WO2008019117A2

WO2008019117A2 - Heat exchanger and method

Info

Publication number: WO2008019117A2
Application number: PCT/US2007/017437
Authority: WO
Inventors: Peter Ambros; Werner Zobel; Stephan Hildinger; Klaus TÜBER
Original assignee: Modine Manufacturing Co
Current assignee: Modine Manufacturing Co
Priority date: 2006-08-05
Filing date: 2007-08-06
Publication date: 2008-02-14
Anticipated expiration: 2009-02-05
Also published as: WO2008019117A3

Abstract

Heat exchangers according to a number of different embodiments are described and illustrated, many of which include one or more partitions in one or more collecting tanks for directing fluid to be cooled through different sections of the heat exchanger. In some embodiments, one or more of such partitions can be movable in longitudinal or transverse directions to provide for control of fluid flow through the heat exchanger. Stationary or movable partitions can separate different flow regions in the heat exchanger, including different sets of tubes dedicated for respective fluid flows in the heat exchanger, and different portions of tubes dedicated for respective fluid flows in the heat exchanger. In some embodiments, the heat exchanger has a number of tubes with contoured ends received within headers associated with collecting tanks of the heat exchanger.

Description

HEAT EXCHANGER AND METHOD

RELATED APPLICATIONS

[0001] Priority is hereby claimed to German Patent App. No. DE 10 2006 036 742.1 filed on August 5, 2006, German Patent App. No. DE 10 2006 042 427.1 filed on September 9, 2006, German Patent App. No. DE 10 2006 056 744.9 filed on November 30, 2006, German Patent App. No. DE 10 2006 061 440.2 filed on December 23, 2006, German Patent App. No. DE 10 2007 031 824.5 filed on July 7, 2007, PCT App. No. PCT/US07/060769 filed on January 19, 2007, PCT App. No. PCT/US07/060774 filed on January 19, 2007, PCT App. No. PCT/US07/060785 filed on January 19, 2007, PCT App. No. PCT/US07/060789 filed on January 19, 2007, and PCT App. No. PCT/US07/060790 filed on January 19, 2007, the entire contents of which are incorporated herein by reference.

BACKGROUND OF THE INVENTION

[0002] Many typical heat exchangers include a header and collecting tank that can be combined to form what can be referred to as a header tank. The header typically contains apertures for connection with heat exchanger tubes in various manners (e.g., brazing, soldering, and the like). Regardless of whether the header is integral with the collecting tank or is a separate piece connected to the collecting tank, the header is often substantially flat. However, some heat exchangers (e.g., many air-conditioning system condensers) have round header tanks, in which case the header can have an approximately semi-circular contour. In ^* such cases, each tube end is typically cut at a right angle to the longitudinal axis of the tube. These ends usually protrude a certain distance into such header tanks, and are tightly connected to the header apertures in which they are received to form a seal. This configuration, however, can cause significant pressure loss of the medium (fluid) flowing in the collecting tank and in the heat exchange tubes.

[0003] Tubes used in heat exchangers are often manufactured from extrusions or from an endless sheet metal strip on a roller train. Individual tubes are usually cut off in a method generally referred to as an "online-cut". In this context, a blade which moves more quickly than the tube (or the strip of material used to form the tube) can be used to cut the tube in a dimcnsionally accurate fashion and in a direction perpendicular to the longitudinal axis of the tube. According to another manufacturing method, a sheet metal strip can be perforated and then cut into individual tubes along the perforations after the tube has been formed.

SUMMARY OF EMBODIMENTS OF THE INVENTION

[0004] Various embodiments of the present invention relate to heat exchangers having tubes and fins arranged between the tubes. The tubes and the fins can define a heat exchange network. Cooling air can flow through the fins (between the tubes), in order to cool a medium, such as a coolant, charge air, and the like flowing through the tubes. Some embodiments of the present invention provide a heat exchanger (e.g., a liquid cooled heat exchanger) that adapts its function or can be adapted in response to fluctuating demands.

[0005] Ends of the tubes interact with openings in a collecting tank, in a header connected to a collecting tank, or in one or more tube plates connected to a header and/or collecting tank. The header in some embodiments is substantially flat, and in other embodiments has a cross-sectional shape (taken along a plane perpendicular to the length of the header tank) having a contour.

[0006] The tubes of heat exchangers according to any of the embodiments herein can include tubes with multiple flow passages and having two narrow sides and two wide sides (e.g., irrespective of the depth of the cooling network), in some embodiments arranged in a single row or stack. This structure can apply to any heat exchange network regardless of the depth of the heat exchange network. For example, the depth dimensions or dimensions of the wide sides of the tubes extending in the direction of flow of the cooling medium can be at least about 20mm and no greater than about 300mm, in some embodiments.

[0007] In some embodiments, the tubes of the heat exchanger are manufactured from a continuous sheet metal strip on a roller train. In this way, tubes with significantly thinner walls can be manufactured, as compared to those manufactured, for example, by extrusion methods. Also in some embodiments, the thickness of the walls of the tubes can be as small as about 0.03 mm, and in some embodiments can be as large as about 0.20 mm, or in other embodiments as large as about 0.15mm. Consequently, a heat exchanger provided using tubes manufactured in this manner can have low mass and efficient heat exchange. [0008] The tubes can be produced from one, two, three, or more shaped sheet metal strips as described above. For example, each tube can each be produced from three sheet metal strips, with two sheet-metal strips forming the wall of the tube and the third corrugated sheet- metal strip forming an inner insert that forms longitudinal flow passages along and within the tube. Creating a tube in this manner can help reduce manufacturing and/or assembly costs, and can positively affect the heat transfer efficiency of the heat exchanger (e.g., due to the small wall thicknesses described above)..

[0009] In some embodiments, the tube ends have contours which, in some cases, can be created in the course of the manufacture of the tubes. For example, the contours of the tube ends can be created when the tubes are cut from a continuous sheet metal strip. In some embodiments, perforations that correspond to the contours of the tube ends are formed in the sheet metal strip by rollers. Also, in some embodiments, these contours are approximately semi-circular, parabola-shaped, or are otherwise curved. However, in other embodiments, these contours can include corrugations, which can allow the tubes to be cut to size and/or shape without waste. In addition, in some embodiments, curved tube ends can be made without waste if one of the tube ends of each tube does not protrude beyond the contour of the collecting tank. For example, in such embodiments, one of the tube ends can have a convex shape, while the other tube end has a concave shape.

[0010] Some embodiments of the present invention provide heat exchangers having a relatively low pressure drop in the medium flowing through the heat exchanger tubes and collecting tank(s). For example, in some embodiments, pressure drop can be reduced by providing tubes having a contoured shape which corresponds to the contoured shape of the header to which they are connected, and/or by providing ends of the tubes that terminate underneath (e.g., are recessed with respect to) the contoured surface of the header facing the interior of the collecting tank, such that the ends of the tubes do not protrude beyond the header into the collecting tank.

[0011] In some embodiments, a heat exchanger having a stack of tubes with fins positioned between the tubes is provided, wherein cooling air can flow through the fins to cool a fluid flowing through the tubes, each of which has two or more different inner flow regions with cross-sectional shapes having the same or different cross-sectional configurations (i.e., shape, size, and number of flow passages). At least one collecting tank including at least one partition can be used for guiding the flow of the fluid into and/or out of such tubes.

[0012] Some embodiments provide heat exchanger tubes produced by deformation of two endless sheet metal strips having longitudinal edges. Such tubes can have two broad sides and two narrow sides, wherein the narrow sides have a thickness at least twice that of the broad sides. A corrugated insert for each tube can be formed by folding one or more sheet metal strips, and can have edges which bear against the narrow walls defining the narrow sides of the tube to reinforce the structure. The corrugations of the insert can provide flow passages through the tubes. In some embodiments, louvers or cuts in the walls of the inserts can provide flow connections that link adjacent flow passages, while in other embodiments, the inserts do not have such flow connections.

[0013] In some embodiments, the tubes have inserts that create multiple adjacent flow passages along the length of the tube. Such tubes can be arranged in a stack, alternating with fins to form a heat exchange network. Since these tubes impose few or no diversions on the heat exchange liquid (in particular, in counter-current flow relationship within the heat exchange network), pressure loss through the tubes can be low, which can result in low energy consumption of the heat exchanger.

[0014] Heat exchangers according to some embodiments of the present invention have at least one partition in at least one of the collecting tanks of the heat exchanger. The partition can be used, for example, to generate a low-temperature flow region and a high-temperature flow region in the heat exchanger, and can interact with a header of the collecting tank in which the partition is located. In embodiments in which low- and high-temperature flow regions are defined by the partition(s), the low-temperature flow to or from the low- temperature flow region can extend over a surface of the heat exchange network onto which heat exchange air flows, and over part of a depth of a heat exchange network, whereas the high-temperature flow to or from the high-temperature flow region can lie behind the low- temperature flow region (with respect to a direction of flow of the heat exchange air between the tubes of the heat exchanger)..

[0015] In some embodiments, the collecting tank that constitutes an inlet collecting tank and the header of the inlet collecting tank is formed without an internal division (i.e., by a partition), whereas the collecting tank that constitutes an outlet collecting tank and the header of the outlet tank includes one or more longitudinal partitions. In some of these embodiments, fluid flows through the tubes in one common direction from the inlet collecting tank to the outlet collecting tank..

[0016] In some embodiments, heat exchangers having tubes with separate flow regions (e.g., formed by corrugations of a tube insert without flow connections between adjacent flow passages along the tube) are aligned with one or more partitions in the collecting tank. The flow passages provided by the inserts can be winding, or can be relatively straight.

[0017] Examples of heat exchangers with partitions and separate tube flow regions include heat exchangers (charge air heat exchangers or exhaust gas heat exchangers, by way of example only) having a first collecting tank with a partition forming two chambers or sections of the collecting tank, each of which has a dedicated inlet port. In such examples, the partition can be aligned with a wall of the corrugated insert in each tube such that two separate flow regions of each tube are formed. A first medium (e.g., charge air) can be input to a first flow region of each tube having an insert configured with flow connections between adjacent passages extending along the tube, while a second medium (e.g., exhaust gas) can be input to a second flow region of each tube having an insert configured without such flow connections. The two cooled mediums can then be combined in a second collecting tank.

[0018] Alternatively or in addition, two separate flow regions defined by a partition in a collecting tank can be defined by low-temperature and high-temperature mediums flowing through the regions, and possibly flowing in a common direction from an inlet header to an outlet header. Therefore, a fluid flow can be divided into at least two portions which leave the heat exchanger at different temperatures. Any number of partitions can be provided in any number of collecting tanks. For example, in some embodiments, an outlet header can include two spaced-apart longitudinal partitions (e.g., parallel longitudinal partitions), wherein the heat exchanger can produce two different low-temperature fluid portions and a total of three temperature flow regions.

[0019] Other examples of heat exchangers with partitions and separate tube flow regions include heat exchangers having an inlet collecting tank with a single opening that serves as the inlet port for fluid coolant (e.g., all or a majority of the cooling liquid flow passing through the cooling network), and an outlet header and collecting tank with two or more outlet openings, wherein fluid can leave the heat exchanger at different temperatures through the outlet openings. Alternatively, the inlet collecting tank can include two or more openings, if desired. Also, any type of collecting tank can include at least one outlet opening and at least one inlet opening. In any of these embodiments, the portions of the collecting tank(s) associated with inlet or outlet openings can be separated by at least one fixed partition or by at least one movable partition (described below).

[0020J Some embodiments of the present invention provide a heat exchanger in which the heat exchange function can be regulated according to the requirements of a heat exchange circuit. In some embodiments, the function of the heat exchanger can be regulated with an adjustable element in the collecting tank. In particular, heat exchangers according to some embodiments have one or more movable flaps, wall, baffles, or other structures (collectively referred to herein as "partitions") in their collecting tanks in order to direct a flow of medium in the collection tank through relatively large or relatively small groups of tubes, and/or through a different cross-sectional amounts of the tubes. In other words, by movement of the partition, a medium flow in the collection tank can be altered by increasing or decreasing the number of tubes into which the medium is permitted to flow, by increasing or decreasing the number of passes a medium through the heat exchanger, by increasing or decreasing the cross-sectional area of one or more tubes into which the medium is permitted to flow, and/or by altering flow through the heat exchanger in any other manner.

[0021] Movable partitions can be utilized in any type of collecting tank to achieve the functions described herein. For example, one or more movable partitions can be provided in inlet and/or outlet collecting tanks of a heat exchanger. In some embodiments, one or more partition can be moved by rotation of the partition about an axis, by linear movement of the partition, or by both types of movement.

[00221 ^m some embodiments, the moveable partition is a moveable longitudinal partition (i.e., extending along a longitudinal direction of a collecting tank), and is movable to different positions across the width of one or more tubes, thereby varying the cross-sectional area of the tubes and/or the number of tubes into or from which a fluid can flow. In other embodiments, and depending upon the position and orientation of the tubes with respect to the collecting tank, the partition can be a lateral partition (i.e., extending across the width of the collecting tank), and is movable to different positions along the longitudinal length of the collecting- tank to achieve the same function(s). Also depending upon the position and orientation of the tubes with respect to the collecting tank, a longitudinal or lateral partition can be moved transversely with respect to the broad sides of the tubes or can be moved transversely with respect to the longitudinal direction of the collecting tank.

[0023] In some embodiments, flow regions of each tube or of a set of tubes can be divided by temperature and/or by direction of flow with respect to the direction of cooling air flow. For example, in some embodiments, the heat exchanger has a high temperature region and a low temperature region, the sizes of which can be varied by movement of the partition. A high-temperature (HT) flow region can be located adjacent a low-temperature (LT) flow region such that cooling air passes the LT portion of the heat exchanger before passing the HT portion, thus providing more efficient heat exchange in many applications.

[0024] One or more moveable partitions can be arranged in combination with one or more fixed partitions in a heat exchanger, such as in the same collecting tank of a heat exchanger, or in different collecting tanks of the heat exchanger.

[0025] . In some embodiments, tubes of the heat exchanger are arranged and formed in a single row, which can improve the adaptability of the heat exchanger, and the ability of the heat exchanger to utilize one or more fixed and/or movable partitions to divide the heat exchanger into different flow regions as described above..

[0026] By way of example with regard to movable partitions as described above, in exhaust gas heat exchangers integrated into exhaust gas recirculation (EGR) systems, such movable partitions are present in order to direct the exhaust gas either through tubes in which the exhaust gas can be cooled and then recirculated, or through other tubes through which the exhaust gas can be recirculated without being cooled. In some embodiments, the partition has a shape corresponding to the cross-sectional shape of the header and/or the tube ends in order to improve the effectiveness of the regulating process.

[0027] Control over partition position (and therefore, over flow conditions through different numbers of tubes as just described) can provide highly desirable regulation of heat exchanger efficiency, flow volume, pressure, and/or other parameters in many cases, such as in coolant heat exchangers, charge air heat exchangers or air-conditioning condensers. Also, further control of such parameters is possible by spatial adaptation (e.g., collecting tank wall contour matching the contour of the header and/or tube ends) of the heat exchanger to various conditions and applications.

[0028] The dimensions of heat exchanger components according to various embodiments of the present invention can also be selected to help limit manufacturing and assembly costs, and to make the resulting cooling network of the heat exchanger more spatially compact. For example, partitions in collecting tanks used in conjunction with separated flow regions of the heat exchanger can elongate a fluid flow path through the heat exchanger such that a relatively large amount of heat exchange can be provided by a heat exchanger with relatively short tubes.

[0029] Heat exchangers according to various embodiments described herein can be used, for example, in motor vehicles, and in some embodiments can achieve temperature differences between the low-temperature flow and the high-temperature flow that are about +/-10 K.

BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figs. 1 through 7 are exploded perspective views of tubes with various insert configurations according to various embodiments of the present invention.

»\ [0031] Fig. 8 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention.

[0032] Fig. 9 is an end view of a tube with an insert according to an embodiment of the present invention.

[0033] Fig. 10 is an exploded perspective view of a portion of a heat exchanger according to an embodiment of the present invention incorporating the tube and insert configuration of Fig. 9.

[0034] Fig. 11 is an exploded perspective view of a heat exchanger according to another embodiment of the present invention.

[0035] Fig. 12 is an exploded perspective view of a heat exchanger according to another embodiment of the present invention. [0036] Fig. 13 is an exploded perspective view of a modified version of the heat exchanger of Fig. 12.

[0037] Fig. 14 is an exploded perspective view of a heat exchanger according to another embodiment of the present invention.

[0038] Fig. 15 is an exploded perspective view of a further modified version of the heat exchangers of Figs. 12-14.

[0039] Fig. 16 is a perspective view of a collecting tank of the heat exchanger of Fig. 15.

[0040] Fig. 17 is a perspective view of part of a heat exchanger according to an embodiment of the present invention.

[0041] Fig. 18 is an exploded view of part of a heat exchanger according to another embodiment of the present invention.

[0042] . Fig. 19 is an exploded view of part of a heat exchanger according to another embodiment of the present invention.

[0043] Fig. 20 is a perspective view of the part of the heat exchanger illustrated in Fig. 19.

[0044] Fig. 21 is a sectioned view of part of a heat exchanger according to an embodiment of the present invention.

[0045] Fig. 22 is a sectioned view of a part of a header according to an embodiment of the invention.

[0046] Fig. 23 is a side view of a heat exchanger tube according to an embodiment of the present invention.

[0047] Figs. 24 and 25 illustrate application examples of heat exchangers according to various embodiments of the present invention.

[0048] Fig. 26 illustrates an schematic view of a heat exchanger according to an embodiment of the present invention.

[0049] Fig. 27 illustrates a side view of the heat exchanger of Fig. 26. [0050] ■ Fig. 28 illustrates a schematic view of a heat exchanger according to another embodiment of the present invention.

[0051] Fig. 29 illustrates a cross-sectional view of a tube of a heat exchanger according to an embodiment of the present invention.

[0052] . Figs. 30 and 31 illustrate perspective and sectional views of a heat exchanger according to another embodiment of the present invention.

[0053] Fig. 32 illustrates a partial view of a heat exchanger having a moveable transverse wall according to an embodiment of the present invention.

[0054] Fig. 33 illustrates a heat exchanger connected to a heat exchange circuit according to an embodiment of the present invention.

[0055] Fig. 34 illustrates various combinations of partitions according to embodiments of the present invention.

[0056] Figs. 35 and 36 illustrate heat exchange circuits with a heat exchanger according to an embodiment of the present invention.

[0057] Figs. 37 through 39 illustrate heat exchange capacities of a heat exchanger based upon a position of a partition included in the heat exchanger according to various embodiments of the present invention.

[0058] Fig. 40 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention.

[0059] Fig. 41 illustrates end views of various tube embodiments according to the present invention.

[0060] Fig. 42 is an exploded perspective view of a heat exchanger according to another embodiment of the present invention.

[0061] Fig. 43 is an end view of a tube formed according to an embodiment of the present invention. [0062] Fig. 44 illustrates end views of a tube according to another embodiment of the present invention, shown in different stages of formation.

[0063] Fig. 45 illustrates end views of a tube according to another embodiment of the present invention, shown in different stages of formation.

[0064] Fig. 46 illustrates end views of tubes according to other embodiments of the present invention.

[0065] Fig. 47 illustrate end views of tubes according to other embodiments of the present invention.

[0066] Fig. 48 schematically illustrates a set of exemplary manufacturing steps that can be used to form a tube according to some embodiments of the present invention.

DETAILED DESCRIPTION

[0067] Before any embodiments of the present 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 the 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 of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. The use of "including," "comprising" or "having", and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof, as well as additional items. The terms "mounted," "connected" and "coupled" are used broadly, and encompass both direct and indirect mounting, connecting and coupling. Further, "connected" and "coupled" are not restricted to physical or mechanical connections or couplings, and can include electrical connections or couplings, whether direct or indirect.

[0068] Figs. 1 through 7 and 9 illustrate constructions of tubes 11 according to various embodiments of the present invention. Any of the tubes 11 illustrated in Figs. 1-7 and 9 and described below in connection with Figs. 1-7 and 9 can be utilized in any of the heat exchanger embodiments also described below. A tube 11 can be formed from any number of components, such as one, two, or three strips of material (e.g., sheet metal) connected together to form the tubular exterior and an optional internal element (hereinafter referred to as an "insert", regardless of whether defined by a separate element inserted into one or more exterior tube components or defined by a part integrally formed with one or more exterior tube components). The insert can define two or more longitudinal channels along any part or all of the tube 1 1. By way of example only, the tube 11 illustrated in Fig. 9 is constructed of three strips of sheet metal 17, 18, and 19. Strips 18 and 17 form the exterior walls of the tube 1 1, and can have substantially the same thickness. Strip 19 forms the internal insert and generally has a thickness less than or equal to the thickness of strips 18 and/or 17. The strips 18 and 17 can be formed identically but arranged in a laterally reversed manner with respect to each other. In such cases, the larger curve formed on one edge of sheet metal strip 18 can engage the smaller curve formed on the other edge of sheet-metal strip 19 (and vice versa). By forming the tube 1 in this manner, the narrow tube sides 112 are double the thickness of the broad sides. In addition, the longitudinal end portions of the insert 19 can bear against the narrow sides 1 12, further increasing their thickness as shown in Fig. 9. Embodiments of the heat exchanger according to the present invention can have tubes formed in this and other manners. .

[0069] Fig. 3 illustrates a tube 11 with two flow regions with the same configuration 1 A, IB, each having the same number of flow passages 14. The flow passages 14 within each region IA, IB are in fluid communication with each other via flow connections 140. In other embodiments, one flow region can have a different size (e.g., number of flow passages 14, volume, and the like) than another region having the same configuration. Also, in some embodiments, the flow connections 140 can be different in size, shape, and/or location with respect to the flow passages 14. As shown in the illustrated embodiment of Fig. 3, a flow separator 145 formed by the insert 19 can be located between the two regions IA, IB. The flow separator 145 can be a wall of the insert 19 having no flow connections 140, or alternatively, an insulating flow passage 14 defined by two adjacent walls having no flow connections 140. As will be described in greater detail below, one or more collecting tanks to which the ends of the tube 11 can be connected can have partitions therein (in appropriate locations) to maintain separation of the various fluids and flow paths (see Fig. 8, for example). Tubes 1 with insert configurations as described above with respect to Fig. 3 can be used in liquid coolant heat exchangers, among other types of heat exchangers. [0070] The embodiments of tubes 1 with insert configurations such as those shown in Figs. 1, 4, and 5 can be used, for example, in charge air and exhaust gas cooling heat exchangers. In such embodiments, the flow paths have inserts of different configurations (e.g., IA, IB), and are isolated from each other via a flow separator 145. As illustrated in Figs. 1, 4, and 5, in some embodiments flow connections 140 are provided in one region (IA) but not in another region (IB). Flow regions without flow connections 140 are considered to have discrete flow passages.

[0071] In the embodiments of Figs. 6 and 7, both flow regions IA, IB have discrete flow passages (i.e., without openings establishing fluid communication between adjacent longitudinal passages 14). However, the configuration of each flow region IA, IB differs in the geometric design of the insert 19. The flow passages of region IB in the illustrated embodiments of Figs. 6 and 7 are relatively straight, while those of region IA are not straight (e.g., are winding or serpentine). As a result, discrete flow passages in the region IA are longer than the discrete flow passages in region IB. Fig. 2 illustrates some of the insert configurations that can be combined in various embodiments according to the present invention to form different flow regions IA through IE. Tubes 11 with similar insert configurations can be used in heat exchangers such as that illustrated in Fig. 8.

[0072] Figs. 1 and 4 show flow connections 140 in the form of vertically-oriented louvers in the walls of the inserts 19. Louvers can be provided by making close adjacent cuts in the insert walls (in the direction of the tube thickness), and bending material adjacent the cut out such that it projects from the cut wall. In contrast, the inserts 19 illustrated in Figs. 2, 3, and 5 have incisions in the insert walls that are spaced farther apart, and are positioned such that adjacent portions of a wall between two incisions are laterally offset to define flow connections 140. Additionally, wings or winglets (not shown) can be formed in the walls of the insert 19, if desired.

[0073] It should be noted that the various types of insert section shapes in the illustrated embodiments of Figs. 1-7 are presented by way of example, as are the particular combinations of such shapes shown in same figures. In this regard, it will be appreciated that the types of insert section shapes shown in Figs. 1-7 and described above can be utilized in any configuration desired, such as inserts 19 without flow connections in any of the two or more flow sections across the width of the tube 11, inserts 19 with flow connections in all of the two or more flow sections across the width of the tube, inserts 19 having a combination of sections with and without flow connections, inserts 19 having the same cross-sectional shape for all corrugations (in all flow sections), inserts 19 having any combination of corrugation shapes, and inserts 19 having flow sections of the same or varying size across the width of the tube 11.

[0074] As shown in the illustrated embodiment of Fig. 8, a heat exchanger according to some embodiments of the present invention have a single stack of tubes 11 , each tube 1 1 having a width W. In some embodiments, the tube width W can be as small as about 10mm. Also, in some embodiments, the tube width W can be as large as about 300mm. The tubes

11 also have a height H and a length L as shown in Figs. 9 and 10. In some embodiments, the height H of the tubes 11 can be as small as about 0.7mm. Also, in some embodiments, the height H of the tubes 11 can be as large as about 15mm. Aluminum sheets having a thickness of, for example as small as about 0.03mm and as large as about 20mm can be used to form the tubes 11 and fins 12. Heat exchangers having structures within these dimensional ranges can be used for various purposes, including applications in motor vehicles.

[0075] The heat exchanger of the embodiment shown in Fig. 8 can be used, for example, to cool or regulate the temperature of various fluids using cooling air. The cooling air is represented by a double-sided arrow in Fig. 8, which indicates that air can flow through the fins between the tubes 11 in either direction (from left to right in Fig. 8 or vice versa). Fins

12 are also visible in the embodiment of Fig. 10. In some embodiments, the tubes 1 1 can be divided into multiple regions of flow passages 14. For example, in the embodiment of Fig. 8, the interior of each tube 11 is divided into four regions IA, IB, 1C, and ID, which are defined at least in part by different configurations of the corrugated internal insert 19 of each tube 11. A heat exchanger according to the present invention can have any number of flow passage regions. Each region can be configured differently as shown in Fig. 8. Alternatively, two or more regions across the width of each tube 11 can have the same configuration. For example, group ID illustrated in Fig. 8 can be formed identically to region IA or to another region. The configuration of each region can be dependent upon the specific requirements of the heat exchanger application.

[0076] As shown in the embodiment of Fig. 8, the heat exchanger can have two collecting tanks 110, 120, which are positioned on either set of open tube ends at the opposite ends of the tubes 11. One collecting tank 110 has three partitions 1101, 1102, and 1 103 which extend transversely with respect to the stacking direction of the tubes 11, and longitudinally within the collecting tank 1 10. The opposite collecting tank 120 has two partitions 1201, 1202 that are similarly positioned within the tank 120 with respect to the tube stacking direction.

[0077] The arrows in Fig. 8 indicate possible flow paths of fluid in the heat exchanger. On the far left side of Fig. 8, a first fluid can flow into the collecting tank 110 through an inlet port 130A. The first fluid can then flow through region IA of the tubes 11 into the opposite collecting tank 120. The first fluid can then flow out of the opposite collecting tank 120 through an outlet port 140A. A second fluid can flow into the collecting tank 110 through an inlet port 130B, through region IB, and into a middle portion of the opposite collecting tank 120. This second fluid can be diverted by the middle portion of the opposite collecting tank 120, and can thereafter flow through region 1C and out of the collecting tank 110 through outlet port 140C. Thus, the partition 1102 can separate the in-flowing second fluid from the out-fiowirig second fluid. In some embodiments, the first fluid can be directed from outlet 140A into inlet 130D of the collecting tank 120, through region ID, and out of collecting tank 110 via outlet port 140D. In other embodiments, a third fluid can flow from the collecting tank 120 to collecting tank 110 through the ID flow region. In alternative embodiments according to the present invention, any of the flow paths described above can be reversed (e.g., 130A becomes an outlet port and 140A becomes an inlet port). In other embodiments, a fluid can pass multiple times through the heat exchanger, in any number of flow paths, utilizing various regions of the heat exchanger. The configuration of fluid flow paths (i.e., direction of flow, number of passes, positional relationship of paths with respect to one another in the heat exchanger, location of ports, and the like) in a particular heat exchanger can be dependent upon the requirements of its application.

[0078] With continued reference to the illustrated embodiment of Fig. 8 by way of example only, the far left region IA (in the orientation of Fig. 8) can be a high-temperature flow pass for charge air CA(HT). Charge air leaving this region from collecting tank 120 can then flow into the far right region ID, creating a low-temperature flow pass for charge air CA(LT). In the central section of a heat exchanger according to this embodiment, region 1 B can be a high-temperature flow region for liquid coolant LC(HT). The liquid coolant can then flow into region 1C, which is positioned upstream (by virtue of the positioning of header partitions and ports), thereby creating a low-temperature flow pass for the liquid coolant LC(LT). In this example, each fluid makes two sequential passes through the heat exchanger. Accordingly, the flow path of each fluid is comprised of two passes.

[0079] In other embodiments, the section 120BC of the collecting tank 120 can include an outlet port (not shown). In such embodiments, some of the second fluid that enters section HOB of the collecting tank 110 can leave the heat exchanger after the high-temperature pass LC(HT), while the rest of the second fluid continues through the low-temperature pass LC(LT) and leaves the heat exchanger through section HOC of the collecting tank 1 10.

10080] The illustrated embodiment of Fig. 10 can be, for example, a liquid coolant heat exchanger with tubes 1 1 according to the embodiment of Fig. 9 for use in a motor vehicle. It will be appreciated, however, that any of the features and elements of the embodiment shown in Fig. 11 can instead be used in any other type of heat exchanger. The tube and material dimensions described above in connection with Fig. 8 can be utilized in the embodiment of Fig. 10.

[0081] Such a liquid coolant heat exchanger can have a flow region IA which can be considered the high-temperature flow region. Fluid is partially cooled in region IA, and can then be directed via a collecting tank 120 (not shown) into region IB, which can be considered the low-temperature region in such an application because fluid that leaves this region is at a lower temperature than that at which it left region IA.

[0082] . Fluid pressure in the IB region can be higher than fluid pressure in region IA at any point in time. In some embodiments, this can occur as a result of the relatively large cross-sectional area of the flow regions IA, IB of the heat exchanger in comparison to the cross-sectional area of the heat exchanger inlet and outlet. In order to accommodate the higher pressure in region IB, the corrugated insert 19 can be configured to have smaller or narrower flow passages (e.g., tighter corrugations). Alternatively or in addition, the thickness of the insert 19 can be greater in region IB. Additionally, and as shown in Fig. 9, the thickness of the narrow side 112 of the tube 11 can be increased to provide further structural reinforcement 16. This can be accomplished by forming additional folds in the insert 19 which bear against the narrow side 112. The narrow side 1 12 shown in Fig. 9 with structural reinforcement 16 has triple thickness compared to the broad sides of the tube 1 , although quadruple^', quintuple, or greater thicknesses are possible with further folds of the material used to construct the tube 11. In this manner, the parts of the tubes 11 that experience more stress can be reinforced, while the other parts can remain thin (0.03mm - 0.15mm in some embodiments) in order to minimize the total mass of the heat exchanger.

[0083] Another feature shown in the embodiment of Fig. 10 is the closing off of at least one flow path between two flow regions IA, IB such that fluid does not pass therethrough. This can be accomplished, for example, by positioning a partition 1 101 in alignment with a closure element 160. The partition 1101 can be one or more walls of the insert 19 as shown in Fig. 9, can be one or more separate longitudinal walls received within or otherwise passing along the tubes 11 to divide the tubes 11 into different lateral sections, can be a longitudinally-extending channel closed at opposite ends (and defined in some embodiments by walls of the insert 19), and the like. In some embodiments, this flow separator 145 between flow regions IA, IB can be filled with another fluid, such as air. This feature can be used in embodiments having adjacent flow regions that may contain fluids of different temperatures, as suggested above. In such embodiments, this flow separator 145 acts as an insulating barrier, preventing heat from flowing from the high-temperature region IA to the low-temperature region IB. Providing a flow separator 145 comprised of one or more adjacent closed channels 14 can also prevent convective transfer of heat from one region to another.

[0084] The various heat exchangers of the present invention disclosed herein can be used as gas heat exchangers. By way of example only, Fig. 11 illustrates a heat exchanger that can be used as a gas heat exchanger (although it should be noted that any of the features and elements disclosed in Fig. 11 can be used in other types of heat exchangers). Compressed charge air CA and exhaust gas EG can flow through separate flow regions to be cooled by ambient air passing between the tubes 11.

[0085] In some embodiments, the tubes 11 of the heat exchanger can be formed of stainless steel, aluminum, or other materials. The thickness of the sheet material used to form the tubes and inserts can be larger than above-mentioned ranges of values. Also, in stainless steel embodiments, the thickness of the inserts 19 can be less than or equal to the thickness of the wall parts 18, 17 of the tubes 11. In the embodiment of Fig. 11, the collecting tank 1 10 is provided with a longitudinal partition 1101 separating the collecting tank 110 into two sections 11OA, HOB that can function as inlet chambers. [0086] Charge air CA flows through region IA, which has flow connections 140 (described above) between adjacent flow passages 14 (also described above). The tubes 11 in such an application can use, for example, a tube insert configuration similar to region IA of Fig. 5. Turbulence created by flow connections 140 can cool gas more efficiently. In contrast, the exhaust gas EG can flow through a region IB similar to region IB of Fig. 5 having no flow connections 140 linking adjacent flow passages 14. In other embodiments, discrete flow passages 14 in this region can be winding, such as those illustrated in Figs. 2 and 6 by way of example only. Such insert configurations can eliminate the buildup of exhaust residues within the passages, insuring consistently efficient cooling through the life of the heat exchanger. Cooled charge air CA and exhaust gas EG can then be combined in the collecting tank 120, if desired, and can be supplied to an internal combustion engine (not shown). This procedure (particularly combining charge air CA and exhaust gas EG after cooling separately) can have considerable thermodynamic advantages which take into account considerable temperature differences between the two gases input to the heat exchanger. A combined heat exchanger such as that shown in Fig. 11 also requires less space and has lower manufacturing and assembly costs in comparison to separate heat exchangers for cooling each gas prior to combination and input to an engine.

[0087] Fig. 12 illustrates a heat exchanger according to another embodiment of the present invention. This heat exchanger can be used, for example, as a liquid heat exchanger, and in some cases can be used for heat exchange between fluids having different temperatures. The illustrated heat exchanger has a low-temperature flow region LT and a high-temperature flow region HT. In such embodiments, fluid from a common collecting tank 110 can flow into flow regions IA and IB of the tubes 11 divided by a flow separator 145. Each flow region IA, IB can empty into a separate section 120A, 12B of a collecting tank 120. Each tank section 120A, 120B can have a dedicated outlet such that fluid from the flow regions HT, LT can be directed to different areas of the heat exchange circuit that can have different cooling requirements. Such embodiments can use tubes 11 with insert configurations similar to those illustrated by Fig. 3, although any other insert configuration(s) are possible. As shown in Fig. 12, a heat exchanger according to some embodiments can have an outlet 140B that extends through a section 120A as shown, such that both outlets 140A, 140B extend from the same side of the heat exchanger. In this way, various structural constraints of the heat exchanger can be accommodated. [0088] Based upon the configuration illustrated in Fig. 12, a temperature difference of 7K between HT and LT flows can be obtained in some embodiments. However, it is not required that the insert configurations (i.e., the number and spacing of flow connections, insert geometry, and the like) be the same as shown in Fig. 12.

[0089] The heat exchanger of Fig. 13 illustrates a variation of a divided collecting tank according to an embodiment of the present invention. In this illustrated embodiment, the partition 1201 is shaped such that both sections of the tank 120 share a common wall. In this embodiment, there is no portion of the outlet 140B that extends through the section 120A.

[0090] Fig. 14 illustrates a heat exchanger according to another embodiment of the present invention. Although the illustrated heat exchanger can be used as a liquid cooling heat exchanger located between two separate heat exchange circuits A, B (not shown) having different cooling requirements (i.e., a low-temperature circuit and a high-temperature circuit), it will be appreciated that the heat exchanger features of Fig. 14 can be utilized in other types of heat exchangers. In the illustrated embodiment of Fig. 14, longitudinal partitions 1101, 1201 are positioned in collecting tanks 110, 120 to isolate the two circuits A, B.

[0091] The heat exchanger illustrated in Figs. 15 and 16 provide examples of collecting tanks 120 each having a longitudinal partition 1101, 1201 with ports (which can be either inlets, outlets or a combination thereof) extending from a common wall of each collecting tank 120. In these embodiments, a port 140B is fused to an outer wall of the collecting tank 120. This design, which does not necessitate an undercut, can be made by use of injection molding dies, making production more cost-effective in many embodiments.

[0092] A heat exchanger according to another embodiment of the present invention is partially shown in Fig. 17. The illustrated heat exchanger can, for example, be a liquid coolant heat exchanger used in a motor vehicle, although any of the features and elements shown in Fig. 17 can instead be utilized in other types of heat exchangers used in other applications. The coolant heat exchanger illustrated in Fig. 17 can be integrated into and receive coolant at a high temperature (HT) from a heat exchange circuit (not illustrated), as indicated by the arrow in the upper right of Fig. 17. The coolant flows into a collecting tank 24 that is connected to a header 25. The header 25 includes openings 23 that receive the ends 21 of the tubes 11 so that coolant can flow from the collecting tank 24 into and through the tubes 11. Cooling fins 106 (not illustrated) through which cooling air flows, as indicated by the unfilled block arrow in Fig. 17, can be arranged between the tubes 11 of the coolant heat exchanger.

[0093] The illustrated header 25 has a contour 220, which is configured in an approximately semicircular shape in the embodiments shown in Figs. 17 and 18. As shown in Figs. 17 and 18, the contour can extend over the entire surface of the header 25. In other embodiments, the contour can have other shapes, including other curved shapes.

[0094] In some embodiments, the end 21 of each tube 11 has a contour 210. The contour 210 can have any shape desired, and in some embodiments is curved. For example, the end 21 of each tube 11 illustrated in Figs. 17 and 18 is semicircular in shape. Tube ends having other shapes (matching the internal header surface shape or otherwise) are possible, and fall within the spirit and scope of the present invention.

[0095] The tube ends 21 can be recessed below the internal surface of the header 25. For example, and as shown in Fig. 17, the ends 21 of the tubes 11 (indicated by dashed lines) terminate beneath the contour 220 of the header 25. In this case, the ends 21 can each have a contour 110, as indicated by reference number 22b, or can be without a contour 110, as indicated by reference number 22a. In some embodiments, since the tube ends 21 terminate beneath the contour 220 of the header 25, a perceptible reduction in pressure loss can be achieved. In Fig. 18, in contrast to Fig. 17, the contour 220 of the header 25 corresponds to and is proximate the contour 1 10 of the tube ends 21 (i.e. the contour 110 of the tube ends 21 is approximately at the level of the contour 220 of the header 25, which can also reduce pressure loss).

10096] The collecting tank 24 in some embodiments can include a movable partition 240 that can extend over the length of the collecting tank 24. The partition 240 can be positioned at a pivot point 241 and can be controlled, for example, to affect the temperature of coolant leaving the heat exchanger. For example, the partition 240 can be moved along the contour 220 of the header 25, and, therefore, can open or essentially close a relatively large or a relatively small cross section of the tubes 11 to the flow depending upon requirements of the heat exchanger. In other embodiments, the partition 240 can be automatically controlled in response to conditions experienced in the heat exchange circuit (e.g., the temperature of coolant entering the heat exchanger). [0097] As shown in Fig. 17, high-temperature coolant (HT) can flow from a heat exchange circuit into the collecting tank 24, and can be directed to a cross-sectional part of the tubes 11 by virtue of the position of the partition 240. The high-temperature coolant (HT) can then be cooled as it flows through cross-sectional part of the tubes 11 by means of the cooling air flowing between the tubes 11 (through the fins 106, not shown). After the coolant has passed through this cross-sectional part of each tube 11, which can be referred to as the high-temperature part (HT) of each tube 11 (or of the heat exchanger), a portion of the coolant (MT out) can be branched off at the other end of the coolant heat exchanger (not shown) and conducted back into the heat exchange circuit. The remaining portion (MT in) can be directed through the remaining cross-sectional part of the heat exchanger, as indicated by an arrow in Fig. 17. The remaining portion of the coolant (MT in) can be cooled further as it passes a second time through the tubes 11 and into the collecting tank 24, in order to be available for particular cooling functions (in the motor vehicle or other application) which require a lower coolant temperature (LT).

[0098] The cross-sectional part of the tubes 11 and the heat exchanger receiving fluid flow from the first cross-sectional part HT described above can be referred to as the low temperature part LT of the tubes 11 (or of the heat exchanger), and can be located on the cooling air inflow side of the heat exchanger. In other embodiments, this cross-sectional part HT of the .tubes 11 and heat exchanger can be located in any other position with respect to the other portions of the tubes 1 1 and heat exchanger.

[0099] In the starting phase of a motor vehicle in which the heat exchanger illustrated in Fig. 17 is installed, little cooling fluid, or even none at all, will often be made available for further cooling since the temperature of all the coolant is rather low. Therefore, the partition 240 of the illustrated embodiment in Fig. 17 can be in a left-most position in such conditions (viewed from the perspective of Fig. 17). In other operating conditions, the partition 240 can be moved in order to vary the sizes of the flow cross sections for the flow regions LT, HT in response to the requirements of the heat exchange circuit. In some embodiments, the partial streams LT and HT are combined at some point in the heat exchange circuit before they pass again to the coolant heat exchanger as a high temperature coolant (HT) stream.

[00100] The exemplary heat exchanger embodiments shown in Figs. 19 and 20 differ from the embodiments shown in Figs. 17 and 18 in that both the contour 210 of each tube end 21 and the contour 220 of the internal surface of the header 25 are corrugated in shape (viewed in a plane that is transverse to the header 25). In other words, the tube ends 21 and the internal surface of the header 25 each have multiple curves, such as at least one concave curve and at least one convex curve. The above-described cross-sectional parts of the tubes 1 1 (and heat exchanger) that define separate flow regions of the heat exchanger and that can be varied by movement of the partition 240 are indicated in Figs. 19 and 20 by LT and HT. The inner configuration of the illustrated tubes 11, which can have a plurality of flow passages 2100 that are essentially not connected in the transverse direction (see also Fig. 21) is not visible in Figs. 19 and 20. In some embodiments, the wall 250 of the collecting tank 24 follows the corrugated shape of the contour 210 of the tube ends 21 and/or the contour 220 of the header 25 in order to correspond to specific structural conditions or requirements of the heat exchanger (e.g., available space in an engine compartment of a motor vehicle or other space constraints in other applications).

[00101] The regulating range of the heat exchanger (i.e., the ratio of the sizes of the cross- sectional parts of the tubes 11, the temperature differential between fluid in the different cross-sectional parts of the tubes 11, and the like) can also be defined at least in part by the structural configuration of the contoured partition 240. For example, in the exemplary embodiment shown in Fig. 21, the LT region can be closed completely (when the partition 240 is moved to the right-most position of Fig. 21). As also shown in Fig. 21, tube ends 21 without a contour 210 terminating below the header 25 with a contour 220 (i.e., not extending into the collecting tank 24) can also be provided in some embodiments according to the present invention. In such embodiments, the partition 240 can still interact with the contour 220 of the header 25 to substantially separate flow in the collecting tank 24 as described above.

[00102] Any of the embodiments described herein can include (or be adapted to include) a heat exchanger network having two or more rows of tubes 11 in the direction of the network depth (i.e., in the direction of cooling flow between the tubes 11). In yet other embodiments, the heat exchanger network can have a single row of tubes in this direction. In cither case, the tubes of either or both rows can be manufactured on a roller train (or in any of the other manners described herein) to be constructed of one or more extremely thin sheet metal strips. [00103] Fig. 22 illustrates a sectioned detail view of a header 25 that can be used in conjunction with any of the embodiments of the present invention. As shown in Fig. 22, the illustrated header 25 includes openings 23 in which the tube ends 21 can extend and be attached. Fig. 22 also illustrates fins 26 between the tubes 11. As previously described, in some applications of heat exchangers according to the present invention, cooling air flows through the fins 106. Also in some embodiments, the material of the collecting tank 24 and header 25 comprises plastic, which can allow easy manufacture of the header contour 220 described above. Alternatively, the collecting tank 24 can comprise plastic, while the header 25 comprises aluminum or another metal, or the collecting tank 24 can comprise aluminum or another metal, while the header 25 comprises plastic. The tubes 11 illustrated in Fig. 22 terminate beneath the contour profile 220, and can be, for example, adhesively bonded or attached in any other seal-forming manner within the openings 23.

[00104] Fig. 23 illustrates a view of a broad side of a tube 11 according to an embodiment of the present invention. As shown in Fig. 23, one tube end 21 (on the right side of Fig. 23) can have a convex contour 22b, while the other tube end 21 (on the left side of Fig. 23) can have a concave contour 22c. In some embodiments, when tubes 11 are cut to size as shown in Fig. 23, little or no material is wasted, since the convex contour 22b of one end 21 of the tube 11 is generated simultaneously with the concave contour 22a of another end 21 of an adjacent tube 1 1 cut or otherwise separated from the same length of tubing material. In these cases, the concave contour 22a of the tube 11 can be slightly recessed or flush with the inner surface contour 220 of a first header 25 in a heat exchanger (e.g., see Fig. 18), and the convex contour 22b of the tube 11 can be positioned with respect to a second header 25 in a manner similar to that indicated by the dashed line 22b in Fig. 17. The convex contour 22b of the tube 11 can terminate beneath the level of the inner surface contour 220 of the second header 25. It should also be noted that the tube ends 21 shown in Figs. 19 and 20 and still other types of tube ends can also be formed without scrap in a manner similar to that described above in connection with Fig. 23.

[00105] In some embodiments, tubes 11 in any of the embodiments of the present invention are cut to size using perforations made in the sheet metal strip(s) used to construct the tubes 11 , such as by perforating rollers. Individual tubes 11 can then be cut off cleanly along the perforations. The perforations can be made to form the above-described tube end

22a, 22b, 22c, among others. [00106] Fig- 24 illustrates an application of a heat exchanger according to an embodiment of the present invention. Although well-suited for use in a motor vehicle, it will be appreciated that any of the features and elements described and illustrated in connection with this embodiment can be utilized in other types of heat exchangers for the same or different applications. Fig. 24 illustrates a side view of opposing ends of a heat exchanger (e.g., a coolant heat exchanger, in the illustrated embodiment). In this embodiment, high temperature coolant HT from a heat exchange circuit (not illustrated) is received to be cooled, and flows into the left-hand collecting tank 24. Coolant HT exits the right hand collecting tank 24 after losing heat to cooling air (indicated by the block arrow shown in Fig. 24), and is available for use within the heat exchange circuit or for further cooling. A movable partition 240 is arranged in each of the collecting tanks 24. Both partitions 240 can be moved by a common actuator or by respective actuators (not shown). As also shown in Fig. 24, a stream LT of a coolant enters the upper part of the coolant heat exchanger at the right hand collecting' tank 24 and, after further cooling, leaves the left hand collecting tank 24 in order to cool, for example, charge air (not shown) or another medium at another location in the heat exchange circuit.

{00107] The structure of the heat exchanger shown in Fig. 24 can provide significant advantages in a number of applications. There are, for example, low load states of a motor vehicle (e.g., when traveling downhill), in which cooled charge air is not demanded. Instead, a hydraulic brake system may need to be operated at full load in order to be able to absorb braking forces. As a result, the temperature of hydraulic fluid in a braking system can increase such that the braking system has an increased cooling requirement. In these operating states, the partitions 240 can be moved by the actuator element(s) described above into the dashed positions shown in Fig. 24, such that the LT circuit is closed or substantially closed. Therefore, a larger cooling capacity can be made available to the HT circuit, which can compensate for the increased cooling requirement arising due to the heated hydraulic fluid.

[00108] Fig. 25 illustrates another embodiment of a heat exchanger (e.g., a coolant heat exchanger, such as that described above in connection with Fig. 24) in which two partitions 240 are regulated individually. Using individually adjustable partitions, coolant streams with different temperature levels (which result from different cooling demands in any number of applications) can be regulated. Coolant MTl that exits the left-hand collecting tank 24 in Fig. 25 can have a higher temperature than the coolant MT2, which exits the right hand collecting tank 24, and which in turn can have a higher temperature than the coolant LT exiting the left-hand collecting tank 24.

[00109] It should be noted that the heat exchangers illustrated in Figs. 24 and 25 are shown in schematic form only, it being understood that the principles of operation described above (using the movable partitions 240 to control flow through the tubes 11) apply to heat exchangers having other shapes and configurations.

[00110] A heat exchanger according to another embodiment of the present invention is schematically illustrated in Figs. 26 and 27, and includes tubes 31 and fins 32 (not shown) arranged between the tubes 31. The tubes 31 and the fins 32 form a cooling network 33. Cooling air can flow through the fins 32 in order to cool fluid flowing inside the tubes 31. First ends of the tubes 31 can open into an inlet collecting tank 314, and second ends of the tubes 31 (opposite from the first ends) can open into an outlet collecting tank 324. Fluid to be cooled can enter the inlet collecting tank 314 through an opening (or port) 341. As also shown in Figs. 26 and 27, the surface of the cooling network 33, with which cooling air or other fluid makes contact, is surrounded by a dashed line and is denoted by reference character A. In some embodiments, the surface onto which cooling air flows covers the entire cooling network surface A.

[00111] As illustrated in Fig. 27, two longitudinal partitions 335 are provided within and can extend over the length of the outlet collecting tank 324. At least one of the two longitudinal partitions 335 can be movable in any of the manners described and illustrated herein. The longitudinal partitions 335 can be used to establish two low-temperature flow regions (LTl , LT3) and a high-temperature (HT) flow region, each having a respective fluid outlet port 342. The mass flow rates, and, as a result, the temperature differences between the LT flow regions and the HT flow region can be regulated by the longitudinal partitions 335.

[00112] Another heat exchanger embodiment is schematically illustrated in Fig. 28, and has many of the same features (e.g., tubes 31, fins 32, collecting tanks 314, 324) as those described above in connection with Figs. 26 and 27. However, the illustrated outlet collecting tank 324 of Fig. 28 includes a single moveable longitudinal partition 335 (indicated as a dashed line in Fig. 33, which illustrates an example of a heat exchanger schematically shown in Fig. 28). [00113] In still other embodiments, one or more longitudinal partitions 335 can also or instead be located within the inlet collecting tank 314 of the embodiments of Figs. 26-28. Any one or more of these partitions 335 can be moved as also described above in order to regulate flow of fluid to be cooled as also described above.

[00114] Any actuator (not shown) can be used to move the longitudinal partitions 335 described above, and can be used in conjunction with any suitable gaskets or other seals (also not shown) to separate the different flow regions within the collecting tanks 324. For example, any sufficient hydraulic, electrical, mechanical, or other type of actuators can be used to move the longitudinal partitions 335, and can be controlled by any suitable open-loop or closed-loop controller. By way of example only, and as shown in Fig. 33, movement of one or more partitions 335 can be facilitated by a pump P included in any open- or closed- loop control system.

[00115] Figs. 29, 31, and 32 each illustrate a cooling network depth T. In some embodiments, the longitudinal parti tion(s) 335 can be arranged in such a way that each flow region LT, HT covers only a specific proportion of the cooling network depth T, but at the same time extends over the entire cooling network area A through which cooling flow passes. For example, the flow regions LT, HT can be oriented to direct fluid through the tubes 31 of each flow region LT, HT in parallel and in a common direction from the inlet collecting tank 314 to the outlet collecting tank 324, as indicated by the arrows in Figs. 26, 28, and 33. In this respect, a flow LT (which can experience the greatest heat exchange based upon its positional relationship to the flow of cooling air or other fluid) can lie on the cooling air inflow side A, since it is there that the temperature difference between the cooling air and the fluid being cooled within the tubes 31 is the greatest. To enable the flow regions LT and HT to be formed, flow within each such region LT, HT can be assigned a separate stack of tubes or a portion of each tube in a stack of tubes having multiple separate fluid flow paths. In some embodiments, the latter arrangement provides structural simplifications within the heat exchanger.

[00116] The size of the broad sides 311 of the tubes 31, which extend in the direction of flow of cooling air, can be as small as about 20mm, and as large as about 300mm in some embodiments, which corresponds to the entire depth dimension T of the cooling network 33. In some embodiments, the thickness of the strip(s) of material (e.g., sheet metal strips) that form the tube walls can be as small as about 0.06mm, and as large as about 0.20mm, whereas the thickness of the strip(s) of material (e.g., sheet metal strips) that form the insert can be as small as about 0.03mm, and as large as about 0.10mm. As illustrated in Fig. 29, the thickness of the narrow sides 310 of each tube 31 can be at least twice the thickness of the broad sides 311. Also, it should be noted that the corrugated strip of material defining the insert can be introduced between the strips of material (or portions of the same strip of material) that form the tube walls, as these strips are brought together during formation of the tube 31.

[00117] Figs. 30 and 31 illustrate an end of a cooling network 33 including tubes 31, corrugated fins 32, and a collecting tank 314 according to an embodiment of the present invention. As also shown in Figs. 30 and 31, the tube ends are inserted into apertures 345 in a header 316 forming a part of the collecting tank 314. As with other embodiments described above, the header 316 illustrated in Figs. 30 and 31 has an approximately semicircular contour, but can instead have other shapes, including other curved shapes. In some embodiments, the collecting tank 314 is provided with an approximately round cross- sectional shape exhibiting good pressure stability. Rotational movement of the moveable longitudinal partition 335 shown in Figs. 30 and 31 can be generated in such a way that the edge 337 of the longitudinal partition 335 moves along the contour 38 of the inner surface of the header 316. It should be understood that in some embodiments, the longitudinal partition 335 can also be adjusted transversely with respect to its longitudinal dimension by a translational movement. In some embodiments, the header 316 can also be produced without a contoured shape as described above, and the collecting tank 314 can be produced without a round or rotund cross sectional shape while still performing the functions described herein. For example, in some embodiments, the collecting tanks 314 can have an approximatelyparallelepiped shape (e.g., with a rectangular cross sectional shape).

[00118] As shown in Figs. 29-31, movement of the longitudinal partition 335 can cause, on one side of the partition 335, an enlargement of the cross-sectional area of the tubes 31 having a fluid flowing therethrough, and can cause, on the other side, a corresponding reduction in size of the cross sectional area having a fluid flowing therethrough. As shown in Fig. 29, the cross-sectional area of each flow region is indicated with a cross-hatched field representing a tube cross-section. In this illustrated embodiment, the left-hand area Ql is assigned to the LT fluid flow, and the right-hand area Q2 is correspondingly assigned to the

HT fluid flow. [00119] In the position of the partition 335 shown in Fig. 31 , the cross-sectional area Q2 of the tubes 31 on the left of the partition 335 is assigned to the HT fluid flow, and is significantly larger than the cross-sectional area on the right of the partition 335 and assigned to the LT fluid flow. As also shown in Fig. 31 , rotational movement of the longitudinal partition 335 can take place about a bearing or about an axis 357, which can be located on or coupled to a wall of the collecting tank 314. Fig. 31 also illustrates, in dashed lines, an alternative configuration in which the bearing or the axis 357 is located approximately centrally in relation to the partition 335 or centrally with respect to the longitudinal axis of the collecting tank 314. Other pivot locations of the longitudinal partition are possible, and fall within the spirit and scope of the present invention. In such embodiments, the bearing or axis 357 can be supported on end walls or by other structure (not shown) of the collecting tank 314.

[00120] In some embodiments, the above description regarding movement of longitudinal partitions 335 also applies to movement of transverse partitions 365. An example of a movable transverse partition according to an embodiment of the present invention is shown in Fig. 32. In this illustrated embodiment, a transverse partition 365 is moved linearly in the longitudinal direction of the collecting tank 314 by an element 350 (e.g., a spindle, hydraulic cylinder, or other actuator). Such linearly-moving partitions can be utilized in any of the embodiments disclosed herein. Alternatively, the linearly-moving transverse partition 365 of Fig. 32 can instead be adapted to rotate in a manner similar to the embodiments described above. Also, in some embodiments of the present invention, longitudinal and lateral partitions can move in still other manners, such as in any combination of linear and rotational movement desired.

[00121] With continued reference to the embodiment of Fig. 32, in some embodiments, the number of tubes 31 dedicated to respective flow regions HT, LT can be varied by linear movement of a partition 365, thereby changing the function of the cooling network 33, For example, fluid can enter the collecting tank 314 via a pipe or other inlet 341, and can flow through a set of tubes 31 on the left side of the partition 335 as viewed in Fig. 32 in the direction of a collecting tank (not shown) at an opposite end of the cooling network 33. At the opposite end of the cooling network 33, a portion of the partially cooled fluid can leave the heat exchanger, in some embodiments. The other portion of the fluid which is to be cooled further (i.e., the LT flow) can be diverted (see the arrow designated LT in Fig. 31) back into the cooling network 33, and can leave the heat exchanger via a pipe or other outlet 342. As also shown in Fig. 31, the cooling network area A subjected to cooling flow (shown in Figs. 26 and 27) can be divided into a LT flow region and a larger HT flow region. Thus, the longer path of the LT fluid flow shown in Fig. 31 can generate a temperature difference in the cooling network 33. By movement of the partition 335, the amount of the cooling network area A dedicated to the HT flow region can be increased or decreased, thereby decreasing or increasing the amount of cooling network area A dedicated to the LT flow region.

[00122] In the heat exchanger embodiment of Fig. 33, however, the entire cooling network area A (shown also in Fig. 28) is occupied by the LT flow region, whereas the HT flow region adjoins the LT flow region in a location behind the LT flow region (with respect to cooling air flow through the illustrated cooling network 33). The LT fluid and the HT fluid each flow through the network 33 in the same direction from the inlet tank 314 to the outlet tank 324, from where they are returned into the circuit. In some embodiments, the flow configuration shown in Fig. 33 results in a relatively low loss of pressure. In addition, the flows can be adjusted according to requirements by the moveable longitudinal partition 335. The schematic illustration of the cooling fluid (e.g., liquid) heat exchanger shown in Fig. 33 can be a plan view of a transverse flow heat exchanger as shown in Fig. 26 (that is to say, with collecting tanks 314, 324 arranged vertically at the left and right in a motor vehicle or other environment), or the schematic illustration can be a side view of a gravity-fed heat exchanger having vertical tubes and horizontal collecting tanks 314, 324 (e.g., as shown in Fig. 28).

[00123] In some embodiments, it is possible to provide different case-specific configurations of heat exchangers according to the present invention such that, for example, LT flow with the lowest temperature is situated at a cooling air inflow side and the entire area A of the cooling network 33 is covered by the LT flow. The same applies for the 32 case- specific heat exchanger configurations shown in Fig. 34 by way of example. The variants shown in Fig. 34 corresponding to arrangements of fixed and moveable longitudinal partitions 335 in inlet and outlet collecting tanks 314, 324, and can be considered possible candidates for use in different cooling systems. In Fig. 34, moveable longitudinal partitions 335 are shown with dashed lines and, in order to be distinguished therefrom, fixed longitudinal partitions 335 are shown with solid lines. [00124] As shown in the various schematically-illustrated embodiments of Fig. 34, the inlet collecting tank 314 is provided at the right-hand side of each embodiment, and the outlet collecting tank 324 is correspondingly situated at the left-hand side. Embodiments 12 and 14 shown in Fig. 34 illustrate the exemplary embodiments of Figs. 26 and 27, embodiment 13 illustrates the exemplary embodiment of Fig. 33, and embodiment 27 illustrates the exemplary embodiments shown in Figs. 24 and 25. It should be understood that although no inlet and outlet openings are shown in the schematic illustrations of Fig. 34, it is conceivable that a different desired flow path pattern can be generated by varying the number and arrangement of inlets and outlets assigned to the chambers in the collecting tanks 314, 324 shown therein.

[00125] Examples of applications for heat exchangers according to various embodiments of the present invention disclosed herein are shown in Figs. 35 and 36. In these examples, fluid that is to be cooled can enter an inlet collecting tank 412 through an opening 421. An outlet collecting tank 416 of each of the heat exchangers shown in Figs. 35 and 36 has a longitudinal partition 455 (indicated as lines in Figs. 35 and 36). The longitudinal partition 455 is used to establish a low-temperature (LT) flow region and a high-temperature (HT) flow region, wherein fluid leaves these regions and the outlet header 416 via respective openings. In some embodiments, the headers 412, 416 comprise plastic, while the longitudinal partition 355 can be an integral component of the collecting tank 412, 416, which can increase structural stability of the heat exchanger without increasing cost. In some embodiments, as shown in Fig. 36, the heat exchanger can include three longitudinal partitions 355, thereby allowing further flow regions to be defined. Any number of such partitions can exist in other embodiments of the present invention.

[00126] As shown in Fig. 34, the low-temperature fluid LT can be used, for example, for transmission oil heat exchange, while the high-temperature fluid HT can be used to cool oil for an engine. Other heat exchange requirements can be satisfied by a plurality of low- or high-temperature circuits in the heat exchange circuit, such as shown by way of example in Fig. 36. For example, one low-temperature flow region can serve to jointly cool electronic components and oil, and another low-temperature flow region can be used for indirect charge-air heat exchange. Yet another low-temperature flow region can be used for heat exchange with refrigerant of an air-conditioning system, or for other purposes. In some embodiments, the heat exchanger can be configured to produce temperature differences of about 7-11 K between low- and high-temperature flow regions, although other temperature differences are possible.

[00127] It should be understood that a longitudinal partition 455 can be located at various positions .within a collecting tank 412, 416 in order to satisfy fluctuating heat exchange demand in a heat exchange circuit. For example, using a longitudinal partition 455, the flow velocity V in a low-temperature LT flow region can be made identical to that in a high- temperature HT flow region. As a result, the heat exchange capacity provided by the heat exchanger can be realized despite the provision of a low-temperature flow region. However, it is also possible to install flow restriction elements used to influence the flow velocities V within certain limits (see Figs. 38 and 39). As shown in Fig. 35, for example, 472 indicates a location of flow resistance in the low-temperature LT flow region, which can include a throttle restrictor or other flow restriction device. A similar arrangement can also or instead be provided in the high-temperature HT flow region, which can allow better reaction to certain operating conditions, such as motor vehicle operating conditions.

[00128] Fig. 37 illustrates temperature profiles established in flows based upon the position of a longitudinal partition 455 in a heat exchanger according to an embodiment of the present invention. The temperature profiles illustrated in Fig. 37 can be generated based upon a heat exchange network with a depth T of about 55mm, which is plotted on the abscissa of the graph illustrated in Fig. 37. Heat exchange capacity is plotted on the right- hand ordinate of the graph, while the temperature of the heat exchange fluid is plotted on the left-hand ordinate of the graph. The curves illustrated in the graph show the temperature profiles in the LT flow region and in the HT flow region as a function of the position of the longitudinal partition 355. For example, if a longitudinal partition 355 is located at 40 mm for the high-temperature flow region and, therefore, at 15 mm for the low-temperature LT flow region, an outlet temperature of approximately 78°C is established in the HT flow region and an outlet temperature of approximately 68°C is established in the LT flow region. The profiles illustrated in Fig. 37 can be established under the boundary conditions of a heat exchange air temperature of approximately 29.5°C, a mass flow of approximately 8.89 kg/s, a heat exchange fluid inlet temperature of approximately 97°C, and mass flow of approximately 6.61 kg/s. [00129] Fig. 40 illustrates a heat exchanger according to another embodiment of the present invention, utilizing tubes 51 illustrated in Fig. 41. In the illustrated embodiment of Figs. 40 and 41, the inside region 575 of each tube 51 has a number of flow channels 516 defined at least in part by an insert 534 uniformly shaped or substantially uniformly shaped across the width of the insert 534. However, the illustrated heat exchanger 563 is provided with two different groups Gl , G2 of tubes 51 having flow channels 516 that are different from one another. In other embodiments, any number of such groups can be provided. Fluid flowing into or out of each group Gl, G2 of tubes 51 is separated from that of the other group G2, Gl by a transverse partition 573 in the collecting tank 567 extending in the direction of the depth of the heat exchanger 563. Different fluids can flow in each group Gl, G2 of tubes 51. For example, in one group Gl, a first media (e.g. oil) can flow, while in the other group G2, a second media (e.g. cooling fluid) can flow. The tubes 51 of group G2 are generally adapted for a medium which is under higher pressure than that in the tubes 51 of group G 1 , as can be seen from the use of narrower flow channels 516, smaller distances between walls of the insert 534, and the larger degree of reinforcement of the narrow sides 518, 520 in the tubes 51 of group G2 for relatively more stability. In some applications, the tubes 51 of group G2 can define a low temperature (LT) flow region of the heat exchanger 563, while the tubes 51 of group Gl can define a high temperature (HT) flow region of the heat exchanger 563.

[00130] Under the assumption that fluid flowing through the tubes 51 of group G2 is under a higher pressure than fluid in the tubes 51 of group Gl, the broad sides 522, 524 and the narrow sides 518, 520 of the tubes 51 of group G2 can be reinforced by the design of the insert 534 used therein. In particular, the corrugations of the inserts 534 in the tubes 51 of the illustrated group G2 are significantly narrower than those of the tubes 51 in the illustrated group Gl. Additionally, the narrow sides 518, 520 of the tubes 51 in the illustrated group G2 have five layers of material (two defined by overlapping longitudinal edges of first and second tube portions at the narrow sides 518, 520, and three defined by two folds on each longitudinal edge 538, 540 of the insert 534), whereas only three layers of material are located at the narrow sides 518, 520 of the tubes 51 in the illustrated group Gl based upon the lack of such insert folds. It should be noted that the tubes 51 within both groups Gl, G2 can be identical or substantially identical, and can both be equally adapted to receive different types of inserts 534, such as those shown in Fig. 41. Accordingly, the two different interior regions 575 in the tubes 51 are created in this particular embodiment by different inserts 534 defining two different groups of tubes 51 for the heat exchanger 563.

100131] Fig. 42 illustrates a heat exchanger according to yet another embodiment of the present invention, utilizing tubes 51 similar to that of Fig. 41. In this particular embodiment, the relative sizes of the interior regions 575a, 575b varies between the tubes 51 of the heat exchanger 563. In some embodiments (including the illustrated embodiment of Fig. 40, for example), the relative sizes of the interior regions 575a, 575b varies gradually from tube 51 to tube 51 across at least a portion of the heat exchanger 563. Accordingly, a collection tank 567 secured to the tubes 51 can have a partition 573a extending obliquely with respect to the ends of the tubes 51. The position of this partition 573a can correspond to the changing size of the interior regions 575a, 575b in the tubes 51. If desired, one or more additional partitions (e.g., partition 573b shown in Fig. 40) can be included in the collection tank 573 to provide further separations of flow through the heat exchanger 563 as desired.

[00132] An example of a one-piece tube 51 that can be utilized in any of the heat exchanger embodiments described above is shown in Fig. 43 by way of example. The one- piece tube 51 in Fig. 42 is substantially the same as the type shown in Fig. 41. The tubes of Fig. 43 have four times the thickness in narrow sides as compared to their broad sides 522, 524. Fig. 43 illustrates a method of forming a tube with a corrugated insert, and in which the tube has reinforced narrow sides.

[00133] The tubes in Figs. 44 and 45 can be produced from a single sheet of material, and can be used in place of any of the tubes in the embodiments described above. It should also be noted that tubes having any number of pieces (e.g., one-piece, two-piece, and three-piece tubes) can be used in place of any of the tubes in the embodiments described above. The narrow sides 518, 520 of both tubes illustrated in Figs. 44 and 45 include a triple thickness of the sheet of material used to form the tube. The sheet of material can be folded twice in the two areas of the sheet of material that will be bent to form the narrow sides 518, 520 of the tube (i.e., the areas adjacent and flanking that portion of the sheet of material shaped to define the integral insert 552), thereby increasing the thickness of the narrow areas by three, times that of the original material thickness. Furthermore, each longitudinal edge 571, 573 of the sheet of material can be bent and moved to encompass a respective reinforced section in the manner shown in Figs. 44 and 45. Both of these reinforced sections can be provided with a gradation for receiving the corresponding longitudinal edges 571, 573 in a recessed manner. In order to further reinforce the narrow sides 518, 520 of the tube, additional folds can be incorporated into the reinforced sections shown in Figs. 44 and 45. In the tube illustrated in Fig. 44, two groups of flow channels 516 are defined, each having a size that is different from those of the other group. In contrast, all the flow channels 516 in the illustrated embodiment of Fig. 45 are substantially the same in size.

[00134] Figs. 46 and 47 show a different tubes that can be produced from a single sheet of material. Like the other one-piece tubes described herein, both of the embodiments shown in Figs. 46 and 47 can be used in any of the heat exchangers described above. In particular, the tubes of Figs. 46 and 47 include narrow sides that are reinforced by the provision of vertical or horizontal folds. Additionally, Fig. 48 illustrates a tube 51 that can be produced from a single piece of sheet material, with an insert 524 that can be produced from another separate sheet of material. This particular tube 51 can also serve as a replacement for any of the tubes described above. In the embodiment of Fig. 48, one reinforced narrow side 518 is formed by bending a portion of the sheet of material having additional folds. The other reinforced narrow side 520 is formed by one longitudinal edge 571 of the sheet of material encompassing the opposite longitudinal edge 573 of the same sheet of material. This other narrow side 520 can also be distinguished by the fact that either or both longitudinal edges 571, 573 of the sheet of material can be folded for further reinforcement. The second sheet of material can be provided with a number of corrugations 552 as described above, and can also be provided with bends or folds at either or both longitudinal edges for further interior reinforcement of either or both narrow sides 518, 520.

[00135] Various features and advantages of the invention are set forth in the following claims.

Claims

CLAIMS •What is claimed is:

1. A heat exchanger comprising: tubes for regulating a temperature of a medium flowing in the tubes, ends of the tubes interacting with at least one of openings in a collecting tank and openings in a header tank connected to the collecting tank, at least one of the header tank and the collecting tank including a contour, the ends of the tubes including a contour.

2. A heat exchanger comprising: tubes for regulating a temperature of a medium flowing in the tubes, ends of the tubes interacting with at least one of openings in a collecting tank and openings in a header tank connected to the collecting tank, at least one of the header tank and the collecting tank including a contour, the ends of the tubes ending underneath the contour.

3. The heat exchanger of Claim 1 , wherein the contour of the tube ends corresponds at least partially to the contour of at least one of the header tank and the collecting tank.

4. The heat exchanger of Claim 1 , wherein the tubes are manufactured from a continuous sheet-metal strip on a roller train.

5. The heat exchanger of Claim 4, wherein the contour of the tube ends is manufactured in the course of the manufacture of the tubes.

6. The heat exchanger of Claim 4, wherein perforations corresponding to the contour of the tube ends are made in the sheet metal strip by means of rollers.

7. The heat exchanger of Claim 1 , wherein at least one of the contour of the tube ends and the contour of at least one of the header tank and the collecting tank is semicircular.

8. The heat exchanger of Claim 1, wherein at least one of the contour of the tube ends and the contour of at least one of the header tank and the collecting tank includes a corrugation.

9. The heat exchanger of Claim 1, wherein a counter on a wall of the collecting tank at least partially follows at least one of a contour of the header tank and the contour of the tube ends.

10. The heat exchanger of Claim 1 , further comprising a movable partition arranged in the collecting tank for directing the medium through a variable cross section of the tubes.

1 1. The heat exchanger of Claim 10, wherein the moveable partition cooperates with at least one of the contour of the tube ends and the contour of at least one of the header tank and the collecting power and permits power of the heat exchanger to be regulated.

12. The heat exchanger of Claim 11 , wherein the heat exchanger has a high temperature range and a low temperature range, wherein the ranges can be varied by the partition, and wherein the tubes are configured with longitudinal ducts that are substantially not connected in the transverse direction, in order to permit the ducts to be separated.

13. The heat exchanger of Claim 1 , wherein the wall thickness of the tubes is between approximately 0.03 mm and 0.15 mm.

14. A cooling liquid heat exchanger comprising:

tubes; fins arranged between the tubes, and at least one collecting tank, the tubes and the fins form a cooling network and have cooling air flowing through them in order to cool the cooling liquid flowing in the tubes, ends of the tubes interact with at least one of openings in collecting tanks or openings in tube bases connected to the collecting tanks, the at least one collecting tank includes at least one partition generating a low- temperature flow and a high temperature flow in the cooling liquid heat exchanger, the , partition moveable in order to vary at least one of the cross-sectional area, which has cooling liquid flowing in, of the tubes with regard to its size in relation to the low- temperature flow and the high-temperature flow and the number of tubes, which have cooling liquid flowing in, assigned to the low-temperature flow and the high-temperature flow, the moveable partition interacting with a tube base/collecting tank.

15. The cooling liquid heat exchanger of Claim 14, wherein the moveable partition is adjusted by at least of a linear movement and a rotational movement.

16. The cooling liquid heat exchanger of Claim 15, wherein the moveable partition includes a moveable longitudinal partition and the cross-sectional area of the tubes is varied by a rotational movement of the longitudinal partition transversely with respect to at least one of wide sides of the tubes and the longitudinal direction of the collecting tank.

17. The cooling liquid heat exchanger of Claim 16, wherein the low-temperature flow and the high-temperature flow extend over an area of the cooling network that has cooling air flowing in and extend over a part of a cooling network depth, wherein the high-temperature flow is situated behind the low-temperature flow as viewed in the flow direction of the cooling air.

18. The cooling liquid heat exchanger of Claim 17, wherein the collecting tank constituting the inlet collecting tank is formed without a division and wherein the moveable longitudinal partition is situated only in the collecting tank constituting the outlet collecting tank.

19. The cooling liquid heat exchanger of Claim 14, wherein the moveable partition includes a moveable transverse partition and wherein a number of tubes assigned to the low- temperature flow and the high-temperature flow are varied by a linear movement of the transverse partition in a longitudinal direction of the collecting tank.

20. The cooling liquid heat exchanger of Claim 14, wherein the at least one moveable partition is arranged in combination with at least one fixed partition.

21. The cooling liquid heat exchanger of Claim 20, wherein the moveable partition and the fixed partition are arranged in one collecting tank.

22. The cooling liquid heat exchanger of Claim 20, wherein the moveable partition is arranged in one collecting tank and the fixed partition is arranged in another collecting tank.

23. The cooling liquid heat exchanger of Claim 14, wherein the tube base/collecting tank includes a contour and the moveable partition being moveable along said contour so as to perform a rotational movement.

24. The cooling liquid heat exchanger of Claim 23, wherein the ends of the tubes do not protrude inwardly beyond the contour but end before the contour.

25. The cooling liquid heat exchanger of Claim 14, wherein the tubes are arranged and formed in a single row of tubes.

26. The cooling liquid heat exchanger of Claim 14, wherein the tubes are arranged in a plurality of rows in the cooling network and each of the plurality of rows being assigned to at least one of the low-temperature flow and the high-temperature flow.

27. The cooling liquid heat exchanger of Claim 14, further comprising a plurality of low- temperature flows.

28. The cooling liquid heat exchanger of Claim 25, wherein the tubes includes two narrow sides and two wide sides and are produced by shaping at least one endless sheet-metal strip with a thickness approximately between 0.03-0.20 mm.

29. The cooling liquid heat exchanger of Claim 28, wherein the tubes are produced from three endless sheet-metal strips, with two sheet-metal strips forming the wall of the tube and with the third sheet-metal strip constituting a corrugated inner insert forming chambers of the tube.

30. The cooling liquid heat exchanger of Claim 29, wherein the sheet-metal strips are of identical design, with one longitudinal edge of the sheet-metal strips having a larger curve than the other longitudinal edge and with two sheet-metal strips being arranged relative to one another in such a way that the larger curve of one sheet-metal strip engages around the smaller curve of the other sheet-metal strip in order to form the two narrow sides of the tube.

31. The cooling liquid heat exchanger of Claim 30, wherein the dimensions of the wide sides, extending in the cooling air flow direction, of the tubes are between approximately 20 and 300 mm.

32. The cooling liquid heat exchanger of Claim 14, further comprising at least two outlet openings on the outlet collecting tank, wherein the low-temperature flow and the high- temperature flow leave the heat exchanger through the at least two outlet openings at different temperatures.

33. The cooling liquid heat exchanger of Claim 14, further comprising an inlet opening on the inlet collecting tank, the inlet opening receiving at least a majority of the total cooling liquid flow.

34. The cooling liquid heat exchanger of Claim 14, further comprising an inlet opening and at least one outlet opening, which are separated by at least one of a fixed partition and a moveable partition, arranged on the inlet collecting tank.

35. A heat exchange liquid heat exchanger comprising: tubes; and fins disposed between the tubes, the tubes and the fins forming a heat exchange network and having heat exchange air flowing through in order to cool heat exchange liquid flowing in the tubes, ends of the tubes interacting with at least one of openings in headers and openings in tube plates connected to the headers, at least one of the headers including at least one partition producing a low- temperature flow and a high-temperature flow, the low-temperature flow extending over a surface of the heat exchange network onto which heat exchange air flows and extending over part of a depth of the heat exchange network, the high- temperature flow lying behind the low- temperature flow with respect to a direction of flow of the heat exchange air in the heat exchange liquid heat exchanger, at least one of the headers representing an inlet header and at least one of the headers representing an outlet header, the inlet header configured without a partition and the outlet header including one or more longitudinal partitions, the high-temperature flow and the low-temperature flow passing through the tubes in a common direction from the inlet header to the outlet header.

36. The heat exchange liquid heat exchanger of Claim 35, wherein the tubes are disposed and formed in a row of flat multi-chamber tubes.

37. The heat exchange liquid heat exchanger of Claim 35, wherein the tubes are disposed in a plurality of rows in the heat exchange network, with each row being assigned to at least one of the high- temperature flow and the low-temperature flow.

38. The heat exchange liquid heat exchanger of Claim 35, wherein the outlet header includes at least two outlet openings, the high-temperature flow and the low-temperature flow leaving the heat exchange liquid heat exchanger through the at least two outlet openings at different temperatures.

39. The heat exchange liquid heat exchanger of Claim 35, wherein the inlet header includes at least one inlet opening receive at least the majority of the heat exchange liquid.

40. The heat exchange liquid heat exchanger of Claim 35, further comprising a plurality of low-temperature flows.

41. The heat exchange liquid heat exchanger of Claim 36, wherein the flat multi-chamber tubes include two narrow sides and two wide sides, the two narrow sides and the two wide sides being produced by deformation of at least one endless sheet-metal strip with a thickness between approximately 0.03 and 0.20 mm.

42. The heat exchange liquid heat exchanger of Claim 36, wherein the flat multi-chamber tubes are produced from three endless sheet-metal strips, with two sheet-metal strips of the three endless sheet-metal strips forming the wall of a multi-chamber tube and a third sheet- metal strip of the three endless sheet-metal strips representing a corrugated inner insert used to form chambers of the multi-chamber tube.

43. The heat exchange liquid heat exchanger of Claim 42, wherein the two sheet-metal strips are identical in form and include a first sheet-metal strip and a second sheet-metal strip, the first sheet-metal strip having a longitudinal edge with a larger arc than a longitudinal edge of the second sheet-metal strip, the first sheet-metal strip and the second sheet-metal strip positioned with the longitudinal edge of the first sheet-metal strip engaged around the longitudinal edge of the second sheet-metal strip in order to form the two narrow sides of the multi-chamber tube.

44. The heat exchange liquid heat exchanger of Claim 41 , wherein the two wide sides of the flat multi-chamber tubes extend in a direction of flow of the heat exchange air and have a depth dimension between approximately 20 and 300 mm.