JP2010025434A - Heat exchanger and method of manufacturing heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger for suppressing accumulation of liquid refrigerant at a lower part of a header. <P>SOLUTION: In the heat exchanger 10, an end section 11c of a flat tube 11 is projected from an inner face 15c of the header 15 while being inclined to a horizontal face. A position of the end section 11c of the flat tube 11 is deflected to one side of a first virtual space and a second virtual space when the inside of the header 15 is divided into the first virtual space and the second virtual space by a virtual plane in parallel with the longitudinal direction of the flat tube 11 including a central shaft X. A refrigerant from the end section of the flat tube 11 is brought into contact with an inner face 15c at one side of the first virtual space and the second virtual space in the header and swirls. The inclined end section 11c of the flat tube 11 allows the refrigerant coming while swirling, to direct to the inclining direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a heat exchanger provided with flat tubes and fins, and a method for manufacturing the heat exchanger.

  Conventionally, a heat exchanger in which a flat portion of a flat tube is horizontal and fins are disposed between the flat portion and the flat portion has been widely used. When such a heat exchanger is used for an air conditioner, a refrigerant in a gas-liquid mixed state flows through the flat tubes and the headers connecting the flat tubes (see Patent Document 1).

However, in a heat exchanger with a specification that the header stands vertically and the refrigerant that has flowed out from the lower flat tube flows through the header to the upper flat tube, the liquid refrigerant is heavier than the gas refrigerant, so it stays below the header. It is easy to make the liquid refrigerant difficult to flow through the upper flat tube, and the performance of the heat exchanger decreases.
JP-A-7-55377

  The subject of this invention is providing the heat exchanger which suppressed that a liquid refrigerant stagnates under the header.

  The heat exchanger according to the first invention includes a plurality of flat tubes, fins, and a cylindrical header. The fin is sandwiched between adjacent flat tubes. In the header, the end of the flat tube penetrates from the outer surface to the inner surface. A swirl flow generation unit and a first direction flow generation unit are formed inside the header. The swirl flow generating unit turns the flow of the refrigerant from the end of the flat tube into a swirl flow along the inner surface of the header. The first direction flow generator changes the direction of the refrigerant that has exited from the end of the flat tube to the first direction in which the ends of the plurality of flat tubes are arranged.

  In this heat exchanger, since the swirling refrigerant is directed in one direction, the refrigerant is given a propulsive force in that direction, so that the refrigerant that has come out of the lower flat tube flows through the header to the upper flat tube. Even at times, the refrigerant can rise in the header against gravity. As a result, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

  The heat exchanger according to the second aspect of the present invention is the heat exchanger according to the first aspect of the present invention, and has a columnar shape in which the internal space of the header has a curved surface. In this heat exchanger, since the inner surface of the header is used as a swirling surface, the swirling flow generating unit can be downsized.

  A heat exchanger according to a third aspect is the heat exchanger according to the second aspect, wherein the end of the flat tube extends perpendicularly or obliquely to the horizontal plane. In this heat exchanger, the end portion of the flat tube can direct the refrigerant that turns while turning along the inner surface of the header in a direction perpendicular to or inclined with respect to the horizontal plane. As a result, if the refrigerant flows in the header from the lower side to the upper side, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

  A heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to the second aspect of the present invention, in which a flat tube is twisted from the center portion to the end portion. In this heat exchanger, the end portion of the flat tube can direct the refrigerant that turns while turning along the inner surface of the header in a direction perpendicular to or inclined with respect to the horizontal plane. As a result, if the refrigerant flows in the header from the lower side to the upper side, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header. Moreover, since the center part of a flat tube is parallel to a horizontal surface, the ventilation resistance with respect to the airflow which passes the center part of a flat tube reduces.

  A heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to the second aspect of the present invention, wherein the swirl flow generating unit includes the inner surface of the header and the end of the flat tube. When the inside of the header is divided into a first virtual space and a second virtual space on a virtual plane including the central axis inside the header and parallel to the longitudinal direction of the flat tube, the position of the end of the flat tube is the first virtual space and It is biased to one of the second virtual spaces. In this heat exchanger, the refrigerant that has exited the end of the flat tube hits the inner surface of either the first virtual space or the second virtual space in the header, so that it can reliably rotate in one direction.

  A heat exchanger according to a sixth aspect is the heat exchanger according to the fifth aspect, wherein the position of the tip of the end portion of the flat tube is biased to one of the first virtual space and the second virtual space. . In this heat exchanger, the refrigerant that has exited the end of the flat tube hits the inner surface of either the first virtual space or the second virtual space in the header, so that it can reliably rotate in one direction.

  A heat exchanger according to a seventh invention is the heat exchanger according to the fifth invention, wherein the base of the end of the flat tube and the position of the tip are both in either the first virtual space or the second virtual space. Is biased. In this heat exchanger, the refrigerant that has exited the end of the flat tube hits the inner surface of either the first virtual space or the second virtual space in the header, so that it can reliably rotate in one direction.

  A heat exchanger according to an eighth aspect of the present invention is the heat exchanger according to the second aspect of the present invention, wherein the swirl flow generating unit causes the direction of the refrigerant coming out from the end of the flat tube to be along the inner surface of the header. Is included. In this heat exchanger, if the refrigerant flows from the bottom to the top in the header, the refrigerant exiting the end of the flat tube can rise while turning along the coiled member, so that the liquid refrigerant is It is suppressed that it stays below.

  A heat exchanger according to a ninth aspect of the present invention is the heat exchanger according to the second aspect of the present invention, wherein the swirl flow generating portion includes a spiral fluid passage formed at least on the inner surface of the header. In this heat exchanger, if the refrigerant flows in the header from below to above, the refrigerant that has exited the end of the flat tube can rise while swirling along the spiral fluid passage. It is suppressed that it stays under the header.

  A heat exchanger according to a tenth aspect of the present invention is the heat exchanger according to the ninth aspect of the present invention, wherein the spiral fluid passage is a spiral groove. In this heat exchanger, if the refrigerant flows in the header from below to above, the refrigerant that has exited the end of the flat tube can rise while swirling along the spiral groove. It is suppressed that it stays in. Further, since the processing is easy, the manufacturing cost can be reduced.

  A heat exchanger according to an eleventh aspect of the present invention is the heat exchanger according to the second aspect of the present invention, wherein the first direction flow generation unit includes an end portion of the flat tube. The end of the flat tube is inclined with respect to the horizontal plane. In this heat exchanger, the end of the flat tube can direct the refrigerant that turns while turning along the inner surface of the header in a direction inclined with respect to the horizontal plane. As a result, if the refrigerant flows in the header from the lower side to the upper side, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

  A heat exchanger according to a twelfth aspect of the present invention is the heat exchanger according to the second aspect of the present invention, wherein the first direction flow generator changes the direction of the refrigerant that has exited the end of the flat tube by a surface that is inclined with respect to the horizontal plane A deflection member is included.

  In this heat exchanger, if the refrigerant flows from the bottom to the top in the header, the direction of the flow of the refrigerant coming out from the end of the flat tube is changed by the deflecting member. It is possible to prevent the liquid refrigerant from staying below the header.

  A heat exchanger according to a thirteenth aspect of the present invention is the heat exchanger according to the second aspect of the present invention, wherein the first direction flow generating part includes a spiral fluid passage formed at least on the inner surface of the header. In this heat exchanger, if the refrigerant flows in the header from below to above, the refrigerant that has exited the end of the flat tube can rise while swirling along the spiral fluid passage. It is suppressed that it stays under the header.

  A heat exchanger according to a fourteenth aspect of the present invention is the heat exchanger according to the thirteenth aspect of the present invention, wherein the spiral fluid passage is a spiral groove. In this heat exchanger, if the refrigerant flows in the header from below to above, the refrigerant that has exited the end of the flat tube can rise while swirling along the spiral groove. It is suppressed that it stays in. Further, since the processing is easy, the manufacturing cost can be reduced.

  A heat exchanger according to a fifteenth aspect of the present invention is the heat exchanger according to any one of the first to fourteenth aspects, wherein the header extends perpendicularly or obliquely to the horizontal plane. In this heat exchanger, even when the header is vertical or inclined with respect to the horizontal plane, the swirl flow generation unit and the first direction flow generation unit give the refrigerant flowing in the header a rising force. Is prevented from accumulating downward.

  A heat exchanger manufacturing method according to a sixteenth aspect of the present invention is the method of manufacturing a heat exchanger according to the ninth or thirteenth aspect of the present invention, wherein the spiral refrigerant passage spirals with the outer surface of the header facing the inner surface. It is formed by being recessed. In this method for manufacturing a heat exchanger, a coolant passage is formed on the inner surface only by applying processing from the outside of the header, so that the manufacturing cost is reduced.

  In the heat exchanger according to the first invention, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

  In the heat exchanger according to the second aspect of the invention, the inner surface of the header is used as a swirling surface, so that the swirling flow generator can be downsized.

  In the heat exchanger according to the third aspect of the invention, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

  In the heat exchanger according to the fourth aspect of the invention, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header. Moreover, since the center part of a flat tube is parallel to a horizontal surface, the ventilation resistance with respect to the airflow which passes the center part of a flat tube reduces.

  In the heat exchanger according to any one of the fifth to seventh inventions, the refrigerant that has exited the end of the flat tube hits the inner surface of either the first virtual space or the second virtual space in the header. Therefore, it can turn reliably in one direction.

  In the heat exchanger according to the eighth or ninth invention, the refrigerant that has exited the end of the flat tube can rise while swirling, so that the liquid refrigerant is prevented from staying below the header.

  In the heat exchanger according to the tenth aspect of the invention, the refrigerant that has exited the end of the flat tube can rise while turning, so that the liquid refrigerant is prevented from staying below the header. Further, since the processing is easy, the manufacturing cost can be reduced.

  In the heat exchanger according to the eleventh or twelfth invention, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

  In the heat exchanger according to the thirteenth aspect of the invention, the refrigerant that has exited the end of the flat tube can be raised while turning, so that the liquid refrigerant is prevented from staying below the header.

  In the heat exchanger according to the fourteenth aspect of the invention, the refrigerant that has exited the end of the flat tube can rise while swirling, so that the liquid refrigerant is prevented from staying below the header. Further, since the processing is easy, the manufacturing cost can be reduced.

  In the heat exchanger according to the fifteenth aspect of the present invention, even when the header is perpendicular to or inclined with respect to the horizontal plane, the swirl flow generation unit and the first direction flow generation unit give a rising force to the refrigerant flowing in the header. Therefore, it is suppressed that a liquid refrigerant accumulates below.

  In the method for manufacturing a heat exchanger according to the sixteenth aspect of the present invention, since the coolant passage is formed on the inner surface only by processing from the outside of the header, the manufacturing cost is reduced.

  Embodiments of the present invention will be described below with reference to the drawings. The following embodiments are specific examples of the present invention and do not limit the technical scope of the present invention.

[First Embodiment]
<Configuration of heat exchanger 10>
FIG. 1 is a perspective view of a heat exchanger according to the first embodiment of the present invention, and FIG. 2 is an enlarged perspective view of a portion A in FIG. 1 and 2, the heat exchanger 10 includes a flat tube 11, a corrugated fin 12, and a header 15.

(Flat tube 11)
The flat tube 11 is formed from aluminum or an aluminum alloy, and includes a flat portion 11a serving as a heat transfer surface and a plurality of refrigerant flow paths 11b through which a refrigerant flows (see FIG. 2). As shown in FIG. 2, the flat tubes 11 are arranged in a plurality of stages with the flat surface portion 11a facing up and down.

(Waveform fin 12)
The corrugated fin 12 is a fin made of aluminum or aluminum alloy bent into a corrugated shape. The corrugated fins 12 are arranged in a ventilation space sandwiched between upper and lower flat tubes 11, and a valley portion and a mountain portion are in contact with a flat portion 11 a of the flat tube 11. In addition, the trough part, the peak part, and the plane part 11a are brazed and welded.

  The heat transfer surface 12a of the corrugated fin 12 is a portion that exchanges heat with the air passing through the ventilation space, and a louver 12c for efficiently exchanging heat is formed. Louver 12c forms an opening penetrating from one surface of heat transfer surface 12a to the other surface. For convenience of explanation, in the front view of FIG. 2, the right surface of the heat transfer surface 12 a is referred to as “first surface”, and the left surface is referred to as “second surface”. The louver 12c group located upstream from the center of the heat transfer surface 12a is inclined so that the air flow flows from the second surface to the first surface, and the louver 12c located downstream from the center of the heat transfer surface 12a. The group is tilted so that the airflow flows from the first surface to the second surface.

(Header 15)
In FIG. 1, the header 15 is connected to both ends of flat tubes 11 arranged in a plurality of stages in the vertical direction. For convenience of explanation, the header on the right side in FIG. 1 is called “first header 151”, and the header on the left side is called “second header 152”. The first header 151 and the second header 152 have a function of supporting the flat tube 11, a function of guiding the refrigerant to the refrigerant flow path 11b of the flat pipe 11, and a function of collecting the refrigerant that has come out of the refrigerant flow path 11b. Have.

(Refrigerant flow)
In FIG. 1, the refrigerant flowing in from the inlet 152 a of the second header 152 is distributed almost evenly to the refrigerant flow paths 11 b of the first and second flat tubes 11 from the bottom and flows toward the first header 151. . The refrigerant reaching the first header 151 is evenly distributed to the respective refrigerant flow paths 11b of the third, fourth, and fifth flat tubes 11 from the bottom and flows toward the second header 152. Then, the refrigerant reaching the second header 152 is evenly distributed to the respective refrigerant flow paths 11b of the sixth, seventh and eighth (uppermost) flat tubes 11 from the bottom to the first header 151. It flows toward you. And the refrigerant | coolant which reached | attained the 1st header 151 gathers, and flows out from the exit 151a. Inside the second header 152, a partition plate 18 is provided between the flat tube 11 at the second level from the bottom and the flat tube 11 at the third level from the bottom, so that the refrigerant does not go back and forth. Further, inside the first header 151, a partition plate 18 is provided between the flat tube 11 at the fifth level from the bottom and the flat tube 11 at the sixth level from the bottom, so that the refrigerant does not come and go. .

  FIG. 3 is a perspective view of the heat exchanger as viewed from the connection portion side between the flat tube and the header. In FIG. 3, the flat tube 11 and the header 15 are connected by the end of the flat tube 11 penetrating into the header 15. The flat tube 11 is twisted from the position away from the header 15 by a predetermined distance to the end.

  FIG. 4 is a perspective view of the heat exchanger as seen from the broken part side, with the upper part of the header partially broken. In FIG. 4, the inside of the header 15 has a cylindrical shape and stands parallel to the vertical direction. The inside of the header 15 is not limited to a cylindrical shape, and may be an elliptical column shape.

  FIG. 5 is a perspective view of the heat exchanger as seen from the broken part side, with the wall surface of the header partially broken so that the end of the flat tube can be seen. In FIG. 5, the flat tube 11 is twisted from the position away from the header 15 by a predetermined distance to the end portion 11 c, so that the end portion 11 c protrudes from the inner surface 15 c of the header 15 while being inclined with respect to the horizontal plane. . The ends 11 c of the flat tubes 11 are arranged in the direction of the central axis X of the header 15.

  FIG. 6 is a perspective view of a heat exchanger in which the wall surface of the header is partially broken so that the refrigerant flow path of the flat tube can be seen, and viewed from the broken portion side, and FIG. 7 is a schematic side view inside the header. is there. 6 and 7, when the inside of the header 15 is divided into two virtual spaces by a virtual plane including the central axis X and parallel to the longitudinal direction of the flat tube 11, the position of the end portion 11c is two virtual spaces. It is biased to either one. Specifically, as shown in FIG. 7, the refrigerant flows out from the end portion 11 c of the flat tube 11 toward the front, and the position of the end portion 11 c of the flat tube 11 faces the outflow direction of the refrigerant. It is biased to the right when viewed.

  As a result, the refrigerant that has passed through the refrigerant flow path 11b of the flat tube 11 flows out from the end portion 11c, then swirls along the nearest inner surface 15c of the header 15, and the inclined end portion 11c of the flat tube 11 It rises by hitting the flat part. The rising refrigerant merges with the refrigerant flowing out of the upper end portion 11c and swirling, and further hits the flat portion of the upper end portion 11c and further rises. That is, the refrigerant rises in the header 15 while turning, so that not only the gas refrigerant but also the liquid refrigerant can rise.

  When the end portion 11c of the flat tube 11 is viewed from the direction opposite to the refrigerant outflow direction, when the end portion 11c of the flat tube 11 is biased to the right side and inclined upward, the end portion 11c is swung while the refrigerant is turning. It hits the flat part of and rises. Similarly, when the end portion 11c of the flat tube 11 is biased to the left side and is inclined upward, the refrigerant hits the flat portion of the end portion 11c while turning. Therefore, the inclination direction and the bias position of the end portion 11c of the flat tube 11 must be determined according to the direction in which the refrigerant is desired to advance. Actually, even if the root of the end portion 11c is not biased as described above, the position of the end surface of the end portion 11c may be finally biased as described above by bending or the like.

  In addition, the arrow in the header 15 of FIG. 6, FIG. 7 has shown the advancing direction of the refrigerant | coolant. Hereinafter, the part that swirls the refrigerant like the inner surface 15c of the header 15 is referred to as a swirl flow generator 16, and the part that raises the refrigerant as the end 11c of the flat tube 11 is referred to as the upflow generator 17.

<Features of First Embodiment>
In this heat exchanger 10, the end 11 c of the flat tube 11 protrudes from the inner surface 15 c of the header 15 in an inclined state with respect to the horizontal plane. The position of the end portion 11c of the flat tube 11 is the first when the inside of the header 15 is divided into a first virtual space and a second virtual space on a virtual plane parallel to the longitudinal direction of the flat tube 11 including the central axis X. It is biased to either the virtual space or the second virtual space. The refrigerant that has exited the end of the flat tube 11 hits the inner surface 15c on either side of the first virtual space or the second virtual space in the header and turns in one direction. The inclined end portion 11c of the flat tube 11 directs the refrigerant that is turned while turning to the inclined direction. As a result, if the refrigerant flows in the header from the lower side to the upper side, not only the gas refrigerant but also the liquid refrigerant can rise in the header, and the liquid refrigerant is suppressed from staying below the header.

<First Modification>
FIG. 8 is a schematic side view of the inside of the header of the heat exchanger according to the first modification of the first embodiment. In FIG. 8, the end portion 11c of the flat tube 11 is twisted so that the plane portion is parallel to the vertical direction. A spirally wound wire 21 is accommodated in the header 15.

  The gas refrigerant out of the refrigerant flowing out from the end portion 11c of the flat tube 11 is pushed by the gas refrigerant flowing out later and rises while turning along the inner surface 15c of the header 15. The liquid refrigerant is pushed up by the liquid refrigerant flowing out later and rises while turning along the spiral wire 21. In the first modification, the wire 21 is a deflecting member that swirls and raises the liquid refrigerant, and serves as both the swirling flow generation unit 16 and the upflow generation unit 17.

<Second Modification>
FIG. 9 is a schematic side view of the inside of the header of the heat exchanger according to the second modification of the first embodiment. In FIG. 9, the end portion 11c of the flat tube 11 is twisted so that the plane portion is parallel to the vertical direction. A spiral groove 22 is formed on the inner surface 15 c of the header 15. In addition, the spiral groove 22 is formed by advancing while rotating the metal tube which is the raw material of the header 15, and applying a cutting tool (cutting blade) to the inner surface of the metal tube.

  The gas refrigerant out of the refrigerant flowing out from the end portion 11c of the flat tube 11 is pushed by the gas refrigerant flowing out later and rises while turning along the inner surface 15c of the header 15. The liquid refrigerant rises while being swung along the spiral groove 22 and pushed by the liquid refrigerant flowing out later. In the second modification, the spiral groove 22 also serves as the swirl flow generation unit 16 and the upward flow generation unit 17.

<Third Modification>
FIG. 10 is a schematic side view of the inside of the header of the heat exchanger according to the third modification of the first embodiment. In FIG. 10, the end portion 11c of the flat tube 11 is twisted so that the plane portion is parallel to the vertical direction. A spiral path 23 is formed on the inner surface 15 c of the header 15. The spiral path 23 is formed by advancing the metal tube that is a material of the header 15 while rotating, and pressing a tool so as to be recessed from the outer surface to the inner surface of the metal tube.

  In the third modified example, since the spiral path 23 of the inner surface 15c can be formed from the outer surface, the spiral path 23 can be formed as necessary at a required place. Since the flow of the refrigerant flowing out from the end portion 11c of the flat tube 11 is the same as that in the second modified example, the description thereof is omitted here. In the third modified example, the spiral path 23 serves as the swirl flow generation unit 16 and the upflow generation unit 17.

[Second Embodiment]
In the first embodiment, the flat portion of the flat tube is twisted from the position away from the header by a predetermined distance to the end portion, but the entire flat tube may be inclined. Hereinafter, a second embodiment will be described with reference to the drawings. In addition, the same code | symbol is provided to the same member as 1st Embodiment, and description is abbreviate | omitted.

  FIG. 11 is a perspective view of the heat exchanger according to the second embodiment, in which the upper part of the header is partially broken and viewed from the broken part side. In FIG. 11, the inside of the header 15 has a cylindrical shape and stands parallel to the vertical direction. The inside of the header 15 is not limited to a cylindrical shape, and may be an elliptical column shape.

  FIG. 12 is a perspective view of the heat exchanger according to the second embodiment, in which the wall surface of the header is partially broken so that the end portion of the flat tube can be seen, and viewed from the broken portion side. In FIG. 12, the flat tube 111 is inclined with respect to the horizontal plane, and the end 111 c protrudes from the inner surface 15 c of the header 15 in an inclined state. The ends 111 c of the flat tubes 111 are arranged in the direction of the central axis X of the header 15.

  FIG. 13 is a perspective view of the heat exchanger according to the second embodiment, in which the wall surface of the header is partially broken so that the refrigerant flow path of the flat tube can be seen, and viewed from the broken portion side. In FIG. 13, when the inside of the header 15 is divided into two virtual spaces by a virtual plane including the central axis X and parallel to the longitudinal direction of the flat tube 111, the position of the end 111c is one of the two virtual spaces. One side is biased.

  As a result, the refrigerant that has passed through the refrigerant flow path 111b of the flat tube 111 flows out of the end portion 111c, then turns along the inner surface 15c of the header 15, and the flat portion of the inclined end portion 111c of the flat tube 111. It rises when hitting. The rising refrigerant merges with the refrigerant flowing out of the upper end portion 111c and swirling, and further rises by hitting the flat portion of the upper end portion 111c. That is, the refrigerant rises in the header 15 while turning, so that not only the gas refrigerant but also the liquid refrigerant can rise. The turning and raising of the refrigerant in the header 15 are the same as in the first embodiment, and the first, second, and third modifications of the first embodiment can be applied.

(Fixing method of partition plate 18)
Here, a fixing method of the partition plate 18 that partitions the inside of the header 15 will be described. FIG. 14 is a perspective view of the heat exchanger according to the second embodiment before the partition plate is fixed to the header. In FIG. 14, the header 15 is previously provided with a slit 15 d that obliquely crosses the central axis X.

  The partition plate 18 is a plate having a thickness enough to be sandwiched between the slits 15d, and has a small diameter portion 18a, a large diameter portion 18b, and a positioning portion 18c. The small diameter portion 18 a is a semicircular disk having a radius slightly larger than the inner diameter of the header 15. The large-diameter portion 18b is a semicircular plate having a radius equivalent to the radius of the small-diameter portion 18a plus the thickness dimension of the header 15. The small-diameter portion 18a and the large-diameter portion 18b are integrally formed from a single plate material by punching. The positioning portion 18c is a step portion between the small diameter portion 18a and the large diameter portion 18b.

  The small diameter portion 18 a of the partition plate 18 is inserted from the slit 15 d of the header 15. When the positioning portion 18c is inserted until it hits the end of the slit 15d, the edge of the peripheral surface of the small diameter portion 18a comes into contact with the inner surface 15c of the header 15, and the peripheral surface of the large diameter portion 18b approaches the outer surface of the header 15. Next, the header 15 and the partition plate 18 are brazed and welded from the side of the slit 15d, so that the solder rotates around the contact portion between the header 15 and the partition plate 18 to complete the fixing. According to this fixing method, since the partition plate 18 can be fixed from the outside of the header 15, the manufacturing is easy.

<Features of Second Embodiment>
In this heat exchanger 10, since the flat tube 111 is connected to the header 15 in an inclined state with respect to the horizontal plane, the end portion 111c of the flat tube 111 is inevitably inclined in the horizontal plane, and the inner surface of the header 15 is inclined. Since it protrudes from 15c and it is not necessary to twist the end part 111c of the flat tube 111, manufacture is easy.

  As described above, the heat exchanger according to the present invention has a specification in which the header stands vertically, and the refrigerant from the lower flat tube flows through the header to the upper flat tube. Since the refrigerant does not stay, it is useful for a heat exchanger of an air conditioner.

The perspective view of the heat exchanger which concerns on 1st Embodiment of this invention. The expansion perspective view of the A section of FIG. The perspective view of the heat exchanger seen from the connection part of a flat tube and a header. The perspective view of the heat exchanger which cut | disconnected the upper part of the header partially and was seen from the fracture | rupture part. The perspective view of the heat exchanger which fractured | ruptured the wall surface of the header partially so that the edge part of a flat tube could be seen, and was seen from the fracture | rupture part side. The perspective view of the heat exchanger which fractured | ruptured the wall surface of the header partially so that the refrigerant | coolant flow path of a flat tube could be seen, and was seen from the fracture | rupture part side. The schematic side view inside a header. The schematic side view inside the header of the heat exchanger which concerns on the 1st modification of 1st Embodiment. The schematic side view inside the header of the heat exchanger which concerns on the 2nd modification of 1st Embodiment. The schematic side view inside the header of the heat exchanger which concerns on the 3rd modification of 1st Embodiment. The perspective view of the heat exchanger which concerns on 2nd Embodiment which fractured | ruptured the upper part of the header and was seen from the fracture | rupture part. The perspective view of the heat exchanger which concerns on 2nd Embodiment which fractured | ruptured the wall surface of the header partially so that the edge part of a flat tube could be seen, and was seen from the fracture | rupture part side. The perspective view of the heat exchanger which concerns on 2nd Embodiment which fractured | ruptured the wall surface of the header so that the refrigerant | coolant flow path of a flat tube could be seen, and was seen from the fracture | rupture part side. The perspective view of the heat exchanger which concerns on 2nd Embodiment before fixing a partition plate to a header.

Explanation of symbols

10 heat exchanger 11 flat tube 11c end (upflow generation part)
12 Fin 15 Header 15c Inner surface (swirl flow generator)
16 Swirl flow generation unit 17 Upflow flow generation unit (first direction flow generation unit)
21 Wire (coiled member)
22 spiral groove 23 spiral path (spiral fluid passage)

Claims (16)

A plurality of flat tubes (11, 111);
A fin (12) sandwiched between the adjacent flat tubes (11, 111);
A cylindrical header (15) through which the end (11c, 111c) of the flat tube (11, 111) penetrates from the outer surface to the inner surface;
With
In the header (15),
A swirl flow generator (16) that turns the flow of the refrigerant out of the end portions (11c, 111c) of the flat tube (11, 111) into a swirl flow along the inner surface (15c) of the header (15);
The direction of the refrigerant discharged from the end portions (11c, 111c) of the flat tubes (11, 111) is changed to the first direction in which the end portions (11c, 111c) of the plurality of flat tubes (11, 111) are arranged. A first direction flow generator (17) to be changed;
Is formed,
Heat exchanger (10). The internal space of the header (15) is a pillar shape having a curved surface,
The heat exchanger (10) according to claim 1. The end (11c, 111c) of the flat tube (11, 111) extends perpendicularly or obliquely to the horizontal plane;
The heat exchanger (10) according to claim 2. The flat tube (11) is twisted from the center to the end (11c),
The heat exchanger (10) according to claim 2. The swirl flow generation unit (16)
The inner surface (15c) of the header (15);
The end (11c, 111c) of the flat tube (11, 111);
Contains
When the interior of the header (15) is divided into a first virtual space and a second virtual space on a virtual plane including the central axis inside the header (15) and parallel to the longitudinal direction of the flat tube (11, 111) The position of the end portion (11c, 111c) of the flat tube (11, 111) is biased to one of the first virtual space and the second virtual space.
The heat exchanger (10) according to claim 2. The position of the tip of the end (11c, 111c) of the flat tube (11, 111) is biased to either the first virtual space or the second virtual space,
The heat exchanger (10) according to claim 5. The base and tip positions of the ends (11c, 111c) of the flat tube (11, 111) are both biased to either the first virtual space or the second virtual space.
The heat exchanger (10) according to claim 5. The swirl flow generating portion (16) is a coil shape that causes the direction of the refrigerant that has come out of the end portions (11c, 111c) of the flat tubes (11, 111) to follow the inner surface (15c) of the header (15). Including a member (21),
The heat exchanger (10) according to claim 2. The swirl flow generator (16) includes a spiral fluid passage (23) formed in the inner surface (15c) of the header (15).
The heat exchanger (10) according to claim 2. The spiral fluid passage is a spiral groove (22);
A heat exchanger (10) according to claim 9. The first direction flow generation unit (17) includes the end portions (11c, 111c) of the flat tubes (11, 111),
The ends (11c, 111c) of the flat tubes (11, 111) are inclined with respect to a horizontal plane;
The heat exchanger (10) according to claim 2. The first direction flow generation unit (17) includes a deflecting member that changes the direction of the refrigerant that has exited from the end portions (11c, 111c) of the flat tube (11, 111) by a surface that is inclined with respect to a horizontal plane. ,
The heat exchanger (10) according to claim 2. The first direction flow generation part (17) includes a spiral fluid passage formed in the inner surface (15c) of the header (15).
The heat exchanger (10) according to claim 2. The spiral fluid passage is a spiral groove;
The heat exchanger (10) according to claim 13. The header (15) extends perpendicularly or obliquely to the horizontal plane;
The heat exchanger (10) according to any one of claims 1 to 14. It is a manufacturing method of the heat exchanger according to claim 9 or 13,
The spiral refrigerant passage is formed by recessing the outer surface of the header (15) spirally toward the inner surface (15c),
Manufacturing method of heat exchanger (10).

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