Heat exchanger

Abstract

Heat exchangers, including: a long tube (101) for the heat exchanger, and at least one collecting pipe (120) having at least one opening (140), wherein at least one end region (136) of the long pipe (101) extends through the opening (140) to connect the pipe (101) to the collecting pipe (120), wherein the pipe (101) comprises the following: - a first end and a second end for connection to the first and second manifolds (120) of the heat exchanger respectively; - an outer wall (110), wherein the outer wall (110) encloses an inner volume (108), the inner volume (108) having at least two channels (116) for conveying the heat exchanger fluid over the length of the tube (101) between the first and second manifold tubes (120); and - at least one seam (104) in the outer wall (110) extending over the length of the tube (101), wherein the seam (104) or each seam (104) comprises a pair of opposing flanges (106), the pair of opposing flanges (106) extending into the inner volume (108) so that the inner volume (108) is divided into the two channels (116), and wherein the outer wall (110) is joined over the length of the seam (104) or seams (104), wherein the long tube (101) has a first end region (136) in the immediate vicinity of the first end (138) and a second end region (136) in the immediate vicinity of the second end (138) and an intermediate region (142) between the first and the second end region (136), wherein the tube (101) is flattened over its entire length, so that the flanges (106) divide the internal volume (108) into at least two flattened wings (130), wherein each wing (130) provides one of the channels (116) and each wing (130) extends laterally away from the flanges (106) relative to the length of the tube (101), and at least two of the wings (130) in the intermediate region (142) are flatter than previously described compared to the wings (130) in at least one of the end regions (136), wherein each wing (130) in the at least one end region (136) is flatter in a front section (132) in the immediate vicinity of the flanges (106) than in a rear section (134) which is further away laterally relative to the length of the tube (101), wherein the rear section (134), which is further away from the flange (106), has a web (114), a side wall (112) extending laterally from the web (114) and having an inclined wall, wherein the converging wall sections of the side wall (112), starting from the web (114), which connect to a flat wide wall section and merge into the front section (132), form the inclined wall, wherein two wide wall sections of the outer wall (110), which are arranged between narrow wall sections, form the side walls (112) and the two narrower wall sections form the webs (114), wherein the front section (132) has a side wall (112) near the flange (106) which extends laterally from the inclined wall, wherein the collecting tube (120) has a flared rim (164) which extends at least around a part of the circumference of the opening (140), wherein the end region (136) of the tube (101) is connected to the flared rim (164), and wherein the shape of an edge of the flared rim (164) over the width of the collector tube (120) is trapezoidal, such that a central area of ​​the flared rim (164), near the seam (104) of the tube (101), cuts the tube (101) further from the end of the tube (101) than outer areas of the flared rim (164) near the webs (114) of the tube (101).

Description

Background of the inventiona. Field of the invention

[0001] The present invention relates to a heat exchanger comprising a long tube for the heat exchanger, in particular folded tubes for use in heat exchangers of motor vehicles. b. Related prior art

[0002] Motor vehicles are typically equipped with an engine cooling system comprising a heat exchanger, such as a radiator. During engine operation, heat is transferred from the engine to a coolant flowing through the engine. The coolant then flows through a series of pipes from the engine to the heat exchanger. At the heat exchanger, heat is transferred from the coolant to cooler air flowing over the outside of the heat exchanger. This process repeats in a continuous cycle, thereby cooling the engine.

[0003] A typical heat exchanger comprises a series of tubes supported by two chambers or headers positioned at each end of the heat exchanger. The headers are typically connected to the tubes by brazing. During engine and cooling system operation, the tubes undergo thermal cycling (a rise and fall in the temperature of the heat exchanger components), which leads to stresses because adjacent tubes can expand to different degrees, thus exerting axial loads on the tubes and their respective adjacent tubes.

[0004] In many systems, the tubes comprise a single enclosed channel. The tubes have a generally elongated, substantially rectangular cross-sectional shape, and include two opposite longer sides or faces, and two opposite curved shorter sides or lands. Within the heat exchanger, the tubes are arranged side by side, with the faces of adjacent tubes facing each other, defining a space or passageway between the tubes through which air can flow. This tube geometry is therefore advantageous because it creates a relatively large surface area over which the cooling air can flow, while minimizing obstruction to the airflow through the heat exchanger.However, these types of manifold / pipe combinations are highly susceptible to failure due to the stress concentrations that occur along the manifold / pipe joints, particularly around the webs of the pipes.

[0005] To overcome some of these disadvantages of single-duct ducts, a variety of duct designs have been developed in which the ducts are formed from a folded sheet of metal. These folded ducts, or "B-ducts," feature a longitudinal seam separating two ducts. However, the overall cross-sectional shape of these ducts is essentially the same as the overall cross-sectional shape of single-duct ducts, taking advantage of the large surface area and minimal airflow disruption.

[0006] However, these folded tubes still suffer from several disadvantages. First, the cross-sectional area of ​​the tubes limits the required dimensions of the headers. In particular, the longer cross-sectional dimensions of the tubes limit the minimum width of the headers and thus the minimum width of the heat exchanger. Second, the elongated cross-sectional shape of the tubes creates a narrow opening at the end of the tube, resulting in undesirable inlet and outlet pressure drops. Third, although the design of folded tubes is known to reduce the probability of failure of the header / pipe joint around the tube webs, the small radius of the webs of each tube still leads to stress concentrations in these areas.

[0007] US 6 810 951 B1 describes a flat tube for a heat exchanger with reduced width.

[0008] US 5 579 832 A describes a heat exchanger tube, a device for producing such a tube and a heat exchanger comprising such a tube.

[0009] US 6 739 386 B2 describes a heat exchanger, in particular a vehicle heat exchanger, which has flat tubes with deformed ends.

[0010] Heat exchangers are also described in FR 914 783 A and WO 86 / 07628 A1.

[0011] JP 2000-055582 A describes a heat exchanger with a tube that divides the fluid flow path into two parts. The heat exchanger is equipped with fins that are inserted between the tubes and brazed or welded to the tubes.

[0012] It is therefore an object of the present invention to provide an improved tube for a heat exchanger which eliminates these problems. ADVANTAGES OF THE INVENTION

[0013] The object is achieved with a heat exchanger having the features of claim 1. According to the invention, a heat exchanger is provided, comprising: a long tube for the heat exchanger and at least one header tube having at least one opening, wherein at least one end portion of the long tube extends through the opening to connect the tube to the header tube, wherein the tube comprises: - a first end and a second end for connection to first and second manifolds of the heat exchanger, respectively; - an outer wall, the outer wall enclosing an inner volume, the inner volume comprising at least two channels for conveying the heat transfer fluid over the length of the tube between the first and second headers; and - at least one seam in the outer wall extending along the length of the tube, the seam or each seam comprising a pair of opposed flanges, the pair of opposed flanges extending into the internal volume to divide the volume into the two channels, and the outer wall being joined along the length of the seam or seams, the long tube having a first end region in the immediate vicinity of the first end and a second end region in the immediate vicinity of the second end, and an intermediate region between the first and second end regions, the tube being flattened substantially over its entire length such that the flanges divide the internal volume into at least two flattened wings, each wing providing one of the channels and each wing extending laterally away from the flanges relative to the length of the tube,and at least two of the wings in the intermediate region are flatter than described above compared to the wings in at least one of the end regions, wherein each wing in the at least one end region is flatter in a front section in the immediate vicinity of the flanges than in a rear section that is further away in the lateral direction relative to the length of the pipe, wherein the rear section that is further away from the flange has a web, a side wall that extends laterally from the web and has an inclined wall, wherein the tapered wall sections of the side wall, starting from the web, adjoin a flat, wide wall section and open into the section, form the inclined wall, wherein two wide wall sections of the outer wall, arranged between narrow wall sections, form the side walls and the two narrower wall sections form the webs,wherein the front portion near the flange has a side wall extending laterally from the inclined wall, wherein the header tube has a flared edge extending at least around a portion of the circumference of the opening, wherein the end portion of the tube is connected to the flared edge, and wherein the shape of an edge of the flared edge is trapezoidal across the width of the header tube, such that a central portion of the flared edge, near the seam of the tube, intersects the tube further from the end of the tube than outer portions of the flared edge near the webs of the tube.

[0014] In a preferred embodiment of the invention, the wings in the intermediate region are flatter than the wings in the two end regions.

[0015] The outer wall may have opposing wide sections, wherein these wide sections are flared outwardly from the intermediate region toward at least one, and preferably both, first and second ends. At least one of the end regions is therefore partially flared outwardly.

[0016] The outer wall may have opposing narrow sections, wherein these narrow sections are flared inwardly from the intermediate region toward at least one, and preferably both, first and second ends. At least one of the end regions is therefore partially flared inwardly.

[0017] The distance between the opposite wide sections is preferably substantially uniform over the length of the seam through the intermediate region and the two end regions.

[0018] In a preferred embodiment of the invention, at least one of the flanges is joined along its length to a portion of the outer wall opposite the corresponding seam, so that adjacent channels on opposite sides of the flanges are not in fluid communication with each other. In a further preferred embodiment, the wings in the intermediate region extend farther away from the pair of flanges than the wings in the at least one end region.

[0019] The outer wall may have a substantially uniform thickness.

[0020] The circumferential lengths of the cross sections around the pipe in a plane perpendicular to the length of the pipe may be substantially equal in the intermediate region and in at least one, and preferably both, end regions.

[0021] The wings may be substantially symmetrical on opposite sides of an engaging pair of flanges.

[0022] In a preferred embodiment of the invention, each wing in one or both end regions is flatter in a section in the immediate vicinity of the flanges than in a section that is further away from the flanges in the lateral direction relative to the length of the pipe.

[0023] According to a second aspect of the invention, a heat exchanger is provided comprising: at least one long tube, wherein the long tube is a long tube of the type claimed in the preceding claims, and at least one header tube comprising at least one opening, wherein the at least one end region of the tube extends through the opening to connect the tube to the header tube.

[0024] The manifold may include a flared rim extending around at least part of the circumference of the opening, the end portion of the tube being connected to the flared rim. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The invention will now be further explained by way of example only and with reference to the accompanying drawings, in which: Fig. 1 is a perspective view of an end portion of a prior art folded tube suitable for use in a heat exchanger; Fig. 2 a view of a front side of the folding tube according to the prior art according to Fig. 1 represents; Fig. 3 is a perspective view of an end portion of a folded tube suitable for use in a heat exchanger according to the present invention; Fig. 4 a view of an end face of the folding tube according to Fig. 4 represents; Fig. 5 is a cross-sectional view of a portion of the header pipe for a heat exchanger showing the end portion of the prior art folded pipe according to Fig. 1 inserted into the manifold; Fig. 6 a perspective view of the collecting pipe and the folding pipe according to Fig. 5 represents; Fig. 7 is a cross-sectional view of a part of the header pipe for a heat exchanger, showing the end region of the folded pipe according to Fig. 3 inserted into the manifold according to the invention; Fig. 8 a perspective view of the collecting pipe and the folding pipe according to Fig. 7 represents; Fig. 9a is a side view of a split mandrel used to form the ends of the tube according to Fig. 3 is used; and Fig. 9b a view of a front side of a split mandrel according to Fig. 9a represents. DETAILED DESCRIPTION

[0026] The Fig. 1 and Fig. 2 show a conventional folded tube 1 for use in a heat exchanger, such as a motor vehicle radiator. This type of folded tube 1 is often referred to as a "B-tube" due to its cross-sectional shape perpendicular to a longitudinal axis 2 of the tube 1. These folded tubes 1 provide greater strength compared to single-channel tubes, while allowing the use of thinner and lighter materials in their construction.

[0027] The folded tubes 1 are typically made of sheet metal, for example, aluminum. Two opposite edges of the sheet metal are joined to form a seam 4 along the length of the tube 1, and the seam 4 is then soldered to seal the tube 1. The edges of the sheet metal forming the seam 4 include flanges 6, and the flanges 6 extend into the resulting internal volume 8 of the tube 1 when the sheet metal is folded to form the tube 1.

[0028] The tube 1 is generally flattened to have a first, wider, dimension and a second, thinner, dimension. In particular, the outer wall 10 of the tube includes opposed, generally planar, wide portions 12 and opposed, generally curved, narrow portions 14 extending between the wide portions. The tube 1 is flattened such that the seaming flanges 6 extend beyond the narrower dimensions of the tube 1, and the flanges 6 thus divide the internal volume 8 of the tube 1 into two channels 16 extending the length of the tube 1 on either side of the flanges 6. A seal is typically formed between these flanges 6 and the opposed portion of the outer wall 10 to define two separate and distinct channels 16 for the passage of a heat transfer fluid (not shown).The flanges are not joined to the opposing wide sections 12 so that the two channels 16 remain in fluid communication even when the two channels 16 are substantially separated from each other.

[0029] In the context of the present invention, the terms "flat" or "flattened" are used to refer to an object having a wide, thin shape, i.e., an object having a relatively wide surface area relative to a thickness or depth. The term "flatter" means that a first shape or object is generally thinner in width than a second shape or object, i.e., the flatter object generally has a higher aspect ratio relative to the cross-sectional shape than the other second object.

[0030] The Fig. 5 and Fig. 6 show one end of a prior art folded tube 1 connected to a part of a header tube 20 of a heat exchanger.

[0031] In a typical heat exchanger, a plurality of folded tubes 1 extend between first and second headers 20 for conveying a heat transfer fluid or refrigerant between the headers. The folded tubes 1 are spaced apart from each other along the length of the heat exchanger, and gaps are defined between opposite wide portions of the outer walls of adjacent tubes 1.

[0032] During operation, a heated refrigerant typically flows through the folded tubes 1, and a coolant, such as air, flows through the gaps between the tubes. Thermal energy from the refrigerant is transferred to the walls of the tubes 1, and this thermal energy is then radiated from the outside of the tubes to the coolant flow. The flattened shape of the tubes 1 maximizes their surface-to-volume ratio, thereby increasing the efficiency of the heat exchanger.

[0033] During heat exchanger operation, the tubes undergo thermal cycling (rise and fall in temperature of the heat exchanger components), which leads to stresses as adjacent tubes may expand to different degrees, resulting in axial loads on tubes 1 and their respective adjacent tubes. These header / tube combinations are therefore susceptible to failure due to the stress concentrations occurring across the header / tube joint 22, with failures most frequently occurring at the interface between the bent, narrow sections 14 of tube 1 and the header 20.

[0034] The Fig. 3 and Fig. 4 show a modified collapsible tube 101 according to the present invention. The collapsible tube 101 includes an outer wall 110 formed from a sheet metal sheet that encloses an interior volume 108 of the tube 101. The outer wall 110 includes two opposing generally planar wide wall portions 112, hereinafter referred to as the sidewalls 112 of the tube 101, and two opposing generally curved narrow wall portions 114, hereinafter referred to as the webs 114 of the tube 101. The curved wall portions 114 extend between and are continuous with the planar wall portions 112 to form a complete perimeter of the tube 101.

[0035] A distance between the opposing sidewalls 112 defines a narrow cross-sectional dimension or width of the tube 101 and a distance between the opposing webs 114 defines a wide cross-sectional dimension or depth of the tube 101.

[0036] A seam 104 of the tube 101, extending the length of the tube 101, includes a pair of flanges 106 extending into the internal volume 108. The seam 104 is formed in one of the sidewalls 112 of the tube 101, and as such, the flanges 106 extend across the width of the tube 101. The flanges 106 extend completely across the tube 101 such that an edge of each flange 106 contacts the opposite sidewall 112 of the tube 101, and in a preferred embodiment, a seal is formed between the flanges 106 and the opposite sidewall 112. The flanges 106 thus divide the internal volume 108 into two separate channels 116 on each side of the flanges 106. The two channels 116 are wing-shaped sections 130 of the inner volume 108. The wings 130 in the inner volume 108 extend laterally away from the flanges 106 relative to the length of the tube 101.Preferably, the seam 104 in the center of the side wall 112 is formed such that two equally sized channels 116 with a symmetrical wing shape 130 are formed.

[0037] The wings 130 extend in opposite directions away from the pair of flanges 106 and a front portion 132 of each wing 130 is defined in close proximity to the flanges 106, and a rear portion 134 of each wing 130 is defined at a distance from the flanges 106 in close proximity to each web 114 of the tube 101.

[0038] In further embodiments, however, the seal may not always be centrally formed, and in further embodiments, the tube may comprise more than one seam extending along the length of the long tube, so that the internal volume is divided into at least three channels. In this case, the two laterally outermost channels have a wing shape similar to the present invention, and the channel, or each channel, need not necessarily be flared inwardly or outwardly between the outer two channels, but may have a substantially uniform cross-sectional shape.

[0039] The folded tube 101 further includes a first end portion 136 at a first end 138 of the tube 101 and a second end portion (not shown) at an opposite second end of the tube 101. In operation, the first and second end portions 136 extend over corresponding openings 140 in the first and second headers 120 of the heat exchanger to mate the tube 101 with the headers 120. An intermediate or middle portion 142 of the tube 101 extends the length of the tube 101 between the first and second end portions 136. The first and second end portions have the same shape and are each a mirror image of each other.

[0040] The vanes 130 in the intermediate region 142 are flatter than the vanes 130 in the respective first and second end regions 136. The cross-sectional shape of each channel 116 in the intermediate region 142 in a plane perpendicular to the length of the tube 101 inherently has a higher aspect ratio than the cross-sectional shape of each channel 116 in the end regions 136.

[0041] In this example, a width of the rear portion 134 of each wing 130 in the end regions 136 is greater than a corresponding width of the rear portion 134 of the wings 130 in the intermediate region 142, thereby forming flared end regions. This increase in the width of the tube 101 in the flared end regions 136 increases the radius of curvature of each land 114 of the tube 101 in these regions.

[0042] In a particularly preferred embodiment, the width of the front portion 132 of each wing 130 in the end regions 136 is not increased relative to the width of the front portions 132 of the wings 130 in the intermediate region 142. This results in the end regions 136 having substantially teardrop-shaped wings 130, and the cross-sectional shape of the tube 101 in the end regions 136 being substantially figure-eight in shape.

[0043] The limited width of the front portions 132 of the vanes 130 means that the flanges 106 still extend across the full width of the fluid flow channel 108, and the division of the channel into the two channels 116 is maintained. Accordingly, the strength and stiffness of the tube 101 in the end regions 136 are not significantly affected.

[0044] The Fig. 7 and Fig. 8 show an end region 136 of a folded tube 101 according to the present invention, which is connected to a header tube 120 of a heat exchanger.

[0045] As in Fig. 7, the depth of the end region 136 of the tube 101 is less than the depth of the intermediate region 142 of the tube 101. The increase in the width of the vanes 130 in the end region 136 results in a corresponding increase in depth, i.e., a length of a narrow dimension of each vane 130 in the intermediate region 142 is increased, and a length of a wide dimension of each vane 130 is reduced. As such, the circumferential lengths of the cross-sections around the tube 101 in a plane perpendicular to the length of the tube 101 are preferably substantially the same in both the intermediate region 142 and the two end regions 136.

[0046] In a preferred method of manufacturing the tubes 101 according to the present invention, a folded tube is first manufactured in a manner known from the prior art. A split mandrel 150, shown in the Fig. 9a and Fig. 9b, is then used to locally deform one or both end regions 136 of the tube 101. A recess 152 in the mandrel 150 is dimensioned to accommodate the seam 104 of the folded tube 101, formed by the flanges 106, and to protect this portion of the tube 101 from deformation. In this way, the seal formed by the flanges 106 between the two wings 130 of the tube 101 is maintained, while primarily the rear portion 134 of the wings 130 is deformed.

[0047] The folded pipe 101 according to the present invention thus has several advantages over prior art pipes. First, the increased radius of curvature of the webs 114 of the end regions 136 at the interface with the manifold 120 reduces the stress concentrations in this area. This, in turn, reduces the probability of failure in this part of the pipe / manifold joint.

[0048] To reduce stress concentrations at the junction between the headers and prior art collapsible tube designs, the shape of the header plates is typically altered to redistribute stresses along the tube / header junction. In particular, it is known to use a header plate having a generally trapezoidal cross-sectional shape rather than a conventional flat header plate. According to the present invention, the lower aspect ratio of the end portions 136, in combination with the increased radius of curvature of the webs 114 of the tube 101, enables the formation of a flared rim or sleeve 160 around the opening 140 in the header tube 120 for receiving the end portion 136 of the collapsible tube 101. The flared sleeve 160 is preferably formed by stamping the header plate 120.

[0049] In the embodiment of the Fig. 7 and Fig.In the tube / manifold combination shown in Figure 8, the flared sleeve 160 is formed in a generally flat manifold plate 120. The sleeve extends from a front surface 162 of the manifold plate 120 toward the end 138 of the tube 101. The sleeve 160 reduces stress concentrations by increasing the area of ​​the joint between the manifold and the tube. In addition, the shape of the edge 164 of the sleeve 160 across the width of the header tube 120 is preferably substantially trapezoidal, such that a central region 166 of the sleeve 160 in the immediate vicinity of the seam 104 of the tube 101 intersects the tube 101 farther from the end 138 of the tube 101 than in the outer regions 168 of the sleeve 160 in the immediate vicinity of the webs 114 of the tube 101. This geometry of the edge 164 of the sleeve 160 distributes stresses more evenly along the tube / header tube joint, thereby increasing the life to failure of the header tube 120.In particular, the higher stresses caused by twisting of the header tube 120 and bending of the tubes 101 during temperature changes are now distributed within a central section of the header tube 120 in the immediate vicinity of the seam 104 of the tube 101, and thus separated from the areas with the greatest stress concentrations around the webs 114 of the tube 101.

[0050] A second advantage of the present invention over prior art tubes is the reduction of pressure losses at the ends of the tubes. The higher aspect ratio of the geometry of prior art tube designs leads to undesirable inlet and outlet pressure losses at the interface between the end of the tube and the header tube. The flared end portions 136 of the tube 101 according to the present invention have a relatively lower aspect ratio of their geometry compared to prior art tubes. Due to the geometry of the opening at the end 138 of the tube 101, the inlet and outlet pressure losses are reduced per se, thereby increasing the overall efficiency of the heat exchanger.However, the aspect ratio of the intermediate region 142 and the tube 101 remains unchanged compared to prior art folded tube designs, and the surface-to-volume ratio in this part of the tube 101 is not significantly affected as such.

[0051] A third advantage of the tube 101 according to the present invention is that the reduced depth of the end regions 136 of the tube 101 allows a reduction in the width W2 of the header tube 120 compared to the width W1 of the header tube used in prior art folded tubes 1. The overall size of the header tube 120 and the heat exchanger can thus be reduced according to the present invention.

[0052] Although the above-described embodiment of the folding tube includes a flared end portion 136 at both ends 138 of the tube 101, it should be recognized that the tube 101 may also include a flared end portion 136 at only one end 138 of the tube 101.

[0053] The present invention thus provides an improved folded tube for a heat exchanger which has several advantages over prior art tube designs. List of reference symbols 1,101 pipe, folding pipe 2 Longitudinal axis 4,104 seam 6.106 flange, seam flange 8.108 internal volume, fluid flow channel 10,110 outer wall 12 wide section 14 narrow section 16, 116 channel 20, 120 manifold 22 Pipe connection 112 side wall 114 narrow wall section, bridge 116 Channel 120 manifold plate, manifold 130 wings, wing-shaped sections 132 front section 134 rear section 136 End area 138 End 140 opening 142 intermediate area, middle area 150 mandrel 152 recess 160 sleeve 162 front 164 Rand 166 Middle range 168 outer area W1 Width 1 W2 Width 2

Claims

[1] Heat exchanger, comprising: a long tube (101) for the heat exchanger, and at least one collecting pipe (120) having at least one opening (140), wherein at least one end region (136) of the long pipe (101) extends through the opening (140) to connect the pipe (101) to the collecting pipe (120), wherein the tube (101) comprises: - a first end and a second end for connection to first and second manifolds (120) of the heat exchanger, respectively; - an outer wall (110), wherein the outer wall (110) encloses an inner volume (108), wherein the inner volume (108) has at least two channels (116) for conveying the heat transfer fluid over the length of the tube (101) between the first and second header tubes (120); and - at least one seam (104) in the outer wall (110) extending over the length of the tube (101), wherein the seam (104) or each seam (104) comprises a pair of opposed flanges (106), wherein the pair of opposed flanges (106) extends into the inner volume (108) so that the inner volume (108) is divided into the two channels (116), and wherein the outer wall (110) is joined over the length of the seam (104) or the seams (104), wherein the long tube (101) has a first end region (136) in the immediate vicinity of the first end (138) and a second end region (136) in the immediate vicinity of the second end (138) and an intermediate region (142) between the first and the second end region (136), wherein the tube (101) is flattened over its entire length so that the flanges (106) divide the inner volume (108) into at least two flattened wings (130), wherein each wing (130) provides one of the channels (116) and each wing (130) extends laterally away from the flanges (106) relative to the length of the tube (101), and at least two of the wings (130) in the intermediate region (142) are flatter than previously described compared to the wings (130) in at least one of the end regions (136), wherein each wing (130) in the at least one end region (136) is flatter in a front section (132) in the immediate vicinity of the flanges (106) than in a rear section (134) which is further away in the laterally direction relative to the length of the tube (101), wherein the rear portion (134) further away from the flange (106) has a web (114), a side wall (112) extending laterally from the web (114) and having an inclined wall, wherein the converging wall portions of the side wall (112), starting from the web (114), adjoin a flat wide wall portion and open into the front portion (132), form the inclined wall, wherein two wide wall sections of the outer wall (110), which are arranged between narrow wall sections, form the side walls (112) and the two narrower wall sections form the webs (114), wherein the front portion (132) has a side wall (112) near the flange (106) extending laterally from the inclined wall, wherein the collecting tube (120) has a flared edge (164) extending around at least part of the circumference of the opening (140), the end region (136) of the tube (101) being connected to the flared edge (164), and wherein the shape of an edge of the flared rim (164) across the width of the header tube (120) is trapezoidal, such that a central region of the flared rim (164), near the seam (104) of the tube (101), intersects the tube (101) farther from the end of the tube (101) than outer regions of the flared rim (164) near the lands (114) of the tube (101). [2] Heat exchanger according to claim 1, wherein the outer wall (110) has opposite wide wall sections, the wide wall sections being widened outwardly from the intermediate region (142) towards the first end (138). [3] Heat exchanger according to claim 1 or 2, wherein the outer wall (110) has opposite wide wall sections, the wide wall sections being widened outwardly from the intermediate region (142) towards the second end (138). [4] Heat exchanger according to one of the preceding claims, wherein the outer wall (110) has opposite narrow wall sections, the narrow wall sections being widened inwardly from the intermediate region (142) towards the first end (138). [5] Heat exchanger according to one of the preceding claims, wherein the outer wall (110) has opposite narrow wall sections, the narrow wall sections being widened inwardly from the intermediate region (142) towards the second end (138). [6] Heat exchanger according to one of the preceding claims, wherein at least one of the flanges (106) is connected along its length to a portion of the outer wall (110) opposite the corresponding seam (114) so ​​that adjacent channels (116) on opposite sides of the flanges (106) are not in fluid communication with each other. [7] Heat exchanger according to one of the preceding claims, wherein the vanes (130) in the intermediate region (142) extend further away from the pair of flanges (106) than the vanes (130) in the at least one end region (136). [8] Heat exchanger according to one of the preceding claims, wherein the outer wall (110) has a uniform thickness. [9] Heat exchanger according to one of the preceding claims, wherein the circumferential length of the cross sections around the tube (101) in a plane perpendicular to the length of the tube (101) in the intermediate region (142) and in the at least one end region (136) are the same. [10] Heat exchanger according to one of the preceding claims, wherein the vanes (130) on opposite sides of the flanges (106) are symmetrical.

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