JP2016186398A - Tube for heat exchanger and heat exchanger using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance manufacturability while reducing the weight of a tube, in a heat exchanger.SOLUTION: In a tube 16 constituting a heat exchanger 10, on outermost partition walls 44a, 44b adjacent to an end wall part 42 formed at both end parts along a width direction of the tube 16, formed are wide parts 48 gradually widening toward the sides of first and second side wall parts 38, 40. By providing the wide parts 48, the first and second side wall parts 38, 40 and the outermost partition walls 44a, 44b having different thicknesses can be connected gently. Consequently, when the tube 16 is formed by extrusion molding, fluidity of material can be enhanced, and further since the thicknesses of outermost partition walls 44a, 44b need not be made larger than required, the weight of the tube can be reduced.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a heat exchanger tube using a heat exchanger tube capable of performing heat exchange between the refrigerant and air circulated through the heat exchanger tube and the heat exchanger tube through which the refrigerant flows.

  Conventionally, in a vehicle such as an automobile, a heat exchanger such as a condenser in which refrigerant flows and a radiator in which cooling water flows is used. This heat exchanger is disclosed in, for example, Patent Document 1. As described above, a pair of first and second headers into which refrigerant is introduced, a third header disposed adjacent to the first header, and a plurality of headers connected between the first to third headers A tube. This tube is formed in a flat cross section, has a plurality of refrigerant passages extending along the longitudinal direction thereof and arranged in parallel in the width direction.

  In this tube, the connecting portion between the partition wall and the outer peripheral wall that partitions each refrigerant passage in the cross section has a cross-sectional R shape, thereby improving the fluidity of the material when the tube is formed by extruding in the longitudinal direction, and manufactured. The improvement of the nature is aimed at.

  In addition, when the heat exchanger as described above is used, for example, as a condenser in the front end surface of a vehicle in an engine room, a stepping stone flying during traveling like the heat exchanger disclosed in Patent Document 2 The outer peripheral wall of the tube needs to be formed thick in consideration of contact with the like. Thereby, while ensuring the strength of the tube when the stepping stones etc. are in contact with each other, the partition wall that is connected to the outer peripheral wall is formed thin, thereby reducing the weight of the partition wall that is not required for the strength. .

JP 2010-185660 A JP 2007-93144 A

  However, in the heat exchanger disclosed in Patent Document 1 described above, there is a problem that the weight is increased by making the connecting portion into a R-shaped cross section in exchange for improving the manufacturability of the tube.

  On the other hand, in the heat exchanger disclosed in Patent Document 2, when the tube including the outer peripheral wall and the partition wall is extruded, the outer peripheral wall and the partition wall have different thicknesses. The fluidity of the material between the two deteriorates, leading to a decrease in manufacturability.

  The present invention has been made in consideration of the above-described problems, and is a heat exchanger tube capable of improving the manufacturability while reducing the weight of the tube, and a heat exchanger using the heat exchanger tube. The purpose is to provide.

In order to achieve the above-mentioned object, the present invention is used in a heat exchanger having a pair of headers that are spaced apart from each other and into which refrigerant is introduced, and is substantially orthogonal to the direction in which the headers extend. In a plurality of heat exchanger tubes that extend to the both ends and are connected to the headers,
The heat exchanger tube is formed to have a flat cross section and a plurality of flow paths are formed along the width direction. The thickness of the widest thickness portion at the end in the width direction is “a”, and the thickness of the partition wall is “ b ”, a> b relationship is established,
In addition, only the partition wall arranged closest to the end in the width direction has a base portion having a substantially constant thickness, and a tapered wide portion that gradually widens with respect to the base portion and connects to the outer peripheral wall. It is characterized by having.

  According to the present invention, in the heat exchanger tube used in the heat exchanger, when the thickness of the widest thickness portion at the end in the width direction is “a” and the thickness of the partition wall is “b”, > B, and only the partition wall arranged closest to the end in the width direction has a base portion having a substantially constant thickness, and a tapered shape that gradually widens with respect to the base portion and connects to the outer peripheral wall. Wide part.

  Therefore, by providing a wide portion only on the partition wall arranged closest to the end in the width direction, when the heat exchanger tube is formed by extrusion molding, the wide portion of the material that has flowed from the end in the width direction to the outer peripheral wall is formed. Therefore, the fluidity of the material can be increased and the productivity can be improved. Moreover, compared with the conventional heat exchanger which makes the connection part with an outer peripheral wall the cross section R shape in all the partition walls, since it has a wide part only in the partition wall arrange | positioned nearest to the width direction edge part. It is possible to achieve a significant weight reduction.

  Further, by setting the thickness of the side wall portion extending along the width direction on the outer peripheral wall of the heat exchanger tube so as to be equal to or greater than the minimum thickness of the partition wall, Manufacturability can be improved while reducing weight.

  Further, in the partition wall arranged closest to the end in the width direction, when the thickness of the widest portion in the wide portion is “c”, the relationship of 1 ≦ a / c ≦ 5 is established. As a result, even if the partition wall is thin, the width-thickness part in the wide part can be brought closer to the thickness of the widest-thickness part in the width direction end part, so the fluidity of the material from the outer peripheral wall to the partition wall Can be improved.

  Furthermore, in the partition wall arranged closest to the end in the width direction, when the thickness of the widest portion in the wide portion is “c”, the relationship 1 ≦ a / c ≦ 4.2 is established. By forming in this way, it becomes possible to further improve the fluidity of the material.

  Further, in the partition wall arranged closest to the end in the width direction, when the length of the partition wall formed with the thickness “b” is “d”, the relationship of d / b ≦ 10 is established. By forming, in the thickness direction of the heat exchanger tube, it is prevented that the material does not sufficiently flow into the vicinity of the substantially central portion of the partition wall and does not fade, and the partition wall is substantially constant along the thickness direction. Can be formed. As a result, it becomes possible to set the thickness of the partition wall small, and it is possible to further reduce the weight of the heat exchanger tube.

  Further, in the partition wall arranged closest to the end in the width direction, when the length of the partition wall formed with the thickness “b” is “d”, the relationship of 4 ≦ d / b ≦ 10 is established. By forming the heat exchanger tube, it is possible to more suitably prevent the thinning of the heat exchanger tube near the center of the partition wall in the thickness direction of the heat exchanger tube. Can be realized.

  Furthermore, in the thickness direction of the heat exchanger tube, the thickness dimension from one side wall part provided across the flow path and the partition wall to the other side wall part is within a range of 1.0 mm to 1.5 mm. It is good to set.

  Furthermore, a plurality of the above-described heat exchanger tubes may be arranged in the heat exchanger along the longitudinal direction of the header.

  Further, the heat exchanger may be a condenser used for a vehicle air conditioner.

  According to the present invention, the following effects can be obtained.

  That is, in the heat exchanger tube used in the heat exchanger, the relationship of a> b is assumed when the thickness of the widest thickness portion at the end in the width direction is “a” and the thickness of the partition wall is “b”. And a base part having a substantially constant thickness only on the partition wall arranged closest to the end in the width direction, and a taper-shaped wide part that gradually widens with respect to the base part and leads to the outer peripheral wall. By providing the portion, when forming the heat exchanger tube by extrusion, it is possible to suitably guide the material that has flowed from the width direction end portion to the outer peripheral wall to the partition wall side through the wide portion, The productivity can be improved by increasing the fluidity of the material. Moreover, compared with the conventional heat exchanger which makes the connection part with an outer peripheral wall the cross section R shape in all the partition walls, since it has a wide part only in the partition wall arrange | positioned nearest to the width direction edge part. It is possible to reduce the weight.

1 is an overall external view of a heat exchanger in which a tube for a heat exchanger according to an embodiment of the present invention is used. 2A is a partially omitted external perspective view of a tube constituting the heat exchanger of FIG. 1, and FIG. 2B is a plan view showing an end surface of the tube of FIG. 2A. 3A is an enlarged plan view showing the vicinity of the end wall portion of the tube shown in FIG. 2B, FIG. 3B is an enlarged front view showing the vicinity of the end wall portion of the tube according to the first modification, and FIG. It is an enlarged front view which shows the end wall part vicinity of the tube which concerns on a 2nd modification.

  BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of a heat exchanger tube according to the present invention and a heat exchanger in which the heat exchanger tube is used will be described in detail below with reference to the accompanying drawings. In FIG. 1, reference numeral 10 indicates a heat exchanger in which the heat exchanger tube according to the embodiment of the present invention is used.

  As shown in FIG. 1, the heat exchanger 10 includes a pair of first and second headers (headers) 12 and 14, and a plurality of heat exchangers 10 provided between the first header 12 and the second header 14. Tube (heat exchanger tube) 16, a plurality of fins 18 that are provided between the tubes 16 and are bent in a wave shape, and a third header (substantially parallel to the first header 12). Header) 20. In addition, this heat exchanger 10 is provided in the front side in the engine room of a vehicle, for example, and is used as a capacitor | condenser for performing heat exchange with the refrigerant | coolant and air which circulate inside.

  The heat exchanger 10 is configured so that the tube 16 is substantially horizontal and the first and second headers 12 and 14 and the third header 20 extend in the vertical direction (arrow A1 and A2 directions) at both ends of the tube 16. Between the adjacent tubes 16, fins 18 that are bent into a corrugated cross-section by press forming a thin plate such as aluminum are provided and connected.

  Moreover, in the heat exchanger 10, the several heat exchange path P which consists of the some tube 16 arrange | positioned along with adjoining the perpendicular direction (arrow A1, A2 direction) is provided.

  For example, the heat exchanger 10 has five heat exchange paths, and the heat exchange path P is provided at the uppermost part, and the first path P1 through which the refrigerant flows from the first header 12 to the second header 14; A second path P2 that is arranged below the first path P1 (in the direction of arrow A2) and returns the refrigerant that has flowed through the first path P1 to the second header 14 to the first header 12 side (in the direction of arrow B1). A third path P3 disposed below the second path P2 and returning the refrigerant that has flowed to the first header 12 through the second path P2 back to the second header 14 side; and below the third path P3 The fourth path P4 for returning the refrigerant that has been arranged and circulated to the second header 14 through the third path P3 to the third header 20, and the lowermost path provided to the third header 20 through the fourth path P4. The circulated refrigerant is used as the second header. Back to 4 and a fifth path P5 Prefecture.

  The first and second headers 12 and 14 are, for example, hollow cylindrical and have a predetermined length along the height direction of the heat exchanger (the directions of arrows A1 and A2). The first header 12 is provided on one end side (arrow B1 direction) along the width direction of the heat exchanger 10, and an inlet connection portion 22 into which a refrigerant is introduced from the outside is connected in the vicinity of the upper end portion. The The inlet connection portion 22 is connected to a supply pipe (not shown) at a port communicating with the inside of the first header 12, and the high-temperature and high-pressure refrigerant supplied through the supply pipe is supplied to the inside of the first header 12. The

  The first header 12 is provided with a first separation wall 24 at a substantially central position along the longitudinal direction (arrows A1 and A2 directions), and the first separation wall 24 creates an internal space. It is separated into an upper side space communicating with the inlet connection part 22 and a lower side space.

  On the other hand, the 2nd header 14 is provided in the other end part side (arrow B2 direction) along the width direction of the heat exchanger 10, and the refrigerant | coolant which circulated through the inside of the said heat exchanger 10 in the lower end part vicinity. Is connected to the outlet connection portion 26 from which the outlet is connected. The outlet connecting portion 26 is connected to a port communicating with the inside of the second header 14 through a discharge pipe (not shown), and the refrigerant is discharged from the second header 14 to the outside through the discharge pipe.

  Further, in the second header 14, a second separation wall 28 provided below a substantially central portion along the longitudinal direction (arrows A1 and A2 directions), the second separation wall 28 and the outlet connection portion 26 are provided. And a third separation wall 30 provided between them.

  As shown in FIGS. 1 to 2B, the tube 16 is formed in a flat cross section from a metal material such as aluminum, and is formed in a predetermined length along the longitudinal direction in the flat cross section. Is connected to the first header 12 or the third header 20, and the other end is connected to the second header 14. In the following description, as shown in FIG. 2A, the width direction of the tube 16 is described as the X direction, the longitudinal direction of the tube 16 is defined as the Y direction, and the thickness direction of the tube 16 is described as the Z direction.

  On the other hand, as shown in FIGS. 2A and 2B, a plurality of refrigerant flow paths (flow paths) 32 are provided in the tube 16 along the width direction (arrow X direction). Each is separated by a partition wall 34. The refrigerant flow path 32 is formed in a rectangular cross section divided by the partition wall 34, and has substantially the same shape and extends along the longitudinal direction (arrow Y direction) of the tube 16.

  Further, the outer wall surface (outer peripheral surface) 36 of the tube 16 formed in a flat cross section is provided with a first side wall portion 38 constituting one side surface of the tube 16, and substantially parallel to the first side wall portion 38. It consists of a second side wall portion 40 constituting the side surface and a pair of end wall portions 42 connected to both end portions along the width direction (arrow X direction) of the first and second side wall portions 38, 40. As shown in FIGS. 2A to 3A, the first and second side wall portions 38 and 40 each have a constant side wall portion thickness Ta in a cross section (XZ cross section) orthogonal to the longitudinal direction (arrow Y direction) of the tube 16. And is formed in a straight line along the width direction (arrow X direction) of the tube 16, and the partition wall 34 is connected to the inside thereof, and the refrigerant flow path 32 is provided.

  The end wall portion 42 is formed, for example, by connecting the end portions of the first side wall portion 38 and the second side wall portion 40 to each other in a substantially semicircular cross section. As shown in FIG. The end wall portion 42 is formed with the thickest end wall portion thickness Tb (complaint correspondence a). It is changed and connected so that the thickness is gradually reduced toward.

  Further, the thickness dimension Tc from the first side wall portion 38 to the second side wall portion 40 in the tube 16 is set to be within a range of 1.0 mm to 1.5 mm, for example (1.0 ≦ Tc). ≦ 1.5).

  The partition wall 34 extends in the thickness direction (arrow Z direction) of the tube 16 so as to be substantially orthogonal to the first and second side wall portions 38 and 40, and extends along the width direction (arrow X direction) of the tube 16. So as to be spaced apart from each other at equal intervals. The partition wall 34 is formed with a substantially constant partition wall thickness Td (claim correspondence b) from the first side wall 38 side to the second side wall 40 side.

  Further, the outermost partition walls 44 a and 44 b formed on the most end wall 42 side (in the direction of the arrow X 1) are a base portion 46 formed with a constant partition wall thickness Td, and a second end from the both ends of the base portion 46. It consists of a pair of wide part 48 which becomes thick gradually toward the 1st and 2nd side wall parts 38 and 40 side, and is connected. The thickness Td of the base portion 46 is set to be the same as the partition wall thickness Td other than the outermost partition walls 44a and 44b. That is, the outermost partition walls 44 a and 44 b are different from each other in that they have a wide portion 48 with respect to the other partition walls 34.

  Further, the thickness Td of the base portion 46 in the outermost partition walls 44a and 44b and the partition wall thickness Td in the other partition walls 34 are formed to be equal to or less than the end wall thickness Tb (Td ≦ Tb). At the same time, the first and second side wall portions 38 and 40 are formed to have a thickness Ta or less (Td ≦ Ta).

  Furthermore, the relationship between the thickness Td of the base portion 46 in the outermost partition walls 44a and 44b and the length Le (claim correspondence d) of the base portion 46 is obtained by dividing the length Le by the thickness Tb. It is set to be 10 or less (Le / Td ≦ 10). It is more preferable to set the lower limit of the value obtained by dividing the length Le by the thickness Td to 4 or more (4 ≦ Le / Td ≦ 10).

  The wide portion 48 is formed in a tapered shape inclined by a predetermined angle so as to widen toward the first and second side wall portions 38 and 40 with respect to the side surface of the base portion 46, and the first side wall portion 38 side. The one wide portion 48 and the other wide portion 48 on the second side wall portion 40 side are formed at substantially the same inclination angle. The wide portion 48 is formed symmetrically in the width direction (arrow X direction) of the tube 16 with the base portion 46 as the center, and in the thickness direction (arrow Z direction) with the base portion 46 as the center. Is also formed symmetrically.

Further, the widest width portion width dimension Wf (claim corresponding c) in the wide portion 48 is set so that the relationship with the end wall portion thickness Tb of the end wall portion 42 is expressed by the equation (1).
1 ≦ Tb / Wf ≦ 5 (1)

Furthermore, it is more preferable that the relationship between the wide part width dimension Wf and the end wall part thickness Tb is set as shown in Expression (2).
1 ≦ Tb / Wf ≦ 4.2 (2)

  That is, by forming the cross-sectional shape (XZ cross-section) in the tube 16 as the dimensional relationship as described above, when the tube 16 is extruded by pressing the material into a mold (not shown) at high pressure, the first and second Even when the side wall portions 38 and 40, the end wall portion 42 and the partition wall 34 are different in thickness, the material is reliably flowed from the thickest end wall portion 42 to the outermost partition walls 44a and 44b through the wide portion 48. It is formed.

  The heat exchanger 10 according to the embodiment of the present invention is basically configured as described above, and its operation and effects will be described.

  First, gaseous refrigerant compressed to a high temperature and high pressure by a compressor (not shown) is supplied to an inlet connection portion 22 through a supply pipe (not shown) and flows into the upper space of the first header 12 from the inlet connection portion 22. Then, the refrigerant is cooled and condensed by the air flowing between the fins 18 by flowing to the second header 14 side (in the direction of arrow B2) through the plurality of tubes 16 constituting the first path P1. 2 is introduced into the upper space of the header 14.

  The refrigerant introduced into the upper space of the second header 14 is cooled and condensed by flowing again toward the first header 12 through the plurality of tubes 16 constituting the second path P2, and then the first header. 12 is further condensed by flowing from the lower space of 12 to the second header 14 side through the third path P3.

  This refrigerant is further condensed by flowing from the internal space of the second header 14 to the third header 20 side through the tube 16 of the fourth path P4, and is introduced into the third header 20. At this time, the refrigerant is in a gas-liquid mixed state, and the liquefied refrigerant accumulates in the lower part of the third header 20 under the action of gravity, and the vaporized refrigerant accumulates in the upper part of the third header 20.

  And after the refrigerant | coolant in the liquid state collected under the 3rd header 20 is overcooled by flowing again to the 2nd header 14 side through the several tube 16 which comprises the 5th path | pass P5, said 2nd It is introduced into the lower space of the header 14 and discharged from a discharge pipe (not shown) through the outlet connection portion 26. The fifth path P5 functions as a supercooling path.

  As described above, in the present embodiment, in the plurality of tubes 16 constituting the heat exchanger 10, a plurality of partition walls 34 for separating the plurality of refrigerant flow paths 32 are provided along the width direction (arrow X direction). The partition wall 34 is provided with outermost partition walls 44 a and 44 b that are formed on the outermost side in the width direction (in the direction of the arrow X <b> 1) and are close to the end wall portion 42. The outermost partition walls 44a and 44b are formed such that a substantially central base 46 along the thickness direction (arrow Z direction) of the tube 16 is formed with substantially the same thickness (Td) as the other partition walls 34. The wide portions 48 which are widened in a tapered shape are formed at both end portions on the first and second side wall portions 38 and 40 side, respectively.

  Therefore, when the tube 16 is formed by extrusion molding, the outermost partition walls 44a and 44b on the tube 16 on the side of the thickest end wall portion 42 are provided with a tapered wide portion 48. The fluidity of the material that flows to the outermost partition walls 44a, 44b through the first and second side wall portions 38, 40 can be enhanced, and at the same time, the connecting portions with the outer peripheral wall are cross-sectioned with respect to all the partition walls. Compared to a conventional heat exchanger having a shape, a large weight reduction can be achieved by providing the wide portion 48 only on the outermost partition walls 44a and 44b. Therefore, it is possible to reduce the weight while improving the manufacturability of the tube 16 constituting the heat exchanger 10.

  Further, the side wall thickness Ta of the first and second side wall portions 38 and 40 is set to be equal to or greater than the thickness Td of the base portion 46 and the partition wall 34 in the outermost partition walls 44a and 44b (Ta ≧ Td). By doing so, productivity can be improved, achieving further weight reduction.

  Further, the value obtained by dividing the end wall portion thickness Tb in the end wall portion 42 by the wide portion width dimension Wf that is the widest thickness of the wide portion 48 is in the range of 1 to 5 (1 ≦ Tb / Wf ≦ 5), the wide portion width dimension Wf can be brought close to the end wall thickness Tb even when the partition wall 34 is thin. Therefore, the first and second side wall portions 38 are provided. , 40 can improve the fluidity of the material from the partition wall 34 to the partition wall 34.

  Furthermore, if the numerical value obtained by dividing the above-mentioned end wall thickness Tb by the wide portion width dimension Wf is 4.2 or less (1 ≦ Tb / Wf ≦ 4.2), the fluidity of the material can be further improved. It becomes.

  Further, the relationship between the thickness Td of the base portion 46 and the length Le of the base portion 46 in the outermost partition walls 44a and 44b is obtained by dividing the length Le by the thickness Td to 10 or less (Le / Td By setting so as to be ≦ 10), it is prevented that the partition wall 34 is not thinned in the vicinity of the center in the thickness direction of the extruded cross section of the tube 16, and the partition wall 34 is not thinned. The partition wall 34 can be formed with a substantially constant thickness along the (Z direction). As a result, the thickness Td of the base portion 46 can be set sufficiently small, and the tube 16 can be further reduced in weight.

  Furthermore, if the lower limit of the value obtained by dividing the length Le by the thickness Td is set to 4 or more (4 ≦ Le / Td ≦ 10), the thinning of the partition wall 34 near the center in the thickness direction is more preferable. Accordingly, the tube 16 can be further reduced in weight.

  In addition, the shape of the wide part 48 in the tube 16 is limited to the case where it is formed so as to widen in the width direction both sides (arrows X1 and X2 directions) with respect to the side surfaces of the outermost partition walls 44a and 44b as described above. For example, as in the tube 60 shown in FIG. 3B, the wide portion 64 is provided only on one side surface of the outermost partition wall 62 on the end wall portion 42 side (arrow X1 direction). Also good. The wide portion 64 is formed so that the widest portion width dimension Wf that is the widest is the same as that of the wide portion 48 described above.

  With such a configuration, when the tube 60 is extruded, the material flows through the wide portion 64 when the material flows from the end wall portion 42 side toward the inner side in the width direction (arrow X2 direction). Can be smoothly flowed to the outermost partition wall 62, so that it is possible to further reduce the weight while improving the manufacturability.

  Further, as in the tube 70 shown in FIG. 3C, by providing the wide portion 74 only on the other side surface on the adjacent partition wall 34 side (arrow X2 direction) in the outermost partition wall 72, the tube 70 can be extruded. When performing molding, when the material flows toward the end wall portion 42 toward the outer side in the width direction (in the direction of the arrow X1), the material can smoothly flow to the outermost partition wall 72 via the wide portion 74. Therefore, further weight reduction can be achieved while improving manufacturability.

  The wide portion 74 is formed such that the widest portion width dimension Wf that is the widest is the same as the wide portions 48 and 64 described above.

  The heat exchanger tube according to the present invention and the heat exchanger in which the heat exchanger tube is used are not limited to the above-described embodiment, and can have various configurations without departing from the gist of the present invention. Of course.

DESCRIPTION OF SYMBOLS 10 ... Heat exchanger 16, 60, 70 ... Tube 18 ... Fin 32 ... Refrigerant flow path 34 ... Partition wall 36 ... Outer wall surface 38 ... 1st side wall part 40 ... 2nd side wall part 42 ... End wall part 44a, 44b, 62 72 ... Outermost partition wall 46 ... Base part 48, 64, 74 ... Wide part

Claims (9)

Used in a heat exchanger that has a pair of headers that are spaced apart from each other and into which refrigerant is introduced, and that extends in a direction substantially orthogonal to the direction in which the header extends, and both ends are connected to the header. In a plurality of heat exchanger tubes
The heat exchanger tube is formed to have a flat cross section, and a plurality of flow paths are formed along the width direction. The thickness of the widest thickness portion at the end in the width direction is “a”, and the thickness of the partition wall is In the case of “b”, the relationship of a> b is established,
In addition, only the partition wall arranged closest to the end in the width direction has a base portion having a substantially constant thickness, and a tapered shape that gradually widens with respect to the base portion and connects to the outer peripheral wall. A heat exchanger tube having a wide portion. The heat exchanger tube according to claim 1,
The heat exchanger tube according to claim 1, wherein a thickness of a side wall portion extending along a width direction of the outer peripheral wall of the heat exchanger tube is set to be equal to or greater than a minimum thickness of the partition wall. In the heat exchanger tube according to claim 1 or 2,
In the partition wall arranged closest to the end in the width direction, when the thickness of the widest portion in the wide portion is “c”,
1 ≦ a / c ≦ 5
A tube for a heat exchanger, characterized in that the relationship is established. In the heat exchanger tube according to claim 1 or 2,
In the partition wall arranged closest to the end in the width direction, when the thickness of the widest portion in the wide portion is “c”,
1 ≦ a / c ≦ 4.2
A tube for a heat exchanger, characterized in that the relationship is established. In the heat exchanger tube according to any one of claims 1 to 4,
In the partition wall arranged closest to the end in the width direction, when the length of the partition wall formed with the thickness “b” is “d”,
d / b ≦ 10
A tube for a heat exchanger, characterized in that the relationship is established. In the heat exchanger tube according to any one of claims 1 to 4,
In the partition wall arranged closest to the end in the width direction, when the length of the partition wall formed with the thickness “b” is “d”,
4 ≦ d / b ≦ 10
A tube for a heat exchanger, characterized in that the relationship is established. In the heat exchanger tube according to any one of claims 1 to 6,
In the thickness direction of the heat exchanger tube, the thickness dimension from one side wall part provided across the flow path and the partition wall to the other side wall part is within a range of 1.0 mm to 1.5 mm. A heat exchanger tube characterized by being set.   A heat exchanger using a heat exchanger tube, wherein a plurality of the heat exchanger tubes according to claim 1 are arranged along a longitudinal direction of the header. The heat exchanger according to claim 8, wherein
The heat exchanger is a condenser used for a vehicle air conditioner, and the heat exchanger uses a heat exchanger tube.

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