EP0450425B1 - Arrangement for heat-exchanger - Google Patents

Arrangement for heat-exchanger Download PDF

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Publication number
EP0450425B1
EP0450425B1 EP19910104510 EP91104510A EP0450425B1 EP 0450425 B1 EP0450425 B1 EP 0450425B1 EP 19910104510 EP19910104510 EP 19910104510 EP 91104510 A EP91104510 A EP 91104510A EP 0450425 B1 EP0450425 B1 EP 0450425B1
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EP
European Patent Office
Prior art keywords
heat
heat exchanger
heat exchangers
exchanger
air
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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.)
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EP19910104510
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German (de)
French (fr)
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EP0450425A2 (en
EP0450425A3 (en
Inventor
Dieter Roschinski
Michael Klocke
Hans Weitzenbürger
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Kloeckner Humboldt Deutz AG
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Kloeckner Humboldt Deutz AG
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Priority claimed from DE19904009726 external-priority patent/DE4009726A1/en
Priority claimed from DE19904033897 external-priority patent/DE4033897A1/en
Application filed by Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to DE59103074T priority Critical patent/DE59103074D1/en
Publication of EP0450425A2 publication Critical patent/EP0450425A2/en
Publication of EP0450425A3 publication Critical patent/EP0450425A3/en
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Publication of EP0450425B1 publication Critical patent/EP0450425B1/en
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    • 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
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0452—Combination of units extending one behind the other with units extending one beside or one above the other

Definitions

  • the invention relates to a heat exchanger arrangement with at least two heat exchangers, which are acted upon by cooling air from a common fan.
  • the coolant heat exchanger is usually arranged in front of the internal combustion engine. There is a fan between the internal combustion engine and the coolant heat exchanger, which conveys the cooling air through the heat exchanger. In order to achieve a uniform loading of the heat exchanger and at the same time a small distance between the heat exchanger and fan, a square active surface of the heat exchanger is usually aimed for.
  • Such heat exchangers are e.g. known from the document US-A-2 264 820.
  • Additional units are often driven by internal combustion engines, which require a considerable cooling capacity for the working medium of the additional unit.
  • the additional heat exchanger required is often larger than the coolant heat exchanger of the internal combustion engine. It is difficult to apply cooling air evenly to both heat exchangers and at the same time to accommodate them at a short distance from the fan.
  • the invention has for its object to provide a heat exchanger fan system with at least two heat exchangers and a fan that requires as little space as possible.
  • the object is achieved by the characterizing features of claim 1.
  • the standard heat exchanger for the coolant of the internal combustion engine has a simple square or rectangular shape, while the additional heat exchanger has an L-shape. This is adapted in size to the heat quantities to be dissipated and realizes the overall square shape of the active surfaces of the heat exchangers. Due to the arrangement according to the invention, even when the fan is at a small distance from the plane of the heat exchanger, the active surfaces of the heat exchanger are uniformly acted on, since these are optimally coated by the fan because of their approximately square shape.
  • a pressure fan also offers advantages, e.g. B. a lower fan power because of the lower volume of the cold air to be conveyed.
  • advantages of the invention apply to both types of fans.
  • An advantageous development of the invention has the effect that, in an internal combustion engine with a constant amount of cooling heat and additional units with different amounts of cooling heat, a coolant heat exchanger of constant dimensions with different sizes of heat exchanger for the working medium can be combined to the optimal combination according to the invention.
  • the flow resistances on the cooling air side of both heat exchangers are designed approximately the same, whereby a uniform cooling air distribution is also promoted.
  • An advantageous development of the invention achieves the same effect even in charge air-cooled engines in which the charge air cooler is arranged upstream of the coolant heat exchanger.
  • This location of the charge air cooler also has the effect that only the cooling air of the first heat exchanger is preheated, while that of the second heat exchanger is not preheated, so that its dimensions do not have to be increased.
  • the effectiveness of the fan is increased by an advantageous embodiment of the invention.
  • the cooling air duct prevents the sucking in or blowing off of external air and thus increases the efficiency and noise level of the fan. If fan efficiency and fan noise play no role in comparison to the purchase costs of the cooling air duct, the cooling air duct can also be omitted.
  • the fan is replaced by a blower with a stator, which enables the use of compact high-performance heat exchangers with increased flow resistance due to the increased cooling air pressure caused thereby.
  • a further cost reduction is achieved by an advantageous development of the invention.
  • the same end box blanks mean only one mold and only one raw part store.
  • the least amount of processing and assembly work and the smallest risk of leakage on the one hand, in which only the required minimum processing of the various end boxes is carried out and the complete equality of all finished end boxes with correspondingly simplified storage, on the other hand, but increased processing and assembly costs and increased Leakage risk, since in this case all holes that are not required but are drilled must be closed.
  • two individual heat exchangers with identical active surfaces can also be used.
  • the equality of the components is contrasted here by the incomplete use of the square area as a disadvantage, whereby the unused area must be covered.
  • the first heat exchanger 1 has a rectangular-shaped active surface, which is supplemented by the second heat exchanger 2 due to its coordinated L-shape to a square shape of the entire active surface.
  • the first heat exchanger 1 is used for recooling the cooling medium of the internal combustion engine
  • the second heat exchanger 2 is used for recooling the working medium of the additional equipment or units of the internal combustion engine.
  • Both heat exchangers have heat exchanger boxes 14, 14 ', 14 ⁇ , 14 ′′′, 14 ⁇ ⁇ , which are used for even distribution and for collecting the respective cooling medium.
  • the arrangement of the charge air cooler 12 is shown in FIG. This is arranged upstream of the first heat exchanger 1 and has the same effective area as this. It does heat the cooling air of the first heat exchanger 1 slightly. However, this has less of an impact on the cooling medium of the first heat exchanger 1 — usually cooling water — in contrast to the coolant of the second — generally hydraulic oil — because of the higher temperature level of the cooling water.
  • the resistance of the cooling air in the two or three heat exchangers is adjusted so that it is constant over the entire surface of the heat exchanger and thus causes a uniform flow of cooling air.
  • the fan 9 is designed as a suction fan. It is located a short distance behind the heat exchangers in the flow direction. Its diameter corresponds to the inner circle of the square area of the active surfaces of the heat exchangers. Between heat exchangers 1, 2, 12 and the fan 9, a cooling air duct 13 is arranged. It serves to guide the cooling air and prevents the fan 9 from sucking in false air. For the same reason, the first and second heat exchangers are joined together at a short distance. The resulting high efficiency of the heat exchanger fan system also lowers the noise level of the fan 9.
  • the arrangement of the heat exchangers according to the invention offers the advantage of uniform application to all active surfaces of the heat exchangers despite the small axial length due to the possible small fan spacing. In addition, heating of the cooling air of the second heat exchanger 2 is avoided, which keeps its dimensions as small as possible.
  • the heat exchanger arrangement according to FIG. 3 consists of a first heat exchanger 1 and a second heat exchanger 2.
  • the associated fan 9 is indicated in FIGS. 3 and 4 by a fan circuit.
  • the active surfaces of the heat exchangers 1, 2 form approximately a square, to which the fan circuit is inscribed.
  • the second heat exchanger 2 consists of two individual heat exchangers 3, 3a, 3b, 3c, 3d, which are arranged in an L-shape and surround the first heat exchanger 1 in half and add a square.
  • the second heat exchanger 2 is used, for example, to cool hydraulic oil.
  • the individual heat exchangers 3, 3a, 3b, 3c, 3d consist of a rectangular active surface 10, 10 ', which is delimited on two opposite sides by two end boxes 4, 4', 4 ⁇ .
  • the active surfaces 10, 10 ', the cooling liquid is supplied or discharged via the end boxes 4, 4', 4 ⁇ .
  • Each end box 4, 4 ', 4 ⁇ is made by different processing from the same blank.
  • Each end box 4, 4 ', 4 ⁇ has an end wall 7 and two end walls 8, 8', the outer surfaces of which intersect in the edges 6, 6 '.
  • a bore 5 is made either in the end wall 7 or in the end wall 8, which serves for the inlet or outlet of the cooling liquid.
  • the holes 5 have the same distance from the edge 6 and are made in the middle of the respective end wall 7 or end wall 8.
  • the end boxes 4, 4 ', 4 ⁇ are attached to the active surfaces 10, 10' so that their bores are diagonally opposite. As a result, a uniform distribution of the cooling liquid on the active surfaces 10, 10 'is achieved.
  • the individual heat exchangers 3, 3a, 3b, 3c, 3d touch each other with the end wall 7 and the end wall 8 of an end box 4, 4 ', 4 ⁇ . They are screwed together at the point of contact.
  • FIG. 3 shows a heat exchanger 2, the individual heat exchangers 3a, 3c of which belong to separate circuits.
  • the individual heat exchangers 3a, 3c are screwed together, but have separate coolant inflows and outflows.
  • FIG. 4 shows a heat exchanger 2, the individual heat exchangers 3, 3b, 3d of which are in flow connection via bores 5 at the contact point and thereby form a cooling unit which belongs to a single-circuit cooling system.
  • the contact surfaces are generally machined and provided with a seal 11 in the single-circuit cooling system.
  • the heat exchanger arrangement according to FIGS. 3 and 4 represents a compact and flexible solution in which low production costs are achieved by using as many standard and identical components as possible.

Description

Die Erfindung bezieht sich auf eine Wärmetauscheranordnung mit mindestens zwei Wärmetauschern, die von einem gemeinsamen Lüfter mit Kühlluft beaufschlagt werden.The invention relates to a heat exchanger arrangement with at least two heat exchangers, which are acted upon by cooling air from a common fan.

Bei flüssigkeitsgekühlten Brennkraftmaschinen wird der Kühlflüssigkeits-Wärmetauscher üblicherweise vor der Brennkraftmaschine angeordnet. Zwischen Brennkraftmaschine und Kühlflüssigkeitswärmetauscher befindet sich ein Lüfter, der die Kühlluft durch den Wärmetauscher fördert. Um eine gleichmäßige Beaufschlagung des Wärmetauschers und zugleich einen geringen Abstand zwischen Wärmetauscher und Lüfter zu erreichen, wird üblicherweise eine quadratische Wirkfläche des Wärmetauschers angestrebt. Solche Wärmetauscher sind z.B. aus der Schrift US-A-2 264 820 bekannt.In liquid-cooled internal combustion engines, the coolant heat exchanger is usually arranged in front of the internal combustion engine. There is a fan between the internal combustion engine and the coolant heat exchanger, which conveys the cooling air through the heat exchanger. In order to achieve a uniform loading of the heat exchanger and at the same time a small distance between the heat exchanger and fan, a square active surface of the heat exchanger is usually aimed for. Such heat exchangers are e.g. known from the document US-A-2 264 820.

Häufig werden von Brennkraftmaschinen Zusatzaggregate angetrieben, die eine erhebliche Kühlleistung für das Arbeitsmedium des Zusatzaggregates benötigen. Der erforderliche zusätzliche Wärmetauscher ist häufig größer als der Kühlflüssigkeits-Wärmetauscher der Brennkraftmaschine. Es ist schwierig, beide Wärmetauscher gleichmäßig mit Kühlluft zu beaufschlagen und zugleich mit geringem Abstand zum Lüfter unterzubringen.Additional units are often driven by internal combustion engines, which require a considerable cooling capacity for the working medium of the additional unit. The additional heat exchanger required is often larger than the coolant heat exchanger of the internal combustion engine. It is difficult to apply cooling air evenly to both heat exchangers and at the same time to accommodate them at a short distance from the fan.

Der Erfindung liegt die Aufgabe zugrunde, ein Wärmetauscher-Lüftersystem mit mindestens zwei Wärmetauschern und einem Lüfter zu schaffen, das möglichst geringen Platzbedarf aufweist.The invention has for its object to provide a heat exchanger fan system with at least two heat exchangers and a fan that requires as little space as possible.

Die Aufgabe wird gelöst durch die kennzeichnenden Merkmale des Anspruchs 1. Der standardmäßig vorgesehene Wärmetauscher für die Kühlflüssigkeit der Brennkraftmaschine hat dabei eine einfache Quadrat- oder Rechteckform, während der Zusatzwärmetauscher eine L-Form aufweist. Diese ist den jeweils abzuführenden Wärmemengen in der Größe angepaßt und verwirklicht die insgesamt quadratische Form der Wirkflächen der Wärmetauscher. Durch die erfindungsgemäße Anordnung wird auch bei geringem Abstand des Lüfters von der Ebene der Wärmetauscher eine gleichmäßige Beaufschlagung der Wirkflächen der Wärmetauscher erreicht, da diese wegen ihrer in etwa quadratischen Form von dem Lüfter optimal bestrichen werden.The object is achieved by the characterizing features of claim 1. The standard heat exchanger for the coolant of the internal combustion engine has a simple square or rectangular shape, while the additional heat exchanger has an L-shape. This is adapted in size to the heat quantities to be dissipated and realizes the overall square shape of the active surfaces of the heat exchangers. Due to the arrangement according to the invention, even when the fan is at a small distance from the plane of the heat exchanger, the active surfaces of the heat exchanger are uniformly acted on, since these are optimally coated by the fan because of their approximately square shape.

Es ist üblich, den Lüfter aus Einbaugründen als Sauglüfter zu betreiben, doch bietet auch ein Drucklüfter Vorteile, z. B. eine geringere Lüfterleistung wegen des geringeren Volumens der zu fördernden Kaltluft. Die Vorteile der Erfindung gelten jedoch für beide Lüfterbauarten.It is common to operate the fan as a suction fan for installation reasons, but a pressure fan also offers advantages, e.g. B. a lower fan power because of the lower volume of the cold air to be conveyed. However, the advantages of the invention apply to both types of fans.

Eine vorteilhafte Weiterbildung der Erfindung bewirkt, daß bei einer Brennkraftmaschine mit konstanter Kühlwärmemenge und Zusatzaggregaten mit unterschiedlichen Kühlwärmemengen jeweils ein Kühlmittelwärmetauscher konstanter Abmessungen mit unterschiedlich großen Wärmetauscher für das Arbeitsmedium zu der erfindungsgemäßen optimalen Kombination zusammengefügt werden können. Dabei sind die kühlluftseitigen Strömungswiderstände beider Wärmetauscher in etwa gleich ausgelegt, wodurch eine gleichmäßige Kühlluftverteilung ebenfalls gefördert wird.An advantageous development of the invention has the effect that, in an internal combustion engine with a constant amount of cooling heat and additional units with different amounts of cooling heat, a coolant heat exchanger of constant dimensions with different sizes of heat exchanger for the working medium can be combined to the optimal combination according to the invention. The flow resistances on the cooling air side of both heat exchangers are designed approximately the same, whereby a uniform cooling air distribution is also promoted.

Durch eine vorteilhafte Weiterbildung der Erfindung wird der gleiche Effekt auch bei ladeluftgekühlten Motoren erreicht, bei denen der Ladeluftkühler in Strömungsrichtung vor dem Kühlmittelwärmetauscher angeordnet ist. Diese Lage des Ladeluftkühlers bewirkt außerdem, daß nur die Kühlluft des ersten Wärmetauschers vorgewärmt wird, während die des zweiten Wärmetauschers nicht vorgewärmt wird, wodurch dessen Abmessungen nicht vergrößert werden müssen.An advantageous development of the invention achieves the same effect even in charge air-cooled engines in which the charge air cooler is arranged upstream of the coolant heat exchanger. This location of the charge air cooler also has the effect that only the cooling air of the first heat exchanger is preheated, while that of the second heat exchanger is not preheated, so that its dimensions do not have to be increased.

Durch eine vorteilhafte Ausbildung der Erfindung wird die Effektivität des Lüfters erhöht. Die Kühlluftführung verhindert das Ansaugen bzw. Abblasen von Fremdluft und bewirkt so eine Wirkungsgradsteigerung und Geräuschsenkung des Lüfters. Spielen Lüfterwirkungsgrad und Lüftergeräusch im Vergleich zu den Anschaffungskosten der Kühlluftführung keine Rolle, so kann die Kühlluftführung auch entfallen.The effectiveness of the fan is increased by an advantageous embodiment of the invention. The cooling air duct prevents the sucking in or blowing off of external air and thus increases the efficiency and noise level of the fan. If fan efficiency and fan noise play no role in comparison to the purchase costs of the cooling air duct, the cooling air duct can also be omitted.

In einer vorteilhaften Weiterbildung der Erfindung wird der Lüfter durch ein Gebläse mit Leitrad ersetzt, das wegen des dadurch bewirkten erhöhten Kühlluftdrucks die Verwendung kompakter Hochleistungswärmetauscher mit erhöhtem Durchströmwiderstand ermöglicht.In an advantageous development of the invention, the fan is replaced by a blower with a stator, which enables the use of compact high-performance heat exchangers with increased flow resistance due to the increased cooling air pressure caused thereby.

Sind mehrere Zusatzwärmetauscher erforderlich, so können zur Gestaltung der L-Form auch zwei Rechtecke verwendet werden. Es sind auch vier Rechteck-Wärmetauscher denkbar, die den Standard-Kühlmittelwärmetauscher gleichsam einrahmen. In jeder denkbaren Anordnung bilden die Wärmetauscher aber eine insgesamt in etwa quadratische Wirkfläche.If several additional heat exchangers are required, two rectangles can also be used to design the L-shape. There are also four rectangular heat exchangers conceivable Frame the standard coolant heat exchanger as it were. In any conceivable arrangement, however, the heat exchangers form an overall approximately square effective area.

Durch eine vorteilhafte Weiterbildung der Erfindung werden Wärmetauschersonderanfertigungen vermieden und nur Standardwärmetauscher mit rechteckigen Wirkflächen zur Bildung eines L-förmigen verwendet. Dadurch werden die Fertigungskosten gesenkt. Gleichzeitig bleibt der Vorteil eines kompakten Wäremtauscher-Lüftersystems mit maximaler Kühlwirkung aufgrund der insgesamt quadratischen Form der Wirkflächen der Wärmetauscher erhalten.An advantageous further development of the invention avoids custom-made heat exchangers and only uses standard heat exchangers with rectangular active surfaces to form an L-shaped one. This reduces manufacturing costs. At the same time, the advantage of a compact heat exchanger fan system with maximum cooling effect is retained due to the overall square shape of the active surfaces of the heat exchangers.

Eine weitere Kostensenkung wird durch eine vorteilhafte Weiterbildung der Erfindung erreicht. Gleiche Endkastenrohlinge bedeuten nur eine Gießform und nur ein Rohteillager. Bei der mechanischen Bearbeitung der Endkästen ist abzuwägen zwischen geringstem Bearbeitungs- und Montageaufwand sowie kleinster Leckagegefahr einerseits, in dem nur die erforderliche Mindestbearbeitung der verschiedenen Endkästen erfolgt und der völligen Gleichheit aller fertigen Endkästen mit entsprechend vereinfachter Lagerhaltung andererseits, jedoch erhöhtem Bearbeitungs- und Montageaufwand sowie erhöhtem Leckagerisiko, da in diesem Falle alle nicht benötigten, jedoch gebohrten, Bohrungen verschlossen werden müssen.A further cost reduction is achieved by an advantageous development of the invention. The same end box blanks mean only one mold and only one raw part store. In the mechanical processing of the end boxes, the least amount of processing and assembly work and the smallest risk of leakage, on the one hand, in which only the required minimum processing of the various end boxes is carried out and the complete equality of all finished end boxes with correspondingly simplified storage, on the other hand, but increased processing and assembly costs and increased Leakage risk, since in this case all holes that are not required but are drilled must be closed.

Durch vorteilhafte Weiterbildung der Erfindung wird erreicht, daß die Einzelwärmetauscher bei der Montage in der gewünschten L-Form mit ihren Anschlüssen zusammenpassen. Durch Kombination passend gebohrter Einzelwärmetauscher können erfindungsgemäß entweder ein einziger Wärmetauscher großer Oberfläche für ein Einkreissystem oder aber zwei getrennte Wärmetauscher für ein Zweikreissystem geschaffen werden.An advantageous further development of the invention ensures that the individual heat exchangers fit together with their connections in the desired L-shape during assembly. By combining suitably drilled individual heat exchangers according to the invention, either a single heat exchanger with a large surface area for a single-circuit system or two separate heat exchangers for a double-circuit system can be created.

Bei komplett bearbeiteten Endkästen mit sämtlichen vorgesehenen Bohrungen werden bei Ein- bzw. Zweikreissystemen die jeweils nicht benötigten Bohrungen durch Stopfen verschlossen.In the case of completely machined end boxes with all the holes provided, the holes that are not required are closed with plugs in single or double-circuit systems.

Erfindungsgemäß können auch zwei Einzelwärmetauscher mit identischen Wirkflächen Verwendung finden. Der Gleichheit der Bauteile steht aber hier die nicht komplette Ausnutzung der quadratischen Fläche als Nachteil gegenüber, wobei die nicht genutzte Fläche abgedeckt werden muß.According to the invention, two individual heat exchangers with identical active surfaces can also be used. The equality of the components is contrasted here by the incomplete use of the square area as a disadvantage, whereby the unused area must be covered.

Desweiteren ist es möglich, zusätzliche Wärmetauscher mit ebenfalls gleichen Endkästen und entsprechend längerer Wirkfläche so anzuordnen, daß der Kühlmittelwärmetauscher in L-Form so eingeschlossen wird, daß sich wieder eine insgesamt quadratische Form aller Wirkflächen ergibt.Furthermore, it is possible to arrange additional heat exchangers with likewise the same end boxes and a correspondingly longer active surface in such a way that the coolant heat exchanger is enclosed in an L-shape in such a way that a total square shape of all active surfaces results again.

Weitere Merkmale der Erfindung ergeben sich aus der folgenden Beschreibung und der Zeichnung, in der Ausführungsbeispiele der Erfindung schematisch dargestellt sind.Further features of the invention result from the following description and the drawing, in which exemplary embodiments of the invention are shown schematically.

Es zeigen:

Fig.1:
eine Ansicht der Wirkflächen der Wärmetauscher,
Fig.2:
eine Draufsicht auf die Wärmetauscher mit vorge schaltetem Lüfter und einer Kühlluftführung.
Fig.3:
Blick auf die Wirkflächen der Wärmetauscher, wobei die Einzelwärmetauscher getrennte Kreisläufe aufweisen,
Fig.4:
Blick auf die Wirkflächen der Wärmetauscher, wobei zwei Einzelwärmetauscher in Strömungsverbindung stehen.
Show it:
Fig.1:
a view of the active surfaces of the heat exchangers,
Fig. 2:
a plan view of the heat exchanger with pre-switched fan and a cooling air duct.
Fig. 3:
View of the active surfaces of the heat exchangers, whereby the individual heat exchangers have separate circuits,
Fig. 4:
View of the active surfaces of the heat exchangers, with two individual heat exchangers in flow connection.

Gemäß Fig. 1 hat der erste Wärmetauscher 1 eine rechteckig geformte Wirkfläche, die durch den zweiten Wärmetauscher 2 aufgrund von dessen abgestimmter L-Form zu einer quadratischen Form der gesamten Wirkfläche ergänzt wird. Der erste Wärmetauscher 1 dient zur Rückkühlung des Kühlmediums der Brennkraftmaschine, der zweite Wärmetauscher 2 zur Rückkühlung des Arbeitsmediums des oder der Zusatzaggregate der Brennkraftmaschine. Innerhalb des zweiten Wärmetauscher 2 befindet sich eine Trennwand 15, die zur inneren Führung des zu kühlenden Mediums dient. Beide Wärmetauscher besitzen Wärmetauscherkästen 14, 14′, 14˝, 14‴, 14˝˝, die zum gleichmäßigen Verteilen und zum Sammeln des jeweiligen Kühlmediums dienen.1, the first heat exchanger 1 has a rectangular-shaped active surface, which is supplemented by the second heat exchanger 2 due to its coordinated L-shape to a square shape of the entire active surface. The first heat exchanger 1 is used for recooling the cooling medium of the internal combustion engine, the second heat exchanger 2 is used for recooling the working medium of the additional equipment or units of the internal combustion engine. Inside the second heat exchanger 2 there is a partition 15 which serves for the internal guidance of the medium to be cooled. Both heat exchangers have heat exchanger boxes 14, 14 ', 14˝, 14 ‴, 14˝˝, which are used for even distribution and for collecting the respective cooling medium.

Aus Figur 2 geht die Anordnung des Ladeluftkühlers 12 hervor. Dieser ist in Strömungsrichtung vor dem ersten Wärmetauscher 1 angeordnet und besitzt die gleiche Wirkfläche wie dieser. Er heizt zwar die Kühlluft des ersten Wärmetauschers 1 geringfügig auf. Das wirkt sich jedoch bei dem Kühlmedium des ersten Wärmetauschers 1 -in der Regel Kühlwasser- im Gegensatz zum Kühlmittel des zweiten -in der Regel Hydrauliköl- wegen des höheren Temperaturniveaus des Kühlwassers weniger stark aus.The arrangement of the charge air cooler 12 is shown in FIG. This is arranged upstream of the first heat exchanger 1 and has the same effective area as this. It does heat the cooling air of the first heat exchanger 1 slightly. However, this has less of an impact on the cooling medium of the first heat exchanger 1 — usually cooling water — in contrast to the coolant of the second — generally hydraulic oil — because of the higher temperature level of the cooling water.

Der Widerstand der Kühlluft in den zwei bzw. drei Wärmetauschern ist so abgestimmt, daß er auf der gesamten Fläche der Wärmetauscher konstant ist und damit eine gleichmäßige Durchströmung mit Kühlluft bewirkt.The resistance of the cooling air in the two or three heat exchangers is adjusted so that it is constant over the entire surface of the heat exchanger and thus causes a uniform flow of cooling air.

Der Lüfter 9 ist als Sauglüfter ausgebildet. Er befindet sich in geringem Abstand in Strömungsrichtung hinter den Wärmetauschern. Sein Durchmesser entspricht dem Innenkreis der quadratischen Fläche der Wirkflächen der Wärmetauscher. Zwischen den Wärmetauschern 1, 2, 12 und dem Lüfter 9 ist eine Kühlluftführung 13 angeordnet. Sie dient zur Führung der Kühlluft und verhindert, daß der Lüfter 9 Falschluft ansaugt. Aus dem gleichen Grunde sind der erste und zweite Wärmetauscher mit geringem Abstand zusammengefügt. Der dadurch ermöglichte hohe Wirkungsgrad des Wärmetauscher-Lüftersystems senkt auch den Geräuschpegel des Lüfters 9.The fan 9 is designed as a suction fan. It is located a short distance behind the heat exchangers in the flow direction. Its diameter corresponds to the inner circle of the square area of the active surfaces of the heat exchangers. Between heat exchangers 1, 2, 12 and the fan 9, a cooling air duct 13 is arranged. It serves to guide the cooling air and prevents the fan 9 from sucking in false air. For the same reason, the first and second heat exchangers are joined together at a short distance. The resulting high efficiency of the heat exchanger fan system also lowers the noise level of the fan 9.

Die erfindungsgemäße Anordnung der Wärmetauscher bietet den Vorteil einer gleichmäßigen Beaufschlagung aller Wirkflächen der Wärmetauscher trotz kleiner axialer Baulänge aufgrund des möglichen geringen Lüfterabstandes. Außerdem wird eine Aufheizung der Kühlluft des zweiten Wärmetauschers 2 vermieden, was dessen Abmessungen kleinstmöglich hält.The arrangement of the heat exchangers according to the invention offers the advantage of uniform application to all active surfaces of the heat exchangers despite the small axial length due to the possible small fan spacing. In addition, heating of the cooling air of the second heat exchanger 2 is avoided, which keeps its dimensions as small as possible.

Die erfindungsgemäße Wärmetauscheranordnung nach Fig.3 besteht aus einem ersten Wärmetauscher 1 und einem zweiten Wärmetauscher 2. Der dazugehörige Lüfter 9 ist in den Fig. 3 und 4 durch einen Lüfterkreis angedeutet.The heat exchanger arrangement according to FIG. 3 consists of a first heat exchanger 1 and a second heat exchanger 2. The associated fan 9 is indicated in FIGS. 3 and 4 by a fan circuit.

Die Wirkflächen der Wärmetauscher 1, 2 bilden insgesamt in etwa ein Quadrat, dem der Lüfterkreis einbeschrieben ist.The active surfaces of the heat exchangers 1, 2 form approximately a square, to which the fan circuit is inscribed.

Der erste Wärmetauscher 1, der beispielsweise für die Kühlflüssigkeit einer Brennkraftmaschine verwendet wird, weist eine rechteckige Wirkfläche auf. Der zweite Wärmetauscher 2 besteht aus zwei Einzelwärmetauschern 3, 3a, 3b, 3c, 3d, die in L-Form angeordnet sind und den ersten Wärmetauscher 1 zur Hälfte einfassen und zu einem Quadrat ergänzen. Der zweite Wärmetauscher 2 dient beispielsweise zur Kühlung von Hydrauliköl.The first heat exchanger 1, which is used, for example, for the cooling liquid of an internal combustion engine, has a rectangular active surface. The second heat exchanger 2 consists of two individual heat exchangers 3, 3a, 3b, 3c, 3d, which are arranged in an L-shape and surround the first heat exchanger 1 in half and add a square. The second heat exchanger 2 is used, for example, to cool hydraulic oil.

Die Einzelwärmetauscher 3, 3a, 3b, 3c, 3d bestehen aus einer rechteckigen Wirkfläche 10, 10′, die an zwei gegenüberliegenden Seiten von je zwei Endkästen 4, 4′, 4˝ begrenzt wird. Den Wirkflächen 10, 10′ wird die Kühlflüssigkeit über die Endkästen 4, 4′, 4˝ zu- bzw. abgeführt.The individual heat exchangers 3, 3a, 3b, 3c, 3d consist of a rectangular active surface 10, 10 ', which is delimited on two opposite sides by two end boxes 4, 4', 4˝. The active surfaces 10, 10 ', the cooling liquid is supplied or discharged via the end boxes 4, 4', 4˝.

Die Wirkflächen 10, 10′ unterscheiden sich lediglich durch ihre Länge, was fertigungstechnisch keinen Mehraufwand bedeutet.The active surfaces 10, 10 'differ only in their length, which means no additional manufacturing technology.

Die verschiedenen Endkästen 4, 4′, 4˝ werden durch unterschiedliche Bearbeitung aus demselben Rohling hergestellt. Jeder Endksten 4, 4′, 4˝ weist eine Endwand 7 und zwei Stirnwände 8, 8′ auf, deren Außenflächen sich in den Kanten 6, 6′ schneiden.The different end boxes 4, 4 ', 4˝ are made by different processing from the same blank. Each end box 4, 4 ', 4˝ has an end wall 7 and two end walls 8, 8', the outer surfaces of which intersect in the edges 6, 6 '.

Im Bereich der Kante 6 jedes Endkastens 4, 4′, 4˝ ist entweder in der Endwand 7 oder in der Stirnwand 8 eine Bohrung 5 angebracht, die zum Zu- oder Ablauf der Kühlflüssigkeit dient. Die Bohrungen 5 haben den gleichen Abstand von der Kante 6 und sind in der Mitte der jeweiligen Endwand 7 bzw. Stirnwand 8 angebracht.In the area of the edge 6 of each end box 4, 4 ', 4˝ a bore 5 is made either in the end wall 7 or in the end wall 8, which serves for the inlet or outlet of the cooling liquid. The holes 5 have the same distance from the edge 6 and are made in the middle of the respective end wall 7 or end wall 8.

Die Endkästen 4, 4′, 4˝ sind an den Wirkflächen 10, 10′ jeweils so angebracht, daß ihre Bohrungen diagonal gegenüberliegen. Dadurch wird eine gleichmäßige Verteilung der Kühlflüssigkeit auf die Wirkflächen 10, 10′ erreicht.The end boxes 4, 4 ', 4˝ are attached to the active surfaces 10, 10' so that their bores are diagonally opposite. As a result, a uniform distribution of the cooling liquid on the active surfaces 10, 10 'is achieved.

Die Einzelwärmetauscher 3, 3a, 3b, 3c, 3d berühren sich mit der Endwand 7 und der Stirnwand 8 jeweils eines Endkastens 4, 4′, 4˝. Sie sind an der Berührungsstelle zusammengeschraubt.The individual heat exchangers 3, 3a, 3b, 3c, 3d touch each other with the end wall 7 and the end wall 8 of an end box 4, 4 ', 4˝. They are screwed together at the point of contact.

Fig. 3 zeigt einen Wärmetauscher 2, dessen Einzelwärmetauscher 3a, 3c zu getrennten Kreisläufen gehören. Die Einzelwärmetauscher 3a, 3c sind zwar zusammengeschraubt, weisen jedoch getrennte Kühlflüssigkeitszu- und -abläufe auf.3 shows a heat exchanger 2, the individual heat exchangers 3a, 3c of which belong to separate circuits. The individual heat exchangers 3a, 3c are screwed together, but have separate coolant inflows and outflows.

Fig. 4 zeigt einen Wärmetauscher 2, dessen Einzelwärmetauscher 3, 3b, 3d über Bohrungen 5 an der Berührungsstelle in Strömungsverbindung stehen und dadurch eine kühltechnische Einheit bilden, die zu einem Einkreiskühlsystem gehört. Die Berührungsflächen sind generell bearbeitet und bei dem Einkreiskühlsystem mit einer Dichtung 11 versehen.4 shows a heat exchanger 2, the individual heat exchangers 3, 3b, 3d of which are in flow connection via bores 5 at the contact point and thereby form a cooling unit which belongs to a single-circuit cooling system. The contact surfaces are generally machined and provided with a seal 11 in the single-circuit cooling system.

Durch Wahl der Länge der Wirkfläche des liegend angeordneten Einzelwärmetauschers kann dessen Kühlleistung den jeweiligen Anforderungen angepaßt werden. Die in den Fig. 3 und 4 strichpunktiert dargestellte Lösung zeigt zwei Einzelwärmetauscher mit identischen Wirkflächen, während die durchgezogen dargestellte Lösung zwar unterschiedliche Wärmetauscher, jedoch die größtmögliche Wirkfläche aufweist.By choosing the length of the active surface of the horizontally arranged individual heat exchanger, its cooling capacity can be adapted to the respective requirements. The solution shown in dash-dotted lines in FIGS. 3 and 4 shows two individual heat exchangers with identical active surfaces, while the solution shown in solid lines has different heat exchangers, but has the largest possible active surface.

Die erfindungsgemäße Wärmetauscheranordnung nach Fig.3 und 4 stellt eine kompakte und flexible Lösung dar, bei der durch Verwendung von möglichst vielen Standard- und Gleichbauteilen niedrige Fertigungskosten erzielt werden.The heat exchanger arrangement according to FIGS. 3 and 4 represents a compact and flexible solution in which low production costs are achieved by using as many standard and identical components as possible.

Claims (9)

  1. A heat-exchanger arrangement comprising at least two heat exchangers (1, 2) supplied with cooling air by air-flow means (9) common to them both, the heat exchangers (1, 2) being arranged adjacent one another, without a gap, in a plane, and the dimensions and shape of the individual heat exchangers (1, 2) being so chosen that the end-faces of the heat exchangers (1, 2) have an approximately four-sided overall surface of projection, the first heat exchanger (1) being provided for the coolant of an internal combustion engine,
    characterised in that the second heat exchanger (2) is provided for the working fluid of additional units driven by the internal combustion engine, and that the dimensions of the first heat exchanger (1) are constant whereas the dimensions of the second heat exchanger (2) are chosen in accordance with the required cooling effect, the first heat exchanger (1) having a square or rectangular end-face whereas the second heat exchanger (2) has an L-shaped end-face.
  2. A heat-exchanger arrangement according to claim 1,
    characterised in that the second heat exchanger (2) comprises two individual heat exchangers (3, 3a, 3b, 3c, 3d) which together form the L shape, each individual heat exchanger (3, 3a, 3b, 3c, 3d) forming an arm of the L.
  3. A heat-exchanger arrangement according to claim 2,
    characterised in that the individual heat exchangers (3, 3a, 3b, 3c, 3d) each have two end boxes (4, 4′) which are substantially identical, at least before being worked on mechanically.
  4. A heat-exchanger arrangement according to claim 2 or 3,
    characterised in that the end faces of the individual heat exchangers (3, 3a, 3b, 3c, 3d) are rectangular and have at least the same width.
  5. A heat-exchanger arrangement according to any one of the preceding claims, comprising end boxes (4, 4′) each having an end wall (7) and two face walls (8, 8′), the end walls (7) and the face walls (8, 8′) intersecting at two edges (6, 6′),
    characterised in that space for a bore (5) is provided in the end wall (7) and in the face wall (8) in the region of the edge (6) of each end box (4, 4′), the bores (5) being equidistant from the edge (6) and the side edges of the end wall (7) and the face wall (8), and that the end boxes (4, 4′) of each individual heat exchanger (3, 3a, 3b, 3c, 3d) are so disposed that their respective edges (6) are diagonally opposite.
  6. A heat-exchanger arrangement according to any one of the preceding claims, characterised in that each pair of end boxes (4, 4′) of the various individual heat exchangers (3, 3a, 3b, 3c, 3d) are rigidly interconnected, and their edges (6) adjacent the bores (5) are directly opposite.
  7. A heat-exchanger arrangement according to any one of the preceding claims, characterised in that the end boxes (4, 4′) of the individual heat exchangers (3, 3a, 3b, 3c, 3d) are machined or worked-on in the area of contact and are each formed with a bore (5), and a seal is disposed in the area of contact between the individual heat exchangers (3, 3a, 3b, 3c, 3d).
  8. A heat-exchanger arrangement according to any one of the preceding claims, characterised in that an air charge cooler (12) of a supercharged, intercooled internal combustion engine is disposed in the flow direction in front of the first heat exchanger (1), and the sum of the cooling-air resistances of the air charge cooler (12) and of the second heat exchanger (1) is approximately equal to the cooling-air resistance of the second heat exchanger (2).
  9. A heat-exchanger arrangement according to any one of the preceding claims, characterised in that a cooling-air passage (13) is provided between the heat exchangers (1, 2) and the air-flow means (9), and that the air-flow means (9) take the form of a blower with an impeller or rotor, the associated heat exchangers being adapted to the increased cooling-air pressure.
EP19910104510 1990-03-27 1991-03-22 Arrangement for heat-exchanger Expired - Lifetime EP0450425B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE59103074T DE59103074D1 (en) 1991-03-22 1991-03-22 Heat exchanger arrangement.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19904009726 DE4009726A1 (en) 1990-03-27 1990-03-27 Two heat exchangers for IC engine - are arranged so that they receive cooling air from common fan
DE19904033897 DE4033897A1 (en) 1990-10-25 1990-10-25 Heat exchanger assembly

Publications (3)

Publication Number Publication Date
EP0450425A2 EP0450425A2 (en) 1991-10-09
EP0450425A3 EP0450425A3 (en) 1991-10-30
EP0450425B1 true EP0450425B1 (en) 1994-09-28

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EP19910104510 Expired - Lifetime EP0450425B1 (en) 1990-03-27 1991-03-22 Arrangement for heat-exchanger

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Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4142023C2 (en) * 1991-12-19 2001-05-10 Behr Gmbh & Co Heat exchanger unit for motor vehicles
FR2777643B1 (en) * 1998-04-20 2000-06-30 Valeo Thermique Moteur Sa MULTIFUNCTIONAL HEAT EXCHANGER, PARTICULARLY FOR A MOTOR VEHICLE
DE29909871U1 (en) * 1999-06-02 2000-10-12 Autokuehler Gmbh & Co Kg Heat exchangers, especially oil coolers
DE10227929A1 (en) * 2002-06-21 2004-01-08 Behr Gmbh & Co. The heat exchanger
DE10328458A1 (en) * 2003-06-25 2005-01-27 Daimlerchrysler Ag Motor vehicle radiator has body divided into segments to divide coolant flow, which is connected to outlet so separate, possibly different cooling powers or coolant temperatures can be realized
BE1025208B1 (en) * 2017-05-12 2018-12-12 Cnh Industrial Belgium Nv COOLER WITH SHRINKED CORE FOR A VEHICLE

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2264820A (en) * 1939-05-17 1941-12-02 Fred M Young Combination oil and water cooler
US2505790A (en) * 1946-07-24 1950-05-02 Perfex Corp Combination radiator and oil cooler
DE3344220A1 (en) * 1983-12-07 1985-06-20 Audi AG, 8070 Ingolstadt Heat exchanging device, in particular for motor vehicles

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EP0450425A2 (en) 1991-10-09
EP0450425A3 (en) 1991-10-30

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