EP0582835B1 - Heat-exchanger - Google Patents

Heat-exchanger Download PDF

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Publication number
EP0582835B1
EP0582835B1 EP19930110974 EP93110974A EP0582835B1 EP 0582835 B1 EP0582835 B1 EP 0582835B1 EP 19930110974 EP19930110974 EP 19930110974 EP 93110974 A EP93110974 A EP 93110974A EP 0582835 B1 EP0582835 B1 EP 0582835B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
cooling
tube
tube sections
exchanger according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19930110974
Other languages
German (de)
French (fr)
Other versions
EP0582835A1 (en
Inventor
Erwin Dipl.-Ing. Haas
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Truck and Bus Osterreich AG
Original Assignee
Steyr Nutzfahrzeuge AG
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Filing date
Publication date
Application filed by Steyr Nutzfahrzeuge AG filed Critical Steyr Nutzfahrzeuge AG
Publication of EP0582835A1 publication Critical patent/EP0582835A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/062—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing tubular conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/14—Fastening; Joining by using form fitting connection, e.g. with tongue and groove

Definitions

  • the invention relates to a heat exchanger for cooling at least one medium flowing through by a cooling medium.
  • a heat exchanger with such a structure is known from DE-A-2 222 610.
  • the profile tubes there are only intended for assembly via plane-parallel outer surfaces and in one plane next to each other. This construction principle would not be applicable for the representation of a heat exchanger used for water and / or oil cooling of an internal combustion engine of a motor vehicle, because it is too expensive, too space-consuming and insufficient in terms of the cooling effect.
  • EP-A-0 061 779 discloses a heat exchanger wound from two tubes, through which the cooling medium is passed through one tube and the medium to be cooled is passed through the other tube.
  • a water cooler was used regularly, which consists of an upper and a lower water box, each connected to the cooling water circuit of the internal combustion engine, between which pipes with a continuous circular cross-section flow through which cooling water flows.
  • the said pipes are arranged in several pipe levels.
  • Between the tubes there are meandering strips of corrugated sheet metal that are used for heat dissipation to the cooling air flowing through the gaps. Since these outer corrugated sheets are not in direct contact with the medium to be cooled, there is a comparatively poor heat transfer, which can be compensated in part by a relatively high cooling air output.
  • Charge air coolers have generally been built on a principle similar to that of water coolers. On the other hand, a different construction principle was used for oil coolers.
  • the heat exchanger according to the invention allows a very compact production due to its construction principle, and it can also be used universally for cooling a wide variety of media. Another particular advantage is the high efficiency of the heat exchanger, since the partition walls given internally to the profile tubes are in direct contact with the medium to be cooled and the cooling medium, thus ensuring excellent heat transfer. Since the heat exchanger according to the invention is composed only of a large number of extruded profiles which can easily be produced on an industrial scale in corresponding systems, it can also be implemented at a reasonable cost. A special design of the partition walls also ensures that both the cooling medium and the medium to be cooled remain exactly separated when flowing through within a profile tube.
  • the heat exchanger is composed of a large number of polygonal, mutually toothed profile tubes 1 (see FIGS. 1 and 2) or 2, 3 (see FIGS. 3 and 4), the interiors of which are each provided by a large number of axially parallel, heat-dissipating partition walls 4 are divided into a plurality of flow channels 5, 6, 7 for such a separate passage of cooling media and media to be cooled.
  • profile tubes 1 of a single type with the same cross-section are used, with interiors of the same shape through the partitions 4.
  • two cross-section different profile tube types 2, 3, each with the same interior space designed specifically by the partition walls 4, but always the same, are used.
  • each of the profile tubes 1, 2, 3 is divided in the illustrated embodiments by the partitions 4 into three different flow areas, namely a central one with a single flow channel 5, an annular around this given with the flow channels 6 and an annular around this given outer with the flow channels 7.
  • the interior of each profile tube 1, 2, 3 is divided by the partitions 4 so that the different media can flow through the respective flow areas 5, 6, 7 separated from each other.
  • each of the profile tubes 1, 2, 3 including all of its partitions 4 can each be made in one piece by extrusion.
  • the outer wall 8, 9, 10 of each profiled tube 1, 2, 3 and the entirety of the associated internal partition walls 4 can each be realized separately by means of a separate extruded profile.
  • the outer wall 8, 9, 10 of each profile tube 1, 2, 3 can be realized together with some of the associated internal partition walls 4 by means of an extruded profile, while the rest of the internal partition walls 4 are realized by at least one further extruded profile.
  • each profile tube 1, 2, 3 and the associated partition walls 4 can, however, also be realized by a plurality of extruded profiles which are inserted coaxially one into the other, which case is shown in the drawing.
  • the outer wall 8 (Fig. 1, 2) or 9, 10 (Fig. 3, 4) of each profile tube 1, 2, 3 is realized by its own extruded profile, while the associated partition walls 4 are realized by two different extruded profiles. This embodiment is discussed in more detail below.
  • the identical profile tubes 1 of the heat exchanger according to FIGS. 1 and 2 have an outer wall 8 which is approximated to a hexagon and made of six different outer wall parts 8/1, 8/2, 8/3, 8/4, 8/5, 8/6 is that the profile tubes 1 are all in the same relative position, that is, not rotated relative to one another about their longitudinal axis, and can be assembled and when they are joined together, their profiled outer wall parts - as can be seen in FIG. 1 - interlockingly interlocked with one another to the system come.
  • the one profile tube type 3 has an outer wall 10 which is approximated to an octagon. Specifically, it consists of four identical, flat, crosswise opposite outer wall parts 10/1, 10/2, 10/3, 10/4 and four, each arranged between two of the aforementioned outer wall parts, and thus also crosswise diametrically opposite same longitudinal grooves 10 / 5, 10/6, 10/7, 10/8 with flat groove base.
  • the other profile tube type 2 however, has an outer wall 9 which is approximated to a square.
  • each other diametrically opposed outer wall parts 9/1, 9/2 which are essentially flat in parallel, but in the middle of their longitudinal extent a projecting, form-fitting into a longitudinal groove 10/5, 10/6, 10/7, 10 / 8 of the other profile tube type 10 have a matching longitudinal web 9/11, 9/21.
  • the other two, mirror images of each other diametrically opposed outer wall parts 9/3, 9/4 are formed by a projecting longitudinal web 9/31, 9/41 having longitudinal constrictions having such a shape that in each of them when joining the profile tubes 9, 10 a profile tube 10 with any two of it flat side surfaces and the groove in between fits exactly.
  • a projecting longitudinal web 9/31, 9/41 having longitudinal constrictions having such a shape that in each of them when joining the profile tubes 9, 10 a profile tube 10 with any two of it flat side surfaces and the groove in between fits exactly.
  • the profile tubes 1, 2, 3 are not each made in one piece with their internal partition walls by appropriate extruded profiles, it is expedient to ensure an exact separation between the media streams to be passed through within a profile tube 1, 2, 3. to realize one or more of the partitions 4 by an unprofiled or profiled tube.
  • the flow channel 5 is delimited by a partition 4/1, which are provided by a profiled tube, on which it integrally integrates with it, several other partition walls 4 directed radially towards the outer wall 8 of the profile tube 1. In this way, a defined separation between the central throughflow channel 5 and the central throughflow region containing the flow channels 6 is ensured.
  • a further partition 4/2 is formed by a profiled tube which is integrally united with several other partitions 4 directed radially towards the outer wall 8 of the profile tube 1.
  • the partitions 4 given radially on the inner tubular partition 4/1 extend to the inside of the outer part annular partition 4/2, two adjacent ones of said partition walls 4 together with the two tubular partition walls 4/1, 4/2 delimiting a flow channel 6.
  • the outgoing on the outer tubular partition 4/2 partitions 4 extend to the inside of the outer wall 8 of the profile tube 1, two of said partition walls together with the outer tubular partition 4/2 and the outer wall 8 of the profile tube 1 each having a flow channel 7 limit.
  • both tubular partitions 4/1, 4/2 can (as shown) radially outwards in the direction of the center of the profile tube 1, axially parallel and in the middle in a flow channel 6 or in the flow channel 5 projecting longitudinal webs 11 are formed, which for Serve to increase the heat transfer.
  • the arranged on the outer tubular partition 4/2 partitions 4 have a different length, so that this extruded profile can only be inserted into the profile tube 1 in a single possible position and thus precisely in terms of position.
  • the outer tubular partition 4/2 preferably has a rosette shape with eight wave crests and wave troughs which extend approximately sinusoidally along a pitch circle.
  • the partition walls 4 arranged on the preferably also rosette-shaped inner partition 4/1 all have the same length, so that this extruded profile can be inserted into the outer tubular partition 4/2 in eight different angular positions (each rotated by 45 °), the respective one Partition 4 extends into the interior of a wave crest.
  • the one profile tube 3 according to FIGS. 3 and 4 and its internal partitions 4,4 / 1, 4/2 are constructed.
  • real dividing walls 4 are arranged on the inside of the outer tubular dividing wall 4/2 radially to the center of the profiled tube 3, which extend to the outer surface of the inner tubular dividing wall 4/1.
  • a flow channel is formed in each case by a partition 4 projecting on the inside of the outer tubular partition 4/2 and a partition 4 projecting on the outside by the inner tubular partition 4/1 together with the inner and outer tubular partition 4/1, 4/2 6 limited.
  • the inner tubular partition 4/1 is designed as an unprofiled flat tube with a smooth outer wall.
  • the flow channels 6 are delimited here in each case by dividing walls 4 protruding on the inside from the outer tubular dividing wall 4/2 and reaching to the outer surface of the inner tubular dividing wall 4/1 together with the two tubular dividing walls 4/1, 4/2.
  • the heat exchanger composed of such internally divided profile tubes 1 or 2, 3 can be used in a variety of ways.
  • the central flow area of the profile pipes 1 or 2, 3 with the flow channels 6 given there by the cooling water of the internal combustion engine and the central (5) and outer flow area of the profile pipes 1 or 2, 3 with the Flow channels 7 flows through the cooling air generated by a cooling fan or an alternative cooling medium.
  • the central flow area 6 of the profile pipes 1 or 2, 3 is from the charge air to be cooled and the central (5) and outer flow area 7 of the profile pipes 1 or 2, 3 from that of one Cooling fan generated cooling air or an alternative cooling medium flows through
  • the central flow area 6 of the profile pipes 1 and 2, 3 is generated by the engine oil to be cooled and the central (5) and outer flow area 7 of the profile pipes 1 and 2, 3 are generated by a cooling fan Cooling air or an alternative cooling medium flows through.
  • the heat exchanger according to the invention advantageously allows the same to be used as a combined water and charge air and / or oil cooler of a supercharged internal combustion engine.
  • the profile tubes 1 or 2, 3 are a coherent heat exchanger area 12 for water cooling and the profile tubes 1 and 2, 3 of another connected heat exchanger area 13 for charge air cooling.
  • 6 schematically shows the use of the heat exchanger according to the invention as a combined water, charge air and oil cooler, the profile tubes 1 and 2, 3 of a first connected heat exchanger area 14 for water cooling, the profile tubes 1 and 2, 3 of a second connected Heat exchanger area 15 for charge air cooling and the profile tubes 1 and 2, 3 of a third coherent heat exchanger area 16 for oil cooling are used.
  • FIG. 7 it can be seen that for the supply of the medium to be cooled - water and / or charge air and / or oil - an inflow tank 17 is arranged on the front of the heat exchanger according to the invention and an outflow tank 18 is arranged on the rear of the heat exchanger according to the invention for collecting the cooled medium.
  • FIG. 8 shows an example for the supply of the medium to be cooled from the inflow container 17 and for the supply of the cooling medium into the heat exchanger according to the invention.
  • connecting pieces 19 which are connected at the end to the flow channels 6 and are sealed by sealing means.
  • a feed pipe 20 leads in from the side, which is connected and sealed at the end to the central flow channel 5 of the profile pipe 1 or 2 or 3 in question and serves to supply the cooling medium.
  • the cooling medium can enter from the environment around a connecting piece 19 on the end face.
  • This solution shown for the inlet area can equally be used for the outlet area of the heat exchanger according to the invention for connection to the outflow tank 18 given there.
  • the profile tubes 1, 2, 3 and the internal partition walls 4, 4, 1, 4, 2 and heat dissipation webs 11 can be made of a highly heat-conductive metallic material, for example aluminum or an aluminum alloy. However, it is also possible to make the outer walls 8, 9, 10 of the profiled tubes 1, 2, 3 from plastic, the partitions 4,4 / 1,4 / 2 and heat dissipation webs 11 from metal, eg aluminum or an aluminum alloy. It is also conceivable, in order to facilitate assembly, to paint the different extrusions in different colors or to produce them from differently colored materials.
  • the inflow container 17 and outflow container 18 are preferably formed together with the connecting piece 19 and feed pipes 20 by essentially one-piece plastic parts.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Description

Die Erfindung betrifft einen Wärmetauscher zur kühlung wenigstens eines durchströmenden Mediums durch ein kühlmedium.The invention relates to a heat exchanger for cooling at least one medium flowing through by a cooling medium.

Ein Wärmetauscher mit einem solchen Aufbau ist aus der DE-A- 2 222 610 bekannt. Die dortigen Profilrohre sind jedoch nur für einen Zusammenbau über planparallele Außenflächen und in einer Ebene nebeneinander vorgesehen. Für die Darstellung eines zur Wasser- und/oder Ölkühlung einer Brennkraftmaschine eines Kraftfahrzeuges dienenden Wärmetauschers wäre dieses Bauprinzip nicht anwendbar, weil zu teuer, zu raumaufwendig und von der Kühlwirkung her gesehen ungenügend.A heat exchanger with such a structure is known from DE-A-2 222 610. The profile tubes there are only intended for assembly via plane-parallel outer surfaces and in one plane next to each other. This construction principle would not be applicable for the representation of a heat exchanger used for water and / or oil cooling of an internal combustion engine of a motor vehicle, because it is too expensive, too space-consuming and insufficient in terms of the cooling effect.

Ferner ist aus der EP-A-0 061 779 ein aus zwei Rohren gewickelter Wärmetauscher bekannt, durch dessen eines Rohr das Kühlmedium und durch dessen anderes Rohr das zu kühlende Medium hindurchgeleitet wird.Furthermore, EP-A-0 061 779 discloses a heat exchanger wound from two tubes, through which the cooling medium is passed through one tube and the medium to be cooled is passed through the other tube.

Demgegenüber sind in Verbindung mit einer Brennkraftmaschine eines Fahrzeuges bisher zur Kühlung des Motorkühlwassers, der Ladeluft und des Motoröles jeweils eigene, ihrem Bauprinzip nach verschiedene Kühlertypen verwendet worden, jeder seinem speziellen Einsatzzweck entsprechend ausgestaltet und bemessen. Als Wasserkühler kam dabei regelmäßig ein solcher zur Anwendung, der aus einem oberen und einem unteren, jeweils an den Kühlwasserkreislauf der Brennkraftmaschine angeschlossenen Wasserkasten besteht, zwischen denen kühlwasserdurchflossene Rohre mit durchgehend kreisringförmigem Querschnitt verlaufen. Die besagten Rohre sind dabei in mehreren Rohrebenen angeordnet. Zwischen den Rohren sind mäanderförmig gefaltete Wellblechstreifen gegeben, die zur Wärmeableitung an die durch die Lücken durchströmende Kühlluft dienen. Da diese äußeren Wellbleche nicht in unmittelbarem Kontakt mit dem zu kühlenden Medium stehen, ergibt sich ein vergleichsweise schlechter Wärmeübergang, was teilweise durch eine relativ hohe Kühlluftleistung kompensierbar ist.In contrast, in connection with an internal combustion engine of a vehicle for cooling the engine cooling water, the charge air and the engine oil, different types of coolers, each based on their construction principle, have been used, each designed and dimensioned according to its specific purpose. A water cooler was used regularly, which consists of an upper and a lower water box, each connected to the cooling water circuit of the internal combustion engine, between which pipes with a continuous circular cross-section flow through which cooling water flows. The said pipes are arranged in several pipe levels. Between the tubes there are meandering strips of corrugated sheet metal that are used for heat dissipation to the cooling air flowing through the gaps. Since these outer corrugated sheets are not in direct contact with the medium to be cooled, there is a comparatively poor heat transfer, which can be compensated in part by a relatively high cooling air output.

Ladeluftkühler wurden bisher in der Regel nach einem ähnlichen Prinzip wie Wasserkühler gebaut. Für Ölkühler dagegen kam ein anderes Bauprinzip zur Anwendung.Charge air coolers have generally been built on a principle similar to that of water coolers. On the other hand, a different construction principle was used for oil coolers.

Es ist daher Aufgabe der Erfindung, einen Wärmetauscher der gattungsgemäßen Art dahingehend auszubilden, daß er universell zur Kühlung unterschiedlichster Medien wie Wasser, Luft oder Öl bei ein und demselben Kühlmedium, insbesondere Luft, verwendbar ist und gegenüber herkömmlichen Kühlern mit besserer Raumausnutzung auch einen höheren Kühlwirkungsgrad erbringt.It is therefore an object of the invention to design a heat exchanger of the generic type in such a way that it can be used universally for cooling a wide variety of media such as water, air or oil with one and the same cooling medium, in particular air, and also has a higher cooling efficiency than conventional coolers with better use of space he brings.

Diese Aufgabe ist erfindungsgemäß durch einem Wärmetauscher mit den im Anspruch 1 angegebenen Merkmalen gelöst.This object is achieved by a heat exchanger with the features specified in claim 1.

Vorteilhafte Ausgestaltungen des erfindungsgemäßen Wärmetauschers sind in den Unteransprüchen gekennzeichnet.Advantageous embodiments of the heat exchanger according to the invention are characterized in the subclaims.

Der erfindungsgemäße Wärmetauscher erlaubt aufgrund seines Bauprinzipes eines sehr kompakte Herstellung, außerdem ist er universell zur Kühlung der unterschiedlichsten Medien einsetzbar. Ein weiterer, besonderer Vorteil ist der hohe Wirkungsgrad des Wärmetauschers, da die intern der Profilrohre gegebenen Trennwände in unmittelbarem Kontakt mit dem zu kühlenden Medium und dem Kühlmedium stehen und somit ein hervorragender Wärmeübergang sichergestellt ist. Da der erfindungsgemäße Wärmetauscher sich nur aus einer Vielzahl von Strangpreßprofilen zusammensetzt, die großtechnisch in entsprechenden Anlagen leicht herstellbar sind, ist er auch mit vertretbarem Kostenaufwand realisierbar. Durch eine spezielle Gestaltung der Trennwände ist außerdem sichergestellt, daß innerhalb eines Profilrohres sowohl das Kühlmedium als auch das zu kühlende Medium beim Durchströmen exakt getrennt bleibt.The heat exchanger according to the invention allows a very compact production due to its construction principle, and it can also be used universally for cooling a wide variety of media. Another particular advantage is the high efficiency of the heat exchanger, since the partition walls given internally to the profile tubes are in direct contact with the medium to be cooled and the cooling medium, thus ensuring excellent heat transfer. Since the heat exchanger according to the invention is composed only of a large number of extruded profiles which can easily be produced on an industrial scale in corresponding systems, it can also be implemented at a reasonable cost. A special design of the partition walls also ensures that both the cooling medium and the medium to be cooled remain exactly separated when flowing through within a profile tube.

Nachstehend ist der erfindungsgemäße Wärmetauscher anhand mehrerer in der Zeichnung dargestellter Ausführungsbeispiele noch näher erläutert. In der Zeichnung zeigen:

Fig. 1
einen Querschnitt durch einen Ausschnitt aus einem erfindungsgemäßen Wärmetauscher, wobei eine erste Ausführungsform von Profilrohren und internen Trennwänden zur Anwendung kommt,
Fig. 2
ein bei der Ausführungsform gemäß Fig. 1 zur Anwendung kommendes Profilrohr samt internen Trennwänden in vergrößerter Einzeldarstellung,
Fig. 3
einen Querschnitt durch einen Ausschnitt aus einem erfindungsgemäßen Wärmetauscher, wobei eine zweite Ausführungsform von Profilrohren und internen Trennwänden zur Anwendung kommt,
Fig. 4
in vergrößerter Einzeldarstellung die beiden beim Ausführungsbeispiel gemäß Fig. 3 zur Anwendung kommenden Profilrohr-Typen samt interner Trennwände,
Fig. 5
in Prinzipdarstellung eine Anwendung des erfindungsgemäßen Wärmetauschers,
Fig. 6
in Prinzipdarstellung eine andere Verwendungsform des erfindungsgemäßen Wärmetauschers,
Fig. 7
in Prinzipdarstellung einen erfindungsgemäßen Wärmetauscher zusammen mit Zu- und Abflußorganen für Kühlmedium und zu kühlendes Medium, und
Fig. 8
eine Ausführungsform des Anschlusses des erfindungsgemäßen Wärmetauschers für Zu- bzw. Abführung des Kühlmediums und des zu kühlenden Mediums.
The heat exchanger according to the invention is explained in more detail below on the basis of several exemplary embodiments shown in the drawing. The drawing shows:
Fig. 1
3 shows a cross section through a section of a heat exchanger according to the invention, a first embodiment of profile tubes and internal partition walls being used,
Fig. 2
1 in the embodiment according to FIG. 1 profile tube including internal partition walls in an enlarged individual representation,
Fig. 3
3 shows a cross section through a section of a heat exchanger according to the invention, a second embodiment of profile tubes and internal partition walls being used,
Fig. 4
in an enlarged individual representation, the two types of profile tubes used in the exemplary embodiment according to FIG. 3, including internal partition walls,
Fig. 5
in principle an application of the heat exchanger according to the invention,
Fig. 6
another embodiment of the heat exchanger according to the invention,
Fig. 7
in a schematic representation of a heat exchanger according to the invention together with inflow and outflow elements for cooling medium and medium to be cooled, and
Fig. 8
an embodiment of the connection of the heat exchanger according to the invention for supplying and removing the cooling medium and the medium to be cooled.

Grundsätzlich ist der Wärmetauscher aus einer Vielzahl polygonaler, miteinander verzahnt direkt aneinander anliegender Profilrohre 1 (siehe Fig. 1 und 2) bzw. 2,3 (siehe Fig. 3 und 4) zusammengesetzt, deren Innenräume jeweils durch eine Vielzahl von achsparallelen, wärmeableitenden Trennwänden 4 in eine Vielzahl von Strömungskanälen 5, 6, 7 für eine solchermaßen getrennte Hindurchleitung von Kühlmedien und zu kühlenden Medien unterteilt sind. Im Beispiel gemäß Fig. 1 und 2 kommen dabei nur querschnittsgleiche Profilrohre 1 eines einzigen Typs mit durch die Trennwände 4 gleichgestalten Innenräumen zur Anwendung. Beim Beispiel gemäß Fig. 3 und 4 dagegen kommen zwei querschnittsverschiedene Profilrohr-Typen 2,3 mit jeweils speziell durch die Trennwände 4 gestalteten, je Profilrohr-Typ aber immer gleichen Innenräumen zur Anwendung.Basically, the heat exchanger is composed of a large number of polygonal, mutually toothed profile tubes 1 (see FIGS. 1 and 2) or 2, 3 (see FIGS. 3 and 4), the interiors of which are each provided by a large number of axially parallel, heat-dissipating partition walls 4 are divided into a plurality of flow channels 5, 6, 7 for such a separate passage of cooling media and media to be cooled. In the example according to FIGS. 1 and 2, only profile tubes 1 of a single type with the same cross-section are used, with interiors of the same shape through the partitions 4. In the example according to FIGS. 3 and 4, on the other hand, two cross-section different profile tube types 2, 3, each with the same interior space designed specifically by the partition walls 4, but always the same, are used.

Der Innenraum jedes der Profilrohre 1, 2, 3 ist bei den dargestellten Ausführungsbeispielen durch die Trennwände 4 in drei unterschiedliche Durchströmbereiche unterteilt, nämlich in einen zentralen mit einem einzigen Strömungskanal 5, einen ringförmig um diesen gegebenen mittleren mit den Strömungskanälen 6 und einen ringförmig um diesen gegebenen äußeren mit den Strömungskanälen 7. Grundsätzlich ist der Innenraum jedes Profilrohres 1, 2, 3 durch die Trennwände 4 so unterteilt, daß die unterschiedlichen Medien exakt von einander getrennt die jeweiligen Durchströmbereiche 5, 6, 7 durchströmen können.The interior of each of the profile tubes 1, 2, 3 is divided in the illustrated embodiments by the partitions 4 into three different flow areas, namely a central one with a single flow channel 5, an annular around this given with the flow channels 6 and an annular around this given outer with the flow channels 7. Basically, the interior of each profile tube 1, 2, 3 is divided by the partitions 4 so that the different media can flow through the respective flow areas 5, 6, 7 separated from each other.

Für die Realisierung der Profilrohre 1, 2, 3 und deren Innenraumaufteilung durch die Trennwände sind generell verschiedene Lösungen möglich. Beispielsweise kann jedes der Profilrohre 1, 2, 3 einschließlich aller seiner Trennwände 4 jeweils einstückig durch Strangpressen realisiert sein. Alternativ hierzu kann die Außenwand 8, 9, 10 jedes Profilrohres 1, 2, 3 und die Gesamtheit der zugehörigen internen Trennwände 4 getrennt davon jeweils durch ein eigenes Strangpreßprofil realisiert sein. In weiterer Alternative kann die Außenwand 8, 9, 10 jedes Profilrohres 1, 2, 3 zusammen mit einigen der zugehörigen internen Trennwände 4 durch ein Strangpreßprofil realisiert sein, während der Rest der internen Trennwände 4 durch wenigstens ein weiteres Strangpreßprofil realisiert ist. Schließlich können die Profilrohre 1, 2, 3 und die zugehörigen Trennwände 4 jedoch auch durch mehrere, koaxial ineinander gesteckte Strangpreßprofile realisiert sein, welcher Fall in der Zeichnung dargestellt ist. Dabei ist die Außenwand 8 (Fig. 1, 2) bzw. 9, 10 (Fig. 3, 4) jedes Profilrohres 1, 2, 3 durch ein eigenes Strangpreßprofil realisiert, während die zugehörigen Trennwände 4 durch zwei verschiedene Strangpreßprofile realisiert sind. Auf diese Ausführungsform ist nachfolgend näher eingegangen.Various solutions are generally possible for the realization of the profile tubes 1, 2, 3 and their interior division by the partition walls. For example each of the profile tubes 1, 2, 3 including all of its partitions 4 can each be made in one piece by extrusion. As an alternative to this, the outer wall 8, 9, 10 of each profiled tube 1, 2, 3 and the entirety of the associated internal partition walls 4 can each be realized separately by means of a separate extruded profile. In a further alternative, the outer wall 8, 9, 10 of each profile tube 1, 2, 3 can be realized together with some of the associated internal partition walls 4 by means of an extruded profile, while the rest of the internal partition walls 4 are realized by at least one further extruded profile. Finally, the profile tubes 1, 2, 3 and the associated partition walls 4 can, however, also be realized by a plurality of extruded profiles which are inserted coaxially one into the other, which case is shown in the drawing. The outer wall 8 (Fig. 1, 2) or 9, 10 (Fig. 3, 4) of each profile tube 1, 2, 3 is realized by its own extruded profile, while the associated partition walls 4 are realized by two different extruded profiles. This embodiment is discussed in more detail below.

Die identischen Profilrohre 1 des Wärmetauschers gemäß Fig. 1 und 2 weisen eine Außenwand 8 auf, die an ein Hexagon angenähert ist und aus sechs verschiedenen, derart in sich profilierten Außenwandteilen 8/1, 8/2, 8/3, 8/4, 8/5, 8/6 besteht, daß die Profilrohre 1 alle in gleicher Relativlage, das heißt, nicht gegeneinander um ihre Längsachse verdreht, zusammensetzbar sind und beim Zusammenfügen deren profilierte Außenwandteile - wie aus Fig. 1 ersichtlich - formschlüssig verzahnt ineinandergreifend aneinander zur Anlage kommen.The identical profile tubes 1 of the heat exchanger according to FIGS. 1 and 2 have an outer wall 8 which is approximated to a hexagon and made of six different outer wall parts 8/1, 8/2, 8/3, 8/4, 8/5, 8/6 is that the profile tubes 1 are all in the same relative position, that is, not rotated relative to one another about their longitudinal axis, and can be assembled and when they are joined together, their profiled outer wall parts - as can be seen in FIG. 1 - interlockingly interlocked with one another to the system come.

Beim Wärmetauscher gemäß Fig. 3 und 4 weist der eine Profilrohrtyp 3 eine Außenwand 10 auf, die an ein Oktogon angenähert ist. Im einzelnen besteht sie aus vier gleichen, ebenen, kreuzweise einander gegenüberliegenden Außenwandteilen 10/1, 10/2, 10/3, 10/4 und vier, jeweils zwischen zwei der vorgenannten Außenwandteilen angeordneten, einander somit auch kreuzweise diametral gegenüberliegenden gleichen Längsnuten 10/5, 10/6, 10/7, 10/8 mit ebenem Nutgrund. Der andere Profilrohrtyp 2 dagegen weist eine Außenwand 9 auf, die an ein Quadrat angenähert ist. Sie umfaßt zwei einander spiegelbildlich diametral gegenüberliegende Außenwandteile 9/1, 9/2, die parallel verlaufend im wesentlichen eben sind, aber in der Mitte ihrer Längserstreckung einen vorspringenden, formschlüssig in eine Längsnut 10/5, 10/6, 10/7, 10/8 des anderen Profilrohrtyps 10 einpassenden Längssteg 9/11, 9/21 haben. Die beiden anderen, einander spiegelbildlichen diametral gegenüberliegenden Außenwandteile 9/3, 9/4 sind durch am Grund einen vorspringenden Längssteg 9/31, 9/41 aufweisende Längseinschnürungen mit solcher Form gebildet sind, daß in jede derselben beim Zusammenfügen der Profilrohre 9,10 ein Profilrohr 10 mit zwei beliebigen seiner ebenen Seitenflächen und der dazwischen liegenden Nut exakt formschlüssig einpaßt. An drei solchermaßen in der Reihenfolge 2, 3, 2 zusammengesetzten Profilrohren (siehe Fig. 3 linke Vertikalreihe) schließen sich beim Zusammenbau seitlich drei in der Reihenfolge 3, 2, 3 zusammengesetzte Profilrohre an (siehe Fig. 3 rechte Vertikalreihe), wobei jedes der beiden Profilrohre 3 mit einer seiner Längsnuten 10/5, 10/6, 10/7, 10/8 den Längssteg 9/11 bzw. 9/21 des in der oberen und unteren Querreihe benachbarten Profilrohres 2 übergreift und das dazwischen gegebene Profilrohr 2 mit einem seiner Längsstege 9/11,9/21 in die zugewandte Längsnut des in der mittleren Querreihe benachbarten Profilrohres 3 eingreift sowie mit den beiderseits dieses Längssteges 9/11 bzw. 9/21 gegebenen Flächenteilen der Seitenfläche 9/1 bzw. 9/2 jeweils an den beiden einander benachbarten Flächenteilen der Seitenflächen 9/1 bzw. 9/2 der in der benachbarten Vertikalreihe gegebenen Profilrohre 2 zur Anlage kommt.3 and 4, the one profile tube type 3 has an outer wall 10 which is approximated to an octagon. Specifically, it consists of four identical, flat, crosswise opposite outer wall parts 10/1, 10/2, 10/3, 10/4 and four, each arranged between two of the aforementioned outer wall parts, and thus also crosswise diametrically opposite same longitudinal grooves 10 / 5, 10/6, 10/7, 10/8 with flat groove base. The other profile tube type 2, however, has an outer wall 9 which is approximated to a square. It comprises two diametrically opposed outer wall parts 9/1, 9/2, which are essentially flat in parallel, but in the middle of their longitudinal extent a projecting, form-fitting into a longitudinal groove 10/5, 10/6, 10/7, 10 / 8 of the other profile tube type 10 have a matching longitudinal web 9/11, 9/21. The other two, mirror images of each other diametrically opposed outer wall parts 9/3, 9/4 are formed by a projecting longitudinal web 9/31, 9/41 having longitudinal constrictions having such a shape that in each of them when joining the profile tubes 9, 10 a profile tube 10 with any two of it flat side surfaces and the groove in between fits exactly. At three such profiled tubes assembled in this way (2, 3, 2) (see Fig. 3 left vertical row) three assembly tubes laterally assembled in sequence 3, 2, 3 (see Fig. 3 right vertical row), each of which two profile tubes 3 with one of its longitudinal grooves 10/5, 10/6, 10/7, 10/8 overlaps the longitudinal web 9/11 or 9/21 of the adjacent profile tube 2 in the upper and lower transverse rows and the profile tube 2 given between them one of its longitudinal webs 9 / 11,9 / 21 engages in the facing longitudinal groove of the profile tube 3 adjacent in the middle transverse row, and with the surface parts of the side surface 9/1 and 9/2 respectively on both sides of this longitudinal web 9/11 and 9/21, respectively comes to rest on the two adjacent surface parts of the side surfaces 9/1 and 9/2 of the profile tubes 2 given in the adjacent vertical row.

Für den Fall, daß die Profilrohre 1, 2, 3 nicht jeweils einstückig mit ihren intern gegebenen Trennwänden durch entsprechende Strangpreßprofile realisiert sind, ist es, um innerhalb eines Profilrohres 1, 2, 3 eine exakte Trennung zwischen den durchzuleitenden Medienströmen zu gewährleisten, zweckmäßig, eine oder mehrere der Trennwände 4 selbst durch ein unprofiliertes bzw. profiliertes Rohr zu realisieren. Beim Ausführungsbeispiel gemäß Fig. 1 und 2 ist der Strömungskanal 5 durch eine Trennwand 4/1 begrenzt, die durch ein profiliertes Rohr, an dem einstückig mit diesem vereinigt, mehrere andere strahlenförmig zur Außenwand 8 des Profilrohres 1 hin gerichtete Trennwände 4 gegeben sind. Auf diese Weise ist eine definierte Trennung zwischen dem zentralen Durchströmkanal 5 und dem die Strömungskanäle 6 enthaltenden mittleren Durchströmbereich gewährleistet. Eine exakte Trennung zwischen dem mittleren und dem äußeren Durchströmbereich ist dadurch gewährleistet, daß eine weitere Trennwand 4/2 durch ein profiliertes Rohr gebildet ist, das einstückig mit mehreren anderen, strahlenförmig zur Außenwand 8 des Profilrohres 1 hin gerichteten Trennwänden 4 vereinigt ist. Dabei erstrecken sich die strahlenförmig an der inneren rohrförmigen Trennwand 4/1 gegebenen Trennwände 4 bis zur Innenseite der äußeren ringförmigen Trennwand 4/2, wobei jeweils zwei benachbarte dieser besagten Trennwände 4 zusammen mit den beiden rohrförmigen Trennwänden 4/1, 4/2 einen Strömungskanal 6 begrenzen. Die an der äußeren rohrförmigen Trennwand 4/2 nach außen abgehenden Trennwände 4 reichen bis zur Innenseite der Außenwand 8 des Profilrohres 1, wobei jeweils zwei dieser besagten Trennwände zusammen mit der äußeren rohrförmigen Trennwand 4/2 und der Außenwand 8 des Profilrohres 1 jeweils einen Strömungskanal 7 begrenzen. An beiden rohrförmigen Trennwänden 4/1, 4/2 können (wie dargestellt) innen strahlenförmig in Richtung Zentrum des Profilrohres 1 abgehende , achsparallel verlaufende und jeweils mittig in einen Strömungskanal 6 bzw. in den Strömungskanal 5 hineinragende Längsstege 11 mit angeformt sein, die zur Erhöhung des Wärmeüberganges dienen. Die an der äußeren rohrförmigen Trennwand 4/2 angeordneten Trennwände 4 haben eine unterschiedliche Länge, so daß dieses Strangpreßprofil nur in einer einzig möglichen Stellung und damit exakt lagemäßig vorgegeben in das Profilrohr 1 eingeschoben werden kann. Ferner hat die äußere rohrförmige Trennwand 4/2 vorzugsweise eine Rosettenform mit acht Wellenbergen und Wellentälern, die sich etwa sinusförmig längs eines Teilkreises erstrecken. Die an der vorzugsweise ebenfalls rosettenförmigen inneren Trennwand 4/1 angeordneten Trennwände 4 haben alle die gleiche Länge, so daß dieses Strangpreßprofil in acht verschiedenen Winkelstellungen (jeweils um 45° verdreht) in die äußere rohrförmige Trennwand 4/2 einsteckbar ist, wobei sich die jeweilige Trennwand 4 in das Innere eines Wellenberges hinein erstreckt.In the event that the profile tubes 1, 2, 3 are not each made in one piece with their internal partition walls by appropriate extruded profiles, it is expedient to ensure an exact separation between the media streams to be passed through within a profile tube 1, 2, 3. to realize one or more of the partitions 4 by an unprofiled or profiled tube. In the embodiment according to FIGS. 1 and 2, the flow channel 5 is delimited by a partition 4/1, which are provided by a profiled tube, on which it integrally integrates with it, several other partition walls 4 directed radially towards the outer wall 8 of the profile tube 1. In this way, a defined separation between the central throughflow channel 5 and the central throughflow region containing the flow channels 6 is ensured. An exact separation between the middle and the outer flow area is ensured by the fact that a further partition 4/2 is formed by a profiled tube which is integrally united with several other partitions 4 directed radially towards the outer wall 8 of the profile tube 1. The partitions 4 given radially on the inner tubular partition 4/1 extend to the inside of the outer part annular partition 4/2, two adjacent ones of said partition walls 4 together with the two tubular partition walls 4/1, 4/2 delimiting a flow channel 6. The outgoing on the outer tubular partition 4/2 partitions 4 extend to the inside of the outer wall 8 of the profile tube 1, two of said partition walls together with the outer tubular partition 4/2 and the outer wall 8 of the profile tube 1 each having a flow channel 7 limit. On both tubular partitions 4/1, 4/2 can (as shown) radially outwards in the direction of the center of the profile tube 1, axially parallel and in the middle in a flow channel 6 or in the flow channel 5 projecting longitudinal webs 11 are formed, which for Serve to increase the heat transfer. The arranged on the outer tubular partition 4/2 partitions 4 have a different length, so that this extruded profile can only be inserted into the profile tube 1 in a single possible position and thus precisely in terms of position. Furthermore, the outer tubular partition 4/2 preferably has a rosette shape with eight wave crests and wave troughs which extend approximately sinusoidally along a pitch circle. The partition walls 4 arranged on the preferably also rosette-shaped inner partition 4/1 all have the same length, so that this extruded profile can be inserted into the outer tubular partition 4/2 in eight different angular positions (each rotated by 45 °), the respective one Partition 4 extends into the interior of a wave crest.

Ähnlich wie das Profilrohr 1 und dessen interne Trennwände 4,4/1,4/2 sind auch das eine Profilrohr 3 gemäß Fig. 3 und 4 sowie dessen interne Trennwände 4,4/1, 4/2 aufgebaut. Unterschiedlich ist jedoch dort, daß anstelle der Längsstege 11 hier echte Trennwände 4 an der äußeren rohrförmigen Trennwand 4/2 innen strahlenförmig zum Zentrum des Profilrohres 3 hingerichtet angeordnet sind, die bis zur Außenfläche der inneren rohrförmigen Trennwand 4/1 reichen. Auf diese Weise wird jeweils von einer innen an der äußeren rohrförmigen Trennwand 4/2 vorspringenden Trennwand 4 und einer außen an der inneren rohrförmigen Trennwand 4/1 vorspringenden Trennwand 4 zusammen mit innerer und äußerer rohrförmiger Trennwand 4/1, 4/2 jeweils ein Strömungskanal 6 begrenzt.Similar to the profile tube 1 and its internal partitions 4,4 / 1,4 / 2, the one profile tube 3 according to FIGS. 3 and 4 and its internal partitions 4,4 / 1, 4/2 are constructed. What is different, however, is that, instead of the longitudinal webs 11, real dividing walls 4 are arranged on the inside of the outer tubular dividing wall 4/2 radially to the center of the profiled tube 3, which extend to the outer surface of the inner tubular dividing wall 4/1. In this way, a flow channel is formed in each case by a partition 4 projecting on the inside of the outer tubular partition 4/2 and a partition 4 projecting on the outside by the inner tubular partition 4/1 together with the inner and outer tubular partition 4/1, 4/2 6 limited.

Innerhalb des anderen Profilrohres 2 gemäß Fig. 3 und 4 sind geringfügige Abweichungen bei der Gestaltung der Trennwände 4,4/1,4/2 gegeben, insofern, als hier die innere rohrförmige Trennwand 4/1 als unprofiliertes Flachrohr mit glatter Außenwand ausgebildet ist. Außerdem werden hier die Strömungskanäle 6 jeweils durch innen an der äußeren rohrförmigen Trennwand 4/2 abragende und bis zur Außenfläche der inneren rohrförmigen Trennwand 4/1 reichende Trennwände 4 zusammen mit den beiden rohrförmigen Trennwänden 4/1, 4/2 begrenzt.3 and 4, there are slight deviations in the design of the partition walls 4.4 / 1.4 / 2, insofar as here the inner tubular partition 4/1 is designed as an unprofiled flat tube with a smooth outer wall. In addition, the flow channels 6 are delimited here in each case by dividing walls 4 protruding on the inside from the outer tubular dividing wall 4/2 and reaching to the outer surface of the inner tubular dividing wall 4/1 together with the two tubular dividing walls 4/1, 4/2.

Der aus solchen intern aufgeteilten Profilrohren 1 bzw. 2, 3 zusammengesetzte Wärmetauscher ist in vielfältiger Weise anwendbar.The heat exchanger composed of such internally divided profile tubes 1 or 2, 3 can be used in a variety of ways.

Bei Verwendung des erfindungsgemäßen Wärmetauschers als Wasserkühler einer Brennkraftmaschine werden der mittlere Durchströmbereich der Profilrohre 1 bzw. 2, 3 mit den dort gegebenen Strömungskanälen 6 vom Kühlwasser der Brennkraftmaschine und der zentrale (5) sowie äußere Durchströmbereich der Profilrohre 1 bzw. 2, 3 mit den Strömungskanälen 7 von der von einem Kühllüfter erzeugten Kühlluft oder einem alternativen Kühlmedium durchströmt.When using the heat exchanger according to the invention as a water cooler of an internal combustion engine, the central flow area of the profile pipes 1 or 2, 3 with the flow channels 6 given there by the cooling water of the internal combustion engine and the central (5) and outer flow area of the profile pipes 1 or 2, 3 with the Flow channels 7 flows through the cooling air generated by a cooling fan or an alternative cooling medium.

Bei Verwendung des erfindungsgemäßen Wärmetauschers als Ladeluftkühler einer aufgeladenen Brennkraftmaschine werden der mittlere Durchströmbereich 6 der Profilrohre 1 bzw. 2, 3 von der zu kühlenden Ladeluft und der zentrale (5) sowie äußere Durchströmbereich 7 der Profilrohre 1 bzw. 2, 3 von der von einem Kühllüfter erzeugten Kühlluft oder einem alternativen Kühlmedium durchströmtWhen using the heat exchanger according to the invention as the charge air cooler of a supercharged internal combustion engine, the central flow area 6 of the profile pipes 1 or 2, 3 is from the charge air to be cooled and the central (5) and outer flow area 7 of the profile pipes 1 or 2, 3 from that of one Cooling fan generated cooling air or an alternative cooling medium flows through

Bei Verwendung des erfindungsgemäßen Wärmetauschers als Ölkühler einer Brennkraftmaschine werden der mittlere Durchströmbereich 6 der Profilrohre 1 bzw. 2, 3 vom zu kühlenden Motoröl und der zentrale (5) sowie äußere Durchströmbereich 7 der Profilrohre 1 bzw. 2, 3 von der von einem Kühllüfter erzeugten Kühlluft oder einem alternativen Kühlmedium durchströmt.When using the heat exchanger according to the invention as an oil cooler of an internal combustion engine, the central flow area 6 of the profile pipes 1 and 2, 3 is generated by the engine oil to be cooled and the central (5) and outer flow area 7 of the profile pipes 1 and 2, 3 are generated by a cooling fan Cooling air or an alternative cooling medium flows through.

Der erfindungsgemäße Wärmetauscher läßt in vorteilhafter Weise eine Verwendung desselben als kombinierter Wasser- und Ladeluft- und/oder Ölkühler einer aufgeladenen Brennkraftmaschine zu.The heat exchanger according to the invention advantageously allows the same to be used as a combined water and charge air and / or oil cooler of a supercharged internal combustion engine.

Bei Verwendung des erfindungsgemäßen Wärmetauschers als kombinierter Wasser- und Ladeluftkühler, was schematisiert in Fig. 5 angedeutet ist, sind die Profilrohre 1 bzw. 2, 3 eines zusammenhängenden Wärmetauscherbereiches 12 zur Wasserkühlung und die Profilrohre 1 bzw. 2, 3 eines anderen zusammenhängenden Wärmetauscherbereiches 13 zur Ladeluftkühlung herangezogen. In Fig. 6 ist schematisch die Verwendung des erfindungsgemäßen Wärmetauschers als kombinierter Wasser-, Ladeluft- und Ölkühler dargestellt, wobei die Profilrohre 1 bzw. 2, 3 eines ersten zusammenhängenden Wärmetauscherbereiches 14 zur Wasserkühlung, die Profilrohre 1 bzw. 2, 3 eines zweiten zusammenhängenden Wärmetauscherbereiches 15 zur Ladeluftkühlung und die Profilrohre 1 bzw. 2, 3 eines dritten zusammenhängenden Wärmetauscherbereiches 16 zur Ölkühlung herangezogen sind.When using the heat exchanger according to the invention as a combined water and charge air cooler, which is indicated schematically in FIG. 5, the profile tubes 1 or 2, 3 are a coherent heat exchanger area 12 for water cooling and the profile tubes 1 and 2, 3 of another connected heat exchanger area 13 for charge air cooling. 6 schematically shows the use of the heat exchanger according to the invention as a combined water, charge air and oil cooler, the profile tubes 1 and 2, 3 of a first connected heat exchanger area 14 for water cooling, the profile tubes 1 and 2, 3 of a second connected Heat exchanger area 15 for charge air cooling and the profile tubes 1 and 2, 3 of a third coherent heat exchanger area 16 for oil cooling are used.

Aus Fig. 7 ist ersichtlich, daß zur Zuführung des zu kühlenden Mediums - Wasser und /oder Ladeluft und/oder Öl - frontseitig des erfindungsgemäßen Wärmetauschers ein Zuströmbehälter 17 und rückseitig des erfindungsgemäßen Wärmetauschers ein Abströmbehälter 18 zur Sammlung des gekühlten Mediums angeordnet ist.From Fig. 7 it can be seen that for the supply of the medium to be cooled - water and / or charge air and / or oil - an inflow tank 17 is arranged on the front of the heat exchanger according to the invention and an outflow tank 18 is arranged on the rear of the heat exchanger according to the invention for collecting the cooled medium.

In Fig. 8 ist ein Beispiel für die Zuführung des zu kühlenden Mediums aus dem Zuströmbehälter 17 und für die Zuführung des Kühlmediums in den erfindungsgemäßen Wärmetauscher dargestellt. Dabei sind zur Verbindung des Zuströmbehälters 17 mit den Profilrohren 1 bzw. 2, 3 Anschlußstutzen 19 gegeben, die stirnseitig an den Strömungskanälen 6 angeschlossen und durch Dichtungsmittel abgedichtet sind. In jeden dieser Anschlußstutzen 19 führt seitlich ein Zuführrohr 20 herein, das am zentralen Strömungskanal 5 des betreffenden Profilrohres 1 bzw. 2 bzw. 3 stirnseitig angeschlossen und abgedichtet ist und zur Zuführung des Kühlmediums dient. In die äußeren Strömungskanäle 7 der Profilrohre 1 bzw. 2 bzw. 3 kann das Kühlmedium aus dem Umfeld um einen Anschlußstutzen 19 stirnseitig eintreten. Diese für den Eintrittsbereich dargestellte Lösung kann gleichermaßen auch für den Austrittsbereich des erfindungsgemäßen Wärmetauschers zur Verbindung mit dem dort gegebenen Abströmbehälter 18 verwendet werden.FIG. 8 shows an example for the supply of the medium to be cooled from the inflow container 17 and for the supply of the cooling medium into the heat exchanger according to the invention. For connecting the inflow container 17 to the profile pipes 1 and 2, 3 there are connecting pieces 19 which are connected at the end to the flow channels 6 and are sealed by sealing means. In each of these connecting pieces 19, a feed pipe 20 leads in from the side, which is connected and sealed at the end to the central flow channel 5 of the profile pipe 1 or 2 or 3 in question and serves to supply the cooling medium. In the outer flow channels 7 of the profile tubes 1 or 2 or 3, the cooling medium can enter from the environment around a connecting piece 19 on the end face. This solution shown for the inlet area can equally be used for the outlet area of the heat exchanger according to the invention for connection to the outflow tank 18 given there.

Die Profilrohre 1, 2, 3 und die intern derselben gegebenen Trennwände 4,4/1,4/2 sowie Wärmeableitstege 11 können aus gut wärmeleitendem metallischem Material, z.B. Aluminium bzw. einer Aluminiumlegierung, hergestellt werden. Es ist jedoch auch möglich, die Außenwände 8, 9, 10 der Profilrohre 1, 2, 3 aus Kunststoff, die Trennwände 4,4/1,4/2 und Wärmeableitstege 11 dagegen aus Metall, z.B. Aluminium bzw. einer Aluminiumlegierung, herzustellen. Ebenso ist es denkbar, um das Zusammenfügen zu erleichtern, die unterschiedlichen Strangpreßteile farbunterschiedlich zu lackieren bzw. diese aus unterschiedlich eingefärbten Materialien herzustellen. Der Zuströmbehälter 17 und Abströmbehälter 18 werden zusammen mit den Anschlußstutzen 19 und Zuführrohren 20 vorzugsweise durch im wesentlichen einstückige Kunststoffteile gebildet.The profile tubes 1, 2, 3 and the internal partition walls 4, 4, 1, 4, 2 and heat dissipation webs 11 can be made of a highly heat-conductive metallic material, for example aluminum or an aluminum alloy. However, it is also possible to make the outer walls 8, 9, 10 of the profiled tubes 1, 2, 3 from plastic, the partitions 4,4 / 1,4 / 2 and heat dissipation webs 11 from metal, eg aluminum or an aluminum alloy. It is also conceivable, in order to facilitate assembly, to paint the different extrusions in different colors or to produce them from differently colored materials. The inflow container 17 and outflow container 18 are preferably formed together with the connecting piece 19 and feed pipes 20 by essentially one-piece plastic parts.

Claims (18)

  1. A heat exchanger for cooling at least one through-flowing medium by a cooling medium, in particular for cooling an internal-combustion engine of a motor vehicle by cooling water and/or charge air and/or oil, formed by a plurality of extruded tube sections arranged extending towards one another, either
    a) of the same type (1) with the same cross-section, or
    b) of two types (2, 3) with different cross-sections,
    but with a generally polygonal external shape such that, when joined together, the tube sections (1 or 2, 3 respectively) come to rest directly against one another with positively locking indentations and form a honeycomb-like join, wherein either
    - a plurality of tube sections of type (1) according to a) can be grouped around a further tube section of the same type (1), or
    - a plurality of tube sections of the same cross-section of one type (2) can be grouped around a tube section of the other type (3) of different cross-section according to b),
    and the interior of each tube section (1, 2, 3) is subdivided by a plurality of axially parallel heat-dissipating partition walls (4, 4/1, 4/2) into a plurality of flow ducts (5, 6, 7) for a separate through passage in this way of cooling medium and medium to be cooled.
  2. A heat exchanger according to Claim 1, characterized in that the tube sections (1, 2, 3) including their partition walls (4, 4/1, 4/2) are each formed integrally by an extruded section.
  3. A heat exchanger according to Claim 1, characterized in that the outer wall (8, 9, 10) of the tube sections (1, 2, 3) and associated partition walls (4, 4/1, 4/2) are formed by a plurality of extruded sections insertible into one another coaxially.
  4. A heat exchanger according to Claim 3, characterized in that the outer wall (8, 9, 10) of a tube section (1, 2, 3) and the partition walls (4, 4/1, 4/2) are each formed by a separate extruded section.
  5. A heat exchanger according to Claim 3, characterized in that the outer wall (8, 9, 10) of a tube section (1, 2, 3) and some of the partition walls (4) attached thereto are formed by an extruded section, whereas the remainder of the partition walls (4, 4/1, 4/2) are formed by at least one further extruded section.
  6. A heat exchanger according to Claim 3, characterized in that the outer wall (8, 9, 10) of a tube section (1, 2, 3) is formed by an extruded section, and the partition walls (4, 4/1, 4/2) are formed by at least two different extruded sections.
  7. A heat exchanger according to one of Claims 1 to 6, characterized in that the tube sections (1) of the type according to a) have an outer wall (8) which resembles a hexagon and comprises six different outer wall parts (8/1, 8/2, 8/3, 8/4, 8/5, 8/6) profiled in such a way that, when the tube sections (1) are joined together, they rest against one another with the profiled outer wall parts thereof engaging in one another with positively locking indentations.
  8. A heat exchanger according to one of Claims 1 to 6, characterized in that the tube section (3) of one type according to b) has an outer wall (10) which resembles an octagon and comprises four equal, flat outer wall parts (10/1, 10/2, 10/3, 10/4) diagonally opposite one another and four equal longitudinal channels (10/5, 10/6, 10/7, 10/8) with a flat base each arranged between two of the aforesaid outer wall parts and also therefore diametrically opposite one another, whereas the tube section (2) of the other type according to b) has an outer wall (9) resembling a square, wherein two outer wall parts (9/1, 9/2) diametrically opposite each other are essentially flat but are each provided in the middle with a projecting longitudinal web (9/11, 9/21) fitting into a longitudinal channel (10/5, 10/6, 10/7, 10/8) in the other type of tube section (3) with positive locking, and wherein the two other outer wall parts (9/3, 9/4) diametrically opposite each other are formed by longitudinal constrictions provided at the base with a projecting longitudinal web (9/31, 9/41) and having such a shape that, when the two types of tube sections (2, 3) are joined together, two flat lateral faces (10/1, 10/4 and 10/2, 10/3 respectively) and the channel (10/8, 10/6) situated therebetween fit with positive locking in the longitudinal constriction (9/3, 9/4) with the longitudinal web (9/31, 9/41).
  9. A heat exchanger according to one of Claims 2 to 6, characterized in that one or more of the partition walls (4) is or are formed by a profiled or non-profiled tube (4/1, 4/2).
  10. A heat exchanger according to Claim 9, characterized in that a partition wall (4/1, 4/2) formed by a profiled tube is used for integrally joining a plurality of other partition walls (4) directed in a radiating manner towards the outer wall (8, 9, 10) of the tube section (1, 2, 3).
  11. A heat exchanger according to one of the preceding Claims, characterized in that the interior of each of the tube sections (1, 2, 3) is subdivided by the partition walls (4, 4/1, 4/2) into three different through-flow areas, namely a central through-flow area (5), an intermediate through-flow area with the flow ducts (6) arranged in an annular manner around the said central through-flow area (5) and an outer through-flow area with the flow ducts (7) arranged in an annular manner around the said intermediate through-flow area.
  12. A heat exchanger according to Claim 11, characterized in that when it is used as a water cooler of an internal-combustion engine the flow ducts (6) of the intermediate through-flow area of the tube sections (1; 2, 3) are traversed by the cooling water of the internal-combustion engine, and the central through-flow area (5) and the through-flow area of the tube sections (1; 2, 3) formed by the outer flow ducts (7) are traversed by the cooling air produced by a cooling fan or a cooling medium as an alternative thereto.
  13. A heat exchanger according to Claim 11, characterized in that when it is used as a charge-air cooler of a supercharged internal-combustion engine the intermediate through-flow area of the tube sections (1; 2, 3) produced by the flow ducts (6) is traversed by the charge air to be cooled, and the central through-flow area (5) and the outer through-flow area of the tube sections (1; 2, 3) formed by the flow ducts (7) are traversed by the cooling air produced by a cooling fan or a cooling medium as an alternative thereto.
  14. A heat exchanger according to Claim 11, characterized in that when it is used as an oil cooler of an internal-combustion engine the intermediate through-flow area of the tube sections (1; 2; 3) produced by the flow ducts (6) is traversed by the engine oil to be cooled, and the central through-flow area (5) and the outer through-flow area of the tube sections (1; 2, 3) formed by the flow ducts (7) are traversed by the cooling air produced by a cooling fan or a cooling medium as an alternative thereto.
  15. A heat exchanger according to Claims 12 and 13, characterized in that when it is used as a combined water and charge-air cooler of a supercharged internal-combustion engine the tube sections (1; 2, 3) of an integrated heat-exchanger area (12) are used for water cooling, and the tube sections (1; 2, 3) of another integrated heat-exchanger area (13) are used for charge-air cooling.
  16. A heat exchanger according to Claims 12 to 14, characterized in that when it is used as a combined water, charge-air and oil cooler of a supercharged internal-combustion engine the tube sections (1; 2, 3) of a first integrated heat-exchanger area (14) are used for water cooling, the tube sections (1; 2, 3) of a second integrated heat-exchanger area (15) are used for charge-air cooling, and the tube sections (1; 2, 3) of a third integrated heat-exchanger area (16) are used for oil cooling.
  17. A heat exchanger according to one of the preceding Claims, characterized in that the tube sections (1; 2, 3), the partition walls (4, 4/1, 4/2) produced in the interior thereof, and the longitudinal webs (11) possibly provided are produced from a good heat-dissipating metallic material,
  18. A heat exchanger according to one of Claims 1 to 16, characterized in that the outer walls (8, 9, 10) of the tube sections (1; 2, 3) are produced from plastics material, whereas the partition walls (4, 4/1, 4/2) and the longitudinal webs (11) possibly provided are produced, on the other hand, from metal, such as aluminium or an aluminium alloy.
EP19930110974 1992-08-11 1993-07-09 Heat-exchanger Expired - Lifetime EP0582835B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT161492A AT401431B (en) 1992-08-11 1992-08-11 HEAT EXCHANGER
AT1614/92 1992-08-11

Publications (2)

Publication Number Publication Date
EP0582835A1 EP0582835A1 (en) 1994-02-16
EP0582835B1 true EP0582835B1 (en) 1997-04-16

Family

ID=3517233

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930110974 Expired - Lifetime EP0582835B1 (en) 1992-08-11 1993-07-09 Heat-exchanger

Country Status (3)

Country Link
EP (1) EP0582835B1 (en)
AT (1) AT401431B (en)
DE (1) DE59306161D1 (en)

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EP3356167A4 (en) * 2015-06-03 2019-06-19 Sfercoci, Petru Air conditioning system and engine cooling for vehicles by means of exhaust gas

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DE10030627A1 (en) * 2000-06-28 2002-01-17 Ultrafilter Internat Ag Heat exchangers for refrigeration dryer systems
DE10038624C2 (en) * 2000-08-03 2002-11-21 Broekelmann Aluminium F W Heat transfer tube with twisted inner fins
DE10149330A1 (en) * 2001-10-06 2003-04-17 Bosch Gmbh Robert Heat exchanger for a gas heater, especially a condensing boiler
DE10261922A1 (en) * 2002-12-24 2004-07-15 Kaeser Kompressoren Gmbh refrigeration dryer
ES2263399B1 (en) * 2006-04-28 2007-11-16 Dayco Ensa S.L. ALUMINUM HEAT EXCHANGER FOR AN "EGR" SYSTEM.
EP2146173B1 (en) * 2008-07-17 2015-09-09 MAHLE International GmbH Plastic heat exchanger
CN103958997A (en) * 2012-02-17 2014-07-30 普罗维涅创新科技有限公司 Heat-exchange apparatus
JP2015102277A (en) * 2013-11-25 2015-06-04 協同アルミ株式会社 Multi-hole pipe
JP2019526016A (en) * 2016-05-10 2019-09-12 モメンティブ パフォーマンス マテリアルズ インコーポレイテッドＭｏｍｅｎｔｉｖｅ Ｐｅｒｆｏｒｍａｎｃｅ Ｍａｔｅｒｉａｌｓ Ｉｎｃ． Pyrolytic graphite tube equipment for directional thermal management
US11781813B2 (en) * 2020-12-18 2023-10-10 Hamilton Sundstrand Corporation Multi-scale unitary radial heat exchanger core

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Also Published As

Publication number Publication date
AT401431B (en) 1996-09-25
DE59306161D1 (en) 1997-05-22
EP0582835A1 (en) 1994-02-16
ATA161492A (en) 1996-01-15

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