CN107076526B - Heat exchanger - Google Patents

Abstract

The flat tubes (63) are arranged along the pipe section direction. The insertion fins (66) are formed with a plurality of notches (67) extending in a tube insertion direction intersecting the tube segment direction and the longitudinal direction of the flat tube, and are arranged along the longitudinal direction of the flat tube (63). The part of the notch part (67) that contacts the flat tube (63) in the state where the flat tube (63) is inserted is the tube insertion part (80), and the insertion fin (66) is formed with: the middle part of the fin ( 81 ), which is sandwiched between the tube insertion parts (80); and the fin near front part (82) towards its near front side. On the insert fin (66), a first fin wing (90) is arranged across the boundary between the fin middle portion (81) and the fin near front portion (82). By cutting the insert fin (66), The first fin wing is formed by bending.

Description

heat exchanger

technical field

The present invention relates to a heat exchanger, and more particularly to a heat exchanger including a plurality of flat tubes and a plurality of insertion fins.

Background technique

Conventionally, as disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 2012-163323 ), there is a heat exchanger including a plurality of flat tubes and a plurality of insertion fins. The flat tubes are arranged along a predetermined pipe segment direction with the flat surfaces facing each other. The insertion fins are formed with a plurality of notches extending in a tube insertion direction intersecting the tube segment direction and the longitudinal direction of the flat tubes for inserting the flat tubes, and the insertion fins are arranged along the longitudinal direction of the flat tubes. Here, the portion of the notch that comes into contact with the flat tube in a state where the flat tube is inserted is the tube insertion portion. Also, the insertion fins are formed with: a plurality of fin middle parts sandwiched between adjacent pipe insertion parts in the pipe section direction; The ends on the near side in the tube insertion direction of the tubes respectively extend toward the near side in the tube insertion direction; The end portion on the inner side in the tube insertion direction of the plurality of fin intermediate portions extends continuously.

Contents of the invention

In the heat exchanger of the above-mentioned Patent Document 1, when inserting the flat tubes into the insertion fins, only the flat tubes are guided to the tube insertion part at the part of the notch that sandwiches the front part of the fins, and the flat tubes are inserted into the insertion fins. In the state of the fin, the flat tube is in contact with the middle part of the fin, but not in contact with the near front part of the fin. Therefore, in a state where the flat tube is inserted into the insertion fin and joined, buckling of the insertion fin may occur at the boundary portion between the fin intermediate portion and the fin near front portion. That is, when the heat exchanger is subjected to an external force or the like in a state where the flat tube is inserted into the insertion fin and joined, the insertion fin may be bent at the boundary between the fin intermediate portion and the fin near portion as the starting point. .

An object of the present invention is to suppress buckling of the insertion fins at the boundary between the fin intermediate portion and the fin near front portion in a heat exchanger including a plurality of flat tubes and a plurality of insertion fins.

The heat exchanger of the first aspect is a heat exchanger including a plurality of flat tubes and a plurality of interposed fins. The flat tubes are arranged along a predetermined pipe segment direction with the flat surfaces facing each other. The insertion fins are formed with a plurality of notches extending along a tube insertion direction intersecting the tube section direction and the length direction of the flat tube for inserting the flat tube, the plurality of insertion fins extending along the length of the flat tube direction configuration. Here, the part of the notch in contact with the flat tube in the state where the flat tube is inserted is the tube insertion part, and a plurality of fin intermediate parts are formed on the insertion fins, which are sandwiched by adjacent tubes in the direction of the tube section. Between the insertion parts; the near front part of the fins, which extends from the ends of the intermediate parts of the plurality of fins on the near side of the tube insertion direction toward the near side of the tube insertion direction; and the inner part of the fins, which extends from the plurality of fins The end portion on the inner side in the tube insertion direction of the intermediate portion extends continuously to the end portion on the inner side in the tube insertion direction of the plurality of fin intermediate portions toward the inner side in the tube insertion direction. In addition, here, the insertion fins are formed by cutting and bending the insertion fins to form first fin wings for holding the insertion fins adjacent in the longitudinal direction of the flat tube. The space between the first fin wings is arranged across the boundary between the fin intermediate portion and the fin near front portion.

Here, since the first fin blade is arranged so as to straddle the boundary portion between the fin intermediate portion and the fin near portion, it is possible to prevent the fin intermediate portion from becoming dislodged in a state where the flat tube is inserted into the insertion fin and joined to the fin. Decrease in fin strength in the direction intersecting the tube insertion direction where the fin is inserted at the boundary portion with the near front portion of the fin. Therefore, in a state where the flat tube is inserted into the insertion fin and joined, occurrence of buckling of the insertion fin at the boundary between the fin intermediate portion and the fin near front portion can be suppressed. Regarding this point, in the case where the fin blades are formed at the front portion of the fins and not disposed at the boundary portion with the middle portion of the fins as in the heat exchanger of Patent Document 1, the fin blades cannot restrain the contact between the middle portion of the fins and the middle portion of the fins. The decrease of the fin strength in the direction intersecting with the tube insertion direction of the insertion fin at the boundary portion near the front portion of the fin, therefore, it is difficult to suppress the flattened tube in the state where the insertion fin is inserted and joined. Buckling of the inserted fin occurs at the boundary portion between the middle portion and the fin near front portion. The same applies to the case where the fin blade is formed in the middle of the fin and not disposed at the boundary with the front portion of the fin.

The heat exchanger of the second aspect is the heat exchanger according to the first aspect, wherein the first fin fin is configured to form a wall portion in the tube insertion direction.

Here, since the first fin blades are arranged in a direction intersecting the boundary between the fin intermediate portion and the fin near portion, it is possible to improve and suppress the decrease in fin strength in the direction intersecting the tube insertion direction where the fin is inserted. Effect. In addition, since the first fin blades are arranged parallel to the passage direction of air along the tube insertion direction, ventilation resistance can be reduced.

A heat exchanger according to a third aspect is the heat exchanger according to the first or second aspect, wherein ribs surrounding the first fin wings are formed on the insertion fins by expanding the insertion fins. Here, the rib does not need to surround the entire periphery of the first fin wing, and may surround most of the first fin wing in a U-shaped shape that surrounds three sides of the first fin wing.

Here, since the ribs surrounding the first fin blades are formed on the insertion fins, it is possible to suppress a reduction in the fin strength of the insertion fins at both end portions of the cut and bent first fin blades.

The heat exchanger of the fourth aspect is the heat exchanger according to any one of the heat exchangers of the first to third aspects, wherein, for the front part of the plurality of fins arranged along the direction of the pipe section and the corresponding middle part of the plurality of fins Each of the parts is configured with a first fin wing.

Here, since the first fin wings are arranged for each of the near front portions of the plurality of fins and the corresponding middle portions of the plurality of fins, when dew occurs in the heat exchanger, the amount of dew on the first fin wings can be reduced. Water retention to ensure the drainage performance of the inserted fins.

The heat exchanger of the fifth aspect is the heat exchanger according to any one of the heat exchangers of the first to fourth aspects, wherein the inner part of the fin is formed by cutting and bending the inserted fin. Two fin wings, the second fin wing is used to maintain the space between the adjacent insertion fins in the length direction of the flat tube.

Here, since the second fin wings are formed in the inner portion of the fins, it is possible to increase the number of positions where adjacent insertion fins contact each other in the longitudinal direction of the flat tube, thereby improving the performance of maintaining the fin intervals.

The heat exchanger of the sixth aspect. The heat exchanger of the fifth aspect, wherein the second fin fin is configured to form a wall portion in the tube insertion direction.

Here, since the second fin blades are arranged parallel to the passage direction of air along the tube insertion direction, ventilation resistance can be reduced.

The heat exchanger of the seventh aspect is the heat exchanger according to the fifth or sixth aspect, wherein the first fin wing and the second fin wing are arranged so as not to overlap each other when the fin is inserted as viewed from the tube insertion direction.

Here, since the first fin blade and the second fin blade are arranged so as not to overlap each other when viewing the insertion fin from the tube insertion direction, the length of the flat tube can be increased when the insertion fin is viewed from the tube insertion direction. The parallelism between the inserted fins adjacent in the direction can further improve the performance of maintaining the fin spacing.

Description of drawings

FIG. 1 is a schematic configuration diagram of an air conditioner including an outdoor heat exchanger as a heat exchanger according to an embodiment of the present invention.

Fig. 2 is a perspective view showing the appearance of the outdoor unit.

Fig. 3 is a plan view showing a state in which the top plate of the outdoor unit is removed.

Fig. 4 is a perspective view showing a state in which the top panel, the front panel, and the side panels of the outdoor unit are removed.

Fig. 5 is a schematic perspective view of the outdoor heat exchanger.

Fig. 6 is a partial enlarged view of the heat exchange unit in Fig. 5 .

Fig. 7 is a partially enlarged view showing a state in which the heat exchange section of Fig. 6 is viewed from a direction along the longitudinal direction of the heat transfer tube.

FIG. 8 is a diagram showing main parts of a heat transfer fin.

Fig. 9 is a sectional view taken along line I-I of Fig. 8 .

Fig. 10 is a sectional view of II-II, a sectional view of III-III and a sectional view of IV-IV of Fig. 8 .

Fig. 11 is a view of Fig. 8 viewed from the front side in the tube insertion direction and a view of Fig. 8 viewed from the rear side in the tube insertion direction.

Fig. 12 is a V-V sectional view of Fig. 8 .

FIG. 13 is a view showing a heat exchanger according to a modified example, and is a view corresponding to FIG. 7 .

FIG. 14 is a diagram showing a heat exchanger according to a modified example, and is a diagram corresponding to FIG. 7 .

detailed description

Next, embodiments of the heat exchanger according to the present invention and modifications thereof will be described with reference to the drawings. In addition, the specific structure of the heat exchanger of this invention is not limited to the following embodiment and its modification, It can change in the range which does not deviate from the summary of invention.

(1) Basic structure of the air conditioner

FIG. 1 is a schematic configuration diagram of an air conditioner 1 including an outdoor heat exchanger 23 as a heat exchanger according to an embodiment of the present invention.

The air conditioner 1 is a device capable of cooling and heating the interior of a building or the like by performing a vapor compression refrigeration cycle. The air conditioner 1 is mainly configured by connecting an outdoor unit 2 and an indoor unit 4 . Here, the outdoor unit 2 and the indoor unit 4 are connected via a liquid refrigerant communication pipe 5 and a gas refrigerant communication pipe 6 . That is, the outdoor unit 2 and the indoor unit 4 are connected via the refrigerant communication pipes 5 and 6 to form a vapor compression refrigerant circuit 10 of the air conditioner 1 .

<indoor unit>

The indoor unit 4 is installed indoors and constitutes a part of the refrigerant circuit 10 . The indoor unit 4 mainly has an indoor heat exchanger 41 .

The indoor heat exchanger 41 is a heat exchanger that functions as an evaporator of the refrigerant to cool the indoor air during the cooling operation, and functions as a radiator of the refrigerant to heat the indoor air during the heating operation. device. The liquid side of the indoor heat exchanger 41 is connected to the liquid refrigerant communication pipe 5 , and the gas side of the indoor heat exchanger 41 is connected to the gas refrigerant communication pipe 6 .

The indoor unit 4 has an indoor fan 42 for sucking indoor air into the indoor unit 4 and exchanging heat with the refrigerant in the indoor heat exchanger 41 to supply the room as supply air. That is, the indoor unit 4 has an indoor fan 42 as a fan that supplies indoor air to the indoor heat exchanger 41 as a heating source or a cooling source of the refrigerant flowing in the indoor heat exchanger 41 . Here, as the indoor fan 42, a centrifugal fan, a multi-blade fan, or the like driven by the indoor fan motor 42a is used.

<outdoor unit>

The outdoor unit 2 is installed outdoors and constitutes a part of the refrigerant circuit 10 . The outdoor unit 2 mainly has a compressor 21 , a four-way switching valve 22 , an outdoor heat exchanger 23 , an expansion valve 24 , a liquid side closing valve 25 and a gas side closing valve 26 .

The compressor 21 is a device that compresses the low-pressure refrigerant in the refrigeration cycle to a high pressure. The compressor 21 has a hermetic structure in which a displacement compression element (not shown) such as a rotary type or a scroll type is driven to rotate by a compressor motor 21a. A suction pipe 31 is connected to the suction side of the compressor 21 , and a discharge pipe 32 is connected to the discharge side. The suction pipe 31 is a refrigerant pipe connecting the suction side of the compressor 21 and the four-way switching valve 22 . The discharge pipe 32 is a refrigerant pipe connecting the discharge side of the compressor 21 and the four-way switching valve 22 .

The four-way switching valve 22 is a switching valve for switching the flow direction of the refrigerant in the refrigerant circuit 10 . During cooling operation, the four-way switching valve 22 switches to a refrigeration cycle state in which the outdoor heat exchanger 23 functions as a radiator for the refrigerant compressed in the compressor 21, Furthermore, the indoor heat exchanger 41 is made to function as an evaporator for the refrigerant that radiates heat in the outdoor heat exchanger 23 . That is, during cooling operation, the four-way switching valve 22 connects the discharge side of the compressor 21 (here, the discharge pipe 32 ) to the gas side of the outdoor heat exchanger 23 (here, the first gas refrigerant pipe 33 ) (see The solid line of the four-way switching valve 22 of Fig. 1). And, the suction side of the compressor 21 (here, the suction pipe 31) is connected to the side of the gas refrigerant communication pipe 6 (here, the second gas refrigerant pipe 34) (see the solid line of the four-way switching valve 22 in FIG. 1 ). . In addition, during the heating operation, the four-way switching valve 22 switches to a heating cycle state in which the outdoor heat exchanger 23 is used as the cooling medium for the refrigerant that radiates heat in the indoor heat exchanger 41 . The evaporator functions as an evaporator, and the indoor heat exchanger 41 functions as a radiator of the refrigerant compressed by the compressor 21 . That is, during the heating operation, the four-way switching valve 22 connects the discharge side of the compressor 21 (here, the discharge pipe 32 ) to the side of the gas refrigerant communication pipe 6 (here, the second gas refrigerant pipe 34 ) (see The dotted line of the four-way switching valve 22 of Fig. 1). And, the suction side of the compressor 21 (here, the suction pipe 31) is connected to the gas side of the outdoor heat exchanger 23 (here, the first gas refrigerant pipe 33) (refer to the dotted line of the four-way switching valve 22 in FIG. 1 ). . Here, the first gas refrigerant pipe 33 is a refrigerant pipe that connects the four-way switching valve 22 and the gas side of the outdoor heat exchanger 23 . The second gas refrigerant pipe 34 is a refrigerant pipe that connects the four-way switching valve 22 and the gas side closing valve 26 .

The outdoor heat exchanger 23 is a heat exchanger that functions as a radiator for refrigerant that uses outdoor air as a cooling source during cooling operation and as an evaporator for refrigerant that uses outdoor air as a heating source during heating operation. switch. The liquid side of the outdoor heat exchanger 23 is connected to the liquid refrigerant pipe 35 , and the gas side is connected to the first gas refrigerant pipe 33 . The liquid refrigerant pipe 35 is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the liquid refrigerant communication pipe 5 side.

The expansion valve 24 is a valve that decompresses the high-pressure refrigerant of the refrigeration cycle that dissipates heat in the outdoor heat exchanger 23 to the low pressure of the refrigeration cycle during cooling operation. In addition, the expansion valve 24 is a valve that decompresses the high-pressure refrigerant of the refrigeration cycle that dissipates heat in the indoor heat exchanger 41 to the low pressure of the refrigeration cycle during the heating operation. The expansion valve 24 is provided at a portion of the liquid refrigerant pipe 35 close to the liquid side shutoff valve 25 . Here, an electric expansion valve is used as the expansion valve 24 .

The liquid-side shutoff valve 25 and the gas-side shutoff valve 26 are valves provided at connection ports connected to external equipment and piping (specifically, the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 ). The liquid side shutoff valve 25 is provided at the end of the liquid refrigerant pipe 35 . The gas side shutoff valve 26 is provided at the end of the second gas refrigerant pipe 34 .

The outdoor unit 2 has an outdoor fan 36 for sucking outdoor air into the outdoor unit 2 and exchanging heat with the refrigerant in the outdoor heat exchanger 23 to discharge it to the outside. That is, the outdoor unit 2 has the outdoor fan 36 as a fan that supplies the outdoor heat exchanger 23 with outdoor air that is a cooling source or a heating source for the refrigerant flowing in the outdoor heat exchanger 23 . Here, as the outdoor fan 36, a propeller fan or the like driven by the outdoor fan motor 36a is used.

<Refrigerant communication tube>

The refrigerant communication pipes 5 and 6 are refrigerant pipes that are installed on site when the air conditioner 1 is installed in a building or other installation place, and are used in accordance with installation conditions such as the installation place and the combination of the outdoor unit 2 and the indoor unit 4. Refrigerant tubes of various lengths and diameters.

(2) Basic operation of the air conditioner

Next, the basic operation of the air conditioner 1 will be described using FIG. 1 . The air conditioner 1 can perform cooling operation and heating operation as basic operations.

<Cooling operation>

During the cooling operation, the four-way switching valve 22 is switched to the refrigeration cycle state (the state indicated by the solid line in FIG. 1 ).

In the refrigeration circuit 10, the low-pressure gas refrigerant of the refrigeration cycle is sucked into the compressor 21, compressed to a high pressure of the refrigeration cycle, and then discharged.

The high-pressure gas refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 through the four-way switching valve 22 .

The high-pressure gas refrigerant sent to the outdoor heat exchanger 23 performs heat exchange with the outdoor air supplied as a cooling source by the outdoor fan 36 in the outdoor heat exchanger 23 functioning as a refrigerant radiator, and radiates heat. Become a high-pressure liquid refrigerant.

The high-pressure liquid refrigerant that dissipates heat in the outdoor heat exchanger 23 is sent to the expansion valve 24 .

The high-pressure liquid refrigerant sent to the expansion valve 24 is decompressed to the low pressure of the refrigeration cycle by the expansion valve 24 to become a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant depressurized by the expansion valve 24 is sent to the indoor heat exchanger 41 through the liquid-side shut-off valve 25 and the liquid-refrigerant communication pipe 5 .

The low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchanger 41 evaporates in the indoor heat exchanger 41 by exchanging heat with indoor air supplied as a heating source by the indoor fan 42 . As a result, the indoor air is cooled and then supplied into the room to cool the room.

The low-pressure gas refrigerant evaporated in the indoor heat exchanger 41 is sucked into the compressor 21 again through the gas refrigerant communication pipe 6 , the gas side closing valve 26 , and the four-way switching valve 22 .

<Heating operation>

During the heating operation, the four-way switching valve 22 is switched to the heating cycle state (the state indicated by the dotted line in FIG. 1 ).

In the refrigerant circuit 10, the low-pressure gas refrigerant of the refrigerating cycle is sucked into the compressor 21, compressed to the high-pressure of the refrigerating cycle, and discharged.

The high-pressure gas refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 through the four-way switching valve 22 , the gas side closing valve 26 , and the gas refrigerant communication pipe 6 .

The high-pressure gas refrigerant sent to the indoor heat exchanger 41 passes through the indoor fan 42 in the indoor heat exchanger 41 to exchange heat with indoor air supplied as a cooling source to dissipate heat, and becomes a high-pressure liquid refrigerant. As a result, the indoor air is heated and then supplied into the room to heat the room.

The high-pressure liquid refrigerant that radiates heat in the indoor heat exchanger 41 is sent to the expansion valve 24 through the liquid refrigerant communication pipe 5 and the liquid-side closing valve 25 .

The high-pressure liquid refrigerant sent to the expansion valve 24 is decompressed to the low pressure of the refrigeration cycle by the expansion valve 24 to become a low-pressure gas-liquid two-phase refrigerant. The low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve 24 is sent to the outdoor heat exchanger 23 .

The low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 passes through the outdoor fan 36 and the outdoor air supplied as a heating source in the outdoor heat exchanger 23 functioning as an evaporator of the refrigerant. It is evaporated by heat exchange and becomes a low-pressure gas refrigerant.

The low-pressure refrigerant evaporated in the outdoor heat exchanger 23 passes through the four-way switching valve 22 and is sucked into the compressor 21 again.

(3) Basic structure of the outdoor unit

Next, the basic configuration of the outdoor unit 2 will be described using FIGS. 1 to 4 . Here, FIG. 2 is a perspective view showing the appearance of the outdoor unit 2 . FIG. 3 is a plan view showing a state in which the top plate 57 of the outdoor unit 2 is removed. FIG. 4 is a perspective view showing a state in which the top plate 57 , front plates 55 , 56 , and side plates 53 , 54 of the outdoor unit 2 are removed. In addition, in the following description, unless otherwise specified, terms such as "upper", "lower", "left", "right", "vertical", "front", "side", "rear", " Words such as "top surface" and "bottom surface" refer to directions and surfaces when the surface on the side of the fan blowing grill 55b is defined as the front.

The outdoor unit 2 has a structure (a so-called box-type structure) in which the inside of the unit casing 51 is divided into a blower chamber S1 and a machine chamber S2 by a partition plate 58 extending in the vertical direction. The outdoor unit 2 is configured to suck outdoor air into the inside from the back surface and part of the side surfaces of the unit casing 51 and then discharge the air from the front surface of the unit casing 51 . The outdoor unit 2 mainly includes: a unit casing 51; equipment/pipes forming the refrigerant circuit 10, the refrigerant circuit includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, and a closing valve 25 , 26 and refrigerant pipes 31 to 35 connecting these devices; and an outdoor fan 36 and an outdoor fan motor 36a. In addition, here, an example in which the blower chamber S1 is formed on the left side of the unit casing 51 and the machine chamber S2 is formed on the right side of the unit casing 51 has been described, but the left and right may be reversed.

The unit casing 51 is formed in a substantially rectangular parallelepiped shape, and mainly accommodates: equipment/pipes constituting the refrigerant circuit 10 including the compressor 21, the four-way switching valve 22, the outdoor heat exchanger 23, the expansion valve 24, the closing Valves 25, 26 and refrigerant pipes 31 to 35 connecting these devices; and an outdoor fan 36 and an outdoor fan motor 36a. The unit casing 51 has: a bottom plate 52 on which the equipment/pipes 21-26, 31-35 and the outdoor fan 36 constituting the refrigerant circuit 10 are mounted; a blower chamber side plate 53, a machine room side plate 54, and a blower chamber Side front board 55 , machine room side front board 56 , top board 57 and two mounting feet 59 .

The bottom plate 52 is a plate-shaped member constituting the bottom portion of the unit case 51 .

The blower chamber side side plate 53 is a plate-shaped member constituting the side portion (here, the left side portion) of the unit casing 51 near the blower chamber S1. The lower part of the blower chamber-side side plate 53 is fixed to the bottom plate 52, and here, the front side end of the blower chamber-side side plate 53 and the left side end of the blower chamber-side front plate 55 are integral members. The side plate 53 on the blower chamber side is formed with a side fan inlet 53 a for sucking outdoor air into the unit case 51 from the side of the unit case 51 by the outdoor fan 36 . In addition, the blower chamber side side plate 53 may be a separate body from the blower chamber side front plate 55 .

The machine compartment side side plate 54 is a plate-shaped portion constituting part of the side portion (here, the right side portion) of the unit case 51 near the machine compartment S2 and the rear portion of the unit case 51 near the machine compartment S2. The lower part of the machine compartment side panel 54 is fixed to the bottom panel 52 . A rear fan suction port 53b for passing the outdoor fan 36 is formed between the rear end of the blower chamber side plate 53 and the end portion of the machine compartment side plate 54 on the blower chamber S1 side. Outdoor air is sucked into the unit case 51 from the back side of the unit case 51 .

The blower chamber side front plate 55 is a plate-shaped member constituting the front part of the blower chamber S1 of the unit case 51 . The lower part of the blower chamber side front plate 55 is fixed to the base plate 52, and here, the left side end of the blower chamber side front plate 55 and the front end of the blower chamber side side plate 53 are integral members. The fan outlet 55a for blowing out the outdoor air sucked into the unit case 51 by the outdoor fan 36 to the outside is provided in the blower chamber side front plate 55 . A fan outlet grill 55b covering the fan outlet 55a is provided on the front side of the blower chamber side front plate 55 . In addition, the blower chamber side front plate 55 may be a separate body from the blower chamber side side plate 53 .

The machine room side front plate 56 is a plate-like member constituting a part of the front part of the machine room S2 of the unit case 51 and a part of the side part of the machine room S2 of the unit case 51 . The end portion of the machine room side front plate 56 on the blower chamber S1 side is fixed to the end portion of the blower room side front plate 55 on the machine room S2 side, and the end portion of the machine room side front plate 56 on the back side is fixed to the machine room side. An end portion on the front side of the side plate 54 .

The top plate 57 is a plate-shaped member constituting the top surface portion of the unit case 51 . The top plate 57 is fixed to the blower chamber side plate 53 , the machine chamber side side plate 54 , and the blower chamber side front plate 55 .

The partition plate 58 is a plate-shaped member arranged on the bottom plate 52 and extending in the vertical direction. Here, the inside of the unit case 51 is divided into left and right by the partition plate 58, and the blower chamber S1 on the left side and the machine room S2 on the right side are formed. The lower part of the partition plate 58 is fixed to the bottom plate 52, the front end of the partition plate 58 is fixed to the fan chamber side front plate 55, and the rear end of the partition plate 58 extends to the machine room of the outdoor heat exchanger 23. The side end of S2.

The mounting feet 59 are plate-shaped members extending in the front-rear direction of the unit case 51 . The mounting leg 59 is a member fixed to the mounting surface of the outdoor unit 2 . Here, the outdoor unit 2 has two mounting legs 59, one is disposed near the blower chamber S1, and the other is disposed near the machine chamber S2.

The outdoor fan 36 is a propeller fan having a plurality of blades, and is disposed on the front side of the outdoor heat exchanger 23 so as to face the front of the unit case 51 (here, the fan outlet 55 a ) in the blower chamber S1. . The outdoor fan motor 36a is disposed between the outdoor fan 36 and the outdoor heat exchanger 23 in the front-rear direction in the blower chamber S1. The outdoor fan motor 36 a is supported by a motor support base 36 b placed on the bottom plate 52 . And the outdoor fan 36 is pivotally supported by the motor 36a for outdoor fans.

The outdoor heat exchanger 23 is a substantially L-shaped heat exchanger panel in plan view, and is placed on the bottom plate 52 along the side (here, the left side) and the back of the unit casing 51 in the blower chamber S1. .

Here, the compressor 21 is a vertical cylindrical hermetic compressor, and is placed on the bottom plate 52 in the machine chamber S2.

(4) Basic structure of outdoor heat exchanger

Next, the basic structure of the outdoor heat exchanger 23 will be described using FIGS. 1 to 6 . Here, FIG. 5 is a schematic perspective view of the outdoor heat exchanger 23 . FIG. 6 is a partial enlarged view of the heat exchange unit 60 in FIG. 5 . In addition, in the following description, unless otherwise specified, words indicating directions and surfaces refer to directions and surfaces based on the state in which the outdoor heat exchanger 23 is mounted on the outdoor unit 2 .

The outdoor heat exchanger 23 mainly has: a heat exchange part 60, which performs heat exchange between the outdoor air and the refrigerant; side (here, the right end side); and a connecting header 74 provided on the other end side (here, the left front end side) of the heat exchange portion 60 . The outdoor heat exchanger 23 is an all-aluminum heat exchanger made of aluminum or aluminum alloy, the refrigerant distributor 70, the inlet and outlet headers 71, the intermediate header 72, the connecting header 74 and the heat exchange part 60 are all aluminum heat exchangers made of aluminum or aluminum alloy. Brazing such as soldering is used to join the parts.

<Heat Exchange Unit>

The heat exchanging unit 60 has an upwind side heat exchanging unit 61 constituting a part on the windward side of the outdoor heat exchanger 23 and a leeward side heat exchanging unit 62 constituting a part on the leeward side of the outdoor heat exchanger 23 . The passing direction of the outside air in the unit casing 51 generated by the driving has a structure in which two rows of heat exchange parts 61 and 62 are arranged in parallel. The windward heat exchange unit 61 is disposed closer to the side (here, the left side) and the rear side of the unit casing 51 than the leeward heat exchange unit 62 . That is, the part of the heat exchange part 60 that is located on the windward side closer to the fan suction ports 53a and 53b with respect to the passing direction of the outdoor air is the windward side heat exchange part 61, and is located farther from the fan suction ports 53a and 53b than the windward side heat exchange part 61. The part on the far leeward side is the leeward side heat exchange unit 62 . Further, the windward side heat exchange unit 61 has an upwind side main heat exchange unit 61 a constituting an upper portion of the outdoor heat exchanger 23 and an upwind side sub heat exchange portion 61 b constituting a lower portion of the outdoor heat exchanger 23 . Moreover, the leeward side heat exchange part 62 has the leeward side main heat exchange part 62a which comprises the upper part of the outdoor heat exchanger 23, and the leeward side sub heat exchange part 62b which comprises the lower part of the outdoor heat exchanger 23.

The heat exchange part 60 is a fin-inserted heat exchanger part composed of a plurality of heat transfer tubes 63 and a plurality of heat transfer fins 66, the heat transfer tubes 63 are formed of flat tubes, and the heat transfer fins 66 Consists of inserted fins. The heat transfer tube 63 is made of aluminum or an aluminum alloy, and is a flat porous tube having a flat surface 64 serving as a heat transfer surface and a plurality of small internal channels 65 through which the refrigerant flows. A plurality of heat transfer tubes 63 are arranged at intervals along a predetermined tube segment direction with flat surfaces 64 facing each other. One end (here, the right end) in the longitudinal direction is connected to the inlet and outlet header 71 or the intermediate header 72. The other end (here, the left front end) is connected to the connection header 74 . That is, the plurality of heat transfer tubes 63 are arranged between the inlet/outlet header 71 , the intermediate header 72 , and the connection header 74 . Here, since the flat surface 64 of the flat tube 63 faces the vertical direction, the pipe segment direction refers to the vertical direction. The length direction of the heat pipe 63 refers to the horizontal direction along the side (here, the left side) and the back of the unit case 51 . The heat transfer fins 66 are made of aluminum or an aluminum alloy, and a plurality of them are arranged at intervals along the longitudinal direction of the heat transfer tube 63 . The heat transfer fins 66 are formed with a plurality of notches 67 extending in a tube insertion direction intersecting the tube segment direction and the length direction of the heat transfer tubes 63 for inserting the heat transfer tubes 63 . Here, the tube section direction is the vertical direction, and the length direction of the heat transfer tube 63 is the horizontal direction along the side (here, the left side) and the back side of the unit case 51, so the tube insertion direction refers to the direction in which the heat transfer tube 63 is aligned. The horizontal direction intersecting the longitudinal direction of the unit casing 51 also coincides with the passage direction of the outdoor air in the unit casing 51 . The notch 67 extends elongately in the horizontal direction from one edge of the heat transfer fin 66 in the tube insertion direction (here, an edge on the windward side with respect to the passing direction of outdoor air). In addition, here, the plurality of heat transfer tubes 63 are divided into: a heat transfer tube group constituting the upwind side main heat exchange part 61a, a heat transfer tube group constituting the upwind side sub heat exchange part 61b, and a heat transfer tube group constituting the leeward side main heat exchange part 62a. The heat transfer tube group and the heat transfer tube group constituting the leeward side sub heat exchange part 62b. In addition, the plurality of heat transfer fins 66 are divided into fin groups constituting an upwind side row common to the upwind side main heat exchange portion 61 a and the upwind side sub heat exchange portion 61 b, and fin groups constituting the leeward side main heat exchange portion 62 a and the leeward side heat exchange portion 62 a. The fin group of the row on the leeward side common to the side sub heat exchange parts 62b.

<Refrigerant splitter>

The refrigerant flow divider 70 is connected between the liquid refrigerant pipe 35 and the lower portion of the inlet/outlet header 71 . The refrigerant flow divider 70 is a member made of aluminum or an aluminum alloy along the vertical direction. The refrigerant flow divider 70 is configured to divide the refrigerant flowing in through the liquid refrigerant pipe 35 and guide it to the lower portion of the inlet/outlet header 71 , or to combine the refrigerant flowing in through the lower portion of the inlet/outlet header 71 and guide it to the liquid refrigerant pipe. 35.

<Entrance and exit header>

The inlet/outlet header 71 is provided on one end side (here, the right end side) of the windward heat exchange unit 61 in the heat exchange unit 60 . Furthermore, one end (here, the right end) of the heat transfer tube 63 constituting the windward side heat exchange unit 61 is connected to the inlet/outlet header 71 . The inlet/outlet header 71 is a member made of aluminum or an aluminum alloy that extends in the vertical direction. The inner space of the inlet/outlet header 71 is partitioned up and down by a waffle (not shown), and its upper space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the main heat exchange part 61a on the windward side, and its lower space The space communicates with one end (here, the right end) of the heat transfer pipe 63 constituting the windward side sub heat exchange portion 61b. Further, the upper portion of the inlet/outlet header 71 is connected to the first gas refrigerant pipe 33 , and refrigerant is exchanged between the windward side main heat exchange portion 61 a and the first gas refrigerant pipe 33 . In addition, the lower portion of the inlet/outlet header 71 is connected to the refrigerant flow divider 70 , and is configured to exchange refrigerant with the refrigerant 70 .

<Intermediate header>

The intermediate header 72 is provided on one end side (here, the right end side) of the leeward side heat exchange portion 62 in the heat exchange portion 60 . Furthermore, one end (here, the right end) of the heat transfer tube 63 constituting the leeward side heat exchange unit 62 is connected to the intermediate header 72 . The intermediate header 72 is a member formed of aluminum or an aluminum alloy and extending in the vertical direction. The internal space of the intermediate header 72 is partitioned up and down by a mountain portion (not shown), and its upper space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the leeward side main heat exchange portion 62a, and its lower space communicates with one end (here, the right end) of the heat transfer pipe 63 constituting the leeward side main heat exchanging portion 62a, and its lower space communicates with the end of the heat transfer tube 63 constituting the leeward side main heat exchange portion 62a, and its lower space communicates with the One end (here, the right end) of the heat transfer pipe 63 of the leeward side sub heat exchange portion 62b communicates. In addition, the upper space and the lower space of the intermediate header 72 are separated into a plurality of spaces by a mountain portion (not shown) according to the number of paths of the heat exchange unit 60 , and the upper space and the lower space are communicated through the intermediate connecting pipe 73 and the like. Furthermore, the intermediate header 72 is configured to exchange refrigerant between the leeward side main heat exchange unit 62a and the leeward side sub heat exchange unit 62b.

<link header>

The connecting header 74 is provided on the other end side (here, the left front end side) of the heat exchange unit 60 . Furthermore, the other end (here, the left end) of the heat transfer tube 63 constituting the heat exchange unit 60 is connected to the connection header 74 . The connecting header 74 is a member made of aluminum or an aluminum alloy that extends in the vertical direction. A connection space is formed in the connection header 74 for connecting the other end (here, the left front end) of the heat transfer tube 63 constituting the windward side heat exchange unit 61 to the heat transfer tube 63 constituting the leeward side heat exchange unit 62 . The other end (here the left front end) is connected. Furthermore, the connection header 74 is configured to exchange refrigerant between the windward heat exchange unit 61 and the leeward heat exchange unit 62 .

When the outdoor heat exchanger 23 having such a structure functions as a refrigerant evaporator, as shown by arrows showing the flow of refrigerant in FIG. 5 , the refrigerant flowing in from the liquid refrigerant pipe 35 passes through The refrigerant flow divider 70 and the lower part of the inlet/outlet header 71 are guided to the windward side sub heat exchange part 61b. Furthermore, the refrigerant having passed through the upwind side sub heat exchange unit 61 b passes through the lower portion of the connection header 74 and is guided to the leeward side sub heat exchange unit 62 b. Furthermore, the refrigerant having passed through the leeward side sub heat exchange unit 62 b is guided to the leeward side main heat exchange unit 62 a through the intermediate header 72 . Furthermore, the refrigerant having passed through the leeward side main heat exchange unit 62 a passes through the upper portion of the connecting header 74 and is guided to the windward side main heat exchange unit 61 a. Furthermore, the refrigerant having passed through the windward main heat exchange unit 61 a passes through the upper portion of the inlet/outlet header 71 and flows out to the first gas refrigerant pipe 33 . The refrigerant evaporates by exchanging heat with the outdoor air during the flow of the refrigerant. In addition, when the outdoor heat exchanger 23 functions as a refrigerant radiator, the refrigerant flowing in from the first gas refrigerant pipe 33 passes through the inlet and outlet as shown by the arrows showing the flow of the refrigerant in FIG. The upper part of the header 71 is guided to the windward side main heat exchange part 61a. Furthermore, the refrigerant having passed through the upwind side main heat exchange unit 61 a passes through the upper portion of the connection header 74 and is guided to the leeward side main heat exchange unit 62 a. Furthermore, the refrigerant having passed through the leeward side main heat exchange unit 62 a passes through the intermediate header 72 and is guided to the leeward side sub heat exchange unit 62 b. Furthermore, the refrigerant having passed through the leeward side sub heat exchange unit 62 b is guided to the windward side sub heat exchange unit 61 b through the lower portion of the connection header 74 . Furthermore, the refrigerant having passed through the windward side sub heat exchange unit 61b flows out to the liquid refrigerant pipe 35 through the lower portion of the inlet/outlet header 71 and the refrigerant flow divider 70 . During the flow of the refrigerant, the refrigerant dissipates heat by exchanging heat with the outdoor air.

(5) Detailed structure of heat transfer fins

Next, the detailed structure of the heat transfer fin 66 is demonstrated using FIGS. 3-12. Here, FIG. 7 is a partially enlarged view illustrating a state in which the heat exchange portion 60 of FIG. 6 is viewed from a direction along the longitudinal direction of the heat transfer tube 63 . FIG. 8 is a diagram showing main parts of the heat transfer fins 66 . Fig. 9 is a sectional view taken along line I-I of Fig. 8 . Fig. 10 is a sectional view of II-II, a sectional view of III-III and a sectional view of IV-IV of Fig. 8 . Fig. 11 is a view of Fig. 8 viewed from the front side in the tube insertion direction and a view of Fig. 8 viewed from the rear side in the tube insertion direction. Fig. 12 is a V-V sectional view of Fig. 8 .

<basic shape>

The heat transfer fins 66 are plate-shaped fins that are long in one direction (here, vertically) formed by pressing a plate made of aluminum or an aluminum alloy.

The plurality of notches 67 of the heat transfer fins 66 are formed at predetermined intervals in the pipe section direction of the heat transfer fins 66 . Here, a portion of the notch portion 67 that contacts the heat transfer tube 63 in a state where the heat transfer tube 63 is inserted constitutes the tube insertion portion 80 . The vertical width of the tube insertion portion 80 is substantially equal to the width between the flat surfaces 64 of the heat transfer tube 63 , and the horizontal width of the tube insertion portion 80 and the width of the flat tube 63 in the direction intersecting the flat surface 64 are substantially equal. substantially equal. The peripheral portion of the tube insertion portion 80 protrudes from the base surface 66a of the heat transfer fin 66 toward one side in the longitudinal direction of the heat transfer tube 63 (here, the near side of the paper in FIGS. 7 and 8 ). In addition, the base surface 66 a of the heat transfer fin 66 refers to the fin surface of the heat transfer fin 66 in a state before each part including the tube insertion part 80 is formed. Furthermore, the heat transfer tube 63 is inserted into the notch part 67, is guided to the tube insertion part 80 which is a part of the notch part 67, and is joined to the peripheral part of the tube insertion part 80 by brazing. Further, the heat transfer fins 66 are formed with a plurality of fin intermediate portions 81 sandwiched between adjacent tube insertion portions 80 in the tube segment direction. In addition, the heat transfer fin 66 is formed with a fin near front portion 82, which is formed from the near side of the pipe insertion direction of the plurality of fin intermediate portions 81 (here, the windward side with respect to the passage direction of outdoor air). ) respectively extend toward the near side of the tube insertion direction. In addition, the heat transfer fin 66 is formed with a fin back portion 83 that is located on the back side of the tube insertion direction of the plurality of fin intermediate portions 81 (here, the leeward side with respect to the passage direction of outdoor air). ) extends toward the inner side in the tube insertion direction and extends continuously with the end of the plurality of fin intermediate portions 81 on the inner side in the tube insertion direction.

In addition, in such heat transfer fins 66 , for example, it is conceivable to form a plurality of mountain portions forming a mountain-shaped inclined surface along the tube insertion direction. However, if such a plurality of mountain portions are formed, when the heat transfer tube 63 is inserted into the notch portion 67 of the heat transfer fin 66, a valley between the adjacent mountain portions along the tube insertion direction may be generated. Buckling of the heat transfer fins 66 . That is, when the heat transfer tubes 63 are inserted into the notches 67 of the heat transfer fins 66 , the valleys between the peaks form V-shaped creases, and the heat transfer fins 66 may be bent. Therefore, buckling of the heat transfer fins 66 needs to be suppressed when the heat transfer tubes 63 are inserted into the notches 67 .

In addition, in such a heat transfer fin 66 , the portion of the notch 67 that sandwiches the fin near front portion 82 guides the heat transfer tube 63 to the tube insertion position only when the heat transfer tube 63 is inserted into the heat transfer fin 66 . 80 , in a state where the heat transfer tube 63 is inserted into the heat transfer fin 66 , the heat transfer tube 63 is in contact with the fin intermediate portion 81 but not in contact with the fin near front portion 82 . Therefore, in the state where the heat transfer tube 63 is inserted into the heat transfer fin 66 and joined, buckling of the heat transfer fin 66 may occur at the boundary portion between the fin intermediate portion 81 and the fin near front portion 82 . . That is, when the outdoor heat exchanger 23 receives an external force or the like in a state where the heat transfer tube 63 is inserted into the heat transfer fin 66 and is joined, the boundary portion between the fin intermediate portion 81 and the fin near portion 82 may be damaged. As a starting point, the heat transfer fins 66 are bent. On the other hand, it is necessary to suppress buckling of the heat transfer fin 66 at the boundary between the fin intermediate portion 81 and the fin near front portion 82 .

Therefore, here, in order to suppress the buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67 and the deformation of the heat transfer fins 66 at the boundary between the fin intermediate portion 81 and the fin near portion 82 Buckling occurs, and the heat transfer fins 66 are designed as follows.

<Base part>

First, on the heat transfer fin 66 , the base portion 84 forming the flat surface 85 is formed on the plurality of fin intermediate portions 81 by expanding the heat transfer fin 66 . The base portion 84 is disposed at a portion near the center of the fin intermediate portion 81 in the tube insertion direction. Here, the flat surface 85 is arranged at a position where the whole thereof protrudes toward one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8 ) than the base surface 66 a of the heat transfer fin 66 .

In this way, here, since the base portion 84 forming the flat surface 85 is formed in the fin intermediate portion 81, it is different from the case where the mountain portion is formed in the heat transfer fin 66. When inserted into the notch 67 of 66, there is no part of a V-shaped crease like a valley between mountains. Therefore, the fin strength in the direction intersecting with the tube insertion direction can be increased, and buckling of the heat transfer fins 66 can be suppressed when the heat transfer tubes 63 are inserted into the notches 67 .

In addition, the protrusion height of the base portion 84 from the base surface 66 a of the heat transfer fin 66 is set to be greater than or equal to the protrusion height of the tube insertion portion 80 . Therefore, the effect of improving the fin strength can be enhanced by forming the base portion 84 .

In addition, the flat surface 85 has: a first side 85a and a second side 85b parallel to each other extending along the tube insertion direction; The third side 85c; and the fourth side 85d that connects the ends on the inner side in the tube insertion direction of the first side 85a and the second side 85b. Here, the first side 85a is along one side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the upper side of each fin intermediate portion 81 in FIG. 7 and FIG. 8 ). And configuration. The second side 85b is along the other side of the pair of tube insertion parts 60 across the fin middle part 81 (here, the tube insertion part 60 on the lower side of each fin middle part 81 in FIGS. 7 and 8 ). configuration. Accordingly, the flat surface 85 formed by the base portion 84 has a substantially square shape. Therefore, the strength of the fin in the direction intersecting the tube insertion direction can be improved particularly by the first side 85a and the second side 85b that are part of the four sides forming the substantially square shape. In addition, here, the ends of the sides 85a to 85d are connected so as to form acute angles, but they may be connected so as to smooth the corners by chamfering or making the corners R-shaped.

In addition, since the first side 85a and the second side 85b have the same length in the tube insertion direction, and the first side 85a and the second side 85b are arranged at the same position in the tube insertion direction, the third side 85c and the fourth side The lengths of 85d in the direction intersecting the tube insertion direction (pipe section direction) are also the same, and the third side 85c and the fourth side 85d are also arranged at the same position in the direction intersecting the tube insertion direction. Therefore, here, the flat surface 85 has a rectangular shape including both sides 85a, 85b parallel to the pipe insertion direction and both sides 85c, 85d parallel to the pipe section direction. Therefore, not only the fin strength in the direction intersecting the tube insertion direction can be increased by the first side 85a and the second side 85b, but also the fin strength in the tube insertion direction can be increased by the third side 85c and the fourth side 85d.

<finned wing>

Next, by cutting and bending the heat transfer fins 66, the first fin wings 90 are formed on the heat transfer fins 66, and the first fin wings are used to hold the heat transfer pipes 63 adjacent in the longitudinal direction. As for the space between the heat fins 66 , the first fin wing 90 is arranged across the boundary between the fin intermediate portion 81 and the fin near front portion 82 . Here, the first fin blade 90 has a substantially square shape protruding from the base surface 66a of the heat transfer fin 66 toward one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8 ). small pieces. The distance between the heat transfer fins 66 is maintained by the first fin fins 90 abutting against the base surfaces 66 a of the heat transfer fins 66 adjacent in the longitudinal direction of the heat transfer tubes 63 . In addition, here, the first fin blade 90 is disposed near the center of the heat transfer fin 66 in the pipe length direction and at a portion of the base portion 84 on the near side in the pipe insertion direction.

In this way, here, since the first fin wing 90 is arranged so as to straddle the boundary portion between the fin intermediate portion 81 and the fin near portion 82, the heat transfer tube 63 is inserted into the heat transfer fin 66 to be joined. In the state where the heat transfer fins 66 are located at the boundary between the fin intermediate portion 81 and the fin front portion 82, the decrease in fin strength in the direction intersecting the tube insertion direction (pipe section direction) can be suppressed. Therefore, in a state where the heat transfer tube 63 is inserted into the heat transfer fin 66 and joined, buckling of the heat transfer fin 66 can be suppressed from occurring at the boundary portion between the fin intermediate portion 81 and the fin near portion 82 . . Regarding this point, when the fin wing is formed on the front portion 82 of the fin and is not arranged at the boundary portion with the middle portion 81 of the fin, the fin wing cannot suppress the contact between the middle portion 81 and the front portion 82 of the fin. The decrease in the fin strength of the heat transfer fin 66 at the boundary portion in the direction intersecting the tube insertion direction, therefore, in the state where the heat transfer tube 63 is inserted into the heat transfer fin 66 and joined, it is difficult to suppress the fin strength. Buckling of the heat transfer fin 66 occurs at the boundary portion between the fin middle portion 81 and the fin near front portion 82 . The same applies to the case where the fin blades are formed on the fin intermediate portion 81 and not disposed on the boundary portion with the fin near portion 82 .

In addition, the first fin wing 90 is configured to form a wall portion along the tube insertion direction. Therefore, since the first fin blade 90 is arranged in a direction intersecting the boundary between the fin intermediate portion 81 and the fin near portion 82, it is possible to improve the suppression of the finning of the heat transfer fin 66 in the direction intersecting the tube insertion direction. The effect of reducing the strength of the tablet. In addition, since the first fin blade 90 is arranged parallel to the passage direction of air along the pipe insertion direction, ventilation resistance can be reduced.

In addition, on the heat transfer fin 66, a second fin wing 91 is formed on the inner part 83 of the fin by cutting and bending the heat transfer fin 66, and the second fin wing 91 is used to maintain the heat transfer position. The interval between adjacent heat transfer fins 66 in the length direction of the tube 63 . Here, the second fin blade 91 is a substantially square shape protruding from the base surface 66a of the heat transfer fin 66 toward one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8 ). small pieces. The distance between the heat transfer fins 66 is maintained by the second fin fins 91 abutting against the base surfaces 66 a of the heat transfer fins 66 adjacent in the longitudinal direction of the heat transfer tubes 63 . In addition, here, the second fin blade 91 is arranged near the center of the heat transfer fin 66 in the pipe section direction and at a portion on the rear side of the base portion 84 in the pipe insertion direction. Accordingly, here, the number of locations where adjacent heat transfer fins 66 contact each other in the longitudinal direction of the heat transfer tube 66 can be increased to improve the performance of maintaining the fin interval.

In addition, the second fin wing 91 is arranged to form a wall portion along the tube insertion direction. Therefore, here, since the second fin blade 91 is arranged parallel to the passing direction of the air along the pipe insertion direction, the ventilation resistance can be reduced.

Moreover, the 1st fin wing 90 and the 2nd fin wing 91 are arrange|positioned so that they may not overlap each other, when viewing the heat transfer fin 66 from the tube insertion direction. Here, the first fin wing 90 is cut and bent so that an opening 90a is formed on one side of the first fin wing 90 in the pipe direction (here, the upper side of the paper in FIGS. 7 and 8 ). The fin wing 90 is arranged at a position deviated from the center of the heat transfer fin 66 in the pipe direction to the other side in the pipe direction (here, the lower side of the paper in FIGS. 7 and 8 ). On the other hand, the second fin blade 91 is arranged at a position deviated from the center of the heat transfer fin 66 in the pipe direction to one side in the pipe direction (here, the upper side of the paper in FIGS. 7 and 8 ). In addition, as a result, when the heat transfer fin 66 is viewed from the tube insertion direction, the first fin wing 90 is disposed on the other side of the second fin wing 91 across the center of the heat transfer fin 66 in the pipe section direction. Deviated position. Therefore, here, the parallelism between adjacent heat transfer fins 66 in the longitudinal direction of the heat transfer tube 63 when viewing the heat transfer fins 66 from the tube insertion direction can be improved, and the performance of maintaining the fin interval can be further improved.

<rib>

Next, ribs 92 and 96 are formed on the heat transfer fin 66 on the front side and the back side of the tube insertion direction of the base part 85 by expanding the heat transfer fin 66 . The near-side rib 92 disposed on the near side in the tube insertion direction of the base portion 85 has: a near-side first rib 93 and a near-side second rib 94 extending in the tube insertion direction; The near side third rib 95 extending in the direction (pipe section direction). The inner rib 96 disposed on the inner side of the tube insertion direction of the base portion 85 has: a first inner rib 97 and a second rib 98 extending along the tube insertion direction; The inner third rib 99 extending in the direction (pipe section direction). Here, the ribs 92 and 96 protrude toward one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8 ) than the base surface 66 a of the heat transfer fin 66 .

The near side first rib 93 is along one side of the pair of tube insertion parts 60 sandwiching the fin middle part 81 (here, the tube insertion part 60 on the upper side of each fin middle part 81 in FIGS. 7 and 8 ). ) configuration. The front side first rib 93 is formed in a mountain shape in which the ridge line 93 a is parallel to the tube insertion direction of the heat transfer fin 66 . That is, the ridgeline 93a of the first rib 93 on the front side is arranged parallel to the passing direction of the outdoor air.

The second rib 94 on the near side is along the other side of the pair of tube insertion parts 60 across the fin middle part 81 (here, the tube insertion part 60 on the lower side of the sheet of each fin middle part 81 in FIGS. 7 and 8 ). ) to configure. The second near-side rib 94 is formed in a mountain shape in which a ridge line 94 a is parallel to the tube insertion direction of the heat transfer fin 66 . That is, the ridgeline 94a of the second near-side rib 94 is arranged parallel to the passage direction of outdoor air.

In addition, the near-side first rib 93 and the near-side second rib 94 extend not only to the fin intermediate portion 81 but also to the fin near front portion 82 . That is, the near-side first rib portion 93 and the near-side second rib portion 94 are arranged across the boundary portion between the fin intermediate portion 81 and the fin near portion 82 .

The third near-side rib 95 is arranged to connect end portions on the base portion 85 side in the tube insertion direction of the first near-side rib 93 and the second near-side rib 94 to each other. The third near-side rib 95 is formed into a mountain shape in which a ridge line 95 a is parallel to a direction intersecting the tube insertion direction of the heat transfer fin 66 . That is, the ridgeline 95a of the third near-side rib 95 is arranged so as to intersect with the passing direction of outdoor air. Also, here, the ridgeline 93a of the first rib 93 on the near side, the ridgeline 95a of the third rib 95 on the near side, and the ridgeline 94a of the second rib 94 on the near side are connected in a U-shape. The entirety of the first rib 93 , the third near-side rib 95 , and the second near-side rib 94 (that is, the near-side rib 92 ) is formed in a U-shaped mountain shape. In addition, the edge 95 b of the base portion 84 side of the third near-side rib 95 coincides with the third side 85 c of the flat surface 85 of the base portion 84 . That is, the edge 95b of the third near-side rib 95 on the base portion 84 side is located on the flat surface 85 protruding from the base surface 66a instead of the base surface 66a of the heat transfer fin 66 . Thus, the third rib 95 on the near side (that is, the rib 92 on the near side including the first rib 93 and the second rib 94 on the near side) is continuous with the third side 85c of the flat surface 85 of the base portion 84 ground configuration. In addition, the near side rib 92 is arranged so as to surround the first fin wing 90 . Here, three sides of the first fin wing 90 other than the near side in the tube insertion direction are surrounded. Further, the near side rib 92 is arranged at a position where the ridges 93 a , 94 a , 95 a protrude from the flat surface 85 of the base portion 84 and the base surface 66 a of the heat transfer fin 66 .

In addition, the back side first rib 97 and the back side second rib 98 are along one side of the pair of tube insertion parts 60 sandwiching the fin middle part 81 (here, each of the fin middle parts 81 in FIGS. 7 and 8 ). The tube insertion portion 60) on the upper side of the paper is arranged. The inner first rib 97 is formed into a mountain shape in which the ridge line 97 a is parallel to the tube insertion direction of the heat transfer fin 66 . That is, the ridgeline 97a of the first back side rib 97 is arranged parallel to the passage direction of outdoor air.

The inner second rib 98 is along the other side of the pair of tube insertion parts 60 across the fin middle part 81 (here, the tube insertion part 60 on the lower side of each fin middle part 81 of Fig. 7 and Fig. 8 ). ) configuration. The inner second rib 98 is formed in a mountain shape in which the ridge line 98 a is parallel to the tube insertion direction of the heat transfer fin 66 . That is, the ridgeline 98a of the second back rib 98 is arranged parallel to the passage direction of outdoor air.

In addition, the inner first rib portion 97 and the inner second rib portion 98 extend not only to the fin intermediate portion 81 but also to the fin inner portion 83 . That is, the rear first rib portion 97 and the rear second rib portion 98 are arranged across the boundary portion between the fin intermediate portion 81 and the fin rear portion 83 .

The inner third rib 99 is disposed so as to connect end portions on the base portion 85 side in the tube insertion direction of the inner first rib 97 and the inner second rib 98 to each other. The inner third rib 99 is formed into a mountain shape in which the ridge line 99 a is parallel to the direction intersecting the tube insertion direction of the heat transfer fin 66 . That is, the ridgeline 99a of the third rear rib 99 is arranged so as to intersect with the passing direction of outdoor air. And, here, the ridge line 97a of the first rib 97 on the back side, the ridge line 99a of the third rib 99 on the back side, and the ridge line 98a of the second rib portion 98 on the back side are connected in a U-shape. The entirety of the first rib 97 , the third rear rib 99 , and the second rib 98 (that is, the rear rib 96 ) is formed in a U-shaped chevron shape. Moreover, the edge 99b of the base part 84 side of the third back side rib 99 coincides with the fourth side 85d of the flat surface 85 of the base part 84 . That is, the edge 99 b of the base portion 84 side of the third rear rib 99 is located on the flat surface 85 protruding from the base surface 66 a , not on the base surface 66 a of the heat transfer fin 66 . Thus, the rear third rib 99 (that is, the rear rib 96 including the rear first rib 97 and the rear second rib 98 ) is continuous with the fourth side 85 d of the flat surface 85 of the base portion 84 . ground configuration. In addition, the inner side rib 96 is arranged so as to surround the second fin wing 91 . Here, three sides of the second fin wing 91 other than the near side in the tube insertion direction are surrounded. In addition, the back side rib 96 is arranged at a position where the ridges 97 a , 98 a , 99 a protrude from the flat surface 85 of the base portion 84 and the base surface 66 a of the heat transfer fin 66 .

Here, as described above, the ribs 92, 96 extending in the tube insertion direction are arranged continuously to the third side 85c and the fourth side 85d of the flat surface 85 on the near side and the back side of the tube insertion direction of the base portion 84. (specifically the first and second ribs 93, 94, 97, 98). Therefore, the third side 85c and the fourth side 85d of the base part 84 can be prevented from forming creases by integrating the ribs 92 and 96 with the base part 84 . Thereby, the fin strength in the direction intersecting the tube insertion direction at the base portion 84 and the portions on the near side and the rear side in the tube insertion direction of the base portion 84 can be improved.

In addition, here, as described above, the ribs 93 and 96 are arranged so as to straddle the boundary between the fin intermediate portion 81 and the fin near portion 82 and the boundary between the fin intermediate portion 81 and the fin inner portion 83 (specifically, The words are the first and second ribs 93, 94, 97, 98). Therefore, the fin strength in the direction intersecting the tube insertion direction at the boundary between the fin intermediate portion 81 and the fin near portion 82 and the boundary between the fin intermediate portion 81 and the fin back portion 83 can be increased. Therefore, when the heat transfer tube 63 is inserted into the notch 67 of the heat transfer fin 66, buckling of the inserted fin starting from the boundary between the fin intermediate portion 81 and the fin inner portion 83 can be suppressed. , in the state where the heat transfer tube 63 is inserted into the heat transfer fin 66 and joined, buckling of the heat transfer fin 66 starting from the boundary portion between the fin intermediate portion 81 and the fin near portion 82 can be suppressed. .

Here, as described above, since the near side rib 93 surrounding the first fin wing 90 is formed on the heat transfer fin 66 , cutting and bending of the heat transfer fin of the first fin wing 90 can be suppressed. The reduction of fin strength at both ends of 66.

(6) Modification

<A>

In the outdoor heat exchanger 23 which is the heat exchanger of the above-mentioned embodiment, the base portion 84 is formed on the heat transfer fin 66 , but nothing is formed on the flat surface 85 . However, it is not limited to this. For example, as shown in FIG. 13 , louvers 86 may be formed on the flat surface 85 of the base portion 84 by cutting and bending the heat transfer fins 66 for the purpose of improving heat transfer performance.

Here, since the louver 86 is formed on the base portion 84, for example, compared with the case where the louver is formed on a portion of the fin intermediate portion 81 where no mountain portion is formed, the portion where the louver is formed in the fin intermediate portion 81 is also formed. The fin strength in the direction intersecting the tube insertion direction can be increased. In addition, compared with the case where the louvers are formed in the mountain portion, the louvers 86 can be provided with a larger size (in particular, a larger size in the pipe section direction). Therefore, buckling of the heat transfer fin 66 when the heat transfer tube 63 is inserted into the notch 67 of the heat transfer fin 66 can be suppressed, and heat transfer performance can be improved.

<B>

In the outdoor heat exchanger 23 as the heat exchanger of the above-mentioned embodiment, the first fin wings 90 are arranged on the plurality of fin near front portions 82 and the corresponding plurality of fin intermediate portions 81 arranged along the pipe section direction. . However, it is not limited thereto, and for example, as shown in FIG. 14 , first fin wings 90 may be arranged for each of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81 .

Here, since the first fin blades 90 are arranged for each of the plurality of fin near front portions 82 and the corresponding plurality of fin intermediate portions 81, when dew occurs in the outdoor heat exchanger 23, the number of first fin blades 90 can be reduced. The drainage performance of the heat transfer fins 66 is ensured by the water retention capacity of the dew. In addition, although not shown here, the second fin blade 91 may be arranged for each stage in the same manner as the first fin blade 90 .

<C>

In the outdoor heat exchanger 23 as the heat exchanger according to the above-mentioned embodiment, the first fin fins 90 are arranged along the tube insertion direction, but it is not limited thereto. 82, the first fin wing 90 does not need to be along the tube insertion direction.

<D>

In the outdoor heat exchanger 23 as the heat exchanger of the above-described embodiment, the near side rib 92 surrounds three sides of the first fin wing 90 except the near side in the tube insertion direction, but is not limited thereto. For example, although not shown here, it is also possible that the near side rib 92 surrounds the periphery of the first fin wing 90 including the near side in the tube insertion direction.

<E>

In the outdoor heat exchanger 23 as the heat exchanger of the above-mentioned embodiment, a heat exchanger in which two rows of heat transfer tubes 63 are arranged in parallel in the passing direction of the outdoor air is cited as an example, but it is not limited thereto, and may be 1 column, or 3 or more columns.

Industrial availability

The present invention can be widely applied to heat exchangers including a plurality of flat tubes and a plurality of inserted fins.

Label description

23 Outdoor heat exchanger (heat exchanger)

63 heat transfer tube (flat tube)

64 flat faces

66 Heat transfer fins (insert fins)

67 Notch

80 tube insertion part

81 Fin middle part

82 near the front of the fin

83 inside the fin

90 first fin wing

91 second fin wing

92 Near front side rib (rib)

Claims (10)

1. A heat exchanger (23), which has: a plurality of flat tubes (63), which are arranged along a prescribed pipe segment direction with flat surfaces (64) facing each other; and a plurality of insertion fins ( 66), they are formed with a plurality of notches (67), the plurality of notches extending along the pipe insertion direction intersecting with the pipe section direction and the length direction of the flat pipe, for inserting the flat pipe, the A plurality of insertion fins are arranged along the longitudinal direction of the flat tube, and the heat exchanger is characterized in that When the part of the notch that is in contact with the flat tube in the state where the flat tube is inserted is used as the tube insertion part (80), a plurality of fin intermediate parts ( 81), they are sandwiched between the tube insertion parts adjacent in the direction of the tube section; The ends of the near front side respectively extend toward the near side of the tube insertion direction, and the width in the direction of the tube section is narrower than that of the middle part of the fins; The inner end of the middle portion in the tube insertion direction extends continuously from the inner end of the plurality of fin intermediate portions in the tube insertion direction toward the inner side in the tube insertion direction, The insertion fins have first fin wings (90) formed by cutting and bending the insertion fins so as to be held between the insertion fins adjacent in the length direction of the flat tube interval, The first fin wing is arranged across a boundary between the fin intermediate portion and the fin near front portion, and is arranged to form a wall portion along the tube insertion direction. 2. The heat exchanger (23) according to claim 1, wherein, A rib (92) surrounding the first fin wing (90) is formed on the insertion fin (66) by expanding the insertion fin. 3. The heat exchanger (23) according to claim 1, wherein, The first fin wings (90) are respectively arranged for the plurality of fin near front parts (82) and the corresponding plurality of fin middle parts (81) arranged along the pipe section direction. 4. The heat exchanger (23) according to claim 2, wherein, The first fin wings (90) are respectively arranged for the plurality of fin near front parts (82) and the corresponding plurality of fin middle parts (81) arranged along the pipe section direction. 5. The heat exchanger (23) according to any one of claims 1 to 4, wherein The inner part of the fin (83) has a second fin wing (91) formed by cutting and bending the inserted fin so as to keep adjacent in the length direction of the flat tube (63). The spacing between the insert fins (66). 6. The heat exchanger (23) according to claim 5, wherein, The second fin wing (91) is configured to form a wall portion along the tube insertion direction. 7. The heat exchanger (23) according to claim 5, wherein, The first fin wing (90) and the second fin wing (91) are configured not to overlap each other when the insertion fin (66) is viewed from the tube insertion direction. 8. The heat exchanger (23) according to claim 6, wherein, The first fin wing (90) and the second fin wing (91) are configured not to overlap each other when the insertion fin (66) is viewed from the tube insertion direction. 9. The heat exchanger (23) according to claim 5, wherein, The insertion fin (66) has: a first opening (90a) formed at one side of the first fin wing (90) in the direction of the tube section; and a second opening (91a) formed at The other side of the pipe section direction of the second fin wing (91), The first opening and the second opening are configured to overlap each other when viewing the insertion fin from the tube insertion direction, The first fin wing and the second fin wing are arranged so as not to overlap each other when the insertion fin is viewed from the tube insertion direction. 10. The heat exchanger (23) according to claim 6, wherein, The insertion fin (66) has: a first opening (90a) formed at one side of the first fin wing (90) in the direction of the tube section; and a second opening (91a) formed at The other side of the pipe section direction of the second fin wing (91), The first opening and the second opening are configured to overlap each other when viewing the insertion fin from the tube insertion direction, The first fin wing and the second fin wing are arranged so as not to overlap each other when the insertion fin is viewed from the tube insertion direction.