JP2016084976A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress occurrence of buckling of an insertion fin in a boundary part between a fin intermediate part and a fin front part, in a heat exchanger including a plurality of flat tubes and a plurality of insertion fins.SOLUTION: Flat tubes (63) are arranged along a tube stage direction. In an insertion fin (66), a plurality of notch parts (67) are formed extending along the tube stage direction and a tube insertion direction orthogonal to a longitudinal direction of the flat tubes, and it is arranged along the longitudinal direction of the flat tubes (63). Out of the notch parts (67), a portion which comes into contact with the flat tube (63) in a state where the flat tube (63) is inserted is a tube insertion part (80), and in the insertion fin (66), a fin intermediate part (81) which is sandwiched between tube insertion parts (80) and a fin front part (82) heading toward the front side are formed. In the insertion fin (66), a first fin tab (90) formed by cutting and raising the insertion fin (66) is arranged by striding over a boundary part between the fin intermediate part (81) and the fin front part (82).SELECTED DRAWING: Figure 8

Description

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

  Conventionally, as shown in Patent Document 1 (Japanese Patent Application Laid-Open No. 2012-163323), there is a heat exchanger provided with a plurality of flat tubes and a plurality of insertion fins. The flat tubes are arranged along a predetermined tube step direction with the flat surfaces facing each other. The insertion fin is formed with a plurality of notches for inserting a flat tube extending along the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube, and is arranged along the longitudinal direction of the flat tube. ing. Here, the portion of the cutout portion that contacts the flat tube while the flat tube is inserted is a tube insertion portion. The insertion fin includes a plurality of fin intermediate portions sandwiched between tube insertion portions adjacent to each other in the tube step direction, and a tube insertion from an end on the near side in the tube insertion direction of the plurality of fin intermediate portions of the insertion fins. A fin front portion extending toward the near side in the direction, and a plurality of fin intermediate portions from the back end in the tube insertion direction toward the back in the tube insertion direction. A fin back portion extending continuously from the side end portion is formed.

  In the heat exchanger of Patent Document 1, the portion of the notch portion that sandwiches the front portion of the fin only guides the flat tube to the tube insertion portion when the flat tube is inserted into the insertion fin. In the state of being inserted into the insertion fin, the flat tube is in contact with the fin intermediate portion but not in front of the fin. For this reason, in a state where the flat tube is inserted and joined to the insertion fin, the insertion fin may be buckled at the boundary between the fin intermediate portion and the fin front portion. That is, when the flat tube is inserted into the insertion fin and joined, when the heat exchanger receives an external force or the like, the insertion fin is bent starting from the boundary between the fin intermediate portion and the fin front portion. There is a risk that.

  The subject of this invention is suppressing the generation | occurrence | production of buckling of the insertion fin in the boundary part of a fin intermediate part and a fin front part in the heat exchanger provided with the some flat tube and the some insertion fin. .

  The heat exchanger according to the first aspect is a heat exchanger including a plurality of flat tubes and a plurality of insertion fins. The flat tubes are arranged along a predetermined tube step direction with the flat surfaces facing each other. The insertion fin is formed with a plurality of notches for inserting a flat tube extending along the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube, and is arranged along the longitudinal direction of the flat tube. ing. Here, the portion of the notch that is in contact with the flat tube in a state in which the flat tube is inserted is a tube insertion portion, and the insertion fin includes a plurality of fins sandwiched between tube insertion portions adjacent to each other in the tube step direction. An intermediate portion, a fin front portion extending from the front end portion of the plurality of fin intermediate portions in the tube insertion direction toward the front side of the tube insertion direction, and a back end of the plurality of fin intermediate portions in the tube insertion direction The fin back part extended continuously from the edge part of the back | inner side of the pipe insertion direction of the some fin intermediate part toward the back | inner side of a pipe insertion direction from a part. And here, the first fin tab for maintaining the space between the insertion fins adjacent to each other in the longitudinal direction of the flat tube is formed on the insertion fin by cutting and raising the insertion fin. The fin is disposed across the boundary between the fin intermediate portion and the fin front portion.

  Here, since the first fin tab is arranged so as to straddle the boundary portion between the fin intermediate portion and the fin front portion, in the state where the flat tube is inserted and joined to the insertion fin, the fin intermediate portion and the fin front portion are connected. The fall of the fin intensity | strength of the direction which cross | intersects the pipe insertion direction of the insertion fin in the boundary part with a part can be suppressed. For this reason, in the state where the flat tube is inserted and joined to the insertion fin, the occurrence of buckling of the insertion fin at the boundary between the fin intermediate portion and the front portion of the fin can be suppressed. In this regard, when the fin tab is formed on the front side of the fin and is not disposed at the boundary with the fin intermediate portion as in the heat exchanger of Patent Document 1, the fin tab is the boundary between the fin intermediate portion and the fin front portion. In the state where the fin strength in the direction intersecting the tube insertion direction of the insertion fin cannot be suppressed, in the state where the flat tube is inserted and joined to the insertion fin, the intermediate portion of the fin and the front portion of the fin It is difficult to suppress the occurrence of buckling of the insertion fin at the boundary. This also applies to the case where the fin tab is formed at the fin intermediate portion and is not disposed at the boundary portion with the fin front portion.

  The heat exchanger according to the second aspect is the heat exchanger according to the first aspect, wherein the first fin tab is arranged so as to form a wall portion along the tube insertion direction.

  Here, since the first fin tab is arranged in a direction intersecting the boundary between the fin intermediate portion and the fin front portion, the fin strength in the direction intersecting the tube insertion direction of the insertion fin is reduced. The suppression effect can be enhanced. And since a 1st fin tab will be arrange | positioned in parallel with the passage direction of the air along a pipe insertion direction, ventilation resistance can be lowered | hung.

  The heat exchanger according to the third aspect is the heat exchanger according to the first or second aspect, wherein a rib portion surrounding the first fin tab is formed on the insertion fin by causing the insertion fin to bulge. Yes. Here, the rib portion may not surround all four sides of the first fin tab, and may surround most of the first fin tab like a U-shape surrounding the three sides of the first fin tab. .

  Here, since the rib part surrounding the 1st fin tab is formed in the insertion fin, the fall of the fin strength of the insertion fin in the both ends where the 1st fin tab was cut and raised can be controlled.

  The heat exchanger according to the fourth aspect corresponds to any one of the heat exchangers according to the first to third aspects, wherein the first fin tab and the plurality of fin front portions arranged along the tube step direction correspond to the first fin tab. It arrange | positions for every several steps of several fin intermediate part.

  Here, since the 1st fin tab is arrange | positioned for every several steps of a several fin front part and a corresponding some fin intermediate part, when condensed water generate | occur | produces in a heat exchanger, the condensed water by a 1st fin tab It is possible to reduce the water retention amount and ensure the drainage performance of the insertion fin.

  The heat exchanger according to the fifth aspect of the present invention, in any one of the heat exchangers according to the first to fourth aspects, maintains a gap between the insertion fins adjacent to each other in the longitudinal direction of the flat tube in the fin back portion. A second fin tab is formed by cutting and raising the insertion fin.

  Here, since the 2nd fin tab is formed in the fin inner part, the place where the insertion fins adjacent to the longitudinal direction of a flat tube contact | abut can be increased, and the holding | maintenance performance of a fin space | interval can be improved.

  The heat exchanger according to a sixth aspect is the heat exchanger according to the fifth aspect, wherein the second fin tab is disposed so as to form a wall portion along the tube insertion direction.

  Here, since the 2nd fin tab is arranged in parallel with the passage direction of the air along a pipe insertion direction, ventilation resistance can be lowered.

  The heat exchanger according to the seventh aspect is the heat exchanger according to the fifth or sixth aspect, wherein the first fin tab and the second fin tab do not overlap each other when the insertion fin is viewed from the tube insertion direction. Are arranged as follows.

  Here, since the first fin tab and the second fin tab are arranged so as not to overlap each other when the insertion fin is viewed from the tube insertion direction, when the insertion fin is viewed from the tube insertion direction, the flatness is flat. The degree of parallelism between the insertion fins adjacent to each other in the longitudinal direction of the tube can be increased, and the fin spacing retention performance can be further improved.

  As described above, according to the present invention, the following effects can be obtained.

  In the heat exchanger according to the first aspect, in a state where the flat tube is inserted and joined to the insertion fin, the occurrence of buckling of the insertion fin at the boundary portion between the fin intermediate portion and the fin front portion is suppressed. be able to.

  In the heat exchanger according to the second aspect, it is possible to increase the effect of suppressing the decrease in fin strength in the direction intersecting the tube insertion direction of the insertion fin, and the first fin tab has an air flow along the tube insertion direction. Since it will be arranged in parallel with the passage direction, ventilation resistance can be lowered.

  In the heat exchanger according to the third aspect, it is possible to suppress a decrease in fin strength of the insertion fins at both ends where the first fin tab is cut and raised.

  In the heat exchanger according to the fourth aspect, when condensed water is generated in the heat exchanger, the amount of condensed water retained by the first fin tab can be reduced, and the drainage performance of the insertion fin can be ensured.

  In the heat exchanger according to the fifth aspect, the number of places where the insertion fins adjacent to each other in the longitudinal direction of the flat tube are in contact with each other can be increased, and the fin spacing retention performance can be improved.

  In the heat exchanger according to the sixth aspect, since the second fin tab is disposed in parallel to the air passage direction along the tube insertion direction, the ventilation resistance can be reduced.

  In the heat exchanger according to the sixth aspect, when the insertion fins are viewed from the tube insertion direction, the degree of parallelism between the insertion fins adjacent to each other in the longitudinal direction of the flat tube can be increased, and the fin spacing retention performance Can be further improved.

It is a schematic block diagram of the air conditioning apparatus which has an outdoor heat exchanger as a heat exchanger concerning one Embodiment of this invention. It is a perspective view which shows the external appearance of an outdoor unit. It is a top view which shows the state which removed the top plate of the outdoor unit. It is a perspective view which shows the state which removed the top plate, the front plate, and the side plate of the outdoor unit. It is a schematic perspective view of an outdoor heat exchanger. It is the elements on larger scale of the heat exchange part of FIG. It is the elements on larger scale which show the state which looked at the heat exchange part of FIG. 6 from the direction along the longitudinal direction of a heat exchanger tube. It is a figure which shows the principal part of a heat-transfer fin. It is II sectional drawing of FIG. It is II-II sectional drawing of FIG. 8, III-III sectional drawing, and IV-IV sectional drawing. It is the figure which looked at FIG. 8 from the near side of the pipe insertion direction, and the figure which looked at the back side of the pipe insertion direction. It is VV sectional drawing of FIG. It is a figure which shows the heat exchanger concerning a modification, Comprising: It is a figure corresponding to FIG. It is a figure which shows the heat exchanger concerning a modification, Comprising: It is a figure corresponding to FIG.

  Hereinafter, an embodiment of a heat exchanger concerning the present invention and its modification are described based on a drawing. In addition, the specific structure of the heat exchanger concerning this invention is not restricted to the following embodiment and its modification, It can change in the range which does not deviate from the summary of invention.

(1) Basic Configuration of Air Conditioner FIG. 1 is a schematic configuration diagram of an air conditioner 1 having 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 a room such as a building 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 tube 5 and a gas refrigerant communication tube 6. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the indoor unit 4 via the refrigerant communication pipes 5 and 6.

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

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

<Outdoor unit>
The outdoor unit 2 is installed outside and constitutes a part of the refrigerant circuit 10. The outdoor unit 2 mainly includes 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 of the refrigeration cycle until it reaches a high pressure. The compressor 21 has a hermetically sealed structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a. The compressor 21 has a suction pipe 31 connected to the suction side and a discharge pipe 32 connected to the discharge side. The suction pipe 31 is a refrigerant pipe that connects the suction side of the compressor 21 and the four-way switching valve 22. The discharge pipe 32 is a refrigerant pipe that connects 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 direction of refrigerant flow in the refrigerant circuit 10. During the cooling operation, the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as a radiator for the refrigerant compressed in the compressor 21 and the indoor heat exchanger 41 for the refrigerant that has radiated heat in the outdoor heat exchanger 23. Switch to the cooling cycle state to function as an evaporator. That is, in the cooling operation, the four-way switching valve 22 is connected between the discharge side of the compressor 21 (here, the discharge pipe 32) and the gas side of the outdoor heat exchanger 23 (here, the first gas refrigerant pipe 33). (See the solid line of the four-way selector valve 22 in FIG. 1). Moreover, the suction side (here, the suction pipe 31) of the compressor 21 and the gas refrigerant communication pipe 6 side (here, the second gas refrigerant pipe 34) are connected (solid line of the four-way switching valve 22 in FIG. 1). See). Further, the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as an evaporator of the refrigerant that has radiated heat in the indoor heat exchanger 41 during the heating operation, and the indoor heat exchanger 41 is compressed in the compressor 21. Switching to a heating cycle state that functions as a refrigerant radiator. That is, in the heating operation, the four-way switching valve 22 is connected to the discharge side (here, the discharge pipe 32) of the compressor 21 and the gas refrigerant communication pipe 6 side (here, the second gas refrigerant pipe 34). (Refer to the broken line of the four-way switching valve 22 in FIG. 1). In addition, the suction side of the compressor 21 (here, the suction pipe 31) and the gas side of the outdoor heat exchanger 23 (here, the first gas refrigerant pipe 33) are connected (four-way switching valve 22 in FIG. 1). See the dashed line). Here, the first gas refrigerant pipe 33 is a refrigerant pipe connecting 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 refrigerant radiator that uses outdoor air as a cooling source during cooling operation, and functions as a refrigerant evaporator that uses outdoor air as a heating source during heating operation. The outdoor heat exchanger 23 has a liquid side connected to the liquid refrigerant pipe 35 and a gas side 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 reduces the high-pressure refrigerant of the refrigeration cycle that has radiated heat in the outdoor heat exchanger 23 to the low pressure of the refrigeration cycle during the cooling operation. The expansion valve 24 is a valve that reduces the high-pressure refrigerant of the refrigeration cycle radiated in the indoor heat exchanger 41 to the low pressure of the refrigeration cycle during heating operation. The expansion valve 24 is provided in a portion of the liquid refrigerant pipe 35 near the liquid side closing 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 with external devices and pipes (specifically, the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6). The liquid side closing valve 25 is provided at the end of the liquid refrigerant pipe 35. The gas side closing 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 and then discharging the air to the outside. That is, the outdoor unit 2 includes an outdoor fan 36 as a fan that supplies outdoor air as a cooling source or a heating source of the refrigerant flowing through the outdoor heat exchanger 23 to the outdoor heat exchanger 23. Here, as the outdoor fan 36, a propeller fan or the like driven by an outdoor fan motor 36a is used.

<Refrigerant communication pipe>
Refrigerant communication pipes 5 and 6 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building. The refrigerant communication tubes 5 and 6 include a combination of the installation location and the outdoor unit 2 and the indoor unit 4. Depending on the installation conditions, those having various lengths and pipe diameters are used.

(2) Basic operation | movement of an air conditioning apparatus Next, basic operation | movement of the air conditioning apparatus 1 is demonstrated using FIG. The air conditioner 1 can perform a cooling operation and a heating operation as basic operations.

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

  In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and is compressed until it reaches the high pressure in 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 radiates heat by exchanging heat with outdoor air supplied as a cooling source by the outdoor fan 36 in the outdoor heat exchanger 23 that functions as a refrigerant radiator. Become a high-pressure liquid refrigerant.

  The high-pressure liquid refrigerant that has radiated 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 depressurized to the low pressure of the refrigeration cycle by the expansion valve 24 and becomes 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 indoor heat exchanger 41 through the liquid-side closing 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 by exchanging heat with indoor air supplied as a heating source by the indoor fan 42 in the indoor heat exchanger 41. As a result, the room air is cooled and then supplied to the room to cool the room.

  The low-pressure gas refrigerant evaporated in the indoor heat exchanger 41 is again sucked into the compressor 21 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 broken line in FIG. 1).

  In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and is compressed until it reaches the high pressure in the refrigeration cycle, and then 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 radiates heat by exchanging heat with indoor air supplied as a cooling source by the indoor fan 42 in the indoor heat exchanger 41 to become a high-pressure liquid refrigerant. . Thereby, indoor air is heated, and indoor heating is performed by being supplied indoors after that.

  The high-pressure liquid refrigerant radiated by 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 depressurized to the low pressure of the refrigeration cycle by the expansion valve 24 and becomes 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 exchanges heat with the outdoor air supplied as a heating source by the outdoor fan 36 in the outdoor heat exchanger 23 that functions as a refrigerant evaporator. Go and evaporate into a low-pressure gas refrigerant.

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

(3) Basic configuration of outdoor unit Next, the basic configuration of the outdoor unit 2 will be described with reference to FIGS. Here, FIG. 2 is a perspective view showing an 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, the front plates 55 and 56, and the side plates 53 and 54 of the outdoor unit 2 are removed. In the following description, “upper”, “lower”, “left”, “right”, “vertical”, “front”, “side”, “back”, “top”, “bottom”, etc. The wording means a direction and a surface when the surface on the fan blowing grill 55b side is a front surface unless otherwise specified.

  The outdoor unit 2 has a structure (so-called trunk type structure) in which the inside of the unit casing 51 is partitioned 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 discharge air from the front surface of the unit casing 51 after sucking outdoor air into the inside from a part of the back surface and side surface of the unit casing 51. The outdoor unit 2 mainly includes a unit casing 51, a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, closing valves 25 and 26, and refrigerant pipes 31 to 35 connecting these devices. It has the apparatus and piping which comprise the refrigerant circuit 10 containing, the outdoor fan 36, and the motor 36a for outdoor fans. Here, an example in which the blower chamber S1 is formed near the left side surface of the unit casing 51 and the machine chamber S2 is formed near the right side surface of the unit casing 51 will be described, but the left and right sides may be reversed.

  The unit casing 51 is formed in a substantially rectangular parallelepiped shape. The unit casing 51 mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, closing valves 25 and 26, and a refrigerant pipe connecting these devices. The apparatus and piping which comprise the refrigerant circuit 10 containing 31-35, the outdoor fan 36, and the outdoor fan motor 36a are accommodated. The unit casing 51 includes a bottom plate 52 on which the devices and pipings 21 to 26, 31 to 35, the outdoor fan 36, and the like constituting the refrigerant circuit 10 are placed, a blower chamber side plate 53, a machine chamber side plate 54, It has a blower room side front plate 55, a machine room side front plate 56, a top plate 57, and two installation legs 59.

  The bottom plate 52 is a plate-like member that constitutes the bottom portion of the unit casing 51.

  The blower chamber side plate 53 is a plate-like member that forms a side surface portion (here, the left side surface portion) of the unit casing 51 near the blower chamber S1. The lower part of the blower chamber side plate 53 is fixed to the bottom plate 52, and here, the front end portion thereof is an integral member with the left end portion of the blower chamber side front plate 55. The blower chamber side plate 53 is formed with a side fan inlet 53 a for sucking outdoor air into the unit casing 51 from the side surface side of the unit casing 51 by the outdoor fan 36. The blower chamber side plate 53 may be a separate member from the blower chamber side front plate 55.

  The machine room side plate 54 is a plate-like member that constitutes a part of the side surface portion (here, the right side surface portion) of the unit casing 51 near the machine room S2 and the back surface portion of the unit casing 51 near the machine room S2. is there. The lower part of the machine room side plate 54 is fixed to the bottom plate 52. Outdoor air is passed into the unit casing 51 from the back side of the unit casing 51 by the outdoor fan 36 between the rear side end of the blower room side plate 53 and the end of the machine room side plate 54 on the blower chamber S1 side. A rear fan inlet 53b for inhalation is formed.

  The blower chamber side front plate 55 is a plate-like member that constitutes the front portion of the blower chamber S <b> 1 of the unit casing 51. The lower portion of the blower chamber side front plate 55 is fixed to the bottom plate 52, and here, the left side end portion is an integral member with the front end portion of the blower chamber side plate 53. The blower chamber side front plate 55 is provided with a fan outlet 55a for blowing the outdoor air sucked into the unit casing 51 by the outdoor fan 36 to the outside. On the front side of the blower chamber side front plate 55, a fan blow grill 55b that covers the fan blow outlet 55a is provided. The blower chamber side front plate 55 may be a separate member from the blower chamber side plate 53.

  The machine room side front plate 56 is a plate-like member that constitutes a part of the front part of the machine room S2 of the unit casing 51 and a part of the side part of the machine room S2 of the unit casing 51. The machine room side front plate 56 has an end portion on the fan chamber S1 side fixed to an end portion on the machine room S2 side of the blower chamber side front plate 55, and an end portion on the back side on the front side of the machine room side plate 54. It is fixed to the end of the.

  The top plate 57 is a plate-like member that constitutes the top surface portion of the unit casing 51. The top plate 57 is fixed to the blower chamber side plate 53, the machine room side plate 54, and the blower chamber side front plate 55.

  The partition plate 58 is a plate-like member that is arranged on the bottom plate 52 and extends in the vertical direction. Here, the partition plate 58 divides the inside of the unit casing 51 into left and right to form a blower chamber S1 near the left side and a machine chamber S2 near the right side. The lower portion of the partition plate 58 is fixed to the bottom plate 52, the front end portion thereof is fixed to the blower chamber side front plate 55, and the rear end portion thereof is the side closer to the machine room S <b> 2 of the outdoor heat exchanger 23. It extends to the end.

  The installation leg 59 is a plate-like member extending in the front-rear direction of the unit casing 51. The installation leg 59 is a member fixed to the installation surface of the outdoor unit 2. Here, the outdoor unit 2 has two installation legs 59, one is arranged near the blower room S1, and the other is arranged near the machine room S2.

  The outdoor fan 36 is a propeller fan having a plurality of blades, and faces the front surface of the unit casing 51 (here, the fan air outlet 55a) at a position on the front surface side of the outdoor heat exchanger 23 in the blower chamber S1. Are arranged as follows. 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. The outdoor fan 36 is pivotally supported by an outdoor fan motor 36a.

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

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

(4) Basic Configuration of Outdoor Heat Exchanger Next, the basic configuration of the outdoor heat exchanger 23 will be described with reference to FIGS. Here, FIG. 5 is a schematic perspective view of the outdoor heat exchanger 23. FIG. 6 is a partially enlarged view of the heat exchange unit 60 of FIG. In the following description, the terms indicating directions and surfaces mean directions and surfaces based on the state in which the outdoor heat exchanger 23 is placed on the outdoor unit 2 unless otherwise specified.

  The outdoor heat exchanger 23 mainly includes a heat exchanging unit 60 that exchanges heat between outdoor air and refrigerant, a refrigerant flow divider 70 provided on one end side (here, the right end side) of the heat exchanging unit 60, and an inlet / outlet header. 71 and an intermediate header 72, and a connection header 74 provided on the other end side (here, the left front end side) of the heat exchanging unit 60. The outdoor heat exchanger 23 is an all-aluminum heat exchanger in which all of the refrigerant flow distributor 70, the inlet / outlet header 71, the intermediate header 72, the connection header 74, and the heat exchange unit 60 are made of aluminum or aluminum alloy. Is performed by brazing such as brazing in a furnace.

<Heat exchange part>
The heat exchanging unit 60 includes an upwind heat exchanging unit 61 that constitutes an upwind portion of the outdoor heat exchanger 23 and an upwind heat exchanging unit 62 that constitutes a downwind portion of the outdoor heat exchanger 23. The heat exchangers 61 and 62 are arranged in two rows in the direction in which the outdoor air passes through the unit casing 51 generated by driving the outdoor fan 36. The windward side heat exchange unit 61 is disposed closer to the side surface (here, the left side surface) and the back side of the unit casing 51 than the leeward side heat exchange unit 62. That is, the portion of the heat exchanging unit 60 that is located on the windward side near the fan suction ports 53 a and 53 b with respect to the direction in which the outdoor air passes is the windward heat exchanging unit 61. A portion located on the leeward side far from the ports 53a and 53b is the leeward heat exchange unit 62. And the windward heat exchange part 61 has the windward main heat exchange part 61a which comprises the upper part of the outdoor heat exchanger 23, and the windward sub heat exchange part 61b which comprises the lower part of the outdoor heat exchanger 23. ing. Further, the leeward side heat exchanging unit 62 includes a leeward side main heat exchanging unit 62 a constituting the upper part of the outdoor heat exchanger 23 and a leeward side sub heat exchanging unit 62 b constituting the lower part of the outdoor heat exchanger 23. ing.

  The heat exchanging unit 60 is an insertion fin type heat exchanging unit constituted by a large number of heat transfer tubes 63 made of flat tubes and a large number of heat transfer fins 66 made of insertion fins. The heat transfer tube 63 is made of aluminum or aluminum alloy, and is a flat multi-hole tube having a flat surface 64 serving as a heat transfer surface and a large number of small internal flow paths 65 through which a refrigerant flows. A large number of heat transfer tubes 63 are arranged in a plurality of stages at intervals along a predetermined tube step direction with the flat surfaces 64 facing each other, and one end in the longitudinal direction (here, the right end) is the inlet / outlet header 71 or the intermediate header. 72 and the other end in the longitudinal direction (here, the left front end) is connected to the connection header 74. That is, the large number of heat transfer tubes 63 are disposed between the inlet / outlet header 71 and the intermediate header 72 and the connection header 74. Here, since the flat surface 64 of the heat transfer tube 63 faces the vertical direction, the tube step direction means the vertical direction, and the heat transfer tube 63 is arranged along the side surface (here, the left side surface) and the back surface of the unit casing 51. Therefore, the longitudinal direction of the heat transfer tube 63 means the horizontal direction along the side surface (here, the left side surface) and the back surface of the unit casing 51. The heat transfer fins 66 are made of aluminum or an aluminum alloy, and a plurality of heat transfer fins 66 are arranged along the longitudinal direction of the heat transfer tube 63 at intervals. The heat transfer fins 66 are formed with a number of notches 67 for inserting the heat transfer tubes 63 extending along the tube insertion direction that intersects the tube step direction and the longitudinal direction of the heat transfer tubes 63. Here, since the tube step direction is the vertical direction and the longitudinal direction of the heat transfer tube 63 is the horizontal direction along the side surface (here, the left side surface) and the back surface of the unit casing 51, the tube insertion direction is the heat transfer tube 63. This means a horizontal direction that intersects the longitudinal direction, and also coincides with the passage direction of outdoor air in the unit casing 51. The notch 67 is elongated in the horizontal direction from one edge of the heat transfer fin 66 in the tube insertion direction (here, the edge on the windward side with respect to the outdoor air passage direction). Here, the large number of heat transfer tubes 63 include a heat transfer tube group constituting the windward main heat exchange unit 61a, a heat transfer tube group constituting the windward sub heat exchange unit 61b, and a leeward main heat exchange unit 62a. The heat transfer tube group is divided into a heat transfer tube group and a heat transfer tube group constituting the leeward side sub heat exchange unit 62b. Further, the large number of heat transfer fins 66 include a group of fins that form a common windward row for the windward main heat exchange unit 61a and the windward sub heat exchange unit 61b, and the leeward main heat exchange unit 62a and the leeward sub The heat exchange section 62b is divided into fin groups that form a common leeward row.

<Refrigerant divider>
The refrigerant distributor 70 is connected between the liquid refrigerant pipe 35 and the lower part of the inlet / outlet header 71. The refrigerant flow divider 70 is a member made of aluminum or aluminum alloy and extending in the vertical direction. The refrigerant distributor 70 divides the refrigerant flowing in through the liquid refrigerant pipe 35 and guides it to the lower part of the inlet / outlet header 71, or joins the refrigerant flowing in through the lower part of the inlet / outlet header 71 and guides it to the liquid refrigerant pipe 35. <Gateway header>
The entrance / exit 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. The inlet / outlet header 71 is connected to one end (here, the right end) of the heat transfer pipe 63 that constitutes the upwind heat exchange unit 61. The entrance / exit header 71 is a member made of aluminum or aluminum alloy and extending in the vertical direction. The internal space of the entrance / exit header 71 is vertically partitioned by a baffle (not shown), and the upper space communicates with one end (here, the right end) of the heat transfer pipe 63 constituting the upwind main heat exchange section 61a. The lower space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the windward side sub heat exchanging portion 61b. And the upper part of the entrance / exit header 71 is connected to the 1st gas refrigerant pipe 33, and exchanges a refrigerant | coolant between the windward main heat exchange part 61a and the 1st gas refrigerant pipe 33. As shown in FIG. Further, the lower part of the inlet / outlet header 71 is connected to the refrigerant distributor 70 so that the refrigerant is exchanged with the refrigerant distributor 70.

<Intermediate header>
The intermediate header 72 is provided on one end side (here, the right end side) of the leeward heat exchange unit 62 in the heat exchange unit 60. The intermediate header 72 is connected to one end (here, the right end) of the heat transfer tube 63 that constitutes the leeward heat exchange unit 62. The intermediate header 72 is a member that is formed of aluminum or an aluminum alloy and extends in the vertical direction. The internal space of the intermediate header 72 is vertically partitioned by a baffle (not shown), and the upper space communicates with one end (here, the right end) of the heat transfer pipe 63 that constitutes the leeward main heat exchange section 62a. The lower space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the leeward side sub heat exchanging portion 62b. Further, the upper space and the lower space of the intermediate header 72 are partitioned into a plurality of spaces by baffles (not shown) according to the number of passes of the heat exchanging unit 60, and the upper space and the lower space through the intermediate connecting pipe 73 and the like. It communicates with the space. The intermediate header 72 exchanges refrigerant between the leeward main heat exchange unit 62a and the leeward sub heat exchange unit 62b.

<Consolidated header>
The connection header 74 is provided on the other end side (here, the left front end side) of the heat exchange unit 60. The connection header 74 is connected to the other end (here, the left front end) of the heat transfer tube 63 constituting the heat exchanging unit 60. The connection header 74 is a member made of aluminum or aluminum alloy and extending in the vertical direction. The connection header 74 includes the other end (here, the left front end) of the heat transfer tube 63 constituting the windward heat exchange unit 61 and the other end (here, the left front end) of the heat transfer tube 63 constituting the leeward side heat exchange unit 62. ) Are connected to each other. And the connection header 74 exchanges a refrigerant | coolant between the windward side heat exchange part 61 and the leeward side heat exchange part 62. As shown in FIG.

  When the outdoor heat exchanger 23 having such a configuration functions as a refrigerant evaporator, the refrigerant flowing from the liquid refrigerant pipe 35 is transferred to the refrigerant flow divider 70 as indicated by the arrows indicating the flow of the refrigerant in FIG. And through the lower part of the inlet / outlet header 71, it is guided to the windward side sub heat exchange part 61b. And the refrigerant | coolant which passed the windward sub heat exchange part 61b is guide | induced to the leeward side sub heat exchange part 62b through the lower part of the connection header 74. FIG. And the refrigerant | coolant which passed the leeward side sub heat exchange part 62b is guide | induced to the leeward side main heat exchange part 62a through the intermediate header 72. FIG. And the refrigerant | coolant which passed the leeward side main heat exchange part 62a is guide | induced to the leeward side main heat exchange part 61a through the upper part of the connection header 74. FIG. Then, the refrigerant that has passed through the windward main heat exchanging portion 61 a flows out to the first gas refrigerant pipe 33 through the upper part of the inlet / outlet header 71. In the course of such a refrigerant flow, the refrigerant evaporates by heat exchange with outdoor air. When the outdoor heat exchanger 23 functions as a refrigerant radiator, the refrigerant flowing from the first gas refrigerant pipe 33 passes through the upper part of the inlet / outlet header 71 as shown by the arrows indicating the refrigerant flow in FIG. Then, it is guided to the windward main heat exchanging part 61a. And the refrigerant | coolant which passed the windward main heat exchange part 61a is guide | induced to the leeward main heat exchange part 62a through the upper part of the connection header 74. FIG. And the refrigerant | coolant which passed the leeward side main heat exchange part 62a is guide | induced to the leeward side sub heat exchange part 62b through the intermediate header 72. FIG. And the refrigerant | coolant which passed the leeward side sub heat exchange part 62b is guide | induced to the leeward side sub heat exchange part 61b through the lower part of the connection header 74. FIG. Then, the refrigerant that has passed through the windward side sub heat exchanging portion 61 b flows out to the liquid refrigerant pipe 35 through the lower portion of the inlet / outlet header 71 and the refrigerant distributor 70. In the course of such a refrigerant flow, the refrigerant radiates heat by heat exchange with the outdoor air.

(5) Detailed structure of heat transfer fin Next, the detailed structure of the heat transfer fin 66 is demonstrated using FIGS. Here, FIG. 7 is a partially enlarged view showing a state in which the heat exchanging unit 60 in FIG. 6 is viewed from the direction along the longitudinal direction of the heat transfer tube 63. FIG. 8 is a view showing a main part of the heat transfer fin 66. 9 is a cross-sectional view taken along the line II of FIG. 10 is a cross-sectional view taken along a line II-II, a cross-sectional view taken along a line III-III, and a cross-sectional view taken along a line IV-IV in FIG. FIG. 11 is a view of FIG. 8 viewed from the front side in the tube insertion direction and a view viewed from the back side in the tube insertion direction. 12 is a cross-sectional view taken along the line VV in FIG.

<Basic shape>
The heat transfer fin 66 is a plate-like fin that is long in one direction (here, vertically long) formed by pressing a plate material made of aluminum or aluminum alloy.

  A large number of notches 67 of the heat transfer fins 66 are formed at predetermined intervals in the tube step direction of the heat transfer fins 66. Here, a portion of the cutout portion 67 that contacts the heat transfer tube 63 in a state where the heat transfer tube 63 is inserted constitutes a tube insertion portion 80. The tube insertion portion 80 has a vertical width substantially equal to the width between the flat surfaces 64 of the heat transfer tubes 63, and a horizontal width substantially equal to the width in the direction intersecting the flat surfaces 64 of the flat tubes 63. It has become. The peripheral edge 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 front side in FIG. 7 and FIG. 8). The base surface 66a of the heat transfer fin 66 means the fin surface of the heat transfer fin 66 fin in a state before the formation of each part including the tube insertion portion 80. The heat transfer tube 63 is inserted into the notch 67 and guided to the tube insertion portion 80 which is a part of the notch 67, and is joined to the peripheral edge of the tube insertion portion 80 by brazing. The heat transfer fins 66 are formed with a plurality of fin intermediate portions 81 sandwiched between the tube insertion portions 80 adjacent in the tube step direction. In addition, the heat transfer fin 66 has a plurality of fin intermediate portions 81 from the front side in the tube insertion direction (here, the windward side with respect to the passage direction of outdoor air) toward the front side in the tube insertion direction. Fin front portions 82 extending respectively are formed. Further, the heat transfer fin 66 has a plurality of fin intermediate portions 81 extending from the end on the back side in the tube insertion direction (here, the leeward side with respect to the passage direction of outdoor air) toward the back side in the tube insertion direction. A fin back portion 83 extending continuously from the back end of the plurality of fin intermediate portions 81 in the tube insertion direction is formed.

  In such heat transfer fins 66, for example, it is conceivable to form a plurality of waffles having a mountain-shaped inclined surface along the tube insertion direction. However, when such a plurality of waffles are formed, when the heat transfer tubes 63 are inserted into the notches 67 of the heat transfer fins 66, the heat transfer fins 66 buckle at the valleys between the waffles adjacent in the tube insertion direction. May occur. That is, when the heat transfer tube 63 is inserted into the cutout portion 67 of the heat transfer fin 66, the valley portion between the waffles becomes a V-shaped fold, and the heat transfer fin 66 may be bent. For this reason, it is necessary to be able to suppress the occurrence of buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67.

  In such a heat transfer fin 66, the portion of the notch 67 sandwiching the fin front portion 82 guides the heat transfer tube 63 to the tube insertion portion 80 when the heat transfer tube 63 is inserted into the heat transfer fin 66. However, in a state where the heat transfer tubes 63 are inserted into the heat transfer fins 66, the heat transfer tubes 63 are in contact with the fin intermediate portion 81 but are not in contact with the fin front portion 82. For this reason, in a state where the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66, the heat transfer fins 66 may be buckled at the boundary between the fin intermediate portion 81 and the fin 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 tubes 63 are inserted and joined to the heat transfer fins 66, a boundary portion between the fin intermediate portion 81 and the fin front portion 82 is a starting point. The heat transfer fins 66 may be bent. On the other hand, it is necessary to be able to suppress the occurrence of buckling of the heat transfer fin 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82.

  Therefore, here, the buckling of the heat transfer fin 66 when the heat transfer tube 63 is inserted into the notch 67 and the occurrence of the buckling of the heat transfer fin 66 at the boundary between the fin intermediate portion 81 and the fin front portion 82 are suppressed. In order to do so, the heat transfer fin 66 is devised as follows.

<Pedestal part>
First, in the heat transfer fin 66, a pedestal portion 84 that forms a flat surface 85 is formed in a plurality of fin intermediate portions 81 by causing the heat transfer fins 66 to bulge. The pedestal portion 84 is disposed near the center of the fin intermediate portion 81 in the tube insertion direction. Here, the entire flat surface 85 is arranged at a position protruding from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). ing.

  Thus, here, since the pedestal portion 84 forming the flat surface 85 is formed in the fin intermediate portion 81, unlike the case where the waffle is formed in the heat transfer fin 66, the notch portion 67 of the heat transfer fin 66 is formed. When the heat transfer tube 63 is inserted, there is no V-shaped crease such as a valley between the waffles. For this reason, it becomes possible to improve the fin strength in the direction intersecting the tube insertion direction, and to suppress the occurrence of buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67. .

  Further, the protruding height of the pedestal portion 84 from the base surface 66 a of the heat transfer fin 66 is set to be higher than the protruding height of the tube insertion portion 80. For this reason, the effect which improves fin intensity | strength can be heightened by forming the base part 84. FIG.

  Further, the flat surface 85 connects the first side 85a and the second side 85b that are parallel to each other extending in the tube insertion direction, and the end portions of the first side 85a and the second side 85b on the near side in the tube insertion direction. It has a third side 85c and a fourth side 85d that connects the ends of the first side 85a and the second side 85b on the back side in the tube insertion direction. 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 the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The second side 85b is arranged along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Has been. As a result, the flat surface 85 formed by the pedestal portion 84 has a substantially square shape. For this reason, in particular, the fin strength in the direction intersecting the tube insertion direction can be improved by the first side 85a and the second side 85b, which are a part of four sides having a substantially rectangular shape. Here, the ends of the sides 85a to 85d are connected so as to form sharp corners. However, even if the corners are chamfered or the corners are rounded to have a round shape, the corners may be smoothed. Good.

  In addition, the first side 85a and the second side 85b have the same length in the tube insertion direction and are arranged at the same position in the tube insertion direction, so the third side 85c and the fourth side 85d are also The lengths in the direction intersecting the tube insertion direction (tube step direction) are the same, and are arranged at positions in the direction intersecting the same tube insertion direction. For this reason, here, the flat surface 85 has a rectangular shape including two sides 85a and 85b parallel to the tube insertion direction and two sides 85c and 85d parallel to the tube step direction. For this reason, not only the fin strength in the direction intersecting the tube insertion direction by the first side 85a and the second side 85b but also the fin strength in the tube insertion direction can be improved by the third side 85c and the fourth side 85d. .

<Fin tab>
Next, the heat transfer fins 66 are formed by cutting up the heat transfer fins 66 with first fin tabs 90 for maintaining the distance between the heat transfer fins 66 adjacent in the longitudinal direction of the heat transfer tubes 63. The first fin tab 90 is disposed across the boundary between the fin intermediate portion 81 and the fin front portion 82. Here, the first fin tab 90 is a substantially square-shaped piece that protrudes from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). is there. The first fin tab 90 is in contact with the base surface 66a of the heat transfer fin 66 adjacent in the longitudinal direction of the heat transfer tube 63, so that the interval between the heat transfer fins 66 is maintained. In addition, here, the first fin tab 90 is disposed in the vicinity of the center of the heat transfer fin 66 in the tube step direction and on the front side of the pedestal portion 84 in the tube insertion direction.

  As described above, since the first fin tab 90 is disposed so as to straddle the boundary between the fin intermediate portion 81 and the fin front portion 82, the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66. In the state, it is possible to suppress a decrease in fin strength in a direction (tube step direction) intersecting the tube insertion direction of the heat transfer fin 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82. For this reason, in the state where the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66, the occurrence of buckling of the heat transfer fins 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82 can be suppressed. . In this regard, when the fin tab is formed on the fin front portion 82 and is not disposed at the boundary between the fin intermediate portion 81 and the fin tab, the heat transfer fin 66 of the heat transfer fin 66 at the boundary between the fin intermediate portion 81 and the fin front portion 82 is provided. Since the decrease in fin strength in the direction intersecting the tube insertion direction cannot be suppressed, the boundary between the fin intermediate portion 81 and the fin front portion 82 in the state where the heat transfer tube 63 is inserted and joined to the heat transfer fin 66. It is difficult to suppress the occurrence of buckling of the heat transfer fins 66 in the section. This also applies to the case where the fin tab is formed in the fin intermediate portion 81 and is not disposed at the boundary portion with the fin front portion 82.

  Moreover, the 1st fin tab 90 is arrange | positioned so that the wall part along a pipe | tube insertion direction may be made. For this reason, here, since the first fin tab 90 is arranged in a direction intersecting with the boundary between the fin intermediate portion 81 and the fin front portion 82, the first fin tab 90 intersects the tube insertion direction of the heat transfer fin 66. The effect which suppresses the fall of the fin strength of a direction can be heightened. And since the 1st fin tab 90 is arrange | positioned in parallel with the passage direction of the air along a pipe insertion direction, ventilation resistance can be lowered | hung.

  Further, in the heat transfer fin 66, the fin fin 83 has a second fin tab 91 for keeping the space between the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tube 63. Is formed. Here, the second fin tab 91 is a substantially square-shaped piece projecting from the base surface 66a of the heat transfer fin 66 to the one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). is there. The second fin tab 91 is in contact with the base surface 66a of the heat transfer fin 66 adjacent in the longitudinal direction of the heat transfer tube 63, so that the interval between the heat transfer fins 66 is maintained. Further, here, the second fin tab 91 is disposed in the vicinity of the center of the heat transfer fin 66 in the tube step direction and on the back side of the pedestal portion 84 in the tube insertion direction. Thereby, here, the place where the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tube 66 abut can be increased, and the retention performance of the fin interval can be improved.

  Moreover, the 2nd fin tab 91 is arrange | positioned so that the wall part along a pipe | tube insertion direction may be made. For this reason, since the 2nd fin tab 91 will be arrange | positioned in parallel with the passage direction of the air along a pipe insertion direction here, ventilation resistance can be lowered | hung.

  Further, the first fin tab 90 and the second fin tab 91 are arranged so as not to overlap each other when the heat transfer fin 66 is viewed from the tube insertion direction. Here, the first fin tab 90 is cut and raised so that an opening 90a is formed on one side of the first fin tab 90 in the tube step direction (here, the upper side in FIG. 7 and FIG. 8). Is disposed at a position shifted from the center of the heat transfer fin 66 in the tube step direction to the other side in the tube step direction (here, the lower side of the drawing in FIGS. 7 and 8). On the other hand, the second fin tab 91 is cut and raised so that an opening 91a is formed on the other side of the second fin tab 91 in the tube step direction (here, on the lower side of the paper in FIGS. 7 and 8). The two fin tabs 91 are arranged at positions shifted from the center of the heat transfer fin 66 in the tube step direction to one side in the tube step direction (here, the upper side of the drawing in FIGS. 7 and 8). Thus, when the heat transfer fin 66 is viewed from the tube insertion direction, the first fin tab 90 is disposed at a position shifted to the other side of the second fin tab 91 across the center of the heat transfer fin 66 in the tube step direction. It has been done. For this reason, here, when the heat transfer fins 66 are viewed from the tube insertion direction, the degree of parallelism between the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tubes 63 can be increased, and the fin gap holding performance can be further increased. Can be improved.

<Rib part>
Next, ribs 92 and 96 are formed on the heat transfer fins 66 by causing the heat transfer fins 66 to bulge on the front side and the back side of the base 85 in the tube insertion direction. The near side rib portion 92 disposed on the near side in the tube insertion direction of the pedestal portion 85 intersects with the near side first rib portion 93 and the near side second rib 94 extending along the tube insertion direction in the tube insertion direction. And a near-side third rib 95 extending in the direction (tube step direction). The back side rib part 96 arrange | positioned at the back | inner side of the pipe insertion direction of the base part 85 cross | intersects the pipe | tube insertion direction with the back side 1st rib part 97 and the back side 2nd rib 98 which extend along a pipe insertion direction. And a rear third rib 99 extending along the direction (tube step direction). Here, the rib portions 92 and 96 bulge from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side in FIG. 7 and FIG. 8).

  The near-side first rib portion 93 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 the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The front-side first rib portion 93 is formed in a mountain shape whose ridge line 93 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 93a of the near-side first rib portion 93 is disposed in parallel to the outdoor air passing direction.

  The front-side second rib 94 is along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The front side second rib portion 94 is formed in a mountain shape whose ridgeline 94 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 94a of the front-side second rib portion 94 is disposed in parallel to the outdoor air passing direction.

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

  The near-side third rib 95 is disposed so as to connect ends of the near-side first rib portion 93 and the near-side second rib portion 94 on the base portion 85 side in the tube insertion direction. The front side third rib 95 is formed in a mountain shape parallel to the direction in which the ridge line 95 a intersects the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 95a of the front-side third rib 95 is disposed so as to intersect the outdoor air passage direction. And here, the ridgeline 93a of the near side first rib part 93, the ridgeline 95a of the near side third rib 95, and the ridgeline 94a of the near side second rib part 94 are connected in a U-shape. The front side first rib portion 93, the front side third rib 95 and the front side second rib portion 94 as a whole (that is, the front side rib portion 92) are formed in a U-shaped mountain shape. Further, the edge 95 b on the pedestal portion 84 side of the front side third rib 95 coincides with the third side 85 c of the flat surface 85 of the pedestal portion 84. That is, the edge 95b on the pedestal portion 84 side of the front side third rib 95 is not located on the base surface 66a of the heat transfer fin 66 but is located on the flat surface 85 protruding from the base surface 66a. Thereby, the front side third rib 95 (that is, the front side rib portion 92 including the front side first rib portion 93 and the front side second rib portion 94) is connected to the third side 85c of the flat surface 85 of the pedestal portion 84. They are arranged continuously. Further, the front rib portion 92 is disposed so as to surround the first fin tab 90. Here, the three sides excluding the front side of the first fin tab 90 in the tube insertion direction are surrounded. The front side rib portion 92 is disposed at a position where the ridgelines 93 a, 94 a, and 95 a protrude from the flat surface 85 of the pedestal portion 84 than the base surface 66 a of the heat transfer fin 66.

  Further, the back side first rib portion 97 and the back side second rib 98 are formed on one side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the paper surface of each fin intermediate portion 81 in FIGS. 7 and 8). It is arranged along the upper tube insertion part 60). The back side first rib portion 97 is formed in a mountain shape whose ridgeline 97 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 97a of the back side first rib portion 97 is arranged in parallel to the outdoor air passing direction.

  The back side second rib 98 is along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The back side second rib portion 98 is formed in a mountain shape whose ridgeline 98 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 98a of the back side second rib portion 98 is arranged in parallel to the outdoor air passage direction.

  Further, the back side first rib portion 97 and the back side second rib portion 98 extend not only to the fin intermediate portion 81 but also to the fin back portion 83. That is, the back side first rib portion 97 and the back side second rib portion 98 are disposed across the boundary portion between the fin intermediate portion 81 and the fin back portion 83.

  The back side third rib 99 is arranged so as to connect ends of the back side first rib part 97 and the back side second rib part 98 on the base part 85 side in the tube insertion direction. The back side third rib 99 is formed in a mountain shape parallel to the direction in which the ridge line 99 a intersects the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 99a of the back side third rib 99 is disposed so as to intersect the outdoor air passing direction. Here, the ridgeline 97a of the back side first rib portion 97, the ridgeline 99a of the backside third rib 99, and the ridgeline 98a of the backside second rib portion 98 are connected in a U-shape, thereby The back side first rib part 97, the back side third rib 99, and the back side second rib part 98 as a whole (that is, the back side rib part 96) are formed in a U-shaped mountain shape. Further, the edge 99 b on the pedestal portion 84 side of the back side third rib 99 coincides with the fourth side 85 d of the flat surface 85 of the pedestal portion 84. That is, the edge 99b of the back side third rib 99 on the pedestal portion 84 side is not positioned on the base surface 66a of the heat transfer fin 66 but is positioned on the flat surface 85 protruding from the base surface 66a. Thereby, the back side third rib 99 (that is, the back side rib part 96 including the back side first rib part 97 and the back side second rib part 98) is connected to the fourth side 85d of the flat surface 85 of the pedestal part 84. They are arranged continuously. Further, the back rib portion 96 is disposed so as to surround the second fin tab 91. Here, the three sides excluding the near side of the second fin tab 91 in the tube insertion direction are surrounded. In addition, the back side rib part 96 is arrange | positioned in the position where the ridgeline 97a, 98a, 99a protruded rather than the base surface 66a of the heat-transfer fin 66 rather than the flat surface 85 of the base part 84. FIG.

  Here, as described above, the rib portions 92 and 96 (specifically, the first and second rib portions 93 and 94) extending along the tube insertion direction toward the front side and the back side of the base portion 84 in the tube insertion direction. , 97, 98) are arranged continuously with the third side 85c and the fourth side 85d of the flat surface 85. For this reason, the rib portions 92 and 96 can be integrated with the pedestal portion 84 so that the third side 85c and the fourth side 85d of the pedestal portion 84 do not fold. Thereby, the fin intensity | strength of the direction which cross | intersects the pipe insertion direction in the near part and the back | inner side of the pipe insertion direction of the base part 84 and the base part 84 can be improved.

  Here, as described above, the rib portions 93 and 96 (specifically, the first and second rib portions 93, 94, 97, and 98) are connected to the boundary portion between the fin intermediate portion 81 and the fin front portion 82. And it arrange | positions so that the boundary part of the fin intermediate part 81 and the fin back part 83 may be straddled. For this reason, the fin strength in the direction intersecting the tube insertion direction at the boundary between the fin intermediate portion 81 and the fin front portion 82 and at the boundary between the fin intermediate portion 81 and the fin back portion 82 can be improved. For this reason, when the heat transfer tube 63 is inserted into the notch 67 of the heat transfer fin 66, buckling of the insertion fin starting from the boundary between the fin intermediate portion 81 and the fin back portion 83 can be suppressed. Further, in the state where the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66, it is possible to suppress buckling of the heat transfer fins 66 starting from the boundary between the fin intermediate portion 81 and the fin front portion 82. it can.

  Here, as described above, since the near-side rib portion 93 surrounding the first fin tab 90 is formed in the heat transfer fin 66, the heat transfer fin 66 at both ends where the first fin tab 90 is cut and raised is formed. A decrease in fin strength can be suppressed.

(6) Modification <A>
In the outdoor heat exchanger 23 as a heat exchanger according to the above embodiment, the pedestal portion 84 is formed on the heat transfer fin 66, but nothing is formed on the flat surface 85. However, the present invention is not limited to this. For example, as shown in FIG. 13, a louver is formed by cutting up the heat transfer fins 66 on the flat surface 85 of the pedestal portion 84 for the purpose of improving the heat transfer performance. 86 may be formed.

  Here, since the louver 86 is formed on the pedestal portion 84, for example, a portion forming the louver of the fin intermediate portion 81 compared to a case where the louver is formed in a portion where the waffle of the fin intermediate portion 81 is not formed. The fin strength in the direction intersecting the tube insertion direction can be improved. In addition, the louver 86 having a large size (particularly, a large size in the tube step direction) can be provided as compared with the case where the louver is formed in the waffle. For this reason, the heat transfer performance can be improved while suppressing buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67 of the heat transfer fins 66.

<B>
In the outdoor heat exchanger 23 as the heat exchanger according to the above-described embodiment, the first fin tabs 90 are formed of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81 arranged along the tube step direction. I try to place them all. However, the present invention is not limited to this. For example, as shown in FIG. 14, the first fin tabs 90 are arranged in a plurality of stages of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81. Also good.

  Here, since the 1st fin tab 90 is arrange | positioned for every several step of the several fin front part 82 and the corresponding several fin intermediate part 81, when dew condensation water generate | occur | produces in the outdoor heat exchanger 23, it is 1st. The amount of condensed water retained by the fin tab 90 can be reduced, and the drainage performance of the heat transfer fin 66 can be ensured. Although not shown here, the second fin tabs 91 may be arranged in a plurality of stages as in the first fin tab 90.

<C>
In the outdoor heat exchanger 23 as the heat exchanger according to the above-described embodiment, the first fin tab 90 is disposed along the tube insertion direction, but is not limited thereto, and the fin intermediate portion 81 is not limited thereto. The first fin tab 90 may not be along the tube insertion direction as long as the first fin tab 90 is disposed across the boundary between the first fin portion 82 and the front fin portion 82.

<D>
In the outdoor heat exchanger 23 as a heat exchanger according to the above-described embodiment, the front side rib portion 92 surrounds the three sides except the front side in the tube insertion direction of the first fin tab 90, but is not limited thereto. It is not something. For example, although not shown here, the front rib portion 92 may surround four sides including the front side of the first fin tab 90 in the tube insertion direction.

<E>
In the outdoor heat exchanger 23 as the heat exchanger according to the above embodiment, a heat exchanger in which the heat transfer tubes 63 are arranged in two rows in the outdoor air passage direction is taken as an example, but the present invention is not limited thereto. It may be one row, or three or more rows.

  The present invention is widely applicable to a heat exchanger provided with a plurality of flat tubes and a plurality of insertion fins.

23 Outdoor heat exchanger (heat exchanger)
63 Heat transfer tube (flat tube)
64 Flat surface 66 Heat transfer fin (insertion fin)
67 Notch portion 80 Pipe insertion portion 81 Fin intermediate portion 82 Fin front portion 83 Fin back portion 90 First fin tab 91 Second fin tab 92 Front side rib portion (rib portion)

JP 2012-163323 A

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

  Conventionally, as shown in Patent Document 1 (Japanese Patent Application Laid-Open No. 2012-163323), there is a heat exchanger provided with a plurality of flat tubes and a plurality of insertion fins. The flat tubes are arranged along a predetermined tube step direction with the flat surfaces facing each other. The insertion fin is formed with a plurality of notches for inserting a flat tube extending along the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube, and is arranged along the longitudinal direction of the flat tube. ing. Here, the portion of the cutout portion that contacts the flat tube while the flat tube is inserted is a tube insertion portion. The insertion fin includes a plurality of fin intermediate portions sandwiched between tube insertion portions adjacent to each other in the tube step direction, and a tube insertion from an end on the near side in the tube insertion direction of the plurality of fin intermediate portions of the insertion fins. A fin front portion extending toward the near side in the direction, and a plurality of fin intermediate portions from the back end in the tube insertion direction toward the back in the tube insertion direction. A fin back portion extending continuously from the side end portion is formed.

  In the heat exchanger of Patent Document 1, the portion of the notch portion that sandwiches the front portion of the fin only guides the flat tube to the tube insertion portion when the flat tube is inserted into the insertion fin. In the state of being inserted into the insertion fin, the flat tube is in contact with the fin intermediate portion but not in front of the fin. For this reason, in a state where the flat tube is inserted and joined to the insertion fin, the insertion fin may be buckled at the boundary between the fin intermediate portion and the fin front portion. That is, when the flat tube is inserted into the insertion fin and joined, when the heat exchanger receives an external force or the like, the insertion fin is bent starting from the boundary between the fin intermediate portion and the fin front portion. There is a risk that.

  The subject of this invention is suppressing the generation | occurrence | production of buckling of the insertion fin in the boundary part of a fin intermediate part and a fin front part in the heat exchanger provided with the some flat tube and the some insertion fin. .

The heat exchanger according to the first aspect is a heat exchanger including a plurality of flat tubes and a plurality of insertion fins. The flat tubes are arranged along a predetermined tube step direction with the flat surfaces facing each other. The insertion fin is formed with a plurality of notches for inserting a flat tube extending along the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube, and is arranged along the longitudinal direction of the flat tube. ing. Here, the portion of the notch that is in contact with the flat tube in a state in which the flat tube is inserted is a tube insertion portion, and the insertion fin includes a plurality of fins sandwiched between tube insertion portions adjacent to each other in the tube step direction. An intermediate portion, a fin front portion extending from the near end in the tube insertion direction of the plurality of fin intermediate portions toward the near side in the tube insertion direction, and narrower than the fin intermediate portion in the tube step direction; and a plurality of fins A fin back portion extending continuously from a back end portion in the tube insertion direction of the fin intermediate portion to a back end portion in the tube insertion direction of the plurality of fin intermediate portions. Is formed. And here, insertion fins, in order to hold the spacing between the plug adjacent fins in the longitudinal direction of the flat tubes has a first Fintabu formed by cutting and raising the plug fin, first Fintabu However, it arrange | positions ranging over the boundary part of a fin intermediate part and a fin front part, and it is arrange | positioned so that the wall part along a pipe insertion direction may be made.

  Here, since the first fin tab is arranged so as to straddle the boundary portion between the fin intermediate portion and the fin front portion, in the state where the flat tube is inserted and joined to the insertion fin, the fin intermediate portion and the fin front portion are connected. The fall of the fin intensity | strength of the direction which cross | intersects the pipe insertion direction of the insertion fin in the boundary part with a part can be suppressed. For this reason, in the state where the flat tube is inserted and joined to the insertion fin, the occurrence of buckling of the insertion fin at the boundary between the fin intermediate portion and the front portion of the fin can be suppressed. In this regard, when the fin tab is formed on the front side of the fin and is not disposed at the boundary with the fin intermediate portion as in the heat exchanger of Patent Document 1, the fin tab is the boundary between the fin intermediate portion and the fin front portion. In the state where the fin strength in the direction intersecting the tube insertion direction of the insertion fin cannot be suppressed, in the state where the flat tube is inserted and joined to the insertion fin, the intermediate portion of the fin and the front portion of the fin It is difficult to suppress the occurrence of buckling of the insertion fin at the boundary. This also applies to the case where the fin tab is formed at the fin intermediate portion and is not disposed at the boundary portion with the fin front portion.

In addition, here, since the first fin tab is arranged in a direction intersecting with the boundary between the fin intermediate portion and the fin front portion, the fin strength in the direction intersecting the tube insertion direction of the insertion fin is reduced. The effect which suppresses a fall can be heightened. And since a 1st fin tab will be arrange | positioned in parallel with the passage direction of the air along a pipe insertion direction, ventilation resistance can be lowered | hung.

Heat exchanger according to a second aspect is the heat exchanger according to a first aspect, the insertion fin, the rib portion surrounding the first Fintabu is formed by bulging the plug fin. Here, the rib portion may not surround all four sides of the first fin tab, and may surround most of the first fin tab like a U-shape surrounding the three sides of the first fin tab. .

  Here, since the rib part surrounding the 1st fin tab is formed in the insertion fin, the fall of the fin strength of the insertion fin in the both ends where the 1st fin tab was cut and raised can be controlled.

The heat exchanger according to the third aspect corresponds to the plurality of fin front portions in which the first fin tab is arranged along the tube step direction in either of the heat exchangers according to the first or second aspect. It arrange | positions for every several steps of several fin intermediate part.

  Here, since the 1st fin tab is arrange | positioned for every several steps of a several fin front part and a corresponding some fin intermediate part, when condensed water generate | occur | produces in a heat exchanger, the condensed water by a 1st fin tab It is possible to reduce the water retention amount and ensure the drainage performance of the insertion fin.

In the heat exchanger according to the fourth aspect , in any one of the heat exchangers according to the first to third aspects, an interval between the insertion fins adjacent to each other in the longitudinal direction of the flat tube is maintained in the fin back portion. For this purpose , a second fin tab is formed by cutting and raising the insertion fin .

  Here, since the 2nd fin tab is formed in the fin inner part, the place where the insertion fins adjacent to the longitudinal direction of a flat tube contact | abut can be increased, and the holding | maintenance performance of a fin space | interval can be improved.

The heat exchanger according to the fifth aspect is the heat exchanger according to the fourth aspect, wherein the second fin tab is disposed so as to form a wall portion along the tube insertion direction.

  Here, since the 2nd fin tab is arranged in parallel with the passage direction of the air along a pipe insertion direction, ventilation resistance can be lowered.

The heat exchanger according to the sixth aspect is the heat exchanger according to the fourth or fifth aspect, wherein the first fin tab and the second fin tab do not overlap each other when the insertion fin is viewed from the tube insertion direction. Are arranged as follows.

The heat exchanger according to a seventh aspect is the heat exchanger according to the fourth or fifth aspect, wherein the insertion fin is formed on the one side in the tube step direction of the first fin tab, and the second A second opening formed on the other side of the fin tab in the tube step direction, and the first opening and the second opening are arranged to overlap each other when the insertion fin is viewed from the tube insertion direction. The first fin tab and the second fin tab are arranged so as not to overlap each other when the insertion fin is viewed from the tube insertion direction.

  Here, since the first fin tab and the second fin tab are arranged so as not to overlap each other when the insertion fin is viewed from the tube insertion direction, when the insertion fin is viewed from the tube insertion direction, the flatness is flat. The degree of parallelism between the insertion fins adjacent to each other in the longitudinal direction of the tube can be increased, and the fin spacing retention performance can be further improved.

  As described above, according to the present invention, the following effects can be obtained.

In the heat exchanger according to the first aspect, in a state where the flat tube is inserted and joined to the insertion fin, the occurrence of buckling of the insertion fin at the boundary portion between the fin intermediate portion and the fin front portion is suppressed. be able to. In addition, the effect of suppressing the decrease in fin strength in the direction intersecting the tube insertion direction of the insertion fin can be enhanced, and the first fin tab is arranged in parallel to the air passage direction along the tube insertion direction. Therefore, the draft resistance can be lowered.

In the heat exchanger according to the second aspect , it is possible to suppress a decrease in fin strength of the insertion fins at both ends where the first fin tab is cut and raised.

In the heat exchanger according to the third aspect , when condensed water is generated in the heat exchanger, the amount of condensed water retained by the first fin tab can be reduced, and the drainage performance of the insertion fin can be ensured.

In the heat exchanger according to the fourth aspect, the number of places where the insertion fins adjacent to each other in the longitudinal direction of the flat tube are in contact with each other can be increased to improve the performance of maintaining the fin interval.

In the heat exchanger according to the fifth aspect , since the second fin tab is disposed in parallel to the air passage direction along the tube insertion direction, the ventilation resistance can be lowered.

In the heat exchanger according to the sixth or seventh aspect , when the insertion fins are viewed from the tube insertion direction, the degree of parallelism between the insertion fins adjacent to each other in the longitudinal direction of the flat tube can be increased. It is possible to further improve the holding performance.

It is a schematic block diagram of the air conditioning apparatus which has an outdoor heat exchanger as a heat exchanger concerning one Embodiment of this invention. It is a perspective view which shows the external appearance of an outdoor unit. It is a top view which shows the state which removed the top plate of the outdoor unit. It is a perspective view which shows the state which removed the top plate, the front plate, and the side plate of the outdoor unit. It is a schematic perspective view of an outdoor heat exchanger. It is the elements on larger scale of the heat exchange part of FIG. It is the elements on larger scale which show the state which looked at the heat exchange part of FIG. 6 from the direction along the longitudinal direction of a heat exchanger tube. It is a figure which shows the principal part of a heat-transfer fin. It is II sectional drawing of FIG. It is II-II sectional drawing of FIG. 8, III-III sectional drawing, and IV-IV sectional drawing. It is the figure which looked at FIG. 8 from the near side of the pipe insertion direction, and the figure which looked at the back side of the pipe insertion direction. It is VV sectional drawing of FIG. It is a figure which shows the heat exchanger concerning a modification, Comprising: It is a figure corresponding to FIG. It is a figure which shows the heat exchanger concerning a modification, Comprising: It is a figure corresponding to FIG.

  Hereinafter, an embodiment of a heat exchanger concerning the present invention and its modification are described based on a drawing. In addition, the specific structure of the heat exchanger concerning this invention is not restricted to the following embodiment and its modification, It can change in the range which does not deviate from the summary of invention.

(1) Basic Configuration of Air Conditioner FIG. 1 is a schematic configuration diagram of an air conditioner 1 having 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 a room such as a building 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 tube 5 and a gas refrigerant communication tube 6. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the indoor unit 4 via the refrigerant communication pipes 5 and 6.

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

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

<Outdoor unit>
The outdoor unit 2 is installed outside and constitutes a part of the refrigerant circuit 10. The outdoor unit 2 mainly includes 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 of the refrigeration cycle until it reaches a high pressure. The compressor 21 has a hermetically sealed structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a. The compressor 21 has a suction pipe 31 connected to the suction side and a discharge pipe 32 connected to the discharge side. The suction pipe 31 is a refrigerant pipe that connects the suction side of the compressor 21 and the four-way switching valve 22. The discharge pipe 32 is a refrigerant pipe that connects 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 direction of refrigerant flow in the refrigerant circuit 10. During the cooling operation, the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as a radiator for the refrigerant compressed in the compressor 21 and the indoor heat exchanger 41 for the refrigerant that has radiated heat in the outdoor heat exchanger 23. Switch to the cooling cycle state to function as an evaporator. That is, in the cooling operation, the four-way switching valve 22 is connected between the discharge side of the compressor 21 (here, the discharge pipe 32) and the gas side of the outdoor heat exchanger 23 (here, the first gas refrigerant pipe 33). (See the solid line of the four-way selector valve 22 in FIG. 1). Moreover, the suction side (here, the suction pipe 31) of the compressor 21 and the gas refrigerant communication pipe 6 side (here, the second gas refrigerant pipe 34) are connected (solid line of the four-way switching valve 22 in FIG. 1). See). Further, the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as an evaporator of the refrigerant that has radiated heat in the indoor heat exchanger 41 during the heating operation, and the indoor heat exchanger 41 is compressed in the compressor 21. Switching to a heating cycle state that functions as a refrigerant radiator. That is, in the heating operation, the four-way switching valve 22 is connected to the discharge side (here, the discharge pipe 32) of the compressor 21 and the gas refrigerant communication pipe 6 side (here, the second gas refrigerant pipe 34). (Refer to the broken line of the four-way switching valve 22 in FIG. 1). In addition, the suction side of the compressor 21 (here, the suction pipe 31) and the gas side of the outdoor heat exchanger 23 (here, the first gas refrigerant pipe 33) are connected (four-way switching valve 22 in FIG. 1). See the dashed line). Here, the first gas refrigerant pipe 33 is a refrigerant pipe connecting 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 refrigerant radiator that uses outdoor air as a cooling source during cooling operation, and functions as a refrigerant evaporator that uses outdoor air as a heating source during heating operation. The outdoor heat exchanger 23 has a liquid side connected to the liquid refrigerant pipe 35 and a gas side 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 reduces the high-pressure refrigerant of the refrigeration cycle that has radiated heat in the outdoor heat exchanger 23 to the low pressure of the refrigeration cycle during the cooling operation. The expansion valve 24 is a valve that reduces the high-pressure refrigerant of the refrigeration cycle radiated in the indoor heat exchanger 41 to the low pressure of the refrigeration cycle during heating operation. The expansion valve 24 is provided in a portion of the liquid refrigerant pipe 35 near the liquid side closing 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 with external devices and pipes (specifically, the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6). The liquid side closing valve 25 is provided at the end of the liquid refrigerant pipe 35. The gas side closing 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 and then discharging the air to the outside. That is, the outdoor unit 2 includes an outdoor fan 36 as a fan that supplies outdoor air as a cooling source or a heating source of the refrigerant flowing through the outdoor heat exchanger 23 to the outdoor heat exchanger 23. Here, as the outdoor fan 36, a propeller fan or the like driven by an outdoor fan motor 36a is used.

<Refrigerant communication pipe>
Refrigerant communication pipes 5 and 6 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building. The refrigerant communication tubes 5 and 6 include a combination of the installation location and the outdoor unit 2 and the indoor unit 4. Depending on the installation conditions, those having various lengths and pipe diameters are used.

(2) Basic operation | movement of an air conditioning apparatus Next, basic operation | movement of the air conditioning apparatus 1 is demonstrated using FIG. The air conditioner 1 can perform a cooling operation and a heating operation as basic operations.

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

  In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and is compressed until it reaches the high pressure in 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 radiates heat by exchanging heat with outdoor air supplied as a cooling source by the outdoor fan 36 in the outdoor heat exchanger 23 that functions as a refrigerant radiator. Become a high-pressure liquid refrigerant.

  The high-pressure liquid refrigerant that has radiated 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 depressurized to the low pressure of the refrigeration cycle by the expansion valve 24 and becomes 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 indoor heat exchanger 41 through the liquid-side closing 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 by exchanging heat with indoor air supplied as a heating source by the indoor fan 42 in the indoor heat exchanger 41. As a result, the room air is cooled and then supplied to the room to cool the room.

  The low-pressure gas refrigerant evaporated in the indoor heat exchanger 41 is again sucked into the compressor 21 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 broken line in FIG. 1).

  In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and is compressed until it reaches the high pressure in the refrigeration cycle, and then 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 radiates heat by exchanging heat with indoor air supplied as a cooling source by the indoor fan 42 in the indoor heat exchanger 41 to become a high-pressure liquid refrigerant. . Thereby, indoor air is heated, and indoor heating is performed by being supplied indoors after that.

  The high-pressure liquid refrigerant radiated by 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 depressurized to the low pressure of the refrigeration cycle by the expansion valve 24 and becomes 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 exchanges heat with the outdoor air supplied as a heating source by the outdoor fan 36 in the outdoor heat exchanger 23 that functions as a refrigerant evaporator. Go and evaporate into a low-pressure gas refrigerant.

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

(3) Basic configuration of outdoor unit Next, the basic configuration of the outdoor unit 2 will be described with reference to FIGS. Here, FIG. 2 is a perspective view showing an 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, the front plates 55 and 56, and the side plates 53 and 54 of the outdoor unit 2 are removed. In the following description, “upper”, “lower”, “left”, “right”, “vertical”, “front”, “side”, “back”, “top”, “bottom”, etc. The wording means a direction and a surface when the surface on the fan blowing grill 55b side is a front surface unless otherwise specified.

  The outdoor unit 2 has a structure (so-called trunk type structure) in which the inside of the unit casing 51 is partitioned 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 discharge air from the front surface of the unit casing 51 after sucking outdoor air into the inside from a part of the back surface and side surface of the unit casing 51. The outdoor unit 2 mainly includes a unit casing 51, a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, closing valves 25 and 26, and refrigerant pipes 31 to 35 connecting these devices. It has the apparatus and piping which comprise the refrigerant circuit 10 containing, the outdoor fan 36, and the motor 36a for outdoor fans. Here, an example in which the blower chamber S1 is formed near the left side surface of the unit casing 51 and the machine chamber S2 is formed near the right side surface of the unit casing 51 will be described, but the left and right sides may be reversed.

  The unit casing 51 is formed in a substantially rectangular parallelepiped shape. The unit casing 51 mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, closing valves 25 and 26, and a refrigerant pipe connecting these devices. The apparatus and piping which comprise the refrigerant circuit 10 containing 31-35, the outdoor fan 36, and the outdoor fan motor 36a are accommodated. The unit casing 51 includes a bottom plate 52 on which the devices and pipings 21 to 26, 31 to 35, the outdoor fan 36, and the like constituting the refrigerant circuit 10 are placed, a blower chamber side plate 53, a machine chamber side plate 54, It has a blower room side front plate 55, a machine room side front plate 56, a top plate 57, and two installation legs 59.

  The bottom plate 52 is a plate-like member that constitutes the bottom portion of the unit casing 51.

  The blower chamber side plate 53 is a plate-like member that forms a side surface portion (here, the left side surface portion) of the unit casing 51 near the blower chamber S1. The lower part of the blower chamber side plate 53 is fixed to the bottom plate 52, and here, the front end portion thereof is an integral member with the left end portion of the blower chamber side front plate 55. The blower chamber side plate 53 is formed with a side fan inlet 53 a for sucking outdoor air into the unit casing 51 from the side surface side of the unit casing 51 by the outdoor fan 36. The blower chamber side plate 53 may be a separate member from the blower chamber side front plate 55.

  The machine room side plate 54 is a plate-like member that constitutes a part of the side surface portion (here, the right side surface portion) of the unit casing 51 near the machine room S2 and the back surface portion of the unit casing 51 near the machine room S2. is there. The lower part of the machine room side plate 54 is fixed to the bottom plate 52. Outdoor air is passed into the unit casing 51 from the back side of the unit casing 51 by the outdoor fan 36 between the rear side end of the blower room side plate 53 and the end of the machine room side plate 54 on the blower chamber S1 side. A rear fan inlet 53b for inhalation is formed.

  The blower chamber side front plate 55 is a plate-like member that constitutes the front portion of the blower chamber S <b> 1 of the unit casing 51. The lower portion of the blower chamber side front plate 55 is fixed to the bottom plate 52, and here, the left side end portion is an integral member with the front end portion of the blower chamber side plate 53. The blower chamber side front plate 55 is provided with a fan outlet 55a for blowing the outdoor air sucked into the unit casing 51 by the outdoor fan 36 to the outside. On the front side of the blower chamber side front plate 55, a fan blow grill 55b that covers the fan blow outlet 55a is provided. The blower chamber side front plate 55 may be a separate member from the blower chamber side plate 53.

  The machine room side front plate 56 is a plate-like member that constitutes a part of the front part of the machine room S2 of the unit casing 51 and a part of the side part of the machine room S2 of the unit casing 51. The machine room side front plate 56 has an end portion on the fan chamber S1 side fixed to an end portion on the machine room S2 side of the blower chamber side front plate 55, and an end portion on the back side on the front side of the machine room side plate 54. It is fixed to the end of the.

  The top plate 57 is a plate-like member that constitutes the top surface portion of the unit casing 51. The top plate 57 is fixed to the blower chamber side plate 53, the machine room side plate 54, and the blower chamber side front plate 55.

  The partition plate 58 is a plate-like member that is arranged on the bottom plate 52 and extends in the vertical direction. Here, the partition plate 58 divides the inside of the unit casing 51 into left and right to form a blower chamber S1 near the left side and a machine chamber S2 near the right side. The lower portion of the partition plate 58 is fixed to the bottom plate 52, the front end portion thereof is fixed to the blower chamber side front plate 55, and the rear end portion thereof is the side closer to the machine room S <b> 2 of the outdoor heat exchanger 23. It extends to the end.

  The installation leg 59 is a plate-like member extending in the front-rear direction of the unit casing 51. The installation leg 59 is a member fixed to the installation surface of the outdoor unit 2. Here, the outdoor unit 2 has two installation legs 59, one is arranged near the blower room S1, and the other is arranged near the machine room S2.

  The outdoor fan 36 is a propeller fan having a plurality of blades, and faces the front surface of the unit casing 51 (here, the fan air outlet 55a) at a position on the front surface side of the outdoor heat exchanger 23 in the blower chamber S1. Are arranged as follows. 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. The outdoor fan 36 is pivotally supported by an outdoor fan motor 36a.

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

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

(4) Basic Configuration of Outdoor Heat Exchanger Next, the basic configuration of the outdoor heat exchanger 23 will be described with reference to FIGS. Here, FIG. 5 is a schematic perspective view of the outdoor heat exchanger 23. FIG. 6 is a partially enlarged view of the heat exchange unit 60 of FIG. In the following description, the terms indicating directions and surfaces mean directions and surfaces based on the state in which the outdoor heat exchanger 23 is placed on the outdoor unit 2 unless otherwise specified.

  The outdoor heat exchanger 23 mainly includes a heat exchanging unit 60 that exchanges heat between outdoor air and refrigerant, a refrigerant flow divider 70 provided on one end side (here, the right end side) of the heat exchanging unit 60, and an inlet / outlet header. 71 and an intermediate header 72, and a connection header 74 provided on the other end side (here, the left front end side) of the heat exchanging unit 60. The outdoor heat exchanger 23 is an all-aluminum heat exchanger in which all of the refrigerant flow distributor 70, the inlet / outlet header 71, the intermediate header 72, the connection header 74, and the heat exchange unit 60 are made of aluminum or aluminum alloy. Is performed by brazing such as brazing in a furnace.

<Heat exchange part>
The heat exchanging unit 60 includes an upwind heat exchanging unit 61 that constitutes an upwind portion of the outdoor heat exchanger 23 and an upwind heat exchanging unit 62 that constitutes a downwind portion of the outdoor heat exchanger 23. The heat exchangers 61 and 62 are arranged in two rows in the direction in which the outdoor air passes through the unit casing 51 generated by driving the outdoor fan 36. The windward side heat exchange unit 61 is disposed closer to the side surface (here, the left side surface) and the back side of the unit casing 51 than the leeward side heat exchange unit 62. That is, the portion of the heat exchanging unit 60 that is located on the windward side near the fan suction ports 53 a and 53 b with respect to the direction in which the outdoor air passes is the windward heat exchanging unit 61. A portion located on the leeward side far from the ports 53a and 53b is the leeward heat exchange unit 62. And the windward heat exchange part 61 has the windward main heat exchange part 61a which comprises the upper part of the outdoor heat exchanger 23, and the windward sub heat exchange part 61b which comprises the lower part of the outdoor heat exchanger 23. ing. Further, the leeward side heat exchanging unit 62 includes a leeward side main heat exchanging unit 62 a constituting the upper part of the outdoor heat exchanger 23 and a leeward side sub heat exchanging unit 62 b constituting the lower part of the outdoor heat exchanger 23. ing.

  The heat exchanging unit 60 is an insertion fin type heat exchanging unit constituted by a large number of heat transfer tubes 63 made of flat tubes and a large number of heat transfer fins 66 made of insertion fins. The heat transfer tube 63 is made of aluminum or aluminum alloy, and is a flat multi-hole tube having a flat surface 64 serving as a heat transfer surface and a large number of small internal flow paths 65 through which a refrigerant flows. A large number of heat transfer tubes 63 are arranged in a plurality of stages at intervals along a predetermined tube step direction with the flat surfaces 64 facing each other, and one end in the longitudinal direction (here, the right end) is the inlet / outlet header 71 or the intermediate header. 72 and the other end in the longitudinal direction (here, the left front end) is connected to the connection header 74. That is, the large number of heat transfer tubes 63 are disposed between the inlet / outlet header 71 and the intermediate header 72 and the connection header 74. Here, since the flat surface 64 of the heat transfer tube 63 faces the vertical direction, the tube step direction means the vertical direction, and the heat transfer tube 63 is arranged along the side surface (here, the left side surface) and the back surface of the unit casing 51. Therefore, the longitudinal direction of the heat transfer tube 63 means the horizontal direction along the side surface (here, the left side surface) and the back surface of the unit casing 51. The heat transfer fins 66 are made of aluminum or an aluminum alloy, and a plurality of heat transfer fins 66 are arranged along the longitudinal direction of the heat transfer tube 63 at intervals. The heat transfer fins 66 are formed with a number of notches 67 for inserting the heat transfer tubes 63 extending along the tube insertion direction that intersects the tube step direction and the longitudinal direction of the heat transfer tubes 63. Here, since the tube step direction is the vertical direction and the longitudinal direction of the heat transfer tube 63 is the horizontal direction along the side surface (here, the left side surface) and the back surface of the unit casing 51, the tube insertion direction is the heat transfer tube 63. This means a horizontal direction that intersects the longitudinal direction, and also coincides with the passage direction of outdoor air in the unit casing 51. The notch 67 is elongated in the horizontal direction from one edge of the heat transfer fin 66 in the tube insertion direction (here, the edge on the windward side with respect to the outdoor air passage direction). Here, the large number of heat transfer tubes 63 include a heat transfer tube group constituting the windward main heat exchange unit 61a, a heat transfer tube group constituting the windward sub heat exchange unit 61b, and a leeward main heat exchange unit 62a. The heat transfer tube group is divided into a heat transfer tube group and a heat transfer tube group constituting the leeward side sub heat exchange unit 62b. Further, the large number of heat transfer fins 66 include a group of fins that form a common windward row for the windward main heat exchange unit 61a and the windward sub heat exchange unit 61b, and the leeward main heat exchange unit 62a and the leeward sub The heat exchange section 62b is divided into fin groups that form a common leeward row.

<Refrigerant divider>
The refrigerant distributor 70 is connected between the liquid refrigerant pipe 35 and the lower part of the inlet / outlet header 71. The refrigerant flow divider 70 is a member made of aluminum or aluminum alloy and extending in the vertical direction. The refrigerant distributor 70 divides the refrigerant flowing in through the liquid refrigerant pipe 35 and guides it to the lower part of the inlet / outlet header 71, or joins the refrigerant flowing in through the lower part of the inlet / outlet header 71 and guides it to the liquid refrigerant pipe 35. <Gateway header>
The entrance / exit 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. The inlet / outlet header 71 is connected to one end (here, the right end) of the heat transfer pipe 63 that constitutes the upwind heat exchange unit 61. The entrance / exit header 71 is a member made of aluminum or aluminum alloy and extending in the vertical direction. The internal space of the entrance / exit header 71 is vertically partitioned by a baffle (not shown), and the upper space communicates with one end (here, the right end) of the heat transfer pipe 63 constituting the upwind main heat exchange section 61a. The lower space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the windward side sub heat exchanging portion 61b. And the upper part of the entrance / exit header 71 is connected to the 1st gas refrigerant pipe 33, and exchanges a refrigerant | coolant between the windward main heat exchange part 61a and the 1st gas refrigerant pipe 33. As shown in FIG. Further, the lower part of the inlet / outlet header 71 is connected to the refrigerant distributor 70 so that the refrigerant is exchanged with the refrigerant distributor 70.

<Intermediate header>
The intermediate header 72 is provided on one end side (here, the right end side) of the leeward heat exchange unit 62 in the heat exchange unit 60. The intermediate header 72 is connected to one end (here, the right end) of the heat transfer tube 63 that constitutes the leeward heat exchange unit 62. The intermediate header 72 is a member that is formed of aluminum or an aluminum alloy and extends in the vertical direction. The internal space of the intermediate header 72 is vertically partitioned by a baffle (not shown), and the upper space communicates with one end (here, the right end) of the heat transfer pipe 63 that constitutes the leeward main heat exchange section 62a. The lower space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the leeward side sub heat exchanging portion 62b. Further, the upper space and the lower space of the intermediate header 72 are partitioned into a plurality of spaces by baffles (not shown) according to the number of passes of the heat exchanging unit 60, and the upper space and the lower space through the intermediate connecting pipe 73 and the like. It communicates with the space. The intermediate header 72 exchanges refrigerant between the leeward main heat exchange unit 62a and the leeward sub heat exchange unit 62b.

<Consolidated header>
The connection header 74 is provided on the other end side (here, the left front end side) of the heat exchange unit 60. The connection header 74 is connected to the other end (here, the left front end) of the heat transfer tube 63 constituting the heat exchanging unit 60. The connection header 74 is a member made of aluminum or aluminum alloy and extending in the vertical direction. The connection header 74 includes the other end (here, the left front end) of the heat transfer tube 63 constituting the windward heat exchange unit 61 and the other end (here, the left front end) of the heat transfer tube 63 constituting the leeward side heat exchange unit 62. ) Are connected to each other. And the connection header 74 exchanges a refrigerant | coolant between the windward side heat exchange part 61 and the leeward side heat exchange part 62. As shown in FIG.

  When the outdoor heat exchanger 23 having such a configuration functions as a refrigerant evaporator, the refrigerant flowing from the liquid refrigerant pipe 35 is transferred to the refrigerant flow divider 70 as indicated by the arrows indicating the flow of the refrigerant in FIG. And through the lower part of the inlet / outlet header 71, it is guided to the windward side sub heat exchange part 61b. And the refrigerant | coolant which passed the windward sub heat exchange part 61b is guide | induced to the leeward side sub heat exchange part 62b through the lower part of the connection header 74. FIG. And the refrigerant | coolant which passed the leeward side sub heat exchange part 62b is guide | induced to the leeward side main heat exchange part 62a through the intermediate header 72. FIG. And the refrigerant | coolant which passed the leeward side main heat exchange part 62a is guide | induced to the leeward side main heat exchange part 61a through the upper part of the connection header 74. FIG. Then, the refrigerant that has passed through the windward main heat exchanging portion 61 a flows out to the first gas refrigerant pipe 33 through the upper part of the inlet / outlet header 71. In the course of such a refrigerant flow, the refrigerant evaporates by heat exchange with outdoor air. When the outdoor heat exchanger 23 functions as a refrigerant radiator, the refrigerant flowing from the first gas refrigerant pipe 33 passes through the upper part of the inlet / outlet header 71 as shown by the arrows indicating the refrigerant flow in FIG. Then, it is guided to the windward main heat exchanging part 61a. And the refrigerant | coolant which passed the windward main heat exchange part 61a is guide | induced to the leeward main heat exchange part 62a through the upper part of the connection header 74. FIG. And the refrigerant | coolant which passed the leeward side main heat exchange part 62a is guide | induced to the leeward side sub heat exchange part 62b through the intermediate header 72. FIG. And the refrigerant | coolant which passed the leeward side sub heat exchange part 62b is guide | induced to the leeward side sub heat exchange part 61b through the lower part of the connection header 74. FIG. Then, the refrigerant that has passed through the windward side sub heat exchanging portion 61 b flows out to the liquid refrigerant pipe 35 through the lower portion of the inlet / outlet header 71 and the refrigerant distributor 70. In the course of such a refrigerant flow, the refrigerant radiates heat by heat exchange with the outdoor air.

(5) Detailed structure of heat transfer fin Next, the detailed structure of the heat transfer fin 66 is demonstrated using FIGS. Here, FIG. 7 is a partially enlarged view showing a state in which the heat exchanging unit 60 in FIG. 6 is viewed from the direction along the longitudinal direction of the heat transfer tube 63. FIG. 8 is a view showing a main part of the heat transfer fin 66. 9 is a cross-sectional view taken along the line II of FIG. 10 is a cross-sectional view taken along a line II-II, a cross-sectional view taken along a line III-III, and a cross-sectional view taken along a line IV-IV in FIG. FIG. 11 is a view of FIG. 8 viewed from the front side in the tube insertion direction and a view viewed from the back side in the tube insertion direction. 12 is a cross-sectional view taken along the line VV in FIG.

<Basic shape>
The heat transfer fin 66 is a plate-like fin that is long in one direction (here, vertically long) formed by pressing a plate material made of aluminum or aluminum alloy.

  A large number of notches 67 of the heat transfer fins 66 are formed at predetermined intervals in the tube step direction of the heat transfer fins 66. Here, a portion of the cutout portion 67 that contacts the heat transfer tube 63 in a state where the heat transfer tube 63 is inserted constitutes a tube insertion portion 80. The tube insertion portion 80 has a vertical width substantially equal to the width between the flat surfaces 64 of the heat transfer tubes 63, and a horizontal width substantially equal to the width in the direction intersecting the flat surfaces 64 of the flat tubes 63. It has become. The peripheral edge 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 front side in FIG. 7 and FIG. 8). The base surface 66a of the heat transfer fin 66 means the fin surface of the heat transfer fin 66 fin in a state before the formation of each part including the tube insertion portion 80. The heat transfer tube 63 is inserted into the notch 67 and guided to the tube insertion portion 80 which is a part of the notch 67, and is joined to the peripheral edge of the tube insertion portion 80 by brazing. The heat transfer fins 66 are formed with a plurality of fin intermediate portions 81 sandwiched between the tube insertion portions 80 adjacent in the tube step direction. In addition, the heat transfer fin 66 has a plurality of fin intermediate portions 81 from the front side in the tube insertion direction (here, the windward side with respect to the passage direction of outdoor air) toward the front side in the tube insertion direction. Fin front portions 82 extending respectively are formed. Further, the heat transfer fin 66 has a plurality of fin intermediate portions 81 extending from the end on the back side in the tube insertion direction (here, the leeward side with respect to the passage direction of outdoor air) toward the back side in the tube insertion direction. A fin back portion 83 extending continuously from the back end of the plurality of fin intermediate portions 81 in the tube insertion direction is formed.

  In such heat transfer fins 66, for example, it is conceivable to form a plurality of waffles having a mountain-shaped inclined surface along the tube insertion direction. However, when such a plurality of waffles are formed, when the heat transfer tubes 63 are inserted into the notches 67 of the heat transfer fins 66, the heat transfer fins 66 buckle at the valleys between the waffles adjacent in the tube insertion direction. May occur. That is, when the heat transfer tube 63 is inserted into the cutout portion 67 of the heat transfer fin 66, the valley portion between the waffles becomes a V-shaped fold, and the heat transfer fin 66 may be bent. For this reason, it is necessary to be able to suppress the occurrence of buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67.

  In such a heat transfer fin 66, the portion of the notch 67 sandwiching the fin front portion 82 guides the heat transfer tube 63 to the tube insertion portion 80 when the heat transfer tube 63 is inserted into the heat transfer fin 66. However, in a state where the heat transfer tubes 63 are inserted into the heat transfer fins 66, the heat transfer tubes 63 are in contact with the fin intermediate portion 81 but are not in contact with the fin front portion 82. For this reason, in a state where the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66, the heat transfer fins 66 may be buckled at the boundary between the fin intermediate portion 81 and the fin 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 tubes 63 are inserted and joined to the heat transfer fins 66, a boundary portion between the fin intermediate portion 81 and the fin front portion 82 is a starting point. The heat transfer fins 66 may be bent. On the other hand, it is necessary to be able to suppress the occurrence of buckling of the heat transfer fin 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82.

  Therefore, here, the buckling of the heat transfer fin 66 when the heat transfer tube 63 is inserted into the notch 67 and the occurrence of the buckling of the heat transfer fin 66 at the boundary between the fin intermediate portion 81 and the fin front portion 82 are suppressed. In order to do so, the heat transfer fin 66 is devised as follows.

<Pedestal part>
First, in the heat transfer fin 66, a pedestal portion 84 that forms a flat surface 85 is formed in a plurality of fin intermediate portions 81 by causing the heat transfer fins 66 to bulge. The pedestal portion 84 is disposed near the center of the fin intermediate portion 81 in the tube insertion direction. Here, the entire flat surface 85 is arranged at a position protruding from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). ing.

  Thus, here, since the pedestal portion 84 forming the flat surface 85 is formed in the fin intermediate portion 81, unlike the case where the waffle is formed in the heat transfer fin 66, the notch portion 67 of the heat transfer fin 66 is formed. When the heat transfer tube 63 is inserted, there is no V-shaped crease such as a valley between the waffles. For this reason, it becomes possible to improve the fin strength in the direction intersecting the tube insertion direction, and to suppress the occurrence of buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67. .

  Further, the protruding height of the pedestal portion 84 from the base surface 66 a of the heat transfer fin 66 is set to be higher than the protruding height of the tube insertion portion 80. For this reason, the effect which improves fin intensity | strength can be heightened by forming the base part 84. FIG.

  Further, the flat surface 85 connects the first side 85a and the second side 85b that are parallel to each other extending in the tube insertion direction, and the end portions of the first side 85a and the second side 85b on the near side in the tube insertion direction. It has a third side 85c and a fourth side 85d that connects the ends of the first side 85a and the second side 85b on the back side in the tube insertion direction. 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 the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The second side 85b is arranged along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Has been. As a result, the flat surface 85 formed by the pedestal portion 84 has a substantially square shape. For this reason, in particular, the fin strength in the direction intersecting the tube insertion direction can be improved by the first side 85a and the second side 85b, which are a part of four sides having a substantially rectangular shape. Here, the ends of the sides 85a to 85d are connected so as to form sharp corners. However, even if the corners are chamfered or the corners are rounded to have a round shape, the corners may be smoothed. Good.

  In addition, the first side 85a and the second side 85b have the same length in the tube insertion direction and are arranged at the same position in the tube insertion direction, so the third side 85c and the fourth side 85d are also The lengths in the direction intersecting the tube insertion direction (tube step direction) are the same, and are arranged at positions in the direction intersecting the same tube insertion direction. For this reason, here, the flat surface 85 has a rectangular shape including two sides 85a and 85b parallel to the tube insertion direction and two sides 85c and 85d parallel to the tube step direction. For this reason, not only the fin strength in the direction intersecting the tube insertion direction by the first side 85a and the second side 85b but also the fin strength in the tube insertion direction can be improved by the third side 85c and the fourth side 85d. .

<Fin tab>
Next, the heat transfer fins 66 are formed by cutting up the heat transfer fins 66 with first fin tabs 90 for maintaining the distance between the heat transfer fins 66 adjacent in the longitudinal direction of the heat transfer tubes 63. The first fin tab 90 is disposed across the boundary between the fin intermediate portion 81 and the fin front portion 82. Here, the first fin tab 90 is a substantially square-shaped piece that protrudes from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). is there. The first fin tab 90 is in contact with the base surface 66a of the heat transfer fin 66 adjacent in the longitudinal direction of the heat transfer tube 63, so that the interval between the heat transfer fins 66 is maintained. In addition, here, the first fin tab 90 is disposed in the vicinity of the center of the heat transfer fin 66 in the tube step direction and on the front side of the pedestal portion 84 in the tube insertion direction.

  As described above, since the first fin tab 90 is disposed so as to straddle the boundary between the fin intermediate portion 81 and the fin front portion 82, the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66. In the state, it is possible to suppress a decrease in fin strength in a direction (tube step direction) intersecting the tube insertion direction of the heat transfer fin 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82. For this reason, in the state where the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66, the occurrence of buckling of the heat transfer fins 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82 can be suppressed. . In this regard, when the fin tab is formed on the fin front portion 82 and is not disposed at the boundary between the fin intermediate portion 81 and the fin tab, the heat transfer fin 66 of the heat transfer fin 66 at the boundary between the fin intermediate portion 81 and the fin front portion 82 is provided. Since the decrease in fin strength in the direction intersecting the tube insertion direction cannot be suppressed, the boundary between the fin intermediate portion 81 and the fin front portion 82 in the state where the heat transfer tube 63 is inserted and joined to the heat transfer fin 66. It is difficult to suppress the occurrence of buckling of the heat transfer fins 66 in the section. This also applies to the case where the fin tab is formed in the fin intermediate portion 81 and is not disposed at the boundary portion with the fin front portion 82.

  Moreover, the 1st fin tab 90 is arrange | positioned so that the wall part along a pipe | tube insertion direction may be made. For this reason, here, since the first fin tab 90 is arranged in a direction intersecting with the boundary between the fin intermediate portion 81 and the fin front portion 82, the first fin tab 90 intersects the tube insertion direction of the heat transfer fin 66. The effect which suppresses the fall of the fin strength of a direction can be heightened. And since the 1st fin tab 90 is arrange | positioned in parallel with the passage direction of the air along a pipe insertion direction, ventilation resistance can be lowered | hung.

  Further, in the heat transfer fin 66, the fin fin 83 has a second fin tab 91 for keeping the space between the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tube 63. Is formed. Here, the second fin tab 91 is a substantially square-shaped piece projecting from the base surface 66a of the heat transfer fin 66 to the one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). is there. The second fin tab 91 is in contact with the base surface 66a of the heat transfer fin 66 adjacent in the longitudinal direction of the heat transfer tube 63, so that the interval between the heat transfer fins 66 is maintained. Further, here, the second fin tab 91 is disposed in the vicinity of the center of the heat transfer fin 66 in the tube step direction and on the back side of the pedestal portion 84 in the tube insertion direction. Thereby, here, the place where the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tube 66 abut can be increased, and the retention performance of the fin interval can be improved.

  Moreover, the 2nd fin tab 91 is arrange | positioned so that the wall part along a pipe | tube insertion direction may be made. For this reason, since the 2nd fin tab 91 will be arrange | positioned in parallel with the passage direction of the air along a pipe insertion direction here, ventilation resistance can be lowered | hung.

  Further, the first fin tab 90 and the second fin tab 91 are arranged so as not to overlap each other when the heat transfer fin 66 is viewed from the tube insertion direction. Here, the first fin tab 90 is cut and raised so that an opening 90a is formed on one side of the first fin tab 90 in the tube step direction (here, the upper side in FIG. 7 and FIG. 8). Is disposed at a position shifted from the center of the heat transfer fin 66 in the tube step direction to the other side in the tube step direction (here, the lower side of the drawing in FIGS. 7 and 8). On the other hand, the second fin tab 91 is cut and raised so that an opening 91a is formed on the other side of the second fin tab 91 in the tube step direction (here, on the lower side of the paper in FIGS. 7 and 8). The two fin tabs 91 are arranged at positions shifted from the center of the heat transfer fin 66 in the tube step direction to one side in the tube step direction (here, the upper side of the drawing in FIGS. 7 and 8). Thus, when the heat transfer fin 66 is viewed from the tube insertion direction, the first fin tab 90 is disposed at a position shifted to the other side of the second fin tab 91 across the center of the heat transfer fin 66 in the tube step direction. It has been done. For this reason, here, when the heat transfer fins 66 are viewed from the tube insertion direction, the degree of parallelism between the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tubes 63 can be increased, and the fin gap holding performance can be further increased. Can be improved.

<Rib part>
Next, ribs 92 and 96 are formed on the heat transfer fins 66 by causing the heat transfer fins 66 to bulge on the front side and the back side of the base 85 in the tube insertion direction. The near side rib portion 92 disposed on the near side in the tube insertion direction of the pedestal portion 85 intersects with the near side first rib portion 93 and the near side second rib 94 extending along the tube insertion direction in the tube insertion direction. And a near-side third rib 95 extending in the direction (tube step direction). The back side rib part 96 arrange | positioned at the back | inner side of the pipe insertion direction of the base part 85 cross | intersects the pipe | tube insertion direction with the back side 1st rib part 97 and the back side 2nd rib 98 which extend along a pipe insertion direction. And a rear third rib 99 extending along the direction (tube step direction). Here, the rib portions 92 and 96 bulge from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side in FIG. 7 and FIG. 8).

  The near-side first rib portion 93 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 the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The front-side first rib portion 93 is formed in a mountain shape whose ridge line 93 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 93a of the near-side first rib portion 93 is disposed in parallel to the outdoor air passing direction.

  The front-side second rib 94 is along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The front side second rib portion 94 is formed in a mountain shape whose ridgeline 94 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 94a of the front-side second rib portion 94 is disposed in parallel to the outdoor air passing direction.

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

  The near-side third rib 95 is disposed so as to connect ends of the near-side first rib portion 93 and the near-side second rib portion 94 on the base portion 85 side in the tube insertion direction. The front side third rib 95 is formed in a mountain shape parallel to the direction in which the ridge line 95 a intersects the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 95a of the front-side third rib 95 is disposed so as to intersect the outdoor air passage direction. And here, the ridgeline 93a of the near side first rib part 93, the ridgeline 95a of the near side third rib 95, and the ridgeline 94a of the near side second rib part 94 are connected in a U-shape. The front side first rib portion 93, the front side third rib 95 and the front side second rib portion 94 as a whole (that is, the front side rib portion 92) are formed in a U-shaped mountain shape. Further, the edge 95 b on the pedestal portion 84 side of the front side third rib 95 coincides with the third side 85 c of the flat surface 85 of the pedestal portion 84. That is, the edge 95b on the pedestal portion 84 side of the front side third rib 95 is not located on the base surface 66a of the heat transfer fin 66 but is located on the flat surface 85 protruding from the base surface 66a. Thereby, the front side third rib 95 (that is, the front side rib portion 92 including the front side first rib portion 93 and the front side second rib portion 94) is connected to the third side 85c of the flat surface 85 of the pedestal portion 84. They are arranged continuously. Further, the front rib portion 92 is disposed so as to surround the first fin tab 90. Here, the three sides excluding the front side of the first fin tab 90 in the tube insertion direction are surrounded. The front side rib portion 92 is disposed at a position where the ridgelines 93 a, 94 a, and 95 a protrude from the flat surface 85 of the pedestal portion 84 than the base surface 66 a of the heat transfer fin 66.

  Further, the back side first rib portion 97 and the back side second rib 98 are formed on one side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the paper surface of each fin intermediate portion 81 in FIGS. 7 and 8). It is arranged along the upper tube insertion part 60). The back side first rib portion 97 is formed in a mountain shape whose ridgeline 97 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 97a of the back side first rib portion 97 is arranged in parallel to the outdoor air passing direction.

  The back side second rib 98 is along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged. The back side second rib portion 98 is formed in a mountain shape whose ridgeline 98 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 98a of the back side second rib portion 98 is arranged in parallel to the outdoor air passage direction.

  Further, the back side first rib portion 97 and the back side second rib portion 98 extend not only to the fin intermediate portion 81 but also to the fin back portion 83. That is, the back side first rib portion 97 and the back side second rib portion 98 are disposed across the boundary portion between the fin intermediate portion 81 and the fin back portion 83.

  The back side third rib 99 is arranged so as to connect ends of the back side first rib part 97 and the back side second rib part 98 on the base part 85 side in the tube insertion direction. The back side third rib 99 is formed in a mountain shape parallel to the direction in which the ridge line 99 a intersects the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 99a of the back side third rib 99 is disposed so as to intersect the outdoor air passing direction. Here, the ridgeline 97a of the back side first rib portion 97, the ridgeline 99a of the backside third rib 99, and the ridgeline 98a of the backside second rib portion 98 are connected in a U-shape, thereby The back side first rib part 97, the back side third rib 99, and the back side second rib part 98 as a whole (that is, the back side rib part 96) are formed in a U-shaped mountain shape. Further, the edge 99 b on the pedestal portion 84 side of the back side third rib 99 coincides with the fourth side 85 d of the flat surface 85 of the pedestal portion 84. That is, the edge 99b of the back side third rib 99 on the pedestal portion 84 side is not positioned on the base surface 66a of the heat transfer fin 66 but is positioned on the flat surface 85 protruding from the base surface 66a. Thereby, the back side third rib 99 (that is, the back side rib part 96 including the back side first rib part 97 and the back side second rib part 98) is connected to the fourth side 85d of the flat surface 85 of the pedestal part 84. They are arranged continuously. Further, the back rib portion 96 is disposed so as to surround the second fin tab 91. Here, the three sides excluding the near side of the second fin tab 91 in the tube insertion direction are surrounded. In addition, the back side rib part 96 is arrange | positioned in the position where the ridgeline 97a, 98a, 99a protruded rather than the base surface 66a of the heat-transfer fin 66 rather than the flat surface 85 of the base part 84. FIG.

  Here, as described above, the rib portions 92 and 96 (specifically, the first and second rib portions 93 and 94) extending along the tube insertion direction toward the front side and the back side of the base portion 84 in the tube insertion direction. , 97, 98) are arranged continuously with the third side 85c and the fourth side 85d of the flat surface 85. For this reason, the rib portions 92 and 96 can be integrated with the pedestal portion 84 so that the third side 85c and the fourth side 85d of the pedestal portion 84 do not fold. Thereby, the fin intensity | strength of the direction which cross | intersects the pipe insertion direction in the near part and the back | inner side of the pipe insertion direction of the base part 84 and the base part 84 can be improved.

  Here, as described above, the rib portions 93 and 96 (specifically, the first and second rib portions 93, 94, 97, and 98) are connected to the boundary portion between the fin intermediate portion 81 and the fin front portion 82. And it arrange | positions so that the boundary part of the fin intermediate part 81 and the fin back part 83 may be straddled. For this reason, the fin strength in the direction intersecting the tube insertion direction at the boundary between the fin intermediate portion 81 and the fin front portion 82 and at the boundary between the fin intermediate portion 81 and the fin back portion 82 can be improved. For this reason, when the heat transfer tube 63 is inserted into the notch 67 of the heat transfer fin 66, buckling of the insertion fin starting from the boundary between the fin intermediate portion 81 and the fin back portion 83 can be suppressed. Further, in the state where the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66, it is possible to suppress buckling of the heat transfer fins 66 starting from the boundary between the fin intermediate portion 81 and the fin front portion 82. it can.

  Here, as described above, since the near-side rib portion 93 surrounding the first fin tab 90 is formed in the heat transfer fin 66, the heat transfer fin 66 at both ends where the first fin tab 90 is cut and raised is formed. A decrease in fin strength can be suppressed.

(6) Modification <A>
In the outdoor heat exchanger 23 as a heat exchanger according to the above embodiment, the pedestal portion 84 is formed on the heat transfer fin 66, but nothing is formed on the flat surface 85. However, the present invention is not limited to this. For example, as shown in FIG. 13, a louver is formed by cutting up the heat transfer fins 66 on the flat surface 85 of the pedestal portion 84 for the purpose of improving the heat transfer performance. 86 may be formed.

  Here, since the louver 86 is formed on the pedestal portion 84, for example, a portion forming the louver of the fin intermediate portion 81 compared to a case where the louver is formed in a portion where the waffle of the fin intermediate portion 81 is not formed. The fin strength in the direction intersecting the tube insertion direction can be improved. In addition, the louver 86 having a large size (particularly, a large size in the tube step direction) can be provided as compared with the case where the louver is formed in the waffle. For this reason, the heat transfer performance can be improved while suppressing buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67 of the heat transfer fins 66.

<B>
In the outdoor heat exchanger 23 as the heat exchanger according to the above-described embodiment, the first fin tabs 90 are formed of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81 arranged along the tube step direction. I try to place them all. However, the present invention is not limited to this. For example, as shown in FIG. 14, the first fin tabs 90 are arranged in a plurality of stages of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81. Also good.

  Here, since the 1st fin tab 90 is arrange | positioned for every several step of the several fin front part 82 and the corresponding several fin intermediate part 81, when dew condensation water generate | occur | produces in the outdoor heat exchanger 23, it is 1st. The amount of condensed water retained by the fin tab 90 can be reduced, and the drainage performance of the heat transfer fin 66 can be ensured. Although not shown here, the second fin tabs 91 may be arranged in a plurality of stages as in the first fin tab 90.

<C>
In the outdoor heat exchanger 23 as the heat exchanger according to the above-described embodiment, the first fin tab 90 is disposed along the tube insertion direction, but is not limited thereto, and the fin intermediate portion 81 is not limited thereto. The first fin tab 90 may not be along the tube insertion direction as long as the first fin tab 90 is disposed across the boundary between the first fin portion 82 and the front fin portion 82.

<D>
In the outdoor heat exchanger 23 as a heat exchanger according to the above-described embodiment, the front side rib portion 92 surrounds the three sides except the front side in the tube insertion direction of the first fin tab 90, but is not limited thereto. It is not something. For example, although not shown here, the front rib portion 92 may surround four sides including the front side of the first fin tab 90 in the tube insertion direction.

<E>
In the outdoor heat exchanger 23 as the heat exchanger according to the above embodiment, a heat exchanger in which the heat transfer tubes 63 are arranged in two rows in the outdoor air passage direction is taken as an example, but the present invention is not limited thereto. It may be one row, or three or more rows.

  The present invention is widely applicable to a heat exchanger provided with a plurality of flat tubes and a plurality of insertion fins.

23 Outdoor heat exchanger (heat exchanger)
63 Heat transfer tube (flat tube)
64 Flat surface 66 Heat transfer fin (insertion fin)
67 Notch portion 80 Pipe insertion portion 81 Fin intermediate portion 82 Fin front portion 83 Fin back portion 90 First fin tab 91 Second fin tab 92 Front side rib portion (rib portion)

JP 2012-163323 A

Claims (7)

A plurality of flat tubes (63) arranged along a predetermined tube step direction with the flat surfaces (64) facing each other, and the tube extending in the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube In a heat exchanger comprising a plurality of insertion fins (66) formed with a plurality of notches (67) for inserting a flat tube and arranged along the longitudinal direction of the flat tube,
If the portion of the notch that is in contact with the flat tube in a state in which the flat tube is inserted is a tube insertion portion (80), the insertion fin has a space between the tube insertion portions adjacent to each other in the tube step direction. A plurality of fin intermediate portions (81) sandwiched, and a fin front portion (82) extending from a front end portion of the plurality of fin intermediate portions toward the front side in the tube insertion direction, respectively. The plurality of fin intermediate portions extend continuously from the end on the back side in the tube insertion direction toward the back side in the tube insertion direction with the end on the back side in the tube insertion direction of the plurality of fin intermediate portions. The fin back (83) is formed,
In the insertion fin, a first fin tab (90) for maintaining a gap between the insertion fins adjacent in the longitudinal direction of the flat tube is formed by raising the insertion fin,
The first fin tab is disposed across a boundary portion between the fin intermediate portion and the fin front portion,
Heat exchanger (23). The first fin tab (90) is arranged to form a wall portion along the tube insertion direction,
The heat exchanger (23) according to claim 1. In the insertion fin (66), a rib portion (92) surrounding the first fin tab (90) is formed by expanding the insertion fin.
The heat exchanger (23) according to claim 1 or 2. The first fin tab (90) is arranged for each of a plurality of stages of the plurality of fin front parts (82) arranged along the tube stage direction and the corresponding plurality of fin intermediate parts (81).
The heat exchanger (23) according to any one of claims 1 to 3. A second fin tab (91) for holding a gap between the insertion fins (66) adjacent to each other in the longitudinal direction of the flat tube (63) cuts the insertion fins in the fin back part (83). Formed by waking up,
The heat exchanger (23) according to any one of claims 1 to 4. The second fin tab (91) is disposed so as to form a wall portion along the tube insertion direction,
The heat exchanger (23) according to claim 5. The first fin tab (90) and the second fin tab (91) are arranged so as not to overlap each other when the insertion fin (66) is viewed from the tube insertion direction.
The heat exchanger (23) according to claim 5 or 6.

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