoor heat exchanger 10 (see FIG. 2) of the air conditioner of the first embodiment. The flow of drain water generated on the surface of 103 is schematically shown. The rear heat exchanger 300 has the same effects as the front upper heat exchanger 201 except for the orientation different from that of the front upper heat exchanger 201, and thus the description of the rear heat exchanger 300 is omitted.

As shown in FIG. 5, in the front upper heat exchanger 201 in which the flat heat transfer tubes 103 are inserted into the fins 101 provided with the notches 102, the flat heat transfer tubes 103 are generated by being cooled and dehumidified on the surfaces of the flat heat transfer tubes 103 and the fins 101. The drained water (droplet) is dropped on the surface of the flat heat transfer tube 103 and the fin 101 by the action of gravity. Further, the drain water flows along the flat surface portion 103a of the flat heat transfer tube 103 arranged with an inclination angle from the horizontal, and flows down toward the side where the flat surface portion 101u of the fin 101 is formed. The droplets that have reached the flat surface portion 101 u flow down to the lower end of the fin 101 on the surface of the flat surface portion 101 u of the fin 101 by the action of gravity and surface tension, and finally from the surface of the upper front heat exchanger 201. Drained. Thus, the drain water generated on the surface of the fin 101 is discharged along the long axis direction of the flat heat transfer tube 103 having an inclination with respect to the horizontal, and the flat surface portion 101u where the notch portion 102 is not formed. The drain water stays in place by being discharged along.

Further, on the upstream side (windward side) in the air flow direction indicated by the white arrow in FIG. 5, the notch 102 is formed adjacent to the notch 102 by forming the notch 102 in the fin 101 and the wide portion 102 b in the notch 102. The length L2 (see FIG. 3) of the front edge (the end surface 101a and the inclined end surfaces 101d and 101e) of the fin 101A (101) is longer than the interval L1 (see FIG. 3) between the adjacent flat heat transfer tubes 103. Yes. At this time, the air flow flows in from the direction substantially orthogonal to the front edge (end surface 101a,

inclined end surfaces

101d, 101e) of the fin 101, as indicated by the broken-line arrows in FIG. A long front edge can be secured. Thereby, since a high heat transfer rate can be ensured, it is possible to improve the heat exchange performance of the fins 101 as a result. Moreover, since the inclined end faces 101d and 101e are formed on the front edge of the fin 101 by forming the wide portion 102b, the length of the front edge directed toward the windward side where air flows can be formed longer, so that heat exchange performance Can be further increased.

The inclined end surfaces 101d and 101e are not limited to those formed in a straight line shape, and can be appropriately changed such as a convexly curved shape, a concavely curved shape, a corrugated shape, and a stepped shape. . By forming a convexly curved shape, a concavely curved shape, a corrugated shape, or a stepped shape, the length L2 of the leading edge can be further increased as compared with the case of forming a linear shape, The exchange performance can be further increased. In this embodiment, the front edge (end surface 101a and inclined end surfaces 101d and 101e) is formed in a trapezoidal shape, but the front edge (end surface 101a and inclined end surfaces 101d and 101e) may be formed in an arc shape.

The wide portion 102b is formed between the insertion-side end portion 103c1 of the flat heat transfer tube 103 and the insertion-side end surface 101a. Thereby, since the end surface of the recessed part 102a of the fin 101 can be brought into surface contact with the

flat surface portions

103a and 103b and the curved surface portion 103d of the flat heat transfer tube 103, heat between the refrigerant flowing in the flat heat transfer tube 103 and the air. Exchange efficiency can be improved.

Thus, in the indoor unit 1 of the first embodiment, the drain water on the surface of the indoor heat exchanger 10 can be efficiently discharged in the cooling operation mode, and the heat transfer performance of the fins 101 can be improved. Therefore, energy saving can be improved.

FIG. 6 is a diagram for explaining the effects of the front lower heat exchanger of the first embodiment. 6 shows the air flow and the surfaces of the fins 101 and the flat heat transfer tubes 103 in the cooling operation mode in the lower front heat exchanger 202 of the indoor heat exchanger 10 (see FIG. 2) of the first embodiment. 4 schematically shows the flow of drain water generated in the water.

As shown in FIG. 6, the front lower heat exchanger 202 installed with the inlet of the notch 102 tilted with the gravitational direction on the upper side is generated by being cooled and dehumidified on the surfaces of the flat heat transfer tubes 103 and the fins 101. Part of the drain water droplets is dropped by the action of gravity on the surfaces of the flat heat transfer tubes 103 and the fins 101. Then, the drain water droplets flow down along the long axis direction of the flat heat transfer tube 103 toward the side where the flat portion 101u is formed below the gravitational direction, and the surface of the flat portion 101u of the fin 101 It flows down toward the lower end of the fin 101 and is finally drained from the surface of the front lower heat exchanger 202.

Further, some of the droplets of drain water move downstream on the flat portion 103a of the flat heat transfer tube 103 by the air flow (wind pressure) indicated by the white arrow in FIG. And in the edge part 103c1 downstream from the flat heat exchanger tube 103, the droplet of drain water flows down along the surface of the curved surface part 103c of the flat heat exchanger tube 103 by gravity and surface tension. Then, the drain water droplets flow down along the inclined end surface 101e, the end surface 101a, and the inclined end surface 101d, which are the rear edges of the fin 101, in order by gravity and surface tension. As described above, the drain water droplets are captured by the end portion 103c1 on the insertion side of the flat heat transfer tube 103 and the rear edge of the fin 101 (the inclined end surface 101e, the end surface 101a, and the inclined end surface 101d) by gravity and surface tension. However, it flows down to the lower end of the fin 101 and is finally drained from the surface of the front lower heat exchanger 202.

As described above, in the air conditioner (indoor unit 1) of the first embodiment, the indoor heat exchanger 10 is inserted with a plurality of flat heat transfer tubes 103 through which refrigerant flows and the flat heat transfer tubes 103. And a fin 101 in which a notch 102 is formed. Further, the flat heat transfer tube 103 is positioned on the inner side of the fin 101 than the end surface 101 a of the fin 101 on the insertion side of the flat heat transfer tube 103, and the notch portion 102 is formed wider than the width of the flat heat transfer tube 103. Part 102b. According to this, when the fin 101 is arranged with the insertion side of the flat heat transfer tube 103 facing forward and upward in the gravity direction like the front upper heat exchanger 201, a wide area for taking in air into the fin 101 is secured. Therefore, the heat transfer performance can be improved (see FIG. 5). Moreover, when the fins 101 are arranged with the insertion side of the flat heat transfer tube 103 rearward and upward in the gravitational direction as in the lower front heat exchanger 202, drain water (droplets) is driven by the cross-flow fan 14. Even if it flows to the leeward side along the long axis direction of the flat heat transfer tube 103 by the wind, it does not scatter from the fin 101, and the end portion 103c1 of the flat heat transfer tube 103, the inclined end surface 101e of the fin 101, the end surface 101a, the inclined end surface Since it flows through 101d, it becomes possible to drain drain water well.

In the first embodiment, since the wide portion 102b is formed in the notch portion 102, drain water easily flows from the inclined end surface 101e to the end surface 101a and from the inclined end surface 101d to the end portion 103c1 of the flat heat transfer tube 103. It becomes possible to improve drainage of drain water.

In the first embodiment, since the inclined end surface 101e is formed by the wide portion 102b from the position of the end portion 103c1 of the flat heat transfer tube 103, the drain water captured by the flat heat transfer tube 103 is used as the inclined end surface 101e of the fin 101. The drainage of drain water can be improved.

In the first embodiment, the distance in the major axis direction g of the flat heat transfer tube 103 from the end surface 101a on the insertion side of the fin 101 to the end portion 103c1 on the insertion side of the flat heat transfer tube 103 is α (see FIG. 3). ). Further, the distance in the major axis direction g of the flat heat transfer tube 103 from the end surface 101b opposite to the insertion side of the fin 101 to the end 103d1 opposite to the insertion side of the flat heat transfer tube 103 is β (FIG. 3). At this time, the relation α <β is set. Thus, since the flat surface portion 101u defined by the distance (width) β becomes a flow path through which water droplets of drain water flow, drainage of drain water is set by setting the distance β larger (wider) than the distance α. Can be improved.

In the first embodiment, the flat heat transfer tube 103 is inserted perpendicularly (or substantially perpendicularly) to the insertion-side end surface 101a. According to this, it becomes easy to put the flat heat transfer tube 103 into the fin 101. In addition, when the flat heat transfer tube 103 is inclined with respect to the end surface 101a, the long axis direction of the flat heat transfer tube 103 is horizontal when the indoor heat exchanger 10 is inclined around the cross-flow fan 14. It will be arranged in. However, in the first embodiment, when the flat heat transfer tube 103 is inserted into the fin 101, the long axis direction g (see FIG. 3) of the flat heat transfer tube 103 is inserted perpendicularly to the end surface 101a of the fin 101, Even if the fins 101 are inclined, the flat heat transfer tubes 103 can be reliably arranged at an angle with respect to the horizontal, and the flat heat transfer tubes 103 can be easily installed in an inclined state. In addition, when the flat heat transfer tube 103 is disposed to be inclined with respect to the end surface 101a, it causes a rise in ventilation resistance. However, in the first embodiment, a factor that increases the ventilation resistance by being arranged perpendicular to the end surface 101a. Can be suppressed.

In the first embodiment, the indoor heat exchanger 10 (the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300) is inclined with respect to the gravity direction G so as to surround the cross-flow fan 14. Installed. Thus, by arranging the once-through fan 14 so as to be surrounded by the indoor heat exchanger 10, the heat transfer performance can be improved.

Further, in the first embodiment, in the indoor heat exchanger 10 (the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300), the insertion side of the flat heat transfer tube 103 is on the upper side in the gravity direction G. The flat heat transfer tube 103 is installed in a state where the major axis direction g (see FIG. 3) is inclined with respect to the horizontal direction Sh (see FIGS. 5 and 6). According to this, like the indoor heat exchanger 10 (front upper heat exchanger 201, front lower heat exchanger 202, and rear heat exchanger 300), the insertion side of the flat heat transfer tube 103 is directed upward in the gravity direction. When the fins 101 are installed, the drainage water droplets generated by cooling and dehumidifying the flat heat transfer tubes 103 and the surfaces of the fins 101 of the flat heat transfer tubes 103 disposed at an angle with respect to the horizontal direction Sh. It flows along the major axis direction g. Then, the drain water droplets flowing down from the flat heat transfer tube 103 flow down on the surface of the flat portion 101u formed continuously in the longitudinal direction of the fin 101, and finally the surface of the indoor heat exchanger 10 (See FIGS. 5 and 6).

In the first embodiment, the

lower end surfaces

201a and 201b of the front upper heat exchanger 201 and the

upper end surfaces

202a and 202b of the front lower heat exchanger 202 are formed such that the fin 101 is horizontal (or substantially horizontal), and the horizontal It joins in the state of (or substantially horizontal) (refer FIG. 2). Thereby, the air flow which does not contribute to heat exchange can be suppressed, and furthermore, since the installation area of the fin 101 can be secured widely, heat exchange efficiency (heat transfer performance) can be improved, and energy saving performance can be improved. Further, in the first embodiment, the drain water drained from the front upper heat exchanger 201 is disposed on the front surface by not providing a gap in the joint portion between the front upper heat exchanger 201 and the front lower heat exchanger 202. Since it can be received by the lower heat exchanger 202, the drainage of drain water can be further improved.

Further, in the first embodiment, the upper end surfaces 201c and 201d of the front upper heat exchanger 201 (first front upper heat exchanger 201A and second front upper heat exchanger 201B) and the rear heat exchanger 300 (first rear heat exchanger). The upper end surface 300a of the exchanger 300A) is joined in a horizontal (or substantially horizontal) state so that the upper end surfaces 201c, 201d, and 300a are flat surfaces. Thereby, the installation area of the fin 101 of the front upper heat exchanger 201 and the rear heat exchanger 300 can be secured widely while minimizing the gap between the air filter 51 and the front upper heat exchanger 201 and the rear heat exchanger 300. Therefore, heat transfer performance can be improved and energy saving performance can be improved.

In the first embodiment, the end surface 201e of the second front upper heat exchanger 201B and the upper end surface 300b of the second back heat exchanger 300B are in contact with each other. As a result, air can be prevented from passing through the gap between the second front upper heat exchanger 201B and the second rear heat exchanger 300B without contributing to heat exchange, so that the heat exchange rate (heat transfer performance) can be reduced. The energy saving performance can be improved.

In the first embodiment, when the flat heat transfer tube 103 is inserted at a substantially right angle with respect to the end surface 101a of the fin 101, the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger. 300 has the same shape of the fin 101, and only in the installation direction (front upper heat exchanger 201 is facing upwards, front lower heat exchanger 202 is plugging side upwards, and rear heat exchanger 300 is plugging sides facing upwards) It can be configured simply by changing (see FIG. 2). Further, as shown in FIG. 2, the first front upper heat exchanger 201A and the second front upper heat exchanger 201B, the first front lower heat exchanger 202A and the second front lower heat exchanger 202B, and the first rear heat exchange. The arrangement intervals (pitch) La, Lb, Lc of the flat heat transfer tubes 103 between the rows at any location of the heat exchangers arranged in a plurality of rows such as the heat exchanger 300A and the second back heat exchanger 300B (see FIG. 2) are all the same. For this reason, when the refrigerant flow path is configured, the members that connect the flat heat transfer tubes 103 to each other in order to configure the refrigerant flow path can be shared, and the manufacturing cost can be reduced.

(Second Embodiment)
7A and 7B show a heat exchanger for an indoor unit according to the second embodiment, in which FIG. 7A is a longitudinal sectional view, and FIG. 7B is a sectional view taken along line AA in FIG. Note that in the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted (the same applies to the following embodiments).
As shown in FIG. 7 (a), the indoor unit 1 of the second embodiment includes the cut and raised

portions

104, 104, 104, and 104 (protrusions), the cut and raised portion 105, and the ribs on the fin 101 of the first embodiment. 106 is added.

A plurality of cut and raised portions 104 are provided between the adjacent flat heat transfer tubes 103 and the flat heat transfer tubes 103. Further, the cut-and-raised portion 104 has a long and narrow plate shape in plan view, and is arranged at intervals along the long axis direction of the flat heat transfer tube 103.

The cut-and-raised portion 105 is formed in the same manner as the cut-and-raised portion 104, and is not formed between the adjacent flat heat transfer tubes 103 and the flat heat transfer tubes 103, but is located outside (difference) from the end portion 103c1 of the flat heat transfer tubes 103. It is formed in the protrusion part 101t of the trapezoid shape of planar view of the fin 101 which protrudes toward the end surface 101a) of the insertion side. Further, the cut and raised portion 105 is formed in parallel with the cut and raised portion 104.

The rib 106 is formed on the flat surface portion 101 u between the end portion 103 d 1 opposite to the insertion side of the flat heat transfer tube 103 and the end surface 101 b opposite to the insertion side of the fin 101. The rib 106 is continuously formed along the flat surface portion 101u (along the longitudinal direction of the fin 101). In addition, the three parallel straight lines shown in FIG. 7A indicate folding curves when the fin 101 is bent.

As shown in FIG. 7B, the cut-and-raised portion 104 has, for example, an extruded portion 104a formed by extruding a sheet metal (thin plate) constituting the fin 101 from one surface side to the other surface side by pressing. is doing. In addition, the cut and raised portion 104 has

slits

104b and 104b (through holes) formed on both sides in the width direction of the extruded portion 104a. The

slits

104b and 104b are formed to penetrate from the windward side toward the leeward side. Further, by forming the cut-and-raised portion 104 in the fin 101, the one surface side and the other surface side of the fin 101 communicate with each other.

The cut-and-raised portion 105 has the same shape as the cut-and-raised portion 104, has an extruded portion 105a, and slits 105b and 105b are formed on both sides in the width direction of the extruded portion 105a.

The rib 106 is formed in a substantially V shape in sectional view by bending the flat surface portion 101u along the end surface 101b. The rib 106 is configured such that the convex side is the same side as the cut and raised side of the cut and raised

portions

104 and 105. Accordingly, the dimension D in the stacking direction of one fin 101 can be reduced (shortened), and the fins 101 can be arranged densely when the fins 101 are stacked and arranged.

Further, the rib 106 has a slope 106a formed on the convex end face 101a side and a slope 106b formed on the end face 101b side. Further, a groove portion 106 c formed in a V shape is formed on the surface opposite to the convex shape of the rib 106.

FIG. 8 is a diagram illustrating the operational effects of the front upper heat exchanger of the second embodiment, and FIG. 9 is a diagram illustrating operational effects of the front lower heat exchanger of the second embodiment. In addition, description about the same effect as 1st Embodiment is abbreviate | omitted.
As shown in FIG. 8, in the front upper heat exchanger 201 with the notch 102 on the front side and in the gravity direction, a droplet of drain water generated by cooling and dehumidification on the surface of the flat heat transfer tube 103 and the fin 101. However, it flows down along the cut and raised

portions

104 and 105 by the action of gravity and flows into the flat portion 103 a of the flat heat transfer tube 103. Then, the drain water droplets flow down along the surface of the flat portion 103 a of the flat heat transfer tube 103 and flow into the rib 106 side. The drain water droplets flow down while being captured by the convex slope 106 a of the rib 106, and are finally drained from the surface of the front upper heat exchanger 201.

Further, since the cut-and-raised

portions

104 and 105 are formed, even if drain water droplets generated on the end surface 101a side of the fin 101 are separated from the fin 101 and scattered from the windward side to the leeward side, they are cut and raised. It is possible to catch (capture) the drain water scattered by the

portions

104 and 105, and to prevent the drain water from scattering toward the cross-flow fan 14 (see FIG. 2) from the end face 101b.

In this way, the drain water generated on the surface of the fin 101 is discharged along the major axis direction g (see FIG. 3) of the flat heat transfer tube 103 arranged with an inclination with respect to the horizontal, and the rib 106. Since the cut-and-raised portion is not provided at the location where the bending process is performed, the retention of drain water is suppressed. In addition, by providing the rib 106 on the side where the notch 102 is not provided (the side opposite to the insertion side), drain water can flow down along the rib 106 and ride on the air flow from the fin 101. Therefore, it is possible to prevent the drain water from separating and splashing into the air outlet 43. Moreover, the intensity | strength of the fin 101 can be raised by providing the rib 106 on the opposite side to the insertion side of the flat heat exchanger tube 103. FIG. In FIG. 8, the front upper heat exchanger 201 has been described as an example, but the same effect can be obtained with the rear heat exchanger 300.

As shown in FIG. 9, in the front lower heat exchanger 202 with the notch 102 rearward and on the upper side in the direction of gravity, the drain water droplets moved to the downstream side by the air flow are converted into flat heat transfer tubes by gravity and surface tension. The water flows down and is drained while being supplemented by the end surface 101a and the

inclined end surfaces

101e and 101d of the fin 101 on the downstream side of 103. At this time, since the cut-and-raised portion 105 is provided in the region indicated by the distance α (see FIG. 7A), it becomes easier to supplement the drain water droplets, and the drain water droplets from the fins 101 It is possible to suppress withdrawal.

In 2nd Embodiment comprised in this way, it extends in parallel (or substantially parallel) with the end surface 101b between the end surface 101b on the opposite side to the insertion side of the fin 101, and the edge part 103d1 of the flat heat exchanger tube 103. Ribs 106 are provided. By providing such a rib 106, it becomes easy to capture the droplet of drain water that has flowed down due to the influence of gravity, and the drainage performance can be improved.

In the second embodiment, the rib 106 is configured by bending the fin 101 into a substantially V shape in a cross-sectional view. Thereby, drainage can be improved, improving the intensity | strength of the fin 101. FIG. Further, since a substantially V-shaped groove 106c (see FIG. 7B) is formed on the opposite side of the rib 106 from the convex side, it is easy to trap the drain water droplets on the surface opposite to the fin 101. It becomes possible to improve drainage.

Moreover, in 2nd Embodiment, the fin 101 has the cut-and-raised part 104 as a protrusion between the adjacent flat heat exchanger tubes 103. FIG. Thereby, the detachment | leave of the drain water of the drain water from the fin 101 can be suppressed, and drainage can be improved. Moreover, in 2nd Embodiment, it has the cut-and-raised part 105 in the protrusion part 101t (refer Fig.7 (a)) of the fin 101. FIG. Thereby, the separation of drain water droplets can be further suppressed, and the drainage can be further improved.

In the second embodiment, as shown in FIG. 7 (b), slits 104b, 104b, which penetrate the cut and raised

portions

104, 105 from the windward side to the leeward side (from the end surface 101a to the end surface 101b), By forming 105b and 105b, it is possible to suppress the air flow from being inhibited and to prevent the airflow resistance from becoming excessive as well as improving drainage (dashed line arrow Y in FIG. 7B). reference).

In the second embodiment, the case where the rib 106 is configured by bending the fin 101 has been described as an example. However, instead of the bending process, a plate-like object is erected on the plane of the fin 101. It may be a configuration.

(Third embodiment)
FIG. 10 shows a heat exchanger for an indoor unit according to the third embodiment, wherein (a) is a longitudinal sectional view, and (b) is a sectional view taken along line BB of (a).
As shown in FIGS. 10A and 10B, the indoor unit 1 of the third embodiment is obtained by removing the cut and raised portion 105 from the configuration of the fin 101 of the second embodiment. That is, the cut-and-raised portion 104 is provided only between the adjacent flat heat transfer tubes 103, and the cut-and-raised portion (projection) is not provided on the protruding portion 101 t of the fin 101.

As described above, in the third embodiment, since the cut and raised portion 105 of the second embodiment is not provided, the deformation of the fin 101 can be suppressed, and the flat heat transfer tube 103 is attached to the fin 101. It is possible to prevent the insertion of the flat heat transfer tube 103 from being difficult, and to improve manufacturability (assembleability).

(Fourth embodiment)
FIG. 11 shows a heat exchanger for an indoor unit according to the fourth embodiment, wherein (a) is a longitudinal sectional view and (b) is a sectional view taken along the line CC of (a).
As shown to Fig.11 (a), the indoor unit 1 of 4th Embodiment is equipped with the rib 107 instead of the rib 106 of 2nd Embodiment and 3rd Embodiment.

The rib 107 is not formed continuously along the longitudinal direction of the fin 101 like the rib 106, and the end surface 101 b and the end portion 103 d 1 of the flat heat transfer tube 103 where the width of the fin 101 is the narrowest (smaller). Is formed intermittently on the flat surface portion 101v.

As shown in FIG. 11B, the rib 107 is formed by press-molding a thin plate-like fin 101. The drain water flows down while being guided by the inclined surface 107 a of the rib 107. Similarly to the rib 106, the V-shaped groove 107c is formed on the opposite side of the convex side of the rib 107, so that the drain water is captured and drained also on the surface opposite to the convex side of the fin 101. can do.

The place where the width of the fin 101 is the narrowest in this way is a place where the droplet of drain water falls due to the influence of gravity, a place where the drain water concentrates, or a place where the water condenses. Therefore, in 4th Embodiment, the rib 107 which becomes a guide here can improve the intensity | strength of the fin 101, and can also improve drainage. By improving the strength of the fin 101 (strength of the flat portion 101v), when the flat heat transfer tube 103 is inserted from one side of the fin 101, it becomes easy to insert, and the manufacturability (assembly) can be improved.

In the fourth embodiment, the rib 107 is intermittently provided in the longitudinal direction of the fin 101, so that the air flow between the rib 107 and the rib 107 can be made smooth and the air flow is inhibited. Can be suppressed.

The rib 107 is not limited to a V-shape in cross-section, and may be a hemispherical, conical or other protrusion-like shape, or a plurality of such shapes as long as it can guide (guide) drain water. It may be.

(Fifth embodiment)
FIG. 12 is a diagram illustrating a configuration of a refrigerant flow path in the indoor unit according to the fifth embodiment.
As shown in FIG. 12, the indoor unit 1 of the fifth embodiment integrates the fin 101 of the first front upper heat exchanger 201A and the fin 101 of the first front lower heat exchanger 202A in the first embodiment. The fin 101B is formed. That is, the fin 101B is configured by laminating a single thin plate made of aluminum or aluminum alloy with a plurality of intervals. Accordingly, the fin 101B is configured to have a boomerang shape (bent shape) in the side view of FIG.

Moreover, the indoor unit 1 of 5th Embodiment is the fin 101C which formed integrally the fin 101 of the 2nd front upper heat exchanger 201B and the fin 101 of the 2nd front lower heat exchanger 202B in 1st Embodiment. It has. That is, the fin 101C is configured by laminating a single thin plate made of aluminum or aluminum alloy with a plurality of intervals. Thereby, it is comprised in the boomerang shape (bent shape) in the side view of FIG.

In the fifth embodiment configured as described above, by providing the

fins

101B and 101C, when drain water (droplets) flows down along the

fins

101B and 101C above the bent portions P1 and P2, the first Compared with the embodiment, it becomes easier to flow from the upper part to the lower part of the bent parts P1 and P2, and the drainage can be improved. Moreover, in 5th Embodiment, since the number of parts can be reduced compared with 1st Embodiment by providing

integrated fin

101B, 101C, the manufacturing process of the indoor unit 1 can be simplified.

In the fifth embodiment, the case where the

fins

101B and 101C are applied to the first embodiment has been described as an example. However, the

fins

101B and 101C may be applied to the second to fourth embodiments. .

As mentioned above, although embodiment was described, embodiment is not limited to these.
For example, in the above-described embodiment, the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300 are configured in two rows in the air flow direction, but depending on the capability of the air conditioner, 1 You may comprise by a row | line | column and may comprise 3 or more rows. Further, the number of rows of the front upper heat exchanger 201, the front lower heat exchanger 202, and the rear heat exchanger 300 need not be the same.

Further, in the above-described embodiment, the long-axis direction g of the flat heat transfer tube 103 is inserted in a direction substantially perpendicular to the end surface 101a of the aluminum fin 101, but when installed in the indoor unit 1 The major axis direction g of the flat heat transfer tube 103 may have an angle with respect to the horizontal so that drain water is drained with respect to the gravity direction G. Moreover, if it installs with a desired angle along the air flow direction so that the further reduction effect of ventilation resistance can be acquired, higher energy saving property can be obtained. Further, when the indoor heat exchangers 10 are arranged in a plurality of rows, different angles may be used in each row or in the rows, and the long axis direction of the flat heat transfer tube has an angle with respect to the horizontal. The effects of the present invention can be obtained.

Further, in the above-described embodiment, the air conditioner having the reheat dehumidifying operation mode has been described as an example. However, the air conditioner having only two operation modes of the cooling operation and the heating operation, or the air conditioner performing only the cooling operation. It can also be applied to the machine. Even in that case, the effects related to energy saving described in the present embodiment can be obtained in the same manner. Therefore, the configuration of the refrigerant flow path is not necessarily the same as that in the present embodiment.

DESCRIPTION OF SYMBOLS 1 Indoor unit 2

Outdoor unit

3, 4 Connection piping 10 Indoor heat exchanger (heat exchanger)
11 First indoor heat exchanger (heat exchanger)
12 Second indoor heat exchanger (heat exchanger)
13 First throttle device 14 Cross-flow fan (blower)
21 Compressor 22 Four-way valve 23 Outdoor heat exchanger 24 Second throttle device 25 Propeller fan 30 Housing 31 Panel 33c Front nose part 41 Front air inlet (air inlet)
42 Top air inlet (air inlet)
43 Air outlet 51 Air filter 52 Air direction control plate 101 Fin 101a Insertion end face 101b

Insertion end face

101d, 101e Inclined end face 101u Plane part 102 Notch part 102a Holding part 102b Wide part 103 Flat

heat transfer tube

103a,

103b Plane part

103c, 103d Curved surface part 103c1 End part on the insertion side 103d1 End part on the opposite side to the insertion side 103s Partition 104, 105 Cut and raised part (protrusion part)
104a, 105a Slit (through hole)
106, 107

Ribs

106a, 107a

Inclined surfaces

106c, 107c Groove 201 Front upper heat exchanger 201A First front upper heat exchanger 201B Second front

upper heat exchanger

201a, 201b

Lower end surface

201c, 201d Front upper heat exchanger Upper end surface of upper heat exchanger 202 Front lower heat exchanger 202A First lower front heat exchanger 202B Second lower

front heat exchanger

202a, 202b Upper end surface of lower front heat exchanger 300 Rear heat exchanger 300A First rear heat Exchanger 300B Second back heat exchanger g Long axis direction of flat heat transfer tube G Gravitational direction Sh Horizontal direction

Claims

A housing having an air inlet and an air outlet;
A heat exchanger for exchanging heat between the air sucked from the air suction port and the refrigerant;
A blower for discharging the air heat-exchanged in the heat exchanger from the air outlet to the outside of the housing, and
The heat exchanger includes a plurality of flat heat transfer tubes through which the refrigerant flows, and fins in which cutout portions into which the flat heat transfer tubes are inserted are formed,
The flat heat transfer tube is located on the inner side of the end surface on the insertion side of the flat heat transfer tube of the fin,
The air conditioner characterized in that the notch has a wide part formed wider than the width of the flat heat transfer tube.
The air conditioner according to claim 1, wherein the wide portion is formed while being widened from an end portion on the insertion side of the flat heat transfer tube toward an end surface on the insertion side.
The distance along the long axis direction of the flat heat transfer tube from the end surface on the insertion side of the fin to the end portion on the insertion side of the flat heat transfer tube is α, and the insertion side of the fin is When the distance along the long axis direction of the flat heat transfer tube from the opposite end surface to the end opposite to the insertion side of the flat heat transfer tube is β, α <β is satisfied. The air conditioner according to claim 1.
The air conditioner according to claim 1, wherein the flat heat transfer tube is inserted perpendicularly or substantially perpendicularly to an end surface on the insertion side.
The air conditioner according to claim 4, wherein the heat exchanger is installed to be inclined with respect to a direction of gravity so as to surround the blower.
The heat exchanger is installed in a state where the insertion side of the flat heat transfer tube is directed upward in the direction of gravity and the long axis direction of the flat heat transfer tube is inclined with respect to the horizontal direction. Item 1 is an air conditioner.
The said fin has a rib extended in parallel or substantially parallel to the said end surface on the opposite side between the said end surface and the said flat heat exchanger tube at least on the opposite side to the said insertion side. Air conditioner.
The air conditioner according to claim 7, wherein the rib is formed by bending the fin into a substantially V shape in a sectional view.
The air conditioner according to claim 7, wherein the fin has a protrusion between the adjacent flat heat transfer tubes.
The air conditioner according to claim 9, wherein the protrusion is a cut-and-raised part formed by cutting and raising the fin.
The air conditioner according to claim 10, wherein the fin does not provide the cut-and-raised portion between the adjacent wide portions.
The air conditioner according to claim 9, wherein the protrusion has a through-hole penetrating from the windward side toward the leeward side.
The air conditioner according to claim 9, wherein the rib and the protrusion are formed so as to protrude on the same surface side.
The heat exchanger includes a front upper heat exchanger located at the upper front of the blower, and a lower front heat exchanger located at the lower front of the blower,
The lower end surface of the front upper heat exchanger and the upper end surface of the lower front heat exchanger are joined in a horizontal or substantially horizontal state. Air conditioner as described in.
The heat exchanger comprises a front upper heat exchanger located at the upper front of the blower, and a rear heat exchanger located at the rear of the blower,
The upper end surface of the front upper heat exchanger and the upper end surface of the rear heat exchanger are joined so as to be horizontal or substantially horizontal and flat. The air conditioner of Claim 1.