EP1763651A1 - Heat exchanger, particularly a charge-air cooler for motor vehicles - Google Patents

Heat exchanger, particularly a charge-air cooler for motor vehicles

Info

Publication number
EP1763651A1
EP1763651A1 EP05772434A EP05772434A EP1763651A1 EP 1763651 A1 EP1763651 A1 EP 1763651A1 EP 05772434 A EP05772434 A EP 05772434A EP 05772434 A EP05772434 A EP 05772434A EP 1763651 A1 EP1763651 A1 EP 1763651A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
flat tubes
depth
range
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.)
Ceased
Application number
EP05772434A
Other languages
German (de)
French (fr)
Inventor
Daniel Hendrix
Joachim Kopp
Jürgen Wegner
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1763651A1 publication Critical patent/EP1763651A1/en
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators

Definitions

  • the invention relates to a heat exchanger, in particular a charge air cooler for motor vehicles, according to the preamble of claim 1.
  • Known heat exchanger consist of a heat exchanger block (or called network) and arranged on both sides collecting boxes for the entry and exit or the collection and distribution of a Cyprusü ⁇ transfer medium, z. As coolant or charge air.
  • the heat exchanger block consists of mutually parallel tubes, z.
  • the corrugated fins used which are soldered to the pipes.
  • On the inside of the tubes in particular in the case of flat tubes, so-called internal corrugated ribs or turbulence generators are arranged to improve the heat transfer and are likewise soldered to the tube. This results in a stable internal pressure-resistant bandage for the heat exchanger block.
  • the tubes open with their tube ends in tube sheets, which parts of the collecting tanks or are connected to the collecting boxes.
  • the tubesheets have passages in which the tube ends are soldered.
  • a similar heat exchanger was known from DE-A 198 57435.
  • single or multi-row systems heat exchanger blocks
  • one or more rows of tubes are separated by an air gap. arranged one behind the other.
  • single-row networks are used for lower powers and double-row networks for higher powers, the latter at depths of more than about 70 mm.
  • Double-row systems have several disadvantages: they are both expensive to manufacture and worse in performance. For the production two rows of tubes must be cassetted with a Maschinentube ⁇ the rib and inserted into two rows of passages in the tube sheets.
  • the passages in the tubesheets must have a minimum distance in the depth direction for production-technical reasons, which also specifies the distance of the rows of tubes in the network. This air gap increases the pressure drop on the cooling air side and increases the overall depth of the heat exchanger.
  • the tube plates only a series of passages, ie the gaps between the passages in the cooling air flow direction and between the rows of tubes omitted.
  • the depth of the flat tubes is in a range of 70 to 100 mm, and particularly advantageously in a range of 80 to 90 mm.
  • the depth of the flat tubes lies in a range of 90 to 120 mm, and particularly advantageously in a range of 90 to 100 mm.
  • the flat tubes have a clear width in a range between 3 and 10 mm, preferably between 5 and 10 mm, in particular in a range of 6 to 8 mm, the optimum at a clear width of 7 mm is located.
  • a clear width in a range between 3 and 10 mm, preferably between 5 and 10 mm, in particular in a range of 6 to 8 mm, the optimum at a clear width of 7 mm is located.
  • inner corrugated ribs or turbulence inserts are arranged in the flat tubes, which are soldered to the flat tubes. This achieves the advantage of a better heat transfer and an increased internal pressure resistance for the flat tubes, which is necessary in particular at an increased depth.
  • the single FIGURE shows a detail of a heat exchanger block 1, which is constructed from a (number word) series of flat tubes 2 and arranged between them corrugated fins 3.
  • Flat tubes 2 and corrugated fins 3 are part of an intercooler, not shown, which cools the air (charge air) of a supercharged, not shown internal combustion engine of a motor vehicle by ambient air (cooling air).
  • the charge air flows through the flat tubes 2 perpendicular to the plane of the drawing, and the ambient or cooling air flows in the direction of the arrow L between the flat tubes 2 via the corrugated fins 3, which are provided with gills 4 to improve the heat transfer.
  • inner corrugated fins 5 are arranged, which form the cross section of the flat tubes 2 into a multiplicity of chambers divide and are soldered to the flat tubes 2 on the inside.
  • the corrugated fins 4 are soldered to the outside of the flat tubes 2. In this respect, there is a good heat conduction from the inside of Flachroh ⁇ re 2 on the outside.
  • the flat tubes 2 are - as explained at the beginning of the prior art - held in non-illustrated passages of tube sheets and soldered to them. On the tube sheets not shown collecting boxes, so-called air boxes are placed.
  • the depth T, d. H. the extent of the flat tubes 2 and the corrugated fins 3 in the air flow direction L is denoted by T.
  • T The depth T, d. H. the extent of the flat tubes 2 and the corrugated fins 3 in the air flow direction L.
  • the inside width of the flat tubes 2 is characterized by the dimension H.
  • the dimension T is in a narrower range of 80 to 90 mm, in a further range between 70 and 100 mm and in a wide range of 70 to 120 mm.
  • the flat tubes 2 are vor ⁇ preferably made of an aluminum sheet and welded to the narrow side in the longitudinal direction.
  • the corrugated fins 3 (cooling air fins) and the inner corrugated fins 5 (charge air fins) are made of thin aluminum sheet and are soldered to the flat tubes 2. This results in a compact, pressure-stable heat transfer block 1.

Landscapes

  • 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)

Abstract

The invention relates to a heat exchanger, particularly a charge-air cooler for motor vehicles, comprised of a heat exchanger block (1), which is formed by flat tubes (2) and corrugated fins (3), and of collecting receptacles that communicate with the flat tubes (2). The flat tubes (2) can be flowed through by a medium to be cooled, and the corrugated fins (3) can be flowed around by ambient air. The invention provides that the flat tubes (2) are arranged in a row and have a depth T, which is measured in the direction of air flow L and which ranges from 70 ≤ T ≤ 120 mm.

Description

BEHR GmbH & Co. KG Mauserstraße 3, 70469 Stuttgart BEHR GmbH & Co. KG Mauserstrasse 3, 70469 Stuttgart
Wärmeübertrager, insbesondere Ladeluftkühler für KraftfahrzeugeHeat exchangers, in particular intercoolers for motor vehicles
Die Erfindung betrifft einen Wärmeübertrager, insbesondere einen Ladeluft¬ kühlerfür Kraftfahrzeuge nach dem Oberbegriff des Patentanspruches 1.The invention relates to a heat exchanger, in particular a charge air cooler for motor vehicles, according to the preamble of claim 1.
Bekannte Wärmeübertrager bestehen aus einem Wärmeübertragerblock (oder auch Netz genannt) und beiderseits angeordneten Sammelkästen für den Ein- und Austritt bzw. die Sammlung und Verteilung eines Wärmeü¬ bertragermediums, z. B. Kühlmittel oder Ladeluft. Der Wärmeübertragerblock besteht aus parallel zueinander angeordneten Rohren, z. B. Flachrohren und Rippen, welche die Wärmeübertragungsfläche auf der Außenseite der Rohre erhöhen und von Umgebungsluft überströmt werden. Bei Flachrohren wer¬ den Wellrippen verwendet, die mit den Rohren verlötet werden. Auf der In¬ nenseite der Rohre, insbesondere bei Flachrohren sind zur Verbesserung der Wärmeübertragung so genannte Innenwellrippen oder Turbulenzerzeu¬ ger angeordnet, die ebenfalls mit dem Rohr verlötet werden. Dadurch ergibt sich ein stabiler innendruckfester Verband für den Wärmeübertragerblock. Die Rohre münden mit ihren Rohrenden in Rohrböden, welche Teile der Sammelkästen oder mit den Sammelkästen verbunden sind. Die Rohrböden weisen Durchzüge auf, in welchen die Rohrenden verlötet sind. Ein ähnlicher Wärmeübertrager wurde durch die DE-A 198 57435 bekannt.Known heat exchanger consist of a heat exchanger block (or called network) and arranged on both sides collecting boxes for the entry and exit or the collection and distribution of a Wärmeü¬ transfer medium, z. As coolant or charge air. The heat exchanger block consists of mutually parallel tubes, z. B. flat tubes and ribs, which increase the heat transfer surface on the outside of the tubes and are covered by ambient air. For flat tubes wer¬ the corrugated fins used, which are soldered to the pipes. On the inside of the tubes, in particular in the case of flat tubes, so-called internal corrugated ribs or turbulence generators are arranged to improve the heat transfer and are likewise soldered to the tube. This results in a stable internal pressure-resistant bandage for the heat exchanger block. The tubes open with their tube ends in tube sheets, which parts of the collecting tanks or are connected to the collecting boxes. The tubesheets have passages in which the tube ends are soldered. A similar heat exchanger was known from DE-A 198 57435.
Je nach Leistung des Wärmeübertragers werden ein- oder mehrreihige Sys¬ teme (Wärmeübertragerblöcke) verwendet, d. h. in Strömungsrichtung der Kühlluft sind eine oder mehrere Rohrreihen, getrennt durch einen Luftspalt, hintereinander angeordnet. Insbesondere bei luftgekühlten Ladeluftkühlem für die Kühlung der Verbrennungsluft von Brennkraftmaschinen für Kraftfahr¬ zeuge werden bei geringeren Leistungen einreihige Netze und bei höheren Leistungen zweireihige Netze eingesetzt, und zwar letztere bei Bautiefen von mehr als etwa 70 mm. Zweireihige Systeme haben verschiedene Nachteile: sie sind sowohl in der Herstellung teurer als auch in der Leistung schlechter. Für die Herstellung müssen zwei Reihen von Rohren mit einer durchgehen¬ den Rippe kassettiert und in zwei Reihen von Durchzügen in den Rohrböden gesteckt werden. Die Durchzüge in den Rohrböden müssen aus fertigungs- technischen Gründen in Tiefenrichtung einen Mindestabstand aufweisen, welcher auch den Abstand der Rohrreihen im Netz vorgibt. Dieser Luftspalt erhöht den Druckabfall auf der Kühlluftseite und vergrößert die Bautiefe des Wärmeübertragers.Depending on the performance of the heat exchanger, single or multi-row systems (heat exchanger blocks) are used, ie in the flow direction of the cooling air one or more rows of tubes are separated by an air gap. arranged one behind the other. Particularly in the case of air-cooled intercoolers for cooling the combustion air of internal combustion engines for motor vehicles, single-row networks are used for lower powers and double-row networks for higher powers, the latter at depths of more than about 70 mm. Double-row systems have several disadvantages: they are both expensive to manufacture and worse in performance. For the production two rows of tubes must be cassetted with a durchgehen¬ the rib and inserted into two rows of passages in the tube sheets. The passages in the tubesheets must have a minimum distance in the depth direction for production-technical reasons, which also specifies the distance of the rows of tubes in the network. This air gap increases the pressure drop on the cooling air side and increases the overall depth of the heat exchanger.
Es ist Aufgabe der Erfindung, einen Wärmeübertrager der eingangs genann¬ ten Art hinsichtlich seiner Herstellungskosten und seiner thermodynamischen Leistung zu verbessern.It is an object of the invention to improve a heat exchanger of the genann¬ th type with respect to its production costs and its thermodynamic performance.
Die Lösung dieser Aufgabe ergibt sich aus den Merkmalen des Patentan- spruchs 1. Erfindungsgemäß ist vorgesehen, dass der Wärmeübertra¬ gerblock nur eine Reihe von Flachrohren mit einer Tiefe T aufweist, die grö¬ ßer als 70 mm und kleiner als 120 mm ist. Ein einreihiger Wärmeübertrager, insbesondere Ladeluftkühler mit einer derartigen Tiefe in Strömungsrichtung der Kühlluft bringt Vorteile sowohl bei der Herstellung und den Kosten als auch in der Leistung. Bekannte Wärmeübertrager, insbesondere Ladeluft¬ kühler wurden bei dieser Tiefe zweireihig ausgeführt. Demgegenüber benö¬ tigt das erfindungsgemäße System nur eine Reihe von Flachrohren, eine durchgehende Wellrippe auf der Kühlluftseite und eine Innenwellrippe auf der Ladeluftseite. Ein solches System lässt sich wesentlich einfacher als ein zweireihiges System kassettieren. Darüber hinaus weisen die Rohrböden nur eine Reihe von Durchzügen auf, d. h. die Spalte zwischen den Durchzügen in Kühlluftströmungsrichtung und zwischen den Rohrreihen entfallen. Es er¬ gibt sich also der zusätzliche Vorteil einer geringeren Bautiefe und eines ge¬ ringeres Druckabfalls auf der Primär- und der Sekundärseite. Nach einer vorteilhaften Weiterbildung der Erfindung liegt die Tiefe der Flachrohre in einem Bereich von 70 bis 100 mm, und besonders vorteilhaft in einem Bereich von 80 bis 90 mm.The solution to this problem results from the features of patent claim 1. According to the invention, it is provided that the heat exchanger block has only a series of flat tubes with a depth T that is greater than 70 mm and less than 120 mm. A single-row heat exchanger, in particular intercooler with such a depth in the flow direction of the cooling air brings advantages in both the production and the cost as well as in the performance. Known heat exchangers, in particular charge air coolers, were designed in two rows at this depth. In contrast, the system according to the invention requires only a series of flat tubes, a continuous corrugated rib on the cooling air side and an inner corrugated rib on the charge air side. Such a system is much easier to cassett than a two-tier system. In addition, the tube plates only a series of passages, ie the gaps between the passages in the cooling air flow direction and between the rows of tubes omitted. Thus, there is the additional advantage of a smaller overall depth and a lower pressure drop on the primary side and the secondary side. According to an advantageous development of the invention, the depth of the flat tubes is in a range of 70 to 100 mm, and particularly advantageously in a range of 80 to 90 mm.
Nach einer weiteren Ausbildung der Erfindung liegt die Tiefe der Flachrohre in einem Bereich von 90 bis 120 mm, und besonders vorteilhaft in einem Be¬ reich von 90 bis 100 mm.According to a further embodiment of the invention, the depth of the flat tubes lies in a range of 90 to 120 mm, and particularly advantageously in a range of 90 to 100 mm.
Nach einer vorteilhaften Weiterbildung der Erfindung weisen die Flachrohre eine lichte Weite in einem Bereich zwischen 3 und 10 mm, bevorzugt zwi¬ schen 5 und 10 mm, insbesondere in einem Bereich von 6 bis 8 mm auf, wobei das Optimum bei einer lichten Weite von 7 mm liegt. Für einen sol¬ chen Querschnitt der Flachrohre ergeben sich erhöhte Leistungen für den Wärmeübertrager.According to an advantageous development of the invention, the flat tubes have a clear width in a range between 3 and 10 mm, preferably between 5 and 10 mm, in particular in a range of 6 to 8 mm, the optimum at a clear width of 7 mm is located. For such a cross section of the flat tubes, there are increased outputs for the heat exchanger.
Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung sind in den Flachrohren Innenwellrippen bzw. Turbulenzeinlagen angeordnet, die mit den Flachrohren verlötet sind. Dadurch erreicht man den Vorteil eines besse¬ ren Wärmeüberganges und einer erhöhten Innendruckfestigkeit für die Flachrohre, was insbesondere bei einer erhöhten Tiefe notwendig ist.According to a further advantageous embodiment of the invention inner corrugated ribs or turbulence inserts are arranged in the flat tubes, which are soldered to the flat tubes. This achieves the advantage of a better heat transfer and an increased internal pressure resistance for the flat tubes, which is necessary in particular at an increased depth.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird im Folgenden näher beschrieben.An embodiment of the invention is illustrated in the drawing and will be described in more detail below.
Die einzige Figur zeigt einen Ausschnitt eines Wärmeübertragerblockes 1, welcher aus einer (Zahlwort) Reihe von Flachrohren 2 und zwischen diesen angeordneten Wellrippen 3 aufgebaut ist. Flachrohre 2 und Wellrippen 3 sind Teil eines nicht dargestellten Ladeluftkühlers, welcher die Luft (Ladeluft) eines aufgeladenen nicht dargestellten Verbrennungsmotors eines Kraftfahr- zeuges durch Umgebungsluft (Kühlluft) kühlt. Die Ladeluft durchströmt die Flachrohre 2 senkrecht zur Zeichenebene, und die Umgebungs- bzw. Kühl¬ luft strömt in Richtung des Pfeils L zwischen den Flachrohren 2 über die Wellrippen 3, welche zur Verbesserung der Wärmeübertragung mit Kiemen 4 versehen sind. Innerhalb der Flachrohre 2 sind Innenwellrippen 5 angeord- net, welche den Querschnitt der Flachrohre 2 in eine Vielzahl von Kammern unterteilen und mit den Flachrohren 2 auf deren Innenseite verlötet sind. Die Wellrippen 4 dagegen sind auf mit der Außenseite der Flachrohre 2 verlötet. Insofern ergibt sich eine gute Wärmeleitung von der Innenseite der Flachroh¬ re 2 auf deren Außenseite. Die Flachrohre 2 sind - wie eingangs zum Stand der Technik erläutert - in nicht dargestellten Durchzügen von Rohrböden gehalten und mit diesen verlötet. Auf die Rohrböden sind nicht dargestellte Sammelkästen, so genannte Luftkästen aufgesetzt.The single FIGURE shows a detail of a heat exchanger block 1, which is constructed from a (number word) series of flat tubes 2 and arranged between them corrugated fins 3. Flat tubes 2 and corrugated fins 3 are part of an intercooler, not shown, which cools the air (charge air) of a supercharged, not shown internal combustion engine of a motor vehicle by ambient air (cooling air). The charge air flows through the flat tubes 2 perpendicular to the plane of the drawing, and the ambient or cooling air flows in the direction of the arrow L between the flat tubes 2 via the corrugated fins 3, which are provided with gills 4 to improve the heat transfer. Inside the flat tubes 2, inner corrugated fins 5 are arranged, which form the cross section of the flat tubes 2 into a multiplicity of chambers divide and are soldered to the flat tubes 2 on the inside. The corrugated fins 4, however, are soldered to the outside of the flat tubes 2. In this respect, there is a good heat conduction from the inside of Flachroh¬ re 2 on the outside. The flat tubes 2 are - as explained at the beginning of the prior art - held in non-illustrated passages of tube sheets and soldered to them. On the tube sheets not shown collecting boxes, so-called air boxes are placed.
Die Bautiefe T, d. h. die Erstreckung der Flachrohre 2 und der Wellrippen 3 in Luftströmungsrichtung L ist mit T bezeichnet. Wesentlich ist allerdings das Maß T für die Flachrohre 2, die Wellrippen 3 dagegen können ein etwas kleineres oder größeres Maß aufweisen, d. h. gegenüber den Schmalseiten der Flachrohre 2 zurück oder über diese hinaus stehen. Die lichte Weite der Flachrohre 2 ist durch das Maß H gekennzeichnet. Für eine bevorzugte Aus- führungsform der Flachrohre 2 liegt das Maß T in einem engeren Bereich von 80 bis 90 mm, in einem weiteren Bereich zwischen 70 und 100 mm so¬ wie in einem breiten Bereich von 70 bis 120 mm. Die Flachrohre 2 sind vor¬ zugsweise aus einem Aluminiumblech hergestellt und an der Schmalseite in Längsrichtung verschweißt. Die Wellrippen 3 (Kühlluftrippen) und die Innen- wellrippen 5 (Ladeluftrippen) sind aus dünnem Aluminiumblech hergestellt und werden mit den Flachrohren 2 verlötet. Dies ergibt einen kompakten, druckstabilen Wärmeübertragerblock 1. The depth T, d. H. the extent of the flat tubes 2 and the corrugated fins 3 in the air flow direction L is denoted by T. However, it is essential that the dimension T for the flat tubes 2, the corrugated fins 3, however, may have a slightly smaller or larger size, d. H. stand back against the narrow sides of the flat tubes 2 or beyond this. The inside width of the flat tubes 2 is characterized by the dimension H. For a preferred embodiment of the flat tubes 2, the dimension T is in a narrower range of 80 to 90 mm, in a further range between 70 and 100 mm and in a wide range of 70 to 120 mm. The flat tubes 2 are vor¬ preferably made of an aluminum sheet and welded to the narrow side in the longitudinal direction. The corrugated fins 3 (cooling air fins) and the inner corrugated fins 5 (charge air fins) are made of thin aluminum sheet and are soldered to the flat tubes 2. This results in a compact, pressure-stable heat transfer block 1.

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Wärmeübertrager, insbesondere Ladeluftkühler für Kraftfahrzeuge, bestehend aus einem durch Flachrohre (2) und Wellrippen (3) gebil¬ deten Wärmeübertragerblock (1 ) sowie aus mit den Flachrohren (2) kommunizierenden Sammelkästen, wobei die Flachrohre (2) von ei¬ nem zu kühlenden Medium durchströmbar und die Wellrippen (3) von Umgebungsluft überströmbar sind, dadurch gekennzeichnet, dass die Flachrohre (2) in einer Reihe (einreihig) angeordnet sind, eine in Luftströmungsrichtung L gemessene Tiefe T aufweisen und dass die Tiefe in einem Bereich von 70 ≤ T < 120 mm liegt.1. Heat exchanger, in particular intercooler for motor vehicles, consisting of a through flat tubes (2) and corrugated fins (3) gebil¬ Deten heat exchanger block (1) and from the flat tubes (2) communicating manifolds, wherein the flat tubes (2) of ei¬ NEM permeable to medium to be cooled and the corrugated fins (3) are surrounded by ambient air, characterized in that the flat tubes (2) in a row (single row) are arranged, having a measured in the air flow direction L depth T and that the depth in a range of 70 ≤ T <120 mm.
2. Wärmeübertrager nach Anspruch 1 , dadurch gekennzeichnet, dass die Tiefe in einem Bereich von 70 ≤ T ≤ 100 mm liegt.2. Heat exchanger according to claim 1, characterized in that the depth is in a range of 70 ≤ T ≤ 100 mm.
3. Wärmeübertrager nach Anspruch 1 oder 2, dadurch gekennzeich¬ net, dass die Tiefe in einem Bereich von 80 ≤ T ≤ 90 mm liegt.3. Heat exchanger according to claim 1 or 2, characterized gekennzeich¬ net, that the depth is in a range of 80 ≤ T ≤ 90 mm.
4. Wärmeübertrager nach Anspruch 1 , dadurch gekennzeichnet, dass die Tiefe in einem Bereich von 90 ≤ T ≤ 120 mm liegt.4. Heat exchanger according to claim 1, characterized in that the depth is in a range of 90 ≤ T ≤ 120 mm.
5. Wärmeübertrager nach einem der Ansprüche 1 bis 4, dadurch ge- kennzeichnet, dass die Flachrohre (2) eine lichte Weite H (quer zur Luftströmungsrichtung L) aufweisen, welche in einem Bereich von 3 ≤ H ≤ 10 mm liegt. 5. Heat exchanger according to one of claims 1 to 4, character- ized in that the flat tubes (2) have a clear width H (transverse to the air flow direction L), which is in a range of 3 ≤ H ≤ 10 mm.
6. Wärmeübertrager nach Anspruch 5, dadurch gekennzeichnet, dass die lichte Weite in einem Bereich von 6 ≤ H ≤ 8 mm, insbesondere bei H = 7 mm liegt.6. Heat exchanger according to claim 5, characterized in that the clear width is in a range of 6 ≤ H ≤ 8 mm, in particular at H = 7 mm.
7. Wärmeübertrager nach einem der vorhergehenden Ansprüche, da¬ durch gekennzeichnet, dass in den Flachrohren (2) Innenwellrippen (5) angeordnet sind.7. Heat exchanger according to one of the preceding claims, da¬ characterized in that in the flat tubes (2) inner corrugated fins (5) are arranged.
8. Wärmeübertrager nach einem der vorhergehenden Ansprüche, da- durch gekennzeichnet, dass der Wärmeübertragerblock (1) aus Aluminiumwerkstoffen hergestellt und verlötet ist. 8. Heat exchanger according to one of the preceding claims, character- ized in that the heat exchanger block (1) is made of aluminum materials and soldered.
EP05772434A 2004-06-29 2005-06-28 Heat exchanger, particularly a charge-air cooler for motor vehicles Ceased EP1763651A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004031566 2004-06-29
PCT/EP2005/006938 WO2006000451A1 (en) 2004-06-29 2005-06-28 Heat exchanger, particularly a charge-air cooler for motor vehicles

Publications (1)

Publication Number Publication Date
EP1763651A1 true EP1763651A1 (en) 2007-03-21

Family

ID=34993045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05772434A Ceased EP1763651A1 (en) 2004-06-29 2005-06-28 Heat exchanger, particularly a charge-air cooler for motor vehicles

Country Status (5)

Country Link
US (1) US20080236781A1 (en)
EP (1) EP1763651A1 (en)
CN (1) CN1977138A (en)
BR (1) BRPI0512812B1 (en)
WO (1) WO2006000451A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BRPI0512812B1 (en) * 2004-06-29 2017-10-10 MAHLE Behr GmbH & Co. KG HEAT TRANSMITTER, SPECIALLY HEAT EXCHANGER OF THE OVERHEAT AIR FOR AUTOMOBILE VEHICLES
EP1899589B1 (en) * 2005-06-03 2012-08-15 Behr GmbH & Co. KG Charge air intercooler
US20140352933A1 (en) * 2013-05-28 2014-12-04 Hamilton Sundstrand Corporation Core assembly for a heat exchanger and method of assembling

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006000451A1 (en) * 2004-06-29 2006-01-05 Behr Gmbh & Co. Kg Heat exchanger, particularly a charge-air cooler for motor vehicles

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2151540A (en) * 1935-06-19 1939-03-21 Varga Alexander Heat exchanger and method of making same
US2782009A (en) * 1952-03-14 1957-02-19 Gen Motors Corp Heat exchangers
FR2269053B1 (en) * 1974-04-25 1976-12-17 Chausson Usines Sa
US4501321A (en) * 1982-11-10 1985-02-26 Blackstone Corporation After cooler, charge air cooler and turbulator assemblies and methods of making the same
JPS59129392A (en) * 1983-01-10 1984-07-25 Nippon Denso Co Ltd Heat exchanger
US5372188A (en) * 1985-10-02 1994-12-13 Modine Manufacturing Co. Heat exchanger for a refrigerant system
GB2268260A (en) * 1992-06-24 1994-01-05 Llanelli Radiators Ltd Heat exchange tubes formed from a unitary portion of sheet or strip material
US5490559A (en) * 1994-07-20 1996-02-13 Dinulescu; Horia A. Heat exchanger with finned partition walls
US5730213A (en) * 1995-11-13 1998-03-24 Alliedsignal, Inc. Cooling tube for heat exchanger
DE19719252C2 (en) * 1997-05-07 2002-10-31 Valeo Klimatech Gmbh & Co Kg Double-flow and single-row brazed flat tube evaporator for a motor vehicle air conditioning system
GB2344643B (en) * 1998-12-07 2002-06-26 Serck Heat Transfer Ltd Heat exchanger core connection
DE10238205A1 (en) * 2002-08-21 2004-03-04 Bayerische Motoren Werke Ag Heat exchanger especially compressor inter-cooler for combustion engine has cooling g pies, guide frame, with inflow and outflow apertures and chambers and protuberance in chamber wall

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006000451A1 (en) * 2004-06-29 2006-01-05 Behr Gmbh & Co. Kg Heat exchanger, particularly a charge-air cooler for motor vehicles

Also Published As

Publication number Publication date
US20080236781A1 (en) 2008-10-02
CN1977138A (en) 2007-06-06
BRPI0512812A (en) 2008-04-08
WO2006000451A1 (en) 2006-01-05
BRPI0512812B1 (en) 2017-10-10

Similar Documents

Publication Publication Date Title
EP1279805B1 (en) Air-cooled intake air cooler
EP2628896B1 (en) Heat transfer arrangement
EP1911946B1 (en) Device for charge air cooling for a combustion motor, system with a device for charge air cooling
DE102014000450B4 (en) Inlet manifold with intercooler
EP1604163A1 (en) Heat exchanger, particularly exhaust gas cooler for motor vehicles
DE112017006549B4 (en) Intercooler
DE602005004160T2 (en) HEAT EXCHANGER WITH TUBE CORE, ESPECIALLY FOR A TURBO HEATING MOTOR
DE102013218444A1 (en) heat exchangers
EP1795847A2 (en) Heat exchanger, more particularly charged air cooler
DE102018106936A1 (en) Intercooler consisting of a liquid-cooled pre-cooler and an air-cooled main cooler
DE102017208494B4 (en) MANIFOLD INTEGRATED INTERCOOLER WITH STRUCTURAL CORE
DE102015110974B4 (en) Exhaust gas heat exchanger with several heat exchanger channels
EP1899589B1 (en) Charge air intercooler
EP2863157B1 (en) Heat exchanger
DE3508240A1 (en) Heat exchanger, in particular charge air cooler with optimised flow resistances for all heat-exchanging media
EP1690056B1 (en) Heat exchanger, in particular for motor vehicles
EP1956212A1 (en) Assembly of a charge air cooler in the intake system of a combustion engine
EP1938035B1 (en) Heat exchanger, in particular for motor vehicles
WO2006000451A1 (en) Heat exchanger, particularly a charge-air cooler for motor vehicles
DE102009007619A1 (en) Heat exchangers, in particular radiators for motor vehicles
EP2236789B1 (en) Device for supplying combustion air to a combustion engine
DE102014212906A1 (en) Intercooler with a plate heat exchanger
DE102018207902A1 (en) Heat exchanger, in particular intercooler, for an internal combustion engine
DE102005030455A1 (en) Heat exchanger used as a charge-air cooler for motor vehicles comprises flat tubes arranged in a row and having a depth which is measured in the direction of air flow
DE102009034723A1 (en) Heat exchanger and charging system

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070129

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20070709

DAX Request for extension of the european patent (deleted)
APBK Appeal reference recorded

Free format text: ORIGINAL CODE: EPIDOSNREFNE

APBN Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2E

APBR Date of receipt of statement of grounds of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA3E

APAF Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R003

APBT Appeal procedure closed

Free format text: ORIGINAL CODE: EPIDOSNNOA9E

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED

18R Application refused

Effective date: 20120605