BR102012029871A2 - HEAT EXCHANGE TUBE, HEAT EXCHANGE TUBE ASSEMBLY AND MANUFACTURING METHODS - Google Patents

Abstract

HEAT EXCHANGE TUBE, HEAT EXCHANGE TUBE ASSEMBLY AND MANUFACTURING METHODS. A tube for use in a tube assembly for a heat exchanger includes a flat section located away from a tube end. The flat section includes broad, flat, parallel pipe sides joined by narrow sides, so that the pipe is relatively thin in one direction. A cylindrical section extends from the pipe end, and a transition section connects the cylindrical section and the flattened pipe section. The geometry of the transition section provides flexural strength at the intersection between the flat tube section and the transition section.

Description

HEAT EXCHANGE TUBE, HEAT EXCHANGE TUBE ASSEMBLY AND MANUFACTURING METHODS

FIELD OF THE INVENTION The present invention generally relates to tubes, fin and tube assemblies and heat exchangers, and methods for their manufacture.

BACKGROUND

Large scale heat exchangers incorporating individually replaceable tube assemblies having a tube for conveying a first fluid and a secondary heat transfer surface area for a second fluid transferring heat to or from the first fluid are well known. As an example, heat exchangers of this type operating as heavy-duty equipment radiators for the transfer of residual heat from an engine to air cooler have been described in Murray US Patent No. 3,391,732, and US Patent No. No. 4,236,577 to Neudeck. The pipe assemblies used in these heat exchangers have a central fin section for heat exchange and cylindrical end sections without fin for insertion into sealing rings.

Heat exchanger tube assemblies of the type described above are typically constructed of copper, with the air side surfaces extended in the fin region being welded to the tube. Copper provides the advantages of high thermal conductivity, easy fabricability, and good strength and durability. However, the ever-rising price of copper has led to a demand for lower cost alternative materials. Aluminum has replaced copper as the preferred building material in other heat exchangers (automotive and commercial radiators, for example), but has not successfully replaced copper in heavy-duty heat exchangers of this type. Aluminum has substantially lower strength than copper, leading to durability issues. This is especially problematic in applications where individual pipe assemblies need to be removed and inserted into the field as damage may occur during handling. Moreover, the bonding of aluminum components requires substantially higher temperatures than copper welding, leading to manufacturing difficulties. Thus, there is still room for improvement.

SUMMARY

According to one embodiment of the invention, a tube assembly for a heat exchanger includes a tube having a flat section with spaced wide tube sides joined by opposite narrow tube sides. The tube assembly further includes two fin structures, each having corrugated and dug ridges connected by flanks, and two generally flat side sheets. The wave troughs of a vane structure are joined to one side of the broad tube, and the wave ridges of that vane structure are joined to one side of a side sheet. The wave troughs of the other fin structure are joined to the other side of the broad tube, and the wave ridges of that fin structure are joined to one face of the other side sheet.

In some embodiments, the tube includes cylindrical sections at the ends along the length of the tube, with the flat section disposed between the cylindrical sections. In some embodiments, the tube, fin structures and side sheets are joined by brazing joints, and in some embodiments they are formed of one or more aluminum alloys. In some embodiments, the thickness of the wide pipe sides is at least twice the thickness of the side sheets.

In another embodiment of the invention, a tube assembly for a heat exchanger includes a fluid flow conduit extending in a lengthwise direction over at least a portion of the tube assembly. The fluid flow conduit has a larger dimension and a smaller dimension, both perpendicular to the lengthwise direction, the smaller dimension being substantially smaller than the larger dimension. A continuous tube wall surrounds the flow conduit. Two generally flat side sheets are spaced equidistantly from the continuous tube wall in the direction of the smallest dimension, and are connected to the tube wall by thin souls.

In some of these embodiments, the continuous tube wall defines a tube wall centroid moment of inertia with respect to a geometry axis in the largest dimension direction. In some embodiments, the centroid inertia moment of the tube assembly with respect to that geometric axis is at least five times the pipe wall centroid inertia moment, and in some embodiments at least ten times.

In some embodiments, a first cylindrical tube section is joined to the continuous tube wall at a first end of the flow duct, and a second cylindrical tube section is joined to the continuous tube wall at a second end of the flow duct. In some of these embodiments, the outer perimeter defined by the continuous tube wall is larger than the outer perimeter of at least one of the cylindrical tube sections.

According to another embodiment of the invention, a method of manufacturing a heat exchange tube assembly includes providing a tube, first and second corrugated fin structures and generally flat first and second side sheets. The first corrugated fin structure is disposed between the first side sheet and the first broad and flat side of the tube, and the second corrugated fin structure is arranged between the second side sheet and a second broad and flat side of the tube. A compressive force is applied to opposite sides of the side sheets for replacing ridges and ridges of the fin structures in contact with the broad flat side sides and sides, and brazing joints are created between the first fin structure and the first side sheet, the first flap structure and the first broad flat side, the second flap structure and the second side sheet, and the second flap structure and the second broad and flat side.

In some of these embodiments, the pipe, fin structures and side sheets have the elevated temperature in a vacuum environment for the creation of brazing joints. In other environments, they have the elevated temperature in a controlled inert gas environment. In some embodiments, the provision of a pipe, fin structures and side sheets includes the provision of a material coated with a brazing filler metal.

In some embodiments, the compressive force is transmitted through a first separating sheet adjacent to the first side sheet, and through a second separating sheet adjacent to the second side sheet. In some of these embodiments, the separator sheets have a coefficient of thermal expansion which is generally combined with that of the tube, side sheets and fin structures. In some embodiments, the first side sheet is one of several separating sheets adjacent the first side sheet.

According to another embodiment of the invention, a method of manufacturing heat exchange tube assemblies includes the provision of multiple tubes, various corrugated fin structures and various generally flat side sheets. Each of the tubes is disposed between pairs of corrugated fin structures, and each of the corrugated fin structures is disposed between one of the tubes and one of the side sheets. The tubes, corrugated fin structures and side sheets are arranged in a stack. The separator sheets are arranged between adjacent pairs of side sheets, and adjacent to the side sheets at the outermost ends of the stack. A compression load is applied to the stack in the stacking direction. Brazed joints are created at the points of contact between the corrugated vane structures and the tubes, and between the corrugated vane structures and the side sheets, and the brazed tube assemblies are removed from the separator sheets.

In some of these embodiments, pipes, fin structures, and side sheets are elevated in a vacuum environment for creating brazed joints. In other environments, they have the elevated temperature in a controlled inert gas environment. In some embodiments, the provision of pipes, fin structures and side sheets includes the provision of a material coated with a brazing filler metal.

According to another embodiment of the invention, a tube for a heat exchanger includes a first cylindrical section extending from a first end of the tube, a second cylindrical section extending from a second end of the tube, and a section located between the ends and having two wide and spaced parallel sides spaced together by two relatively short sides. The transition regions are located between each of the cylindrical sections and the flat section. The intersections of the transition regions and each of the wide flat sides of the tube define curvilinear paths.

In some of these embodiments, the two relatively short sides are arcuate in profile. In some embodiments, each curvilinear path includes a vertex located in a central plane of the tube, and in some of these embodiments, an arcuate path segment is located at the vertex.

In some embodiments, the transition region adjacent one of the cylindrical sections extends for a length that is at least equal to the diameter of that section. In some embodiments, the outer perimeter of the flattened section of the pipe is larger than the outer perimeter of at least one of the cylindrical sections, and in some embodiments is at least twenty-five percent larger.

In some embodiments, the flattened tube section defines a larger tube size between outermost points on both relatively short sides, and the curvilinear paths are each longer than the larger tube size. In some embodiments, the tube is made from an aluminum alloy.

According to another embodiment of the invention, a heat exchange pipe is formed from a round pipe by reducing a diameter of the round pipe into a first section of the round pipe and flattening a second section adjacent to the first section. for the definition of two wide flat sides spaced in the second section. In some embodiments, the first section ends at one end of the tube. In some embodiments, the second section is flattened after reducing the diameter of the first section.

In embodiments, the diameter of the first section is reduced by a rotary forging operation. In some embodiments, the second section is flattened by the impact of that section on a stamping die. In some embodiments, the tube is made from an aluminum alloy.

In some embodiments, a mandrel is inserted into the tube prior to flattening the second section and is removed from the tube after flattening the second section.

In some embodiments, the diameter of a third section of the round tube is reduced, the third section being adjacent to the second section. In some of these embodiments, the third section ends at a second end of the tube. In some embodiments, the second section is flattened after reducing the diameter of the third section.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a perspective view of a heat exchange tube assembly according to one embodiment of the invention. Figure 2 is an elevation view of the heat exchange tube assembly of Figure 1. Figure 3 is a detailed view of the portion of Figure 2 delimited by line III-11. Figure 4 is a plan view of the heat exchange tube assembly of Figure 1. Figure 5 is an exploded perspective view of the heat exchange tube assembly of Figure 1. Figure 6 is an elevation view of a stack of heat exchange tube assemblies being made according to one embodiment of the invention. Figure 7 is a plan view of certain components of the stack of Figure 6. Figure 8 is a perspective view of a heat exchange tube according to an embodiment of the invention. Figure 9 is a partial perspective view of a prior art heat exchange tube. Figure 10 is a partial cross-sectional view along lines XX of Figure 8. Figure 11 is a cross-sectional view along lines XI-XI of Figure 8. Figure 12 is a partial perspective view of the partially formed tube of figure 8.

Figures 13A and B are diagrammatic views of a forming operation for producing the tube of Figure 8.

DETAILED DESCRIPTION

Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or performed in various ways. Also, it is to be understood that the phraseology and terminology used herein is for purposes of description, and should not be construed as limiting. The use of "including", "comprising" or "having" and variations thereof thereof is meant to encompass the items listed hereinafter and their equivalents as well as additional items. Unless otherwise specified or limited, the terms "mounted", "connected", "supported" and "coupled" and variations thereof are used widely and involve direct and indirect mounts, fittings, brackets and couplings. Also, "connected" and "coupled" are not restricted to physical or mechanical connections or couplings.

A heat exchange tube assembly 1 according to one embodiment of the invention is shown in Figures 1 to 5. Such a tube assembly 1 can be used as one of many individual heat exchanger tubes, for example a radiator, on a large heavy load equipment such as an excavator, a mining truck, a generator and engine assembly, etc. It should be understood, however, that tube assembly 1 may be used in heat exchangers of various types and sizes. Tube assembly 1 includes a tube 2 extending from a first end 7 to a second end 8. Tube 2 defines a fluid flow conduit whereby a fluid (by way of example, a coolant of may be transported through tube assembly 1. As an example, tube assembly 1 may be used in an engine cooler radiator so as to reject the residual heat from an engine coolant flow, depending on that flow. of engine coolant flow through the pipe 2 from one end 7,8 to the other ends 7,8. The pipe 2 includes a flat section 3 located between the ends 7,8. The flat section 3 (better described with reference to FIG. 11) includes first and second parallel broad and flat sides 12. The broad and flat sides 12 are spaced apart, and are joined by two opposite spaced narrow tube sides 15. Although the narrow tube sides 15 are show As being bent profile in the exemplary embodiment, in other embodiments, the narrow tube sides 15 may be straight, or they may be of some other profile shape. The two broad flat sides 12 and the two narrow sides 15 together define a continuous pipe wall 25 of the fluid flow duct, with defined open spaces interior to the continuous pipe wall 25, to allow fluid flow. Although none are shown in the exemplary embodiment, it may be preferable in some cases to provide surface improvement or flow swirling features in the flow duct so as to improve the heat transfer rate between a fluid passing through tube 2 and tube wall 25.

Continuing with reference to Figure 11, the flat section 3 of the tube 2 has a smaller tube dimension, d1, defined as the distance between the outwardly facing surfaces of the two broad and flat sides 12, and a larger tube dimension, d2, defined as the distance between the outermost points of the two narrow sides 15. In some highly preferable embodiments, the largest dimension, d2, is several times greater than the smaller dimension, dl. As an example, the largest dimension of the example embodiment is nine times larger than the smallest dimension. The tube assembly 1 further includes two convoluted fin structures 10 disposed along the flat section 3. The fin structures 10 include multiple flanks 16 alternately connected by ridges 18 and dug 17 so that each of the fin structures 10 is approximately sinusoidal in shape (best seen in Figure 3). The vane structures 10 may be of a flat type as shown in Figure 3, or they may include additional features for increased heat transfer, structural strength, durability, or combinations of the above. By way of example, in some embodiments, fin structures 10 may include shutters, protrusions, slits, harpoons or other features that are known to improve heat transfer and / or structural stiffness of flanks 16. In other embodiments, a Edge sheath may be provided at one or both ends of a vane structure 10 adjacent to narrow tube sides 15. Such an edge sheath may be especially beneficial in providing resistance to damage that can be caused by rock impingement. or other waste.

Thin side sheets 11 may also be included in tube assembly 1. These side sheets 11 are parallel to the opposite wide flat sides 12 of tube 2 and are spaced equidistantly on either side by the flap structures 10. Thus, the flanks 16, the ridges 18 and dug 17 of the fin structures 10 provide a plurality of thin souls for spacing the side sheets 11 of the continuous tube wall 25. The side sheets 11 are generally flat, but may include features such as bent edges, for example, to provide increased stiffness and / or to aid assembly.

The spaces between the flanks 16 provide flow channels for a fluid to be placed in a heat transfer relationship with the fluid passing through the tube 2 so that heat can be exchanged between the two fluids. As an example, ambient air may be directed through the flow channels to cool the engine jacket cooler by passing through pipe 2. It should be understood, however, that various other fluids may be placed in a ratio of heat transfer using tube assembly 1. Each of the flow channels between the flanks 16 is further defined by one of the troughs 17 and ridges 18, and one of the flat sides 12 of tube 2 and the generally flat side sheets 11 By completely enclosing the flow channels in this manner, fluid passing through those channels is prevented from prematurely exiting the channels, thereby improving the ability to transfer heat. Tube 2, fin structures 10 and side sheets 11 are preferably bonded together to form a monolithic structure so as to provide good thermal contact between the fluids to be placed in a heat transfer ratio and good structural integrity. Although a variety of materials may be used to construct tube assembly 1, in highly preferred embodiments, tube 2, vane structures 10 and side sheets 11 are formed from metals having a high thermal conductivity, such as aluminum, copper and the like. The components may be joined together for forming tube assembly 1 by a variety of processes including brazing, welding, gluing, etc.

In order to promote good heat transfer between the fluids, it may be advantageous for the flap structures 10 and the side sheets 11 to extend over the full larger dimension d2 of the flat section 3. In some cases, it may be preferable to extend the flange structures. vane 10 and side sheets 11 slightly beyond the outer edges of narrow tube sides 15 to protect the fluid flow conduit from damage by rock or other debris. The inclusion of even very thin side sheets 11 has been shown to greatly stiffen tube assembly 1, especially with respect to bending around the centroid geometry on the larger tube dimension d2. The fin structures 10 provide very little stiffness in this direction due to their convoluted nature, so that in the absence of the side sheets 11 the continuous tube wall 25 provides only the flexural strength around that centroid geometrical axis. Due to the relatively smaller minor dimension dl of that flat tube section 3, the flexural strength around that centroid geometry by the continuous tube wall 25 is only reasonably small, and the spacing of the side sheets 11 of that centroid geometry by a distance substantially greater than the smaller dimension dl provides a substantial benefit. The impact of the side sheets 11 on the flexural stiffness of the tube assembly 1 about the centroid geometry on the larger tube dimension d2 can be quantified by comparing the centroid inertia moment around that geometry of the tube assembly 1 with that of tube 2 alone (vane structures 10 may be assumed to provide no contribution to the centroid inertia moment apart by maintaining the displacement of the side sheets 11 of the flattened sides 12 of tube 2). For an exemplary embodiment having a pipe wall thickness of 0.8 mm, a side sheet thickness of 0.25 mm, a fin frame height of 6.55 mm, a smaller dimension of 3.7 mm and larger than 23.27 mm, the centroid moments of inertia around the largest tube geometry for the tube assembly and the tube alone are calculated to be 925 mm4 and 76 mm4, respectively. In other words, the centroid moment of inertia of the tube assembly about the largest tube geometry is approximately twelve times that of the tube itself. In preferable embodiments, the centroid moment of inertia of the tube assembly about the larger tube geometry is equal to at least five times that of the tube itself, and in highly preferable embodiments at least ten times. This is especially preferable when tube 2 is constructed of a material exhibiting a relatively low modulus of elasticity, for example aluminum alloys. The tube 2 of the exemplary embodiment further includes a first cylindrical section 4 adjacent to the first end 7, and a second cylindrical section 5 adjacent to the second end 8, with the flat section 3 disposed between the first and second cylindrical sections. These cylindrical sections 4, 5 allow reliable and leak-free insertion of pipe assembly 1 into insulation rings arranged on opposite collectors of a heat exchanger (not shown). In order to maximize the amount of pipe available for effective heat transfer, the length of the cylindrical end sections is preferably kept to a minimum, and the length of the flat section 3 is preferably 90% or more of the overall length of the pipe. 2. A circumferential rib 9 is provided in the cylindrical section 5 of the exemplary embodiment to limit downward movement of tube assembly 1 when vertically disposed in a heat exchanger.

While the exemplary embodiments shown in the accompanying figures include the cylindrical end sections at both ends of the pipe, it should be understood that in some cases the pipe assembly 1 may be devoid of one or both cylindrical end sections 4, 5. When these cylindrical end sections are not included, the corresponding receive isolation rings may be provided with receive openings that correspond to the continuous pipe wall profile 25 in the flat section 3.

In certain preferred embodiments of the invention, a heat exchange tube assembly 1 is made by creating brazing joints between an aluminum tube 2, first and second corrugated fin structures 10, and first and second aluminum side sheets 11. The first corrugated fin structure 10 is disposed between the first side sheet 11 and a first broad and flat side 12 of tube 2, while the second corrugated fin structure 10 is disposed between the second side sheet 11 and a second broad and flat side. 12 of tube 2. The assembly is compressed so that the ridges 18 and dug 17 of the vane structures 10 are in contact with adjacent parts so that the brazing joints can be formed at the contact points.

A brazing filler metal having a melting temperature that is lower than the melting temperatures of tube 2, vane structures 10, and side sheets 11 is used for the creation of brazing joints. Such a filler metal is typically aluminum with small amounts of other elements (silicon, copper, magnesium and zinc, for example) added to reduce melting temperature. The brazing filler metal may advantageously be provided as a coating on one or more of the components to be brazed. In some embodiments, both sides of the sheet material used for forming the corrugated fin structures 10 are coated with brazing filler metal, thereby providing the brazing filler metal required at all contact points where Brazing joints are desired, while avoiding having brazing filler metal in locations where joints are not required or undesirable.

While many methods can be used to raise the temperature of pipe 2, vane structures 10, and side sheets 11 to fuse brazing filler metal and form brazing joints, two especially preferable methods are brazing. vacuum and controlled atmosphere brazing. In vacuum brazing, the assembled parts are placed in a sealed oven and substantially all air is removed to create a vacuum environment. In this process, the magnesium present in the alloys is released as the parts are heated and serves to break the oxide layer present on the outer surfaces of the components, allowing the molten brazing filler metal to bond to the exposed aluminum. The oxide layer is prevented from re-forming and interfering with metallurgical bonding by the absence of oxygen in the vacuum environment.

In a controlled atmosphere brazing, a flux is applied to the components before heating. The heating of the parts takes place in an inert gas environment so as to avoid reformation of the oxide layer after the flow reacts and displace the oxide layer present on the combination surfaces of the parts. With the oxide layer shifted, the molten brazing filler metal binds to exposed aluminum to create brazed joints.

It may be especially preferable to braze several of the pipe assemblies 1 at a time, in order to increase the production rate in a production manufacturing environment. Figure 6 illustrates a method according to one embodiment of the invention, wherein four tube assemblies 1 are made simultaneously. It should be understood that the same method may be used for manufacturing more than four or less than four of the pipe assemblies at one time.

In the embodiment of Figure 6, tubes 2, corrugated fin structures 10 and generally flat side sheets 11 are provided. Each of the tubes 2 is disposed between pairs of corrugated fin structures 10, and each of the corrugated fin structures 10 is disposed between one of the tubes 2 and one of the generally flat side sheets 11. The separator sheets 19 are arranged between adjacent pairs. of the generally flat side sheets 11. The tubes 2, the corrugated fin structures 10 and the generally flat side sheets 11 are arranged in a stack 26. The additional separating sheets 19 are arranged adjacent to the generally flat side sheets 11 at the outermost ends of the stack 26, and a compression load is applied to stack 26 in the stacking direction so that the ridges 18 and dug 17 of the convolute fin structures are brought into contact with the adjacent side sheets 11 and the broad flat sides 12 of the tubes 2.

In order to provide a uniform compressive load to the stack 26, bars 21 having a high stiffness (e.g., structural steel channels) may be used at the outermost ends of the stack 26. The compressive load may be maintained after being applied to the stack. through the use of metal bands 22 surrounding the stack 26 at various locations. The bands 22 are tightened over the bars 21 while the stack 26 is compressed, so that attraction in the bands 22 maintains the compressive load. After so assembled, the stack 26 is placed in a brazing furnace to create the individual tube assemblies 1. The stack 26 is heated inside the furnace to a temperature suitable for melting the filler metal. brazing, after which the stack 26 is cooled to solidify the molten brazing filler metal again, thereby brazing joints at the contact points. After cooling, the individual tube assemblies 1, having been brazed into individual monolithic structures, may be removed from the separator sheets 19. The separator sheets 19 may be provided with a coating to prevent any metallurgical bonding between the separator sheets 19 and the side sheets 11, since such an undesirable bond may otherwise occur at the brazing temperature even without the presence of a brazing filler metal.

As stack 26 is heated to a brazing temperature, thermal expansion of the metal materials in stack 26 will occur. In aluminum brazing, the components typically are heated to a brazing temperature of 550 ° C to 650 ° C. This temperature range is substantially higher than that used for welding copper components, and consequently the thermal expansion experienced by the components of the pipe assemblies 1 during the bonding process is substantially greater if the components are aluminum of the that if they are copper.

The inventors have found that care should be taken during the brazing process to ensure that the corrugated fin structures 10 are not distorted by heating to a brazing temperature and cooling back to room temperature. Unlike a traditional brazed aluminum radiator fabrication involving multiple rows of tubes and fin structures joined together in a monolithic brazed core, the flanks 16 of corrugated fin structures 10 are prone to distortion by shear forces introduced through Differences in thermal expansion between the components of the tube assemblies 1 and the separator sheets 19. In some embodiments of the invention, this problem is remedied by generally combining the coefficient of thermal expansion of the separator sheets 19 with that of the pipes 2 of corrugated fin 10 and side sheets 11. This can be achieved by forming the separator sheets 19 from similar aluminum alloys, or from another material exhibiting a similar rate of thermal expansion.

Alternatively or additionally, multiple individual separator sheets 19 may be used between each adjacent tube assembly 1 as shown in Figure 7. Spaces 20 are provided between adjacent individual separator sheets 19. In the case where separator sheets 19 are constructed of a material having a coefficient of thermal expansion substantially different from that of the materials from which pipes 2, corrugated fin structures 10 and side sheets 11 are constructed, spaces 20 may increase or decrease during heating and cooling of the material. stack 26, thereby substantially alleviating the distortion of corrugated fin structures 10 which might otherwise result from the mismatch of thermal expansion coefficients. The spaces 20 serve as breaks to prevent the accumulation of thermal expansion-induced distortion, so that any such distortion is limited to the discrete contact areas below each of the individual separator sheets 19. The mounting method described in Figure 7 It may be especially beneficial when a more temperature resistant material, such as stainless steel, is used for the separator sheets 19, and the components of the tube assemblies 1 are made of aluminum. Tube 2 will now be discussed in more detail with specific reference to Figures 8 to 13. As previously described, the embodiment of tube 2 shown in Figure 8 includes a flattened tube section 3 located between a first cylindrical tube section 4 and a second cylindrical tube section 5. The first cylindrical tube section 4 extends from the first end 7 of tube 2, while the second cylindrical tube section 5 extends from the second end 8 of tube 2. The transition regions 6 are located between the flat section 3 and each of the cylindrical sections 4 and 5. The transition regions 6 provide a smooth continuous flow path for a fluid passing through the tube 2, as well as avoiding locations of mechanical stress concentration in the material. of tube.

As shown in detail in the partial cross-sectional view of Figure 10, a transition region 6 extends over a length L, which covers from a location 27 proximal to the end 7 of the tube 2 to a distal location 14 of the end 7. The length L preferably it is at least equal to the diameter of the cylindrical end section 4, although in some alternative embodiments it may be smaller in size than the corresponding end section diameter. As seen in Figure 8, the wide flat side 12 extends in front of locations 14 at either end, so that at least a portion of the wide flat side 12 is located along the tube 2 between the defining locations 27 and 14. the beginning and end of a transition region 6.

In preferred embodiments, the intersections of the transition regions 6 and the broad flat sides 12 of the flat tube section 3 define curvilinear paths 13. These curvilinear paths 13 provide a beneficial stiffening of the flat section 3 of tube 2 with respect to a moment at bending around the larger pipe geometry. For comparison, a prior art tube 102 is shown in Figure 9, and includes a flat section 103 joined to a cylindrical section 104 by means of a transition region 106. The intersection of transition region 106 and flat section 103 defines a straight path 113 on the wide flat side 112 of the flat section 103. The straight path 113 extends over the larger tube dimension, and bending around the larger geometrical axis is fairly easy. This can be especially detrimental during installation and / or removal of a tube assembly containing tube 102 from a heat exchanger, as such installation and removal often applies moments of such bending to the tube. This problem is especially exacerbated when the pipe is constructed of a reasonably low strength material such as annealed aluminum.

The inventors have found that the curvilinear path 13 provides a substantial stiffening effect for one-time bending strength of the mentioned type, and prevents buckling or other damage to tube 2 during installation, removal and any other handling of tube 2 or a tube assembly 1 containing a tube 2. While a benefit may be derived from any nonlinear path, it may be especially beneficial for path 13 to be defined by a series of connected arcuate path segments.

In the exemplary embodiment, each of the curvilinear paths 13 includes a vertex located in the approximate central plane of the tube, so that the vertex is located at point 14 along the path 13 that is farthest from the end 7 (in case the region between the flat section 3 and the first cylindrical end 4) or the end 8 (in the case of the transition region between the flat section 3 and the second cylindrical end 5). The path 13 preferably includes an arcuate path segment at the vertex so that stress concentrations are avoided at the vertex.

In some preferred embodiments, the outer perimeter (i.e. the circumference) of at least one of the two cylindrical sections 4, 5 is smaller than the outer perimeter of the continuous pipe wall 25 in the flat section 3. This advantageously permits a surface area. relatively large heat transfer per unit length in the flat section 3, without requiring a correspondingly large diameter at one or both ends 7, 8. A smaller diameter at the ends may be preferable as it may allow closer spacing of sets of adjacent pipe and requires less sealing surface at the ends, for example. In some preferred embodiments, the outer perimeter of the flat section 3 exceeds the outer perimeter of at least one of the two cylindrical end sections by at least 25%.

Heat exchangers including fluid-bearing pipes having a flattened profile for their entire length are well known in the art and have been used for decades as radiators and the like. Flattened tubes of this type are usually constructed in one of two ways. They are extruded and / or flattened from a billet of material and cut to discrete lengths, or they are created in a tube lamination from a coil sheet by forming the sheet shape into a round shape, by seam welding, roll flattening to the flat tube shape and cutting to discrete tube lengths.

In the case of pipes, such as the prior art pipe 102 (Figure 9) having a flat section 103 and a cylindrical end section 104, the ends of the flat tube are formed into a cylindrical shape for forming the cylindrical end section 104. and transition region 106. This operation can be performed quickly and easily when the pipe is constructed from a highly malleable material such as copper and only requires the extreme ends of the pipe 2 to be formed. However, this method is not able to obtain a transition section 6 as previously described.

The transition regions 6 may be formed by the initial formation of the tube 2 in a round shape having an outside diameter equal to the desired outer perimeter of continuous tube wall 25 in the flat section 3. Next, with specific reference to figure 12, the ends of round tube 2 are reduced in diameter for formation of cylindrical ends 4 and 5, as well as a tapered transition region 6 'between ends 4, 5 and central section 3', which retains the original round shape. This reduction in diameter can be accomplished, for example, by rotating forging of pipe ends. In some preferred embodiments, the ends are of at least 20% reduced diameter so as to obtain the desired ratio of outer perimeters between the flat section 3 and the cylindrical end sections 4,5.

As described in Figures 13A and 13B, the profile of the flat section 3 of tube 2 may be defined by forming that 3 'portion of tube 2 between a first forming die half 22 and a second forming die half 23. The tube 2 is inserted between the matrix halves 22, 23 when the matrix is in an open position, that is, when two matrix halves are separated from each other as in Figure 13A. With tube 2 thus located, the die closes to be in the closed position of figure 13B, thereby forming the flat section 3 of tube 2 for the smallest dimension d1 and the largest dimension d2. Optionally, a mandrel 24 may be positioned in tube 2 prior to the forming operation so as to prevent buckling or other undesirable deformation of the broad and flat tube walls 12 during the forming operation. The mandrel 24, when used, can be removed from tube 2 after the forming operation is completed. The geometry of the transition regions 6 can be produced by including complementary negative representations of the contact faces geometry of the matrix halves 22 and 23, so that the desired geometry of the transition regions 6 is formed in tube 2 during the operation of formation. Various alternatives for certain features and elements of the present invention are described with reference to specific embodiments of the present invention. With the exception of features, elements, and modes of operation that are mutually exclusive to or inconsistent with each embodiment described above, it should be noted that the alternative features, elements, and modes of operation described with reference to a particular embodiment are applicable to other modalities.

The embodiments described above and illustrated in the figures are given by way of example only, and are not intended as a limitation on the concepts and principles of the present invention. As such, it will be appreciated by one having a common knowledge in the art that various changes in elements and their configuration and arrangement are possible without departing from the spirit and scope of the present invention.

Claims (20)

1. Tube for a heat exchanger, characterized in that it comprises: a first cylindrical section extending from a first tube end; a second cylindrical section extending from a second tube end opposite the first tube end; a flattened tube section located between the first and second ends, the flattened tube section comprising two broad and parallel spaced flat sides joined by two relatively short sides; a first transition region located between the first cylindrical section and the first end of the flattened tube section proximal to the first cylindrical section; and a second transition region located between the second cylindrical section and a second end of the flattened tube section proximal to the second cylindrical section, the intersections of each of the first and second transition regions and each of the broad and flat sides defining pathways. curvilinear. Pipe according to Claim 1, characterized in that the two relatively short sides are arcuate in profile. Pipe according to Claim 1, characterized in that each of the curvilinear paths includes a vertex located in a central plane of the pipe. Pipe according to Claim 3, characterized in that each of the curvilinear paths includes an arcuate path segment at the apex. Pipe according to Claim 1, characterized in that the first cylindrical section defines a pipe diameter and the first transition region extends in the axial direction of the pipe for a length at least equal to the pipe diameter. Pipe according to Claim 5, characterized in that the pipe diameter is a first pipe diameter, the second cylindrical section defines a second pipe diameter, and the second transition region extends in the axial direction of the pipe. pipe, for a length at least equal to the second pipe diameter. Pipe according to Claim 1, characterized in that the first cylindrical section defines a first outer pipe perimeter and the flattened pipe section defines a second outer pipe perimeter larger than the first outer pipe perimeter. Pipe according to Claim 7, characterized in that the second outer tube perimeter exceeds the first outer tube perimeter by more than twenty-five percent. Pipe according to Claim 1, characterized in that the flattened pipe section defines a larger pipe dimension between a first outermost point on one relatively short side and a second outermost point on the other relatively short side. , and each of the curvilinear paths is longer than the larger tube dimension. Pipe according to Claim 1, characterized in that at least one of the first and second cylindrical sections includes a circumferential frieze. Pipe according to Claim 1, characterized in that the pipe comprises an aluminum alloy. Tube for a heat exchanger, characterized in that it comprises: a tube end; a flattened pipe section located away from the pipe end, the flattened pipe section comprising two parallel spaced wide and flat sides joined by two relatively short sides; a cylindrical section extending from the pipe end to a proximal first location of the pipe end; and a transition region connecting the cylindrical section and the flattened pipe section and extending in an axial direction of pipe from the first location to a second distal location to the pipe end, wherein at least a portion of the flattened pipe section is between the first location and the second location. Pipe according to Claim 12, characterized in that the transition region tapers to a vertex at the second location. Pipe according to Claim 12, characterized in that the intersection of the transition region and one of the wide flat sides defines a curvilinear path. Pipe according to Claim 12, characterized in that the cylindrical section defines a pipe diameter and the distance in the pipe axial direction between the first and second locations is at least equal to the pipe diameter. Pipe according to Claim 12, characterized in that the cylindrical section defines a first outer pipe perimeter and the flattened pipe section defines a second outer pipe perimeter larger than the first outer pipe perimeter. Pipe according to Claim 16, characterized in that the second outer perimeter exceeds the first outer perimeter of the pipe by more than twenty-five percent. Pipe according to Claim 12, characterized in that the pipe end is a first pipe end, the cylindrical section is a first cylindrical section and the transition region is a first transition region, the pipe further comprising : a second tube end disposed opposite the first tube end; a second cylindrical section extending from the second tube end to a third location proximal to the second tube end; and a second transition region connecting the second cylindrical section and the flattened pipe section and extending in an axial direction of pipe from the third location to a fourth distal location of the second pipe end, wherein at least a portion of the Flattened tube section is between the third location and the fourth location. Pipe according to Claim 12, characterized in that the intersections of each of the first and second transition regions and each of the broad and flat sides define curvilinear paths. Tube according to Claim 19, characterized in that each of the curvilinear paths includes a vertex located in a central plane of the tube.