EP2157388A2 - Heat exchanger for a motor vehicle - Google Patents

Heat exchanger for a motor vehicle Download PDF

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Publication number
EP2157388A2
EP2157388A2 EP09165657A EP09165657A EP2157388A2 EP 2157388 A2 EP2157388 A2 EP 2157388A2 EP 09165657 A EP09165657 A EP 09165657A EP 09165657 A EP09165657 A EP 09165657A EP 2157388 A2 EP2157388 A2 EP 2157388A2
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EP
European Patent Office
Prior art keywords
heat exchanger
region
collector
fluid
exchanger according
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Granted
Application number
EP09165657A
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German (de)
French (fr)
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EP2157388B1 (en
EP2157388A3 (en
Inventor
Thomas Bensel
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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Publication of EP2157388A3 publication Critical patent/EP2157388A3/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures

Definitions

  • the invention relates to a heat exchanger for a motor vehicle according to the preamble of claim 1.
  • DE 195 36 116 A1 describes a coolant radiator for a motor vehicle, on the integrated construction of a further oil cooler is designed for cooling an oil circuit of a power steering or an internal combustion engine.
  • Several sections for forming the separate circuits are formed on opposite collectors, wherein in a portion of the oil circuit, a partition wall is provided with a bypass bore to limit a pressure drop across the oil cooler.
  • the heat exchanger has a first outlet for a first cooling branch of the fluid, and a second outlet for a second cooling branch of the fluid, wherein in particular the second outlet is arranged on the second zone.
  • a heat exchanger is formed, in which the same inflowing fluid is branched to different temperatures tempered.
  • the second area is connected to the second outlet, wherein the second area is in particular part of a low-temperature cooling section integrated into the heat exchanger.
  • the heat exchanger has a second collector, wherein the first sequence is formed on the second collector.
  • the low-temperature cooling section is flowed through in a U-shape in order to achieve particularly good cooling.
  • the first fluid flow leads to an internal combustion engine of the motor vehicle.
  • the second fluid stream expediently leads to a further heat exchanger of the motor vehicle, in particular from the group exhaust gas cooler, intercooler or oil cooler.
  • the heat exchanger is designed so that a flow-through cross-sectional area of the collector is reduced by the throttle member, in particular by a factor between about 5 and about 200.
  • a ratio of a number of exchanger tubes of the first region to a number of exchanger tubes of the third region is between about 4 and about 20, in particular between about 5 and about 12.
  • the throttle member is designed as a partition used in the collector with at least one opening or recess. It can be, for example, a hole to act of a defined diameter. Alternatively, a plurality of openings, for example in the manner of a perforated plate or a flow grid, may be provided.
  • the heat exchanger is designed in the interest of simple mass production as a whole aluminum heat exchanger.
  • the heat exchanger according to the invention is designed as a all-aluminum coolant radiator for a motor vehicle.
  • all-aluminum construction is understood to mean that the collectors, including the base and box parts, are made of aluminum and, if possible, are soldered in a single step to the exchanger tubes, ribs and other components in a soldering oven.
  • the heat exchanger has a first header 1 and a second header 2, between which extends a stack of evenly spaced exchanger tubes 3, which are formed as aluminum flat tubes. Between adjacent flat tubes 3 is in each case a ribbed layer 4, through which the heat transfer to the network of pipes and fins flowing air is improved.
  • the heat exchanger is flowed through by a liquid fluid in the form of a coolant of an engine cooling circuit of the motor vehicle.
  • the heat exchanger is subdivided into a first region A and a second region B via a fluid-tight dividing wall 5 arranged in the first collector.
  • a further dividing wall 6 divides a third region C which lies between the first region A and the second region B in the first collector 1 .
  • the second partition wall 6 is not formed as a fluid-tight barrier, but as a sheet metal part with a defined dimensioned opening 7 in the form of a circular bore.
  • the first region A and the third region C are connected to each other via the second partition 6 in the manner of a Drosseglieds, wherein a flow between the regions A, C is significantly inhibited against a flow within the respective region A or C.
  • the collector 1 in the vicinity of the partition wall 6 has an inner cross section of about 3 cm X 3.5 cm, the bore 7 has a diameter of about 0.6 cm.
  • the geometric Sti ömungsquer bain in the longitudinal direction of the collector in the region of the throttle member 6, 7 is reduced by about a factor of 40.
  • a single inlet 8 is provided for the coolant.
  • a first outlet 9 is formed over its entire length of continuous second collector 2, which is arranged on the first collector opposite end of the flat tubes,
  • a second outlet 10 is arranged on the second region of the first collector 1.
  • a coolant radiator is given, in which a first cooling branch of the incoming through the inlet 8 coolant leaves the first outlet 9, after the exchanger tubes, starting from the areas A and C once has flowed through in the longitudinal direction.
  • This cooling branch is led as a return to the vehicle engine to cool it.
  • a second cooling branch or partial flow of the coolant additionally passes in the second region B arranged exchanger tubes in the opposite direction, starting from the second collector 2 to the first collector 1, where the second cooling branch leaves the collector area B through the second outlet 2.
  • This cooling branch which flows through the coolant radiator overall U-shaped, serves as a flow for a further heat exchanger of the motor vehicle, for example, an indirect or liquid-cooled exhaust gas cooler, intercooler or oil cooler.
  • the second cooling branch is designed as a low-temperature branch.
  • inlet temperatures of 120 ° C inlet temperatures of 120 ° C, the outlet temperatures of the coolant at the first outlet 9 are typically about 80 ° C and at the second outlet 10 of the low-temperature cooling section at typically 60 ° C.
  • the volume flows per exchanger tube of the individual areas A, B, C are indicated by differently thick directional arrows. This makes it clear that the flow in the first region A and in the third region C is rectified with respect to the exchanger tubes.
  • the flow in each case leads from the regions A, C into the exchanger tubes, wherein in a modified embodiment, a respective reverse flow direction can also be present.
  • the extent of the third region C in the longitudinal direction of the collector 1 is considerably smaller than that of the first region A.
  • the ratio of the number of exchanger tubes arranged on the first region A to that of the exchanger tubes arranged on the third region C is about 8.
  • the invention now works as follows;
  • the throttle member 6, 7, the volume flow in the exchanger tubes of the region C is significantly reduced, so that the exchange tubes of the area C in operation assume a lower temperature than that of the area A.
  • This is particularly advantageous for a cold start of the vehicle.
  • the outlet 10 of the low-temperature branch is regularly closed at a time when hot coolant flows from the internal combustion engine into the inlet 8 and out of the first outlet 9.
  • the inflow often takes place via a switched-cycle valve, so that, for a short time, particularly large temperature differences occur occur between the tubes of the first region A and the not yet flowed through the second region B. This would be due to the different pipe expansions in the border area (solid line in Fig.

Abstract

The exchanger has a collector (1) with an inlet (8) for a fluid and divided into a region (A) and another region (B) in a fluid-tight manner. A third region (C) arranged between the two regions is formed by a throttle element (6). A fluid flow is throttled between the first region and the third region in a defined manner. The fluid flows into the first region and into the third region in a direction with respect to exchanger pipes (3) connected with the first and third regions. The element is formed as a partition wall with a through hole, where the wall is inserted into the collector.

Description

Die Erfindung betrifft einen Wärmetauscher für ein Kraftfahrzeug nach dem Oberbegriff des Anspruchs 1.The invention relates to a heat exchanger for a motor vehicle according to the preamble of claim 1.

DE 195 36 116 A1 beschreibt einen Kühlmittelkühler für ein Kraftfahrzeug, an dem in integrierter Bauweise ein weiter Ölkühler zur Kühlung eines Ölkreislaufs einer Servolenkung oder eines Verbrennungsmotors ausgebildet ist. Dabei sind an gegenüberliegenden Sammlern mehrere Abschnitte zur Ausbildung der getrennten Kreisläufe ausgebildet, wobei in einem Abschnitt des Ölkreislaufs eine Trennwand mit einer Bypassbohrung vorgesehen ist, um einen Druckabfall über dem Ölkühler zu begrenzen. DE 195 36 116 A1 describes a coolant radiator for a motor vehicle, on the integrated construction of a further oil cooler is designed for cooling an oil circuit of a power steering or an internal combustion engine. Several sections for forming the separate circuits are formed on opposite collectors, wherein in a portion of the oil circuit, a partition wall is provided with a bypass bore to limit a pressure drop across the oil cooler.

Es ist die Aufgabe der Erfindung, einen Wärmetauscher für ein Kraftfahrzeug anzugeben, bei dem temperaturbedingte Materialspannungen verringert sind.It is the object of the invention to provide a heat exchanger for a motor vehicle, are reduced in the temperature-induced material stresses.

Diese Aufgabe wird für einen eingangs genannten Wärmetauscher erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst. Durch die Strömungsbegrenzung zwischen zwei benachbarten, bezüglich der Tauscherrohre in gleicher Richtung strömenden Bereichen des Sammlers wird in dem dritten Bereich eine gegenüber dem ersten Bereich gemäßigte Temperatur der Tauscherrohre erzielt. Eine je nach Betriebsbedingungen auftretende maximale Temperaturdifferenz zu dem dritten Bereich benachbarten Rohren des zweiten Bereichs wird hierdurch verringert. Somit wird auch eine durch thermische Längendehnung der Rohre der verschiedenen Bereiche bedingte maximale mechanische Verspannung reduziert.This object is achieved according to the invention for a heat exchanger mentioned above with the characterizing features of claim 1. As a result of the flow limitation between two adjacent regions of the collector which flow in the same direction with respect to the exchanger tubes, a temperature of the exchanger tubes which is moderate in relation to the first region is achieved in the third region. A maximum temperature difference, which occurs depending on the operating conditions, with respect to the third region of adjacent tubes of the second region is thereby reduced. Consequently Also, a maximum mechanical strain caused by thermal elongation of the tubes of the various regions is reduced.

Bei einer bevorzugten Ausführungsform der Erfindung hat der Wärmetauscher einen ersten Ablauf für einen ersten Kühlzweig des Fluids, und einen zweiten Ablauf für einen zweiten Kühlzweig des Fluids, wobei insbesondere der zweite Ablauf an dem zweiten Bereich angeordnet ist. Hierdurch ist ein Wärmetauscher gebildet, bei dem dasselbe einströmende Fluid verzweigt auf verschiedene Temperaturen temperierbar ist. In zweckmäßiger Detailgestaltung ist dabei der zweite Bereich mit dem zweiten Ablauf verbunden, wobei der zweite Bereich insbesondere Teil einer in den Wärmetauscher integrierten Niedertemperatur-Kühlstrecke ist. Bei einer einfachen Bauweise hat dabei der Wärmetauscher einen zweiten Sammler, wobei der erste Ablauf an dem zweiten Sammler ausgebildet ist. Besonders bevorzugt wird die Niedertemperatur-Kühlstrecke dabei zur Erzielung einer besonders guten Kühlung U-förmig durchströmt.In a preferred embodiment of the invention, the heat exchanger has a first outlet for a first cooling branch of the fluid, and a second outlet for a second cooling branch of the fluid, wherein in particular the second outlet is arranged on the second zone. In this way, a heat exchanger is formed, in which the same inflowing fluid is branched to different temperatures tempered. In an expedient detailed design, the second area is connected to the second outlet, wherein the second area is in particular part of a low-temperature cooling section integrated into the heat exchanger. In a simple construction of the heat exchanger has a second collector, wherein the first sequence is formed on the second collector. Particularly preferably, the low-temperature cooling section is flowed through in a U-shape in order to achieve particularly good cooling.

Bei einer bevorzugten Auslegung des Wärmetauschers führt der erste Fluidstrom zu einem Verbrennungsmotor des Kraftfahrzeugs. Der zweite Fluidstrom führt zweckmäßig zu einem weiteren Wärmetauscher des Kraftfahrzeugs, insbesondere aus der Gruppe Abgaskühler, Ladeluftkühler oder Ölkühler.In a preferred embodiment of the heat exchanger, the first fluid flow leads to an internal combustion engine of the motor vehicle. The second fluid stream expediently leads to a further heat exchanger of the motor vehicle, in particular from the group exhaust gas cooler, intercooler or oil cooler.

Allgemein vorteilhaft ist der Wärmetauscher so ausgelegt, dass durch das Drosselglied eine durchströmbare Querschnittsfläche des Sammlers reduziert ist, insbesondere um einen Faktor zwischen etwa 5 und etwa 200.In general terms, the heat exchanger is designed so that a flow-through cross-sectional area of the collector is reduced by the throttle member, in particular by a factor between about 5 and about 200.

Weiterhin ist in optimierter Auslegung des Wärmetauschers vorgesehen, dass ein Verhältnis einer Anzahl von Tauscherrohren des ersten Bereichs zu einer Anzahl von Tauscherrohren des dritten Bereichs zwischen etwa 4 und etwa 20, insbesondere zwischen etwa 5 und etwa 12 beträgt.Furthermore, in an optimized design of the heat exchanger, it is provided that a ratio of a number of exchanger tubes of the first region to a number of exchanger tubes of the third region is between about 4 and about 20, in particular between about 5 and about 12.

In einfacher baulicher Realisierung ist das Drosselglied als in den Sammler eingesetzte Trennwand mit zumindest einer Durchbrechung beziehungsweise Aussparung ausgebildet. Es kann sich dabei zum Beispiel um eine Bohrung von definiertem Durchmesser handeln. Alternativ können auch mehrere Durchbrechungen, etwa nach Art eines Lochbleches oder eines Strömungsgitters, vorgesehen sein.In a simple structural realization, the throttle member is designed as a partition used in the collector with at least one opening or recess. It can be, for example, a hole to act of a defined diameter. Alternatively, a plurality of openings, for example in the manner of a perforated plate or a flow grid, may be provided.

Allgemein vorteilhaft ist der Wärmetauscher im interesse einer einfachen Serienfertigung als Ganzaluminium-Wärmetauscher ausgebildet ist.Generally advantageous, the heat exchanger is designed in the interest of simple mass production as a whole aluminum heat exchanger.

Weitere Vorteile und Merkmale der Erfindung ergeben sich aus dem nachfolgend beschriebenen Ausführungsbeispiel sowie aus den abhängigen Ansprüchen.Further advantages and features of the invention will become apparent from the embodiment described below and from the dependent claims.

Nachfolgend wird ein bevorzugtes Ausführungsbeispiel der Erfindung beschrieben und anhand der anliegenden Zeichnungen näher erläutert.

Fig. 1
zeigt eine räumliche Teilansicht eines erfindungsgemäßen Wärmetauschers.
Fig. 2
zeigt eine Draufsicht auf den Wärmetauscher aus Fig. 1
Fig. 3
zeigt eine aufgeschnittene räumliche Teilansicht eines Sammlers des Wärmetauschers aus Fig. 1 und Fig. 2.
Hereinafter, a preferred embodiment of the invention will be described and explained in more detail with reference to the accompanying drawings.
Fig. 1
shows a partial spatial view of a heat exchanger according to the invention.
Fig. 2
shows a plan view of the heat exchanger Fig. 1
Fig. 3
shows a cut-open partial spatial view of a collector of the heat exchanger Fig. 1 and Fig. 2 ,

Der erfindungsgemäße Wärmetauscher ist als Ganzaluminium-Kühlmittelkühler für ein Kraftfahrzeug ausgebildet. Unter Ganzaluminium-Bauweise wird dabei verstanden, dass die Sammler einschließlich Boden- und Kastenteilen aus Aluminium bestehen und nach Möglichkeit in einem einzigen Schritt mit den tauscherrohren, Rippen und weiteren Bauteilen in einem Lötofen verlötet werden.The heat exchanger according to the invention is designed as a all-aluminum coolant radiator for a motor vehicle. The term "all-aluminum construction" is understood to mean that the collectors, including the base and box parts, are made of aluminum and, if possible, are soldered in a single step to the exchanger tubes, ribs and other components in a soldering oven.

Der Wärmetauscher hat einen ersten Sammler 1 und einen zweiten Sammler 2, zwischen denen sich ein Stapel von gleichmäßig beabstandeten Tauscherrohren 3 erstreckt, die als Aluminium-Flachrohre ausgebildet sind. Zwischen benachbarten Flachrohren 3 befindet sich jeweils eine Rippenlage 4, durch die der Wärmeübertrag auf das Netz aus Rohren und Rippen durchströmende Luft verbessert ist. Der Wärmetauscher wird von einem flüssigen Fluid in Form eines Kühlmittels eines Motor-Kühlkreislaufs des Kraftfahrzeugs durchströmt.The heat exchanger has a first header 1 and a second header 2, between which extends a stack of evenly spaced exchanger tubes 3, which are formed as aluminum flat tubes. Between adjacent flat tubes 3 is in each case a ribbed layer 4, through which the heat transfer to the network of pipes and fins flowing air is improved. The heat exchanger is flowed through by a liquid fluid in the form of a coolant of an engine cooling circuit of the motor vehicle.

Der Wärmetauscher ist über eine im ersten Sammler angeordnete fluiddichte Trennwand 5 in einen ersten Bereich A und einen zweiten Bereich B unterteilt Eine weitere Trennwand 6 teilt einen dritten Bereich C ab, der zwischen dem ersten Bereich A und dem zweiten Bereich B im ersten Sammler 1 liegt. Die zweite Trennwand 6 ist nicht als fluiddichte Sperre, sondern als Blechteil mit einer definiert dimensionierten Durchbrechung 7 in Form einer kreisrunden Bohrung ausgebildet. Hierdurch sind der erste Bereich A und der dritte Bereich C über die zweite Trennwand 6 nach Art eines Drosseiglieds miteinander verbunden, wobei eine Strömung zwischen den Bereichen A, C deutlich gegenüber einer Strömung innerhalb des jeweiligen Bereichs A oder C gehemmt ist.The heat exchanger is subdivided into a first region A and a second region B via a fluid-tight dividing wall 5 arranged in the first collector. A further dividing wall 6 divides a third region C which lies between the first region A and the second region B in the first collector 1 , The second partition wall 6 is not formed as a fluid-tight barrier, but as a sheet metal part with a defined dimensioned opening 7 in the form of a circular bore. As a result, the first region A and the third region C are connected to each other via the second partition 6 in the manner of a Drosseglieds, wherein a flow between the regions A, C is significantly inhibited against a flow within the respective region A or C.

Vorliegen hat der Sammler 1 in der Nähe der Trennwand 6 einen inneren Querschnitt von etwa 3 cm X 3,5 cm, wobei die Bohrung 7 einen Durchmesser von etwa 0,6 cm hat. Hierdurch ist der geometrische Sti-ömungsquerschnitt in der Längsrichtung des Sammlers im Bereich des Drosselglieds 6, 7 ungefähr um den Faktor 40 reduziert.Present the collector 1 in the vicinity of the partition wall 6 has an inner cross section of about 3 cm X 3.5 cm, the bore 7 has a diameter of about 0.6 cm. As a result, the geometric Sti ömungsquerschnitt in the longitudinal direction of the collector in the region of the throttle member 6, 7 is reduced by about a factor of 40.

In dem ersten Bereich A ist ein einziger Zulauf 8 für das Kühlmittel vorgesehen. Ein erster Ablauf 9 über seine gesamte Länge durchgängigen zweiten Sammler 2 ausgebildet, welcher am dem ersten Sammler gegenüberliegenden Ende der Flachrohre angeordnet ist, Ein zweiter Ablauf 10 ist an dem zweiten Bereich des ersten Sammlers 1 angeordnet.In the first area A, a single inlet 8 is provided for the coolant. A first outlet 9 is formed over its entire length of continuous second collector 2, which is arranged on the first collector opposite end of the flat tubes, A second outlet 10 is arranged on the second region of the first collector 1.

Durch diese Anordnung von Trennwänden 5, 6 in den Sammlern 1, 2 ist ein Kühlmittelkühler gegeben, bei dem ein erster Kühlzweig des durch den Zulauf 8 eintretenden Kühlmittels aus dem ersten Ablauf 9 verlässt, nachdem er die Tauscherrohre ausgehend von den Bereichen A und C einmal in Längsrichtung durchströmt hat. Dieser Kühlzweig wird als Rücklauf zum Fahrzeugmotor geführt, um diesen zu kühlen.By this arrangement of partitions 5, 6 in the collectors 1, 2, a coolant radiator is given, in which a first cooling branch of the incoming through the inlet 8 coolant leaves the first outlet 9, after the exchanger tubes, starting from the areas A and C once has flowed through in the longitudinal direction. This cooling branch is led as a return to the vehicle engine to cool it.

Ein zweiter Kühlzweig bzw. Teilstrom des Kühlmittels durchläuft zusätzlich im zweiten Bereich B angeordneten Tauscherrohre in Gegenrichtung ausgehend vom zweiten Sammler 2 zum ersten Sammler 1, wo der zweite Kühlzweig den Sammlerbereich B durch den zweiten Ablauf 2 verlässt. Dieser Kühlzweig, der den Kühlmittelkühler insgesamt U-förmig durchströmt, dient als Vorlauf für einen weiteren Wärmetauscher des Kraftfahrzeugs, zum Beispiel einen indirekt bzw. flüssigkeitsgekühlten Abgaskühler, Ladeluftkühler oder Ölkühler.A second cooling branch or partial flow of the coolant additionally passes in the second region B arranged exchanger tubes in the opposite direction, starting from the second collector 2 to the first collector 1, where the second cooling branch leaves the collector area B through the second outlet 2. This cooling branch, which flows through the coolant radiator overall U-shaped, serves as a flow for a further heat exchanger of the motor vehicle, for example, an indirect or liquid-cooled exhaust gas cooler, intercooler or oil cooler.

Entsprechend der längeren Kühlstrecke ist der zweite Kühlzweig als Niedertemperaturzweig ausgelegt. Bei im Normalbetrieb üblichen Eintrittstemperaturen von 120° C liegen die Austrittstemperaturen des Kühlmittels am ersten Ablauf 9 bei typisch etwa 80 °C und am zweiten Ablauf 10 der Niedertemperatur-Kühlstrecke bei typisch 60 °C.Corresponding to the longer cooling distance, the second cooling branch is designed as a low-temperature branch. In normal inlet operation inlet temperatures of 120 ° C, the outlet temperatures of the coolant at the first outlet 9 are typically about 80 ° C and at the second outlet 10 of the low-temperature cooling section at typically 60 ° C.

Die Volumenströme je Tauscherrohr der einzelnen Bereiche A, B, C sind durch unterschiedlich dicke Richtungspfeile angedeutet. Hierdurch wird deutlich, dass die Strömung im ersten Bereich A und im dritten Bereich C bezüglich der Tauscherrohre gleichgerichtet ist. Im vorliegenden Ausführungsbeispiel führt die Strömung jeweils von den Bereichen A, C in die Tauscherrohre hinein, wobei in abgewandelter Ausführung auch eine jeweils umgekehrte Strömungsrichtung vorliegen kann.The volume flows per exchanger tube of the individual areas A, B, C are indicated by differently thick directional arrows. This makes it clear that the flow in the first region A and in the third region C is rectified with respect to the exchanger tubes. In the present exemplary embodiment, the flow in each case leads from the regions A, C into the exchanger tubes, wherein in a modified embodiment, a respective reverse flow direction can also be present.

Die Ausdehnung des dritten Bereichs C in Längsrichtung des Sammlers 1 ist erheblich kleiner als die des ersten Bereichs A. Das Verhältnis der Anzahl der am ersten Bereich A angeordneten Tauscherrohre zu dem der am dritten Bereich C angeordneten Tauscherrohre beträgt etwa 8.The extent of the third region C in the longitudinal direction of the collector 1 is considerably smaller than that of the first region A. The ratio of the number of exchanger tubes arranged on the first region A to that of the exchanger tubes arranged on the third region C is about 8.

Die Erfindung funktioniert nun wie folgt;
Durch das Drosselglied 6, 7 ist der Volumenstrom in den Tauscherrohren des Bereichs C deutlich reduziert, so dass auch die Tauschrohre des Bereichs C im Betrieb eine niedrigere Temperatur annehmen als die des Bereichs A. Die ist insbesondere bei einem Kaltstart des Fahrzeugs vorteilhaft. Dabei ist der Ablauf 10 des Niedertemperaturzweigs regelmäßig noch zu einem Zeitpunkt geschlossen, zu dem bereits heißes Kühlmittel vom der Verbrennungsmotor in den Zulauf 8 und aus dem ersten Ablauf 9 strömt. Bei modernen Kühlmittelsteuerungen erfolgt der Zustrom oft über ein getaktet geschaltetes Ventil, so dass kurzzeitig besonders große Temperaturdifferenzen zwischen den Rohren des ersten Bereichs A und den des noch nicht durchströmten zweiten Bereichs B auftreten. Hierdurch würden aufgrund der unterschiedlichen Rohrdehnungen im Grenzbereich (durchgezogene Linie in Fig. 2) erhebliche Materialspannungen bzw. Biegemomente auf die Sammler einwirken. Insbesondere sind hiervon die gelöteten Anschlüsse der Rohre an den Bodenbereichen der Sammler betroffen. Mittels des Drosselglieds 6, 7 wird der Temperaturgradient über die Rohre des dritten Bereichs C abgestuft verteilt, so dass die verschiedenen Rohrdehnungen über einen größeren Sammlerbereich verteilt werden und das maximale Biegemoment bzw, die maximale Materialspannung verringert ist.The invention now works as follows;
By the throttle member 6, 7, the volume flow in the exchanger tubes of the region C is significantly reduced, so that the exchange tubes of the area C in operation assume a lower temperature than that of the area A. This is particularly advantageous for a cold start of the vehicle. In this case, the outlet 10 of the low-temperature branch is regularly closed at a time when hot coolant flows from the internal combustion engine into the inlet 8 and out of the first outlet 9. In modern coolant control systems, the inflow often takes place via a switched-cycle valve, so that, for a short time, particularly large temperature differences occur occur between the tubes of the first region A and the not yet flowed through the second region B. This would be due to the different pipe expansions in the border area (solid line in Fig. 2 ) significant material stresses or bending moments act on the collector. In particular, this affects the soldered connections of the pipes to the bottom areas of the collectors. By means of the throttle member 6, 7, the temperature gradient over the tubes of the third region C is distributed in steps, so that the different pipe expansions are distributed over a larger collector area and the maximum bending moment or, the maximum material tension is reduced.

Es versteht sich, dass dieses Prinzip auch auf andere Bauformen von Wärmetauschern ausdehnbar ist. Insbesondere könnten in abgewandelter Bauform, zum Beispiel einer Trennwand im zweiten Sammler, zwei vollständig von einander getrennte Fluidkreise mit gegebenenfalls verschiedenen Fluiden vorgesehen sein.It is understood that this principle can be extended to other types of heat exchangers. In particular, in a modified design, for example a partition wall in the second collector, two completely separate fluid circuits with possibly different fluids could be provided.

Claims (11)

Wärmetauscher für ein Kraftfahrzeug, umfassend
einen Sammler (1) mit zumindest einem Zulauf (8) für ein Fluid,
eine Mehrzahl von an dem Sammler (1) angeordneten Tauscherrohren (3),
wobei der Sammler (1) fluiddicht in einen ersten Bereich (A) und einen zweiten Bereich (B) unterteilt ist,
wobei ein Drosselglied (6) vorgesehen ist, mittels dessen ein zwischen erstem und zweitem Bereich (A, B) angeordneter dritter Bereich (C) ausgebildet ist, wodurch eine Fluidströmung zwischen dem ersten Bereich (A) und dem dritten Bereich (C) definiert gedrosselt ist,
dadurch gekennzeichnet,
dass das Fluid in dem ersten Bereich (A) und in dem dritten Bereich (C) in derselben Richtung bezüglich mit den Bereichen (A. C) jeweils verbundener Tauscherrohre (3) strömt.Heat exchanger for a motor vehicle, comprising
a collector (1) with at least one inlet (8) for a fluid,
a plurality of exchanger tubes (3) arranged on the collector (1),
wherein the collector (1) is divided into a first area (A) and a second area (B) in a fluid-tight manner,
wherein a throttle member (6) is provided, by means of which a third region (C) arranged between the first and second regions (A, B) is formed, whereby a fluid flow between the first region (A) and the third region (C) defined throttled is
characterized,
in that the fluid in the first area (A) and in the third area (C) flows in the same direction with respect to the exchanger tubes (3) respectively connected to the areas (A.C). Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, dass der Wärmetauscher einen ersten Ablauf (9) für einen ersten Kühlzweig des Fluids, und einen zweiten Ablauf (10) für einen zweiten Kühlzweig des Fluids umfasst, wobei insbesondere der zweite Ablauf (10) an dem zweiten Bereich (B) angeordnet ist.Heat exchanger according to claim 1, characterized in that the heat exchanger comprises a first outlet (9) for a first cooling branch of the fluid, and a second outlet (10) for a second cooling branch of the fluid, in particular the second outlet (10) at the second Region (B) is arranged. Wärmetauscher nach Anspruch 2, dadurch gekennzeichnet, dass der zweite Bereich (B) mit dem zweiten Ablauf (10) verbunden ist, wobei der zweite Bereich (B) insbesondere Teil einer in den Wärmetauscher integrierten Niedertemperatur-Kühlstrecke ist.Heat exchanger according to claim 2, characterized in that the second region (B) with the second outlet (10) is connected, wherein the second region (B) is in particular part of an integrated into the heat exchanger low-temperature cooling section. Wärmetauscher nach Anspruch 3, dadurch gekennzeichnet, dass der Wärmetauscher einen zweiten Sammler (2) umfasst, wobei der erste Ablauf (9) an dem zweiten Sammler (2) ausgebildet ist.Heat exchanger according to claim 3, characterized in that the heat exchanger comprises a second collector (2), wherein the first outlet (9) is formed on the second collector (2). Wärmetauscher nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Niedertemperatur-Kühlstrecke U-förmig durchströmt wird.Heat exchanger according to claim 3 or 4, characterized in that the low-temperature cooling section is flowed through in a U-shape. Wärmetauscher nach einem der Ansprüche 3 bis 5, dadurch gekennzeichnet, dass der erste Fluidstrom zu einem Verbrennungsmotor des Kraftfahrzeugs führt.Heat exchanger according to one of claims 3 to 5, characterized in that the first fluid flow leads to an internal combustion engine of the motor vehicle. Wärmetauscher nach einem der Ansprüche 3 bis 6, dadurch gekennzeichnet, dass der zweite Fluidstrom (B) zu einem weiteren Wärmetauscher des Kraftfahrzeugs führt, insbesondere aus der Gruppe Abgaskühler, Ladeluftkühler oder Ölkühler.Heat exchanger according to one of claims 3 to 6, characterized in that the second fluid flow (B) leads to a further heat exchanger of the motor vehicle, in particular from the group exhaust gas cooler, intercooler or oil cooler. Wärmetauscher nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass durch das Drosselglied (6) eine durchströmbare Querschnittsfläche des Sammlers reduziert ist, insbesondere um einen Faktor zwischen etwa 5 und etwa 200.Heat exchanger according to one of the preceding claims, characterized in that a flow-through cross-sectional area of the collector is reduced by the throttle member (6), in particular by a factor of between about 5 and about 200. Wärmetauscher nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein Verhältnis einer Anzahl von Tauscherrohren des ersten Bereichs (A) zu einer Anzahl von Tauscherrohren des dritten Bereichs (C) zwischen etwa 4 und etwa 20, insbesondere zwischen etwa 5 und etwa 12 beträgt.Heat exchanger according to one of the preceding claims, characterized in that a ratio of a number of exchanger tubes of the first region (A) to a number of exchanger tubes of the third region (C) between about 4 and about 20, in particular between about 5 and about 12. Wärmetauscher nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Drosselglied (6) als in den Sammler (1) eingesetzte Trennwand mit zumindest einer Durchbrechung (7) ausgebildet ist.Heat exchanger according to one of the preceding claims, characterized in that the throttle member (6) as in the collector (1) inserted partition with at least one opening (7) is formed. Wärmetauscher nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Wärmetauscher als Ganzaluminium-Wärmetauscher ausgebildet ist.Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger is designed as a whole aluminum heat exchanger.
EP09165657.9A 2008-08-20 2009-07-16 Heat exchanger for a motor vehicle Not-in-force EP2157388B1 (en)

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DE102008038498A DE102008038498A1 (en) 2008-08-20 2008-08-20 Heat exchanger for a motor vehicle

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EP2157388A3 EP2157388A3 (en) 2013-10-16
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Publication number Priority date Publication date Assignee Title
DE102016213801A1 (en) 2016-07-27 2018-02-01 Mahle International Gmbh Heat exchanger

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JPH03247993A (en) * 1990-02-23 1991-11-06 Calsonic Corp Lamination type heat exchanger
EP0818663A2 (en) * 1996-07-02 1998-01-14 Längerer & Reich GmbH Heat exchanger,more particularly radiator
EP1065453A2 (en) * 1999-07-02 2001-01-03 Denso Corporation Refrigerant evaporator with refrigerant distribution
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JP2001241806A (en) * 2000-02-28 2001-09-07 Sanden Corp Pressure-proof component, heat exchanger with pressure- proof component and freezer with pressure-proof component
EP1712868A2 (en) * 2005-04-15 2006-10-18 Behr GmbH & Co. KG Evaporator
WO2007027354A1 (en) * 2005-08-31 2007-03-08 Valeo, Inc. Heat exchanger
FR2912209A1 (en) * 2007-02-06 2008-08-08 Valeo Systemes Thermiques Exchanger for cooling e.g. heat engine and gearbox, in vehicle, has tubes circulating fluid from circuit, and mechanical connecting element connecting structure of inlet chamber to collecting chamber and constituted by spacer/metallic rod

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DE102005012082A1 (en) * 2005-03-16 2006-09-21 Modine Manufacturing Co., Racine Heat exchangers, in particular cooling liquid coolers

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03247993A (en) * 1990-02-23 1991-11-06 Calsonic Corp Lamination type heat exchanger
EP0818663A2 (en) * 1996-07-02 1998-01-14 Längerer & Reich GmbH Heat exchanger,more particularly radiator
EP1065453A2 (en) * 1999-07-02 2001-01-03 Denso Corporation Refrigerant evaporator with refrigerant distribution
DE10039386A1 (en) * 1999-08-20 2001-02-22 Denso Corp Heat exchange system for vehicle air conditioning comprises first second and third exchangers feeding heat release elements with progressively cooled product fluid.
JP2001241806A (en) * 2000-02-28 2001-09-07 Sanden Corp Pressure-proof component, heat exchanger with pressure- proof component and freezer with pressure-proof component
EP1712868A2 (en) * 2005-04-15 2006-10-18 Behr GmbH & Co. KG Evaporator
WO2007027354A1 (en) * 2005-08-31 2007-03-08 Valeo, Inc. Heat exchanger
FR2912209A1 (en) * 2007-02-06 2008-08-08 Valeo Systemes Thermiques Exchanger for cooling e.g. heat engine and gearbox, in vehicle, has tubes circulating fluid from circuit, and mechanical connecting element connecting structure of inlet chamber to collecting chamber and constituted by spacer/metallic rod

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EP2157388A3 (en) 2013-10-16
DE102008038498A1 (en) 2010-02-25

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