JPWO2019008697A1 - Heat exchanger, refrigeration cycle device, and method for manufacturing heat exchanger - Google Patents

Abstract

The heat exchanger includes a first flat tube (10) having a flow path through which a refrigerant flows, a fin (11) provided in parallel with the first flat tube (10), and a first flat tube. A heat transfer portion (12), which is a long member, for transferring the heat of the pipe (10) to the fins (11); An inclined surface that is inclined with respect to the surface is formed, and the heat transfer section (12) is provided on the first flat tube (10) and the fin (11).

Description

  The present invention relates to a heat exchanger including a flat tube having a flow path through which a refrigerant flows, a refrigeration cycle device including the heat exchanger, and a method of manufacturing the heat exchanger.

  As a conventional heat exchanger, a corrugated heat exchanger including a plurality of flat tubes and corrugated fins disposed between adjacent flat tubes has been proposed (for example, see Patent Document 1). . In the corrugated fin heat exchanger, the heat of the refrigerant is also transmitted to the corrugated fins via the flat tubes. Since the corrugated fin heat exchanger includes the corrugated fins, the heat transfer area with the air is increased accordingly. As a result, the corrugated fin heat exchanger has improved heat exchange efficiency between refrigerant and air.

  Here, when the corrugated fin heat exchanger functions as an evaporator, the corrugated fins may condense. A drainage groove is formed in the flat tube of the corrugated fin heat exchanger of Patent Document 1. In other words, when the corrugated fins of the corrugated fin heat exchanger disclosed in Patent Document 1 are condensed, the condensed water on the fins is discharged from the drain groove. However, the dew water adheres to the surface of the fin. In addition, a horizontal surface is formed on the fin of the corrugated fin heat exchanger of Patent Document 1. For this reason, the dew water on the fins is not easily discharged to the drain groove. As described above, in the corrugated fin heat exchanger, since the shape of the fin is corrugated, dew condensation water tends to stay on the fin.

  If the corrugated fin heat exchanger functions as an evaporator, and if low-temperature air is supplied to the corrugated fin heat exchanger, for example, in winter, the dew condensation water remaining on the fins may freeze. is there. If the dew water remaining on the fin freezes, the gap between the fin and the flat tube is filled with the frozen dew water, and it becomes difficult for air to pass through the fin and the flat tube. As a result, the heat exchange performance of the corrugated fin heat exchanger is reduced.

  Therefore, as a conventional heat exchanger, a heat exchanger having a configuration in which corrugated fins are removed from a corrugated fin heat exchanger has been proposed (for example, see Patent Document 2). The heat exchanger described in Patent Literature 2 includes a plurality of flat tubes, but does not include fins. That is, the heat exchanger described in Patent Literature 2 is a finless heat exchanger. Since the heat exchanger described in Patent Document 2 has no fins, the drainage of dew condensation water is improved.

JP-A-9-280754 JP-T-2008-528943

  Since the heat exchanger described in Patent Document 2 has no fins, there is a problem that it is difficult to improve the heat exchange performance as compared with the corrugated fin heat exchanger.

  The present invention has been made in order to solve the above problems, and has an object to provide a heat exchanger, a refrigeration cycle device, and a method of manufacturing a heat exchanger that can improve heat exchange performance. I have.

  The heat exchanger according to the present invention includes a first flat tube having a flow path through which a refrigerant flows, a fin provided in parallel with the first flat tube, and a fin that transfers heat of the first flat tube. To the heat transfer portion, which is a long member, the outer peripheral surface of the heat transfer portion is formed with a slope inclined with respect to a surface orthogonal to the fin, the heat transfer portion, It is provided on one flat tube and fin.

  According to the present invention, since the above configuration is provided, the heat exchange performance of the heat exchanger can be improved.

FIG. 2 is an explanatory diagram illustrating a refrigerant circuit configuration of a refrigeration cycle device 100 including the heat exchanger 300 according to Embodiment 1. FIG. 3 is a front view of the heat exchanger 300 according to Embodiment 1. FIG. 3 is an explanatory diagram of the flat tube 10 and the heat transfer unit 12 when the heat exchanger 300 according to Embodiment 1 is viewed from the side. FIG. 3 is an enlarged view of a region R shown in FIG. 2. FIG. 3 is a cross-sectional view of the heat transfer section 12 parallel to the YZ plane. It is AA sectional drawing of the flat tube 10 shown in FIG. FIG. 3 is a cross-sectional view of the fin 11 parallel to the XY plane. 3 shows a state after the insertion step of the method for manufacturing the heat exchanger 300 according to Embodiment 1 has been completed. 3 shows a state after a pipe expanding step of the method for manufacturing the heat exchanger 300 according to Embodiment 1 is completed. It is sectional drawing of 23 A of 1st fixing members, 2nd fixing member 23B of the heat exchanger which concerns on Embodiment 2. FIG. It is a perspective view of 23 A of 1st fixing members. It is a perspective view of the 2nd fixing member 23B. FIG. 10 is an explanatory diagram of a first insertion step of the method for manufacturing a heat exchanger according to Embodiment 2. FIG. 11 is an explanatory diagram of a first press-fitting step of the method for manufacturing a heat exchanger according to Embodiment 2. FIG. 14 is an explanatory diagram of a second insertion step of the method for manufacturing a heat exchanger according to Embodiment 2. FIG. 13 is an explanatory diagram of a second press-fitting step of the method for manufacturing a heat exchanger according to Embodiment 2. FIG. 11 is an explanatory diagram of a state after the second insertion step and the second press-fitting step of the method for manufacturing a heat exchanger according to Embodiment 2 are repeated. FIG. 13 is an explanatory diagram of a state after the first insertion step and the first press-fitting step of the method for manufacturing a heat exchanger according to Embodiment 2 are performed again. FIG. 14 is a front view of a heat exchanger 300C according to Embodiment 3. FIG. 14 is a side view of a heat exchanger 300C according to Embodiment 3. FIG. 13 is a cross-sectional view of a heat exchanger 300C according to Embodiment 3. FIG. 14 is a perspective view of a heat transfer unit 34A, a heat transfer unit 34B, and a heat transfer unit 34C included in a heat exchanger 300C according to Embodiment 3. FIG. 21 is an explanatory diagram of an insertion step of the method for manufacturing the heat exchanger 300C according to Embodiment 3, and shows a state before the flat tube 30 and the like are inserted into the heat transfer unit 34A. FIG. 21 is an explanatory diagram of an insertion step of the method for manufacturing the heat exchanger 300C according to Embodiment 3, and shows a state after the flat tube 30 and the like have been inserted into the heat transfer unit 34A. FIG. 14 is an explanatory diagram of a pressurizing step in a method for manufacturing a heat exchanger 300C according to Embodiment 3, and shows a pressing force F of a heat transfer unit 34A. FIG. 14 is an explanatory diagram of a pressurizing step of the method for manufacturing the heat exchanger 300C according to Embodiment 3, and shows a deformed portion T. FIG. 14 is a front view of a heat exchanger 300D according to Embodiment 4. It is an explanatory view of a part of heat exchanger 300D. The front view of the heat transfer part 44 is shown. FIG. 4 shows a cross-sectional view of the heat transfer section 44. FIG. 19 is an explanatory diagram of an insertion step of the fourth embodiment, and shows a state before the heat transfer unit 44 is inserted into the fin 41. FIG. 19 is an explanatory diagram of an insertion step of the fourth embodiment, and shows a state after the heat transfer unit 44 is inserted into the fin 41. FIG. 15 is an explanatory diagram of a pressing step according to the fourth embodiment. FIG. 15 is an explanatory diagram of an arrangement step according to the fourth embodiment. FIG. 19 is an explanatory diagram of a deformation process according to the fourth embodiment. This shows a state before the flare portion 44A is deformed. This shows a state after the flare portion 44A is deformed. 14 is a modification of the heat transfer section 44 of the heat exchanger according to Embodiment 4. It is explanatory drawing of the manufacturing method of the module U provided with the heat transfer part 440 concerning a modification.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. In addition, in the drawings including FIG. 1, the same reference numerals denote the same or corresponding components, and this is common throughout the entire specification. Furthermore, the forms of the components shown in the entire text of the specification are merely examples, and the present invention is not limited to these descriptions.

Embodiment 1 FIG.
FIG. 1 is an explanatory diagram illustrating a refrigerant circuit configuration of a refrigeration cycle apparatus 100 including the heat exchanger 300 according to Embodiment 1. In FIG. 1, the direction of the flow of the refrigerant during the heating operation is indicated by a solid-line arrow AR1. In FIG. 1, the direction of the flow of the refrigerant during the cooling operation and the defrosting operation is indicated by a broken-line arrow AR2. In the first embodiment, description will be given assuming that refrigeration cycle apparatus 100 is an air conditioner.

  The refrigeration cycle apparatus 100 includes an outdoor unit 101 and an indoor unit 102. The refrigeration cycle apparatus 100 includes a compressor 1, a four-way valve 2, a heat exchanger 300, a throttle device 4, and a heat exchanger 5. The refrigeration cycle apparatus 100 includes a control device Cnt that controls the compressor 1 and the like. Further, the refrigeration cycle apparatus 100 includes a blower 7 for supplying air to the heat exchanger 300 and a blower 8 for supplying air to the heat exchanger 5. The outdoor unit 101 is provided with a compressor 1, a heat exchanger 300, a throttle device 4, a four-way valve 2, and a blower 7. The indoor unit 102 is provided with a heat exchanger 5 and a blower 8. The outdoor unit 101 and the indoor unit 102 are connected to a refrigerant pipe Rp1. The outdoor unit 101 and the indoor unit 102 are connected to a refrigerant pipe Rp2. In the refrigeration cycle apparatus 100, the refrigerant flows through the compressor 1, the heat exchanger 300, the expansion device 4, and the heat exchanger 5 when the compressor 1 is driven. The heat exchanger 300 exchanges heat between the refrigerant and the air supplied by the blower 7. The heat exchanger 5 exchanges heat between the refrigerant and the air supplied by the blower 8.

  The refrigeration cycle apparatus 100 can execute a cooling operation for cooling indoor air, a heating operation for warming indoor air, and a defrosting operation for melting frost attached to the heat exchanger 300. The four-way valve 2 can be constituted by an electromagnetic valve that switches the flow path of the refrigerant. The four-way valve 2 supplies the refrigerant from the compressor 1 to the heat exchanger 300 and supplies the refrigerant from the heat exchanger 5 to the compressor 1 during the cooling operation and the defrosting operation. Further, the four-way valve 2 supplies the refrigerant from the compressor 1 to the heat exchanger 5 during the heating operation, and supplies the refrigerant from the heat exchanger 300 to the compressor 1.

  During the cooling operation of the refrigeration cycle device 100, the refrigerant compressed by the compressor 1 is supplied to the heat exchanger 300. In the heat exchanger 300, heat exchange is performed between the air and the refrigerant. Thereby, the refrigerant is condensed in the heat exchanger 300. The refrigerant flowing out of the heat exchanger 300 is supplied to the expansion device 4. In the expansion device 4, the pressure of the refrigerant is reduced. The refrigerant flowing out of the expansion device 4 is supplied to the heat exchanger 5. In the heat exchanger 5, heat exchange is performed between the air and the refrigerant. Thereby, the refrigerant evaporates in the heat exchanger 5. Thereafter, the refrigerant returns from the heat exchanger 5 to the compressor 1. Thus, during the cooling operation of the refrigeration cycle apparatus 100, the heat exchanger 300 functions as a condenser, and the heat exchanger 5 functions as an evaporator.

  During the heating operation of the refrigeration cycle device 100, the refrigerant compressed by the compressor 1 is supplied to the heat exchanger 5. In the heat exchanger 5, heat exchange is performed between the air and the refrigerant. Thereby, the refrigerant is condensed in the heat exchanger 5. The refrigerant flowing out of the heat exchanger 5 is supplied to the expansion device 4. In the expansion device 4, the pressure of the refrigerant is reduced. The refrigerant flowing out of the expansion device 4 is supplied to the heat exchanger 300. In the heat exchanger 300, heat is exchanged between the air and the refrigerant. Thereby, the refrigerant evaporates in the heat exchanger 300. Thereafter, the refrigerant returns from the heat exchanger 300 to the compressor 1. Thus, during the heating operation of the refrigeration cycle apparatus 100, the heat exchanger 300 functions as an evaporator, and the heat exchanger 5 functions as a condenser. During the heating operation, moisture contained in the air may be generated in the heat exchanger 300 as dew water. This dew water is cooled by air and a refrigerant and frozen. That is, the dew water of the heat exchanger 300 may form frost on the heat exchanger 300. When frost is formed on the heat exchanger 300, it becomes difficult for air to pass through the heat exchanger 300. As a result, heat exchange between the air and the refrigerant is hindered, and the heat exchange performance of the heat exchanger 300 is reduced. That is, when frost is formed on the heat exchanger 300, the heat exchange performance of the heat exchanger 300 is reduced. Therefore, when frost is formed on the heat exchanger 300, the refrigeration cycle apparatus 100 temporarily stops the heating operation and performs the defrosting operation.

  During the defrosting operation of the refrigeration cycle device 100, the blowers 7 and 8 are stopped. During the defrosting operation, the four-way valve 2 is switched to the same state as during the cooling operation. Thus, when the compressor 1 is driven during the defrosting operation, the flow of the refrigerant becomes the same as that during the cooling operation. That is, during the defrosting operation, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is supplied to the heat exchanger 300. Thereby, the frost formed in the heat exchanger 300 is melted by the heat of the high-temperature and high-pressure gas refrigerant. The refrigerant radiated by the heat exchanger 300 returns to the compressor 1 via the expansion device 4 and the heat exchanger 5.

FIG. 2 is a front view of the heat exchanger 300 according to the first embodiment.
FIG. 3 is an explanatory diagram of the flat tube 10 and the heat transfer unit 12 when the heat exchanger 300 according to Embodiment 1 is viewed from the side.
FIG. 4 is an enlarged view of a region R shown in FIG.
FIG. 5 is a cross-sectional view of the heat transfer unit 12 parallel to the YZ plane.
FIG. 6 is an AA cross-sectional view of the flat tube 10 shown in FIG.
FIG. 7 is a cross-sectional view of the fin 11 parallel to the XY plane. Note that the cross section of FIG. 7 is the same plane as the AA cross section of FIG.

  The X direction is a direction parallel to the direction in which the plurality of flat tubes 10 are arranged. The Y direction is parallel to the direction in which air passes. The Z direction is a direction parallel to the vertical direction. In the first embodiment, a description will be given assuming that the X direction is orthogonal to the Y direction, the X direction is orthogonal to the Z direction, and the Y direction is orthogonal to the Z direction.

  One of the plurality of flat tubes 10 included in the heat exchanger 300 corresponds to the first flat tube of the present invention. Further, one of the plurality of fins 11 included in the heat exchanger 300 corresponds to the fin of the present invention.

  As shown in FIG. 2, the heat exchanger 300 includes a plurality of flat tubes 10 and a plurality of fins 11. Fins 11 are arranged between adjacent flat tubes 10. The fins 11 are provided in parallel with the flat tube 10. In the flat tube 10, a flow path 10r through which the refrigerant flows is formed. The fin 11 is flat. The fin 11 has a rectangular shape. Further, the heat exchanger 300 includes a first header Hd1 provided with one end of the plurality of flat tubes 10 and a second header Hd2 provided with the other ends of the plurality of flat tubes 10. ing. Further, the heat exchanger 300 includes a plurality of heat transfer units 12 provided on the plurality of fins 11. The heat transfer section 12 transfers the heat of the flat tube 10 to the fin 11. The heat transfer section 12 is a long member.

  As shown in FIG. 5, an inclined surface 12 </ b> Lp that is inclined with respect to a horizontal plane is formed on an outer peripheral surface 12 p of the heat transfer unit 12. In the first embodiment, the horizontal plane is parallel to the XY plane. In the first embodiment, the horizontal plane is orthogonal to the fins 11. In the first embodiment, the cross section of heat transfer section 12 parallel to the YZ plane is circular. For this reason, even if the dew water adhering to the surface of the fins 11 and the surface of the flat tube 10 flows to the heat transfer part 12, the dew water flowing to the heat transfer part 12 is quickly formed along the inclined surface 12Lp. Flows to As described above, since the inclined surface 12Lp is formed on the outer peripheral surface 12p of the heat transfer section 12 of the heat exchanger 300, the heat exchanger 300 has improved drainage.

  As shown in FIG. 4, the heat transfer section 12 is provided on the flat tube 10 and the fin 11. Specifically, the heat transfer section 12 and the flat tube 10 are joined by brazing. The heat transfer section 12 and the fins 11 are joined by brazing. Thereby, the strength of the heat exchanger 300 is improved. In addition, heat is easily transmitted from the flat tube 10 to the heat transfer unit 12, and heat is easily transmitted between the heat transfer unit 12 and the fins 11.

  As shown in FIG. 6, the flat tube 10 has a through hole 10a. In the first embodiment, three rows of the through holes 10a of the flat tube 10 are formed in the Y direction. Further, the through-holes 10a of the flat tube 10 are formed in 16 rows in the Z direction. That is, the flat tube 10 is formed with 48 through holes 10a. As shown in FIG. 7, the fin 11 has a through hole 11a. The arrangement of the through holes 11a of the fins 11 is the same as the arrangement of the through holes 10a of the flat tube 10. That is, in the first embodiment, three rows of the through holes 11a of the fin 11 are formed in the Y direction. Also, the through holes 11a of the fins 11 are formed in 16 rows in the Z direction. That is, the fin 11 has 48 through holes 10a.

  The heat transfer section 12 is inserted into the through hole 10a and the through hole 11a. In the first embodiment, the flat tube 10 has 48 through holes 10a, and the fin 11 has 48 through holes 11a. Therefore, as shown in FIG. 3, the heat exchanger 300 includes 48 heat transfer units 12. The heat transfer section 12 is a tubular member. That is, the inside of the heat transfer section 12 is hollow.

  As shown in FIG. 7, the fin 11 includes a cylindrical portion 11A provided on a peripheral portion of the through hole 11a. The through hole 11a of the fin 11 is formed by burring. The cylindrical portion 11A is a portion that is raised when the through-hole 11a is formed in the fin 11 by burring. The outer peripheral surface 12p of the heat transfer portion 12 is in contact with the flat tube 10 and the cylindrical portion 11A of the fin 11. Specifically, the outer peripheral surface 12p of the heat transfer section 12 is in contact with a portion of the flat tube 10 where the through hole 10a is formed. Further, the outer peripheral surface 12p of the heat transfer unit 12 is in contact with the inner peripheral surface of the cylindrical portion 11A. Therefore, the heat of the flat tube 10 is transmitted to the heat transfer unit 12. The heat of the heat transfer section 12 is transmitted to the fins 11. That is, not only does the flat tube 10 exchange heat with air, but also the fins 11 exchange heat with air. Thus, the heat exchange area of the heat exchanger 300 is increased by the area of the fins 11. Therefore, the heat exchanger 300 has improved heat exchange performance.

FIG. 8 shows a state after the insertion step of the method of manufacturing heat exchanger 300 according to Embodiment 1.
FIG. 9 shows a state after the pipe expansion step of the method for manufacturing the heat exchanger 300 according to the first embodiment.
With reference to FIG. 8 and FIG. 9, a method of manufacturing the heat exchanger 300 according to the first embodiment will be described.

  The method for manufacturing heat exchanger 300 of the first embodiment includes a first through-hole forming step, a second through-hole forming step, an inserting step, and a pipe expanding step. In the first through hole forming step, a through hole 10a is formed in the flat tube 10. In the second through-hole forming step, the fin 11 is burred to form a through-hole 11a in the fin 11 and to form a cylindrical portion 11A rising from the peripheral edge of the through-hole 11a.

  As shown in FIG. 8, in the insertion step, the heat transfer section 12, which is a long tubular member, is inserted into the through hole 10 a of the flat tube 10 and the through hole 11 a of the fin 11. As shown in FIG. 9, in the pipe expanding step, the heat transfer section 12 is expanded, and the outer peripheral surface 12 p of the heat transfer section 12 is brought into close contact with the inner peripheral surface of the cylindrical portion 11 A of the fin 11. That is, in the pipe expansion step, the outer diameter of the heat transfer section 12 is increased by applying pressure to the inner circumference of the heat transfer section 12, and the outer circumference 12 p of the heat transfer section 12 is The heat transfer section 12 is fixed to the fins 11 by being in close contact with the surface. The heat transfer between the heat transfer unit 12 and the fins 11 is facilitated by bringing the outer circumferential surface 12p of the heat transfer unit 12 into close contact with the inner circumferential surface of the cylindrical portion 11A of the fin 11. After the above steps are completed, the heat exchanger 300 is put into a brazing furnace to perform brazing.

Embodiment 2 FIG.
FIG. 10 is a cross-sectional view of the first fixing member 23A and the second fixing member 23B of the heat exchanger according to Embodiment 2. FIG. 11 is a perspective view of the first fixing member 23A. FIG. 12 is a perspective view of the second fixing member 23B. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the contents different from the first embodiment will be described.

  In the first embodiment, the heat transfer section 12 is expanded, but in the second embodiment, the heat transfer section 12 is not expanded. Instead, the heat exchanger according to Embodiment 2 includes a first fixing member 23A and a second fixing member 23B. Further, the fin 11 of the heat exchanger according to the second embodiment does not include the cylindrical portion 11A of the fin 11 of the heat exchanger 300 according to the first embodiment. The through hole 11a of the fin 11 can be formed by, for example, performing a shearing process.

  The first fixing member 23A is provided in the through hole 10a of the flat tube 10. The first fixing member 23A is interposed between the flat tube 10 and the heat transfer section 12. The first fixing member 23A is a cylindrical member. The heat transfer section 12 is inserted into the first fixing member 23A. That is, the first fixing member 23A includes the first hole 23A1 into which the heat transfer section 12 is inserted. The first fixing member 23A is interposed between the flat tube 10 and the heat transfer section 12. The first fixing member 23A includes a first outer peripheral surface 23A2 that contacts the flat tube 10. The first fixing member 23A is tapered in a direction from the fin 11 toward the flat tube 10. That is, the first fixing member 23A is tapered in a direction opposite to the X direction. Therefore, the first fixing member 23A can be easily attached to the flat tube 10 by inserting the tip of the first fixing member 23A into the through hole 10a.

  The second fixing member 23B is provided in the through hole 11a of the fin 11. The second fixing member 23B is interposed between the fin 11 and the heat transfer section 12. The second fixing member 23B is a cylindrical member. The heat transfer section 12 is inserted into the second fixing member 23B. That is, the second fixing member 23B includes the second hole 23B1 into which the heat transfer section 12 is inserted. The second fixing member 23B is interposed between the fin 11 and the heat transfer section 12. The second fixing member 23B includes a second outer peripheral surface 23B2 that comes into contact with the peripheral edge of the through hole 11a of the fin 11. The second fixing member 23B tapers in a direction from the fin 11 toward the flat tube 10. That is, the second fixing member 23B tapers in a direction opposite to the X direction. Therefore, the first fixing member 23A can be easily attached to the flat tube 10 by inserting the tip of the second fixing member 23B into the through hole 11a.

The heat transfer unit 12 of the heat exchanger according to the second embodiment has the same configuration as the heat transfer unit 12 of the heat exchanger 300 according to the first embodiment. The heat exchanger according to the second embodiment also has improved drainage, similarly to the heat exchanger 300 according to the first embodiment. The first fixing member 23A and the second fixing member 23B are cylindrical members. For this reason, even if the dew water adhering to the surface of the flat tube 10 flows to the first fixing member 23A, the dew water flowing to the first fixing member 23A remains on the surface of the first fixing member 23A. It flows quickly along. Further, even if the dew water adhering to the surface of the fin 11 flows to the second fixing member 23B, the dew water flowing to the second fixing member 23B flows along the surface of the second fixing member 23B. It flows quickly. Thus, even if the heat exchanger according to Embodiment 2 includes the first fixing member 23A and the second fixing member 23B, it is possible to prevent drainage from being impaired.
The heat of the flat tube 10 is transmitted to the heat transfer section 12 via the first fixing member 23A. The heat of the heat transfer section 12 is transmitted to the fin 11 via the second fixing member 23B. That is, not only does the flat tube 10 exchange heat with air, but also the fins 11 exchange heat with air. Thus, the heat exchange area of the heat exchanger according to Embodiment 2 is increased by the area of the fins 11. Therefore, the heat exchanger according to Embodiment 2 has improved heat exchange performance.

FIG. 13 is an explanatory diagram of a first insertion step of the method for manufacturing a heat exchanger according to the second embodiment.
FIG. 14 is an explanatory diagram of a first press-fitting step of the method for manufacturing a heat exchanger according to the second embodiment.
FIG. 15 is an explanatory diagram of a second insertion step of the method for manufacturing a heat exchanger according to the second embodiment.
FIG. 16 is an explanatory diagram of a second press-fitting step of the method for manufacturing a heat exchanger according to the second embodiment.
FIG. 17 is an explanatory diagram of a state after the second insertion step and the second press-fitting step of the method for manufacturing a heat exchanger according to Embodiment 2 are repeated.
FIG. 18 is an explanatory diagram of a state after the first insertion step and the first press-fitting step of the method for manufacturing a heat exchanger according to Embodiment 2 are performed again.
The method for manufacturing a heat exchanger according to the second embodiment includes a first through-hole forming step, a second through-hole forming step, a first inserting step, a first press-fitting step, a first inserting step, and a second Including a press-fitting step.

  In the first through hole forming step, a through hole 10a is formed in the flat tube 10. In the second through hole forming step, a through hole 11 a is formed in the fin 11. In the second through hole forming step, for example, a shearing process is performed.

  As shown in FIG. 13, in the first insertion step, the heat transfer section 12 is inserted into the through hole 10 a of the flat tube 10. As shown in FIG. 14, in the first press-fitting step, the first fixing member 23A is inserted into the heat transfer section 12, and the first fixing member 23A is press-fitted into the through hole 10a of the flat tube 10.

As shown in FIG. 15, in the second insertion step, the heat transfer section 12 is inserted into the through hole 11 a of the fin 11. As shown in FIG. 16, in the second press-fitting step, the second fixing member 23B is inserted into the heat transfer section 12, and the second fixing member 23B is press-fitted into the through hole 11a of the fin 11.
Then, as shown in FIG. 17, the second insertion step and the second press-fitting step are repeated twice more. Further, as shown in FIG. 18, the first insertion step and the first press-fitting step are performed again. After the above steps are completed, the heat exchanger according to Embodiment 2 is put into a brazing furnace to perform brazing. Through the above steps, the heat exchanger according to Embodiment 2 can be manufactured.

Embodiment 3 FIG.
FIG. 19 is a front view of a heat exchanger 300C according to the third embodiment. FIG. 20 is a side view of heat exchanger 300C according to Embodiment 3. FIG. 21 is a cross-sectional view of a heat exchanger 300C according to Embodiment 3. FIG. 22 is a perspective view of a heat transfer unit 34A, a heat transfer unit 34B, and a heat transfer unit 34C included in the heat exchanger 300C according to Embodiment 3. In the third embodiment, the same components as those in the first and second embodiments are denoted by the same reference numerals, and the contents different from the first and second embodiments will be described.

  The heat exchanger 300C according to Embodiment 3 includes a heat transfer unit 34A, a heat transfer unit 34B, and a heat transfer unit 34C. The heat transfer section 34A, the heat transfer section 34B, and the heat transfer section 34C are arranged in order from the upstream side in the air flow direction. The heat transfer section 34A, the heat transfer section 34B, and the heat transfer section 34C are long members parallel to the X direction. The heat transfer section 34A, the heat transfer section 34B, and the heat transfer section 34C have wing-shaped cross sections parallel to the fins 31. Thereby, the pressure loss of the air passing through the heat exchanger 300C can be suppressed.

  The heat transfer section 34A includes a first insertion section 34A1 in which a gap is formed, and a second insertion section 34A2 in which a gap is formed. The width of the gap between the second insertion portions 34A2 is smaller than the width of the gap between the first insertion portions 34A1. The longitudinal end of the flat tube 30 is inserted into the gap of the first insertion portion 34A1. The long axis direction of the flat tube 30 is parallel to the Y direction. The short axis direction of the flat tube 30 is parallel to the X direction. The end of the fin 31 parallel to the longitudinal direction is inserted into the gap of the second insertion portion 34A2. Note that the longitudinal direction of the fins 31 is parallel to the Z direction. The first insertion portion 34A1 and the second insertion portion 34A2 are formed at the downstream end of the heat transfer portion 34A in the air flow direction.

The heat transfer portion 34B includes a first insertion portion 34B1 having a gap formed therein and a first insertion portion 34B2 having a gap formed therein. The first insertion portion 34B1 is formed at the end of the heat transfer portion 34B on the upstream side in the air flow direction. The first insertion portion 34B2 is formed at the end of the heat transfer portion 34B on the downstream side in the air flow direction. The width of the gap between the first insertion portions 34B1 is the same as the width of the gap between the first insertion portions 34B2.
The heat transfer portion 34B has a second insertion portion 34B3 having a gap formed therein and a second insertion portion 34B4 having a gap formed therein. The second insertion portion 34B3 is formed at the end of the heat transfer portion 34B on the upstream side in the air flow direction. The second insertion portion 34B4 is formed at the end of the heat transfer portion 34B on the downstream side in the air flow direction. The width of the gap between the second insertion portions 34B3 is the same as the width of the gap between the second insertion portions 34B4. The width of the gap between the second insertion portions 34B3 is smaller than the width of the gap between the first insertion portions 34B1. The width of the gap between the second insertion portions 34B4 is smaller than the width of the gap between the first insertion portions 34B2.
The longitudinal end of the flat tube 30 is inserted into the gap between the first insertion portions 34B1, and the longitudinal end of the flat tube 30 is inserted into the gap between the first insertion portions 34B2. ing. An end parallel to the longitudinal direction of the fin 31 is inserted into the gap between the second insertion portions 34B3, and an end parallel to the longitudinal direction of the fin 31 is inserted into the gap between the second insertion portions 34B4. ing.

  The heat transfer section 34C includes a first insertion section 34C1 in which a gap is formed, and a second insertion section 34C2 in which a gap is formed. The width of the gap between the second insertion portions 34C2 is smaller than the width of the gap between the first insertion portions 34C1. The longitudinal end of the flat tube 30 is inserted into the gap of the first insertion portion 34C1. The end of the fin 31 parallel to the longitudinal direction is inserted into the gap of the second insertion portion 34C2. The first insertion portion 34C1 and the second insertion portion 34C2 are formed at the upstream end of the heat transfer portion 34C in the air flow direction.

The heat transfer section 34A, the heat transfer section 34B, and the heat transfer section 34C have wing-shaped cross sections parallel to the fins 31. That is, the upper surface of the heat transfer portion 34A, the upper surface of the heat transfer portion 34B, and the upper surface of the heat transfer portion 34C are inclined with respect to a surface orthogonal to the fin 31. For this reason, the dew water on the surface of the heat transfer section 34A immediately flows along the surface of the heat transfer section 34A. In addition, the dew water on the surface of the heat transfer part 34B quickly flows along the surface of the heat transfer part 34B, and the dew water on the surface of the heat transfer part 34C flows quickly along the surface of the heat transfer part 34C.
The heat of the flat tube 30 is transmitted to the heat transfer sections 34A, 34B, and 34C. The heat of the heat transfer section 34A, the heat of the heat transfer section 34B, and the heat of the heat transfer section 34C are transferred to the fins 31. That is, not only does the flat tube 30 exchange heat with air, but also the fins 31 exchange heat with air. Thus, the heat exchange area of the heat exchanger 300 </ b> C is increased by the area of the fins 11. Therefore, the heat exchanger 300C has improved heat exchange performance.

FIG. 23 is an explanatory diagram of an insertion step of the method for manufacturing the heat exchanger 300C according to Embodiment 3, and shows a state before the flat tube 30 and the like are inserted into the heat transfer unit 34A.
FIG. 24 is an explanatory diagram of an insertion step of the method for manufacturing the heat exchanger 300C according to Embodiment 3, and shows a state after the flat tube 30 and the like are inserted into the heat transfer unit 34A.
FIG. 25 is an explanatory diagram of the pressurizing step of the method of manufacturing the heat exchanger 300C according to Embodiment 3, and shows the pressing force F of the heat transfer unit 34A.
FIG. 26 is an explanatory diagram of a pressurizing step of the method for manufacturing the heat exchanger 300C according to Embodiment 3, and shows a deformed portion T.
The method for manufacturing heat exchanger 300C according to Embodiment 3 includes a gap forming step, an inserting step, and a pressurizing step. Here, a process of manufacturing the heat transfer section 34A will be described. In the method of manufacturing heat exchanger 300C according to Embodiment 3, there is no need to form through-holes in flat tubes 30 and fins 31, so that processing costs can be reduced accordingly.

  In the gap forming step, a first insertion section 34A1 including a gap for inserting the flat tube 30 and a second insertion section 34AB including a gap for inserting the fin 11 are formed in the elongated heat transfer section 34A. As shown in FIGS. 23 and 24, in the insertion step, the longitudinal end of the flat tube 30 is inserted into the gap between the first insertion portions 34A1 of the heat transfer portion 34A. In the insertion step, the end of the fin 31 parallel to the longitudinal direction is inserted into the gap between the second insertion portions 34A2 of the heat transfer portion 34A.

  As shown in FIG. 25, in the pressing step, the heat transfer section 34A is pressed, and the flat tubes 30 and the fins 31 are fitted to the heat transfer section 34A. In the pressurizing step, the pressing force F is applied to the end of the heat transfer section 34A on the downstream side in the air flow direction. Thereby, the first insertion portion 34A1 and the second insertion portion 34A2 are deformed, and a deformed portion T is formed in the heat transfer portion 34A as shown in FIG. By forming the deformed portion T, the flat tube 30 and the fin 31 are fitted to the heat transfer portion 34A. Thereby, the strength of the heat exchanger 300C is improved. Further, heat is easily transmitted from the flat tube 30 to the heat transfer unit 34A, and heat is easily transmitted between the heat transfer unit 34A and the fins 31. After the above steps are completed, the heat exchanger 300C is put into a brazing furnace to perform brazing.

Embodiment 4 FIG.
FIG. 27 is a front view of a heat exchanger 300D according to Embodiment 4. FIG. 28 is an explanatory diagram of a part of the heat exchanger 300D. FIG. 28 shows four modules U and five flat tubes 40. FIG. 29 shows a front view of the heat transfer section 44. FIG. 30 shows a cross-sectional view of the heat transfer section 44. In the fourth embodiment, the same components as those in the first to third embodiments are denoted by the same reference numerals, and contents different from the first to third embodiments will be described.

  One end of the heat transfer section 44 in the longitudinal direction is in contact with one flat tube 40, and the other end of the heat transfer section 44 is in contact with the other flat tube 40. The heat transfer section 44 includes a body section 44a that is a columnar member. The trunk portion 44a is inserted into the through hole 41A of the fin 41. The cross section of the body 44a of the heat transfer section 44 parallel to the YZ plane is circular. Further, as shown in FIGS. 29 and 30, the heat transfer section 44 includes a flare section 44A provided at an end of the body section 44a. The flare section 44A is provided at one end or the other end of the heat transfer section 44. The outer diameter of the flare portion 44A is larger than the outer diameter of the body portion 44a. The flare portion 44A is hollow. Thus, when the heat transfer section 44 is pressed in the longitudinal direction of the heat transfer section 44, the flare section 44A is deformed, and the width of the heat transfer section 44 in the longitudinal direction is reduced. That is, since the flare portion 44A is deformed, the pitch of the flat tubes 40 of the heat exchanger 300D can be easily reduced.

The flare portion 44A is hollow, but the body portion 44a is not hollow. If the body portion 44a is hollow, when the heat transfer portion 44 is pressed in the longitudinal direction of the heat transfer portion 44, the body portion 44a expands not only outside but also inside. That is, the outer diameter of the trunk 44a increases, and the inner diameter of the trunk 44a decreases. When the body 44a swells outward, the contact force between the body 44a and the fin 41 increases. As a result, the body 44a is fixed to the fin 41. However, when the trunk portion 44a swells inward, the contact force between the trunk portion 44a and the fin 41 does not increase.
Therefore, if the body portion 44a is hollow, when the heat transfer portion 44 is pressed in the longitudinal direction of the heat transfer portion 44, the body portion 44a swells not only outside but also inside, and the body portion 44a There is a possibility that the contact force between the fins 41 and the fins 41 cannot be secured. For this reason, the trunk 44a is a columnar member, and the trunk 44a is not hollow. Since the body 44a is not hollow, the body 44a expands only outward when the heat transfer section 44 is pressed in the longitudinal direction of the heat transfer section 44. Therefore, the contact force between the body portion 44a and the fin 41 increases. As a result, the body 44a is firmly fixed to the fin 41.

One flat tube 40 corresponds to one of the first flat tube and the second flat tube of the present invention, and the other flat tube 40 corresponds to one of the first flat tube and the second flat tube of the present invention. Corresponding to the other. One end of the heat transfer section 44 corresponds to one of the first end and the second end of the present invention. Further, the other end of the heat transfer section 44 corresponds to the other of the first end and the second end of the present invention.
In the fourth embodiment, the heat transfer sections 44 are arranged in 16 rows in the Z direction. In the fourth embodiment, the heat transfer sections 44 are arranged in three rows in the Y direction. Further, in the fourth embodiment, the heat transfer sections 44 are arranged in 16 rows in the X direction.

Since the cross section of the heat transfer unit 44 parallel to the YZ plane is circular, the dew water on the surface of the heat transfer unit 44 flows quickly along the surface of the heat transfer unit 44. Therefore, the heat exchanger 300D has improved drainage performance.
The heat of the flat tube 40 is transmitted to the heat transfer section 44. Further, the heat of the heat transfer section 44 is transferred to the fin 41. That is, not only does the flat tube 40 exchange heat with air, but also the fin 41 exchanges heat with air. Thus, the heat exchange area of the heat exchanger 300D is increased by the area of the fins 11. Therefore, the heat exchanger 300D has improved heat exchange performance.

Hereinafter, a method of manufacturing heat exchanger 300D according to Embodiment 4 will be described.
The method for manufacturing heat exchanger 300D according to Embodiment 4 includes an insertion step, a diameter expansion step, an arrangement step, and a deformation step.

  FIG. 31 is an explanatory diagram of the insertion step of the fourth embodiment, and shows a state before the heat transfer unit 44 is inserted into the fin 41. FIG. 32 is an explanatory diagram of the insertion step of the fourth embodiment, and shows a state after the heat transfer unit 44 has been inserted into the fin 41. In the insertion step, the heat transfer section 44, which is a long member, is inserted into the through hole 41A of the fin 41.

  FIG. 33 is an explanatory diagram of the diameter expanding step according to the fourth embodiment. In the diameter expanding step, the heat transfer unit 44 is fixed to the fins 41 by performing processing to increase the outer diameter of the heat transfer unit 44. Specifically, one end in the longitudinal direction of the heat transfer section 44 and the other end in the longitudinal direction of the heat transfer section 44 are pressurized, and the body section 44a of the heat transfer section 44 expands outward. Thereby, the outer diameter of the trunk portion 44a increases. As the outer diameter of the trunk 44a increases, the contact force between the trunk 44a and the fin 41 increases. Therefore, the heat transfer section 44 is fixed to the fin 41. When the diameter expanding step is performed, the heat transfer section 44 and the fin 41 are integrated, and the module U can be manufactured. Module U includes a heat transfer section 44 and fins 41.

  FIG. 34 is an explanatory diagram of an arrangement process according to the fourth embodiment. In the arrangement step, the plurality of flat tubes 40 are arranged, and the module U is arranged between the adjacent flat tubes 40.

  FIG. 35 is an explanatory diagram of a deformation process according to the fourth embodiment. FIG. 36 shows a state before the flare portion 44A is deformed. FIG. 37 shows a state after the flare portion 44A is deformed. As shown in FIG. 35, in the deformation step, the heat transfer section 44 is pressurized by applying a pressing force F to the flat tubes 40 at both ends. Thereby, the flare portion 44A is deformed. That is, the flare portion 44A is crushed, and the width of the heat transfer portion 44 in the X direction is reduced. The deformation step is performed when the pitch of the flat tubes 40 is to be reduced. When it is not necessary to reduce the pitch of the flat tubes 40, the deformation step may not be performed. When it is not necessary to adjust the pitch of the flat tubes 40, the flare portion 44A may not be formed in the heat transfer portion 44. After completing the above steps, the heat exchanger 300 is put into a brazing furnace to perform brazing.

  FIG. 38 is a modification of the heat transfer unit 44 of the heat exchanger according to Embodiment 4. FIG. 39 is an explanatory diagram of the method of manufacturing the module U including the heat transfer unit 440 according to the modification. In the fourth embodiment, the body 44a is a columnar member and is not hollow. The heat transfer section 440 according to the modification has a hollow body 440a. The diameter expansion step of the method for manufacturing a heat exchanger including the heat transfer section 440 is different from the diameter expansion step of the fourth embodiment. Specifically, by applying pressure to the inner peripheral surface of the trunk 440a, the trunk 440a is expanded. As a result, the contact force between the body 440a and the fin 41 increases. As a result, the body 440a is fixed to the fin 41.

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 four-way valve, 4 throttling device, 5 heat exchanger, 7 blower, 8 blower, 10 flat tube, 10a through hole, 10r flow path, 11 fin, 11A cylindrical part, 11a through hole, 12 heat transfer Part, 12Lp inclined surface, 12p outer peripheral surface, 23A first fixing member, 23A1 first hole portion, 23A2 first outer peripheral surface, 23B second fixing member, 23B1 second hole portion, 23B2 second outer periphery Surface, 30 flat tubes, 31 fins, 34A heat transfer section, 34A1 first insert section, 34A2 second insert section, 34AB second insert section, 34B heat transfer section, 34B1 first insert section, 34B2 first Insertion section, 34B3 second insertion section, 34B4 second insertion section, 34C heat transfer section, 34C1 first insertion section, 34C2 second insertion section, 40 flat tube, 41 fin, 41A through hole, 4 4 heat transfer part, 44a trunk, 44A flare part, 440 heat transfer part, 440a trunk, 100 refrigeration cycle device, 101 outdoor unit, 102 indoor unit, 300 heat exchanger, 300C heat exchanger, 300D heat exchanger, Cnt controller, Hd1 first header, Hd2 second header, Rp1 refrigerant pipe, Rp2 refrigerant pipe, T deformed part, U module.

The heat exchanger according to the present invention includes a first flat tube having a flow path through which a refrigerant flows, fins provided in parallel with the first flat tube, and heat of the first flat tube. To the fins, a heat transfer portion that is a long member, and a second flat tube provided in parallel with the first flat tube , wherein the fin has a through hole, An inclined surface that is disposed between the first flat tube and the second flat tube and that is inclined with respect to a surface orthogonal to the fins is formed on an outer peripheral surface of the heat transfer unit. The heat transfer portion is provided on the first flat tube and the fin , and is inserted into the through hole, and a first end portion of the heat transfer portion in the longitudinal direction contacts the first flat tube. A second end of the heat transfer section in the longitudinal direction is in contact with the second flat tube .

Claims (18)

A first flat tube in which a flow path through which the refrigerant flows is formed;
A fin provided in parallel with the first flat tube;
A heat transfer portion that is a long member, and transfers heat of the first flat tube to the fin;
With
On the outer peripheral surface of the heat transfer section, a slope inclined with respect to a plane orthogonal to the fins is formed,
The heat exchanger is a heat exchanger provided on the first flat tube and the fin. A second flat tube provided in parallel with the first flat tube,
The fin has a through hole formed therein, and is arranged between the first flat tube and the second flat tube,
In the heat transfer unit, a first end in a longitudinal direction of the heat transfer unit contacts the first flat tube, and a second end in a longitudinal direction of the heat transfer unit contacts the second flat tube. The heat exchanger according to claim 1, wherein the heat exchanger is inserted into the through hole. The heat transfer section,
A flare portion provided at the first end of the heat transfer portion or the second end of the heat transfer portion,
The heat exchanger according to claim 2, wherein an outer diameter of the flare portion is larger than an outer diameter of a portion of the heat transfer portion inserted into the through hole. The first flat tube has a first through hole formed therein, and the fin has a second through hole formed therein,
The heat exchanger according to claim 1, wherein the heat transfer section is inserted into the first through hole and the second through hole. The heat exchanger according to claim 4, wherein the fin includes a tubular portion provided at a peripheral portion of the second through hole. The heat transfer section is a tubular member,
The heat exchanger according to claim 5, wherein the outer peripheral surface of the heat transfer unit is in contact with the first flat tube and the tubular portion of the fin. A first cylindrical fixing member provided in the first through hole and into which the heat transfer section is inserted;
A cylindrical second fixing member provided in the second through hole and into which the heat transfer section is inserted;
The first fixing member includes a first outer peripheral surface that contacts the first flat tube,
The heat exchanger according to any one of claims 4 to 6, wherein the second fixing member includes a second outer peripheral surface that contacts the fin. The first fixing member is tapered in a direction from the fin to the first flat tube,
The heat exchanger according to claim 7, wherein the second fixing member is tapered in a direction from the fin to the first flat tube. The heat transfer section includes a first insertion section in which a first gap is formed, and a second gap in which a longitudinal width of the heat transfer section is smaller than a width of the first gap. A second insertion portion,
The longitudinal end of the first flat tube is inserted into the first gap,
The heat exchanger according to claim 1, wherein an end of the fin parallel to a longitudinal direction is inserted into the second gap. The heat exchanger according to claim 9, wherein the heat transfer unit has a blade-shaped cross section parallel to the fin. The heat transfer unit and the first flat tube are joined,
The heat exchanger according to any one of claims 1 to 10, wherein the heat transfer section and the fin are joined. A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 1 to 11. An insertion step of inserting the heat transfer portion, which is a long member, into the through hole of the fin,
A pipe expansion step of fixing the heat transfer section to the fins by performing processing to increase the outer diameter of the heat transfer section on the heat transfer section, and manufacturing a module including the heat transfer section and the fins,
An arranging step of arranging the module manufactured in the expanding step between a first flat tube and a second flat tube;
A method for manufacturing a heat exchanger, comprising: The said pipe expansion process WHEREIN: The heat transfer part is fixed to the said fin by pressurizing the 1st longitudinal end of the said heat transfer part and the 2nd longitudinal end of the said heat transfer part. Production method of heat exchanger. A deformation step of pressing the heat transfer portion by pressing the first flat tube and the second flat tube to deform a flare portion provided at the first end or the second end. The method for manufacturing a heat exchanger according to claim 14, further comprising: A first through-hole forming step of forming a first through-hole in the flat tube;
A second through-hole forming step of burring the fin, forming a second through-hole in the fin, and forming a cylindrical portion rising from a peripheral edge of the second through-hole;
An insertion step of inserting a heat transfer portion that is a long tubular member into the first through hole of the flat tube and the second through hole of the fin;
A pipe expanding step of expanding the heat transfer section and bringing an outer peripheral surface of the heat transfer section into close contact with an inner peripheral surface of the cylindrical portion of the fin;
A method for manufacturing a heat exchanger, comprising: A first through-hole forming step of forming a first through-hole in the flat tube;
A second through-hole forming step of forming a second through-hole in the fin;
A first insertion step of inserting a heat transfer portion, which is a long tubular member, into the first through hole of the flat tube;
A first press-fitting step of inserting a cylindrical first fixing member into the heat transfer section and press-fitting the first fixing member into the first through hole of the flat tube;
A first insertion step of inserting the heat transfer section into the second through hole of the fin;
A second press-fitting step of inserting a cylindrical second fixing member into the heat transfer section and press-fitting the second fixing member into the second through hole of the fin;
A method for manufacturing a heat exchanger, comprising: A gap forming step of forming the first gap and the second gap in the elongated heat transfer section;
An insertion step of inserting a longitudinal end of the flat tube into the first gap of the heat transfer section, and inserting an end parallel to a longitudinal direction of the fin into the second gap of the heat transfer section; ,
Pressurizing the heat transfer section, a pressurizing step of fitting the fin and the flat tube to the heat transfer section,
A method for manufacturing a heat exchanger, comprising:

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