EP1876407B1 - Cooling device for a motor vehicle - Google Patents

Cooling device for a motor vehicle Download PDF

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Publication number
EP1876407B1
EP1876407B1 EP07013151A EP07013151A EP1876407B1 EP 1876407 B1 EP1876407 B1 EP 1876407B1 EP 07013151 A EP07013151 A EP 07013151A EP 07013151 A EP07013151 A EP 07013151A EP 1876407 B1 EP1876407 B1 EP 1876407B1
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EP
European Patent Office
Prior art keywords
fan
cooling device
frame
accordance
radiator
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EP07013151A
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German (de)
French (fr)
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EP1876407A1 (en
Inventor
Uwe Blass
Ulrich Vollert
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F28F9/002—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core with fastening means for other structures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/10—Guiding or ducting cooling-air, to, or from, liquid-to-air heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/06—Guiding or ducting air to, or from, ducted fans
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the invention relates to a cooling device for a motor vehicle according to the preamble of claim 1.
  • a cooling device is for example from the DE 4015259 known.
  • Cooling devices for motor vehicles with coolant-cooled internal combustion engines generally consist of a coolant radiator through which the coolant and ambient air flow, a fan associated with the coolant radiator and a frame arranged between fan and radiator, also called radiator frame, fan cowl or fan cowl.
  • the latter has the task of supplying the cooling air leaving the coolant radiator as completely as possible to the fan.
  • the fan is generally designed as axial fan, shell fan (axial fan with shrouded blade tips) or as a radial fan.
  • the fan is driven by the internal combustion engine via a fluid friction clutch and is therefore firmly connected to the engine block, which is suspended elastically relative to the vehicle frame.
  • the coolant radiator is also attached to the vehicle frame.
  • the at least one movement compensating device or the at least one sealing element is arranged, fixed and / or sealed directly to the at least one coolant radiator.
  • the other end of the at least one motion compensation device connects to the radiator-side end of the at least one radiator or fan cowl.
  • the axial depth is shortened, improves the flow guidance on the at least one frame, ie the pressure loss is reduced and also the production costs are reduced.
  • an attachment point frame part opposite the radiator
  • the Camber depth fan cowl depth
  • the movement compensation element may be formed as a sleeve made of an elastomer, which is fastened or sealed on the one hand to the coolant radiator and on the other hand to the front side of the frame. This bridges the gap between the radiator and the frame.
  • an embodiment of the motion compensation element as an elastically deformable strip, which is also fastened on both sides. The relatively smooth design - compared to a concertina-like cuff - results in lower flow losses.
  • the motion compensation element only on one side, z. B. to attach to the frame; the other side abuts with an elastic bias on the circumference of the coolant radiator.
  • the sealing effect is maintained when relative movements occur because the sealing surface can follow the movements of the coolant radiator due to the elastic prestressing.
  • this solution eliminates the second attachment, which is replaced by a sliding seal.
  • the fan can advantageously be designed as an axial fan, preferably as a shell fan, which is also equipped with an inlet nozzle.
  • the entire frame including Zargenring and inlet nozzle can be made in one piece, in particular as a plastic injection molded part.
  • the advantage here are the low production costs and the significantly improved flow conditions due to the smooth wall of the frame, which is not interrupted by a gap.
  • the dimension for the radial gap is less than 9 mm, preferably less than 6 mm, wherein the lower limit is preferably above 3.5 mm.
  • These gaps in the area from 3.5 to 9 mm apply to fan outer diameter in the range of 400 to 900 mm, preferably in the range of 500 to 800 mm, wherein there is no fixed ratio of radial gap to fan outer diameter.
  • Fig. 1 shows a partially illustrated cooling device 1, which consists of a coolant radiator 2, a jacket fan 3 and a frame 4.
  • the coolant radiator is connected to a coolant circuit, not shown, of an internal combustion engine and on the one hand by the coolant and on the other hand by ambient air in the direction of the arrow L flows through.
  • the jacket fan 3 has an axial blading 3a and a jacket 3b connected to the blading 3a.
  • the frame 4 is connected via a motion compensation element 5 with the circumference of the radiator 2 and sealed, so that from the coolant radiator 2 exiting air channeled through the frame 4 and the fan 3 is supplied.
  • the frame 4 has a Zargenring 4a, which surrounds the rotating fan casing 3b, and an inlet nozzle 4b, in which the frontal, protruding part of the shell 3b protrudes.
  • the frame 4 including the frame ring 4a and inlet nozzle 4b is integrally formed as a plastic tip part.
  • the fan 3 is - which is not shown - compared to an engine block of an internal combustion engine, not shown Motor vehicle stored and is driven by the internal combustion engine.
  • the frame 4 with Zargenring 4a and inlet nozzle 4b is - which is also not shown - motor-mounted, so that there is a minimum radial gap 6 between the casing 3b and the ring frame 4a.
  • the coolant radiator 2 is - as known from the prior art - compared to the vehicle frame (body), not shown supported. This results in the known relative movements between frame 4 and coolant radiator 2, which are compensated by the motion compensation element 5 shown here only schematically.
  • the movement compensation element 5 is arranged directly on the radiator 2 and on the radiator-side front end of the frame 4.
  • Embodiments of the motion compensation element 5 are as a detail X in the FIGS. 3, 4, 5 shown.
  • Fig. 2 shows a further cooling device 7 with a coolant radiator 2 (as in Fig. 1 ), a frame 8 with Zargenring 8a and an axial fan 9 (here without coat), which rotates in the Zargenring 8a, leaving a small radial gap 10.
  • the axial fan 9 and the frame 8 are arranged fixed to the motor, so that also relative movements occur, which via the arranged on the radiator 2 compensation element 5 (analog Fig. 1 ) are compensated.
  • the in Fig. 1 and Fig. 2 illustrated minimum radial gaps 6, 10 in a range between 3.5 and 9 mm, preferably in a range between 4 and 8.5 mm.
  • the radial gap results from half the difference between the outer diameter of the fan and the inner ring diameter of the inner ring.
  • the radial gap is the extent to which the fan 3 or 9 is displaced before it touches the frame 4a or 8a.
  • the specified ranges for the gap size apply to fan diameters in the range of 400 to 900 mm, which the Applicant has determined by measurements. There is no fixed ratio between radial gap and fan diameter, but constant gap dimensions were measured for a larger diameter range. These are therefore absolute gap dimensions that are not or at least in a larger area not dependent on the fan diameter.
  • Fig. 3 shows a first embodiment of the motion compensation element 5 according to Fig. 1 and 2 , which is provided here with the reference numeral 11.
  • the movement compensation element 11 is formed as a concertina-like cuff, preferably made of an elastomer and has two end faces 11a, 11b which are fastened on the one hand to the circumference 2b of the coolant cooler 2 and on the other hand to the end face 4a of the frame 4.
  • the type of attachment of the sleeve 11 to the frame 4, 4a and the radiator 2 are not shown in detail, they correspond to the known prior art.
  • Fig. 4 shows a further embodiment of the motion compensation element 5, which is formed as a slightly curved sealing strip 13 with two frontal mounting edges 13a, 13b.
  • the preferably made of an elastomer strip 13 is also connected to the front side 4a of the frame 4 and the circumference 2b of the radiator 2.
  • the gap 12 between coolant radiator 2 and end face 4 a of the frame 4 is thus bridged and sealed. Due to the flexible design of the strip element 13 relative movements are possible.
  • the sleeve 11 is here a smooth transition between the radiator 2 and frame 4, ie without substantial disturbance of the voltage applied to the frame flow.
  • Fig. 5 shows a further embodiment of the movement compensation element 5, namely a prestressed, sliding seal 14, which has a fastening edge 14a on the frame side and a sealing region 14b on the radiator side, which bears under pretension on the circumference 2b of the radiator 2 and thus effects a seal.
  • the attachment edge 14a is firmly connected to the frame 4, so that a clamping of the elastic seal 14 is given. Therefore, the sealing region 14b, which may be formed, for example, as a brush seal, is constantly on the circumference 2b of the radiator 2. If relative movements between radiator 2 and frame 4 occur, follows the sealing region 14b due to its bias to the circumference 2b of the radiator second

Abstract

The device (1) has a cooling fluid radiator (2), through which the air flows. A blower (3) is arranged behind the cooling fluid radiator in air flow direction. A case (4) is arranged between the cooling fluid radiator and the blower and has a case ring (4a). A movement compensating unit (5) is provided within an area of the case. The movement compensating unit is fastened on one side with the case and on the other side with the cooling fluid radiator.

Description

Die Erfindung betrifft eine Kühlvorrichtung für ein Kraftfahrzeug nach dem Oberbegriff des Patentanspruches 1. Eine derartige Kühlvorrichtung ist z.B. aus der DE 4015259 bekannt.The invention relates to a cooling device for a motor vehicle according to the preamble of claim 1. Such a cooling device is for example from the DE 4015259 known.

Kühlvorrichtungen für Kraftfahrzeuge mit kühlmitteigekühlten Verbrennungsmotoren bestehen im Allgemeinen aus einem Kühlmittelkühler, der vom Kühlmittel und Umgebungsluft durchströmt wird, einem dem Kühlmittelkühler zugeordneten Lüfter und einer zwischen Lüfter und Kühler angeordneten Zarge, auch Kühlerzarge, Lüfterzarge oder Lüfterhaube genannt. Letztere hat die Aufgabe, die aus dem Kühlmittelkühler austretende Kühlluft möglichst vollständig dem Lüfter zuzuleiten. Der Lüfter ist im Allgemeinen als Axiallüfter, Mantellüfter (Axiallüfter mit ummantelten Blattspitzen) oder auch als Radiallüfter ausgebildet. Insbesondere bei Nutzfahrzeugen wird der Lüfter von der Brennkraftmaschine über eine Flüssigkeitsreibungskupplung angetrieben und ist daher fest mit dem Motorblock verbunden, welcher elastisch gegenüber dem Fahrzeugrahmen aufgehängt ist. Auch der Kühlmittelkühler ist am Fahrzeugrahmen befestigt. Wegen der Schwingungen des Motors gegenüber dem Fahrzeugrahmen ergeben sich Relativbewegungen zwischen Kühler bzw. kühlerfeste Zarge und motorfestem Lüfter, welche kompensiert werden müssen. Dies kann entweder durch einen relativ großen Spalt zwischen Lüfter und Zargenring oder durch ein Bewegungsausgleichselement im Bereich der Zarge erfolgen, welche somit geteilt ist.Cooling devices for motor vehicles with coolant-cooled internal combustion engines generally consist of a coolant radiator through which the coolant and ambient air flow, a fan associated with the coolant radiator and a frame arranged between fan and radiator, also called radiator frame, fan cowl or fan cowl. The latter has the task of supplying the cooling air leaving the coolant radiator as completely as possible to the fan. The fan is generally designed as axial fan, shell fan (axial fan with shrouded blade tips) or as a radial fan. In particular, in commercial vehicles, the fan is driven by the internal combustion engine via a fluid friction clutch and is therefore firmly connected to the engine block, which is suspended elastically relative to the vehicle frame. The coolant radiator is also attached to the vehicle frame. Because of the vibrations of the engine relative to the vehicle frame resulting relative movements between radiator or radiator frame and motor-resistant fan, which must be compensated. This can be done either by a relatively large gap between the fan and Zargenring or by a motion compensation element in the frame, which is thus divided.

Durch die US-A 4,398,508 wurde eine Kühlvorrichtung mit einem motorfesten Axiallüfter und einer kühlerfesten Zarge bekannt, wobei zwischen Lüfterumfang und Kühlerzarge ein relativ großer Spalt belassen ist, welcher durch eine Bürstendichtung überbrückt wird. Eine ähnliche Kühlvorrichtung mit einem ummantelten Axiallüfter, einem so genannten Mantellüfter, wurde durch die DE 198 03 502 A1 der Anmelderin bekannt. Der Ringspalt zwischen kühlerfester Zarge, an welcher auch eine Einlaufdüse angeordnet ist, wird durch eine Bürstendichtung weitestgehend abgedichtet. Eine weitere Bürstendichtung wurde durch die DE 33 39 059 A1 einerseits für einen Axiallüfter und andererseits für einen Radiallüfter bekannt. Wegen der relativ großen Spalte und dem Verschleiß der Bürstendichtungen sind derartige Kühlvorrichtungen unzureichend.By the US-A 4,398,508 was a cooling device with a motor-fixed axial fan and a cooler-solid frame known, between the fan circumference and radiator frame, a relatively large gap is left, which is bridged by a brush seal. A similar cooling device with a sheathed axial fan, a so-called sheath fan, was characterized by the DE 198 03 502 A1 the applicant known. The annular gap between the radiator frame, on which an inlet nozzle is arranged, is largely sealed by a brush seal. Another brush seal was through the DE 33 39 059 A1 known on the one hand for an axial fan and on the other hand for a radial fan. Because of the relatively large gaps and wear of the brush seals, such cooling devices are inadequate.

Um den Spalt zwischen Lüfter und Zargenring möglichst gering zu halten, werden Lüfter und Zargenring jeweils motorseitig befestigt, und die Zarge wird zwischen Zargenring und Kühler geteilt, sodass ein Spalt gebildet wird, welcher durch ein Bewegungsausgleichs- bzw. elastisches Dichtelement überbrückt wird. Durch die DE 44 38 814 C1 der Anmelderin wurde eine solche Kühlvorrichtung mit einem motorfesten Axiallüfter und einem motorfesten Zargenring (Mantel) bekannt. Die bekannte Kühlvorrichtung weist einen Kühlmittelkühler auf, an den eine Kühlerzarge angeschlossen ist, welche über eine elastische, ringförmige Lippendichtung mit dem motorfesten Mantel verbunden ist. Damit können Relativbewegungen zwischen motorfestem Zargenring (Mantel) und Kühlerzarge ausgeglichen werden, wobei gleichzeitig die Zarge geschlossen ist. Nachteilig hierbei ist, dass die Zarge geteilt und der Spalt durch ein zusätzliches Bauteil, nämlich das Dicht- bzw. Bewegungsausgleichelement, überbrückt werden muss, was eine Vergrößerung der axialen Bautiefe der Kühlvorrichtung bedeutet.In order to keep the gap between fan and Zargenring as low as possible, fan and Zargenring are respectively fixed on the engine side, and the frame is divided between Zargenring and radiator, so that a gap is formed, which is bridged by a Bewegungsausgleichs- or elastic sealing element. By the DE 44 38 814 C1 The applicant has been known such a cooling device with a motor-fixed axial fan and a motor-fixed frame ring (jacket). The known cooling device has a coolant radiator, to which a radiator frame is connected, which is connected via a resilient, annular lip seal with the engine-fixed shell. This relative movements between the motor-fixed Zargenring (jacket) and radiator frame can be compensated, while the frame is closed. The disadvantage here is that the frame divided and the gap by an additional component, namely the sealing or motion compensation element, must be bridged, which means an increase in the axial depth of the cooling device.

Durch die DE 33 04 297 C2 der Anmelderin wurde eine weitere Kühlvorrichtung mit einem motorfesten Mantellüfter sowie einer motorfesten Einlaufdüse für den Mantellüfter bekannt. Am Kühlmittelkühler ist eine Kühlerzarge befestigt, welche mittels einer elastischen Lippe gegenüber der Einlaufdüse abgedichtet ist. Auch hier ergibt sich eine erhöhte axiale Bautiefe infolge des Einbaus der Dichtlippe.By the DE 33 04 297 C2 the applicant, a further cooling device with a motor-resistant shell fan and a fixed motor inlet nozzle for the shell fan was known. At the coolant radiator, a radiator frame is fixed, which is sealed by means of an elastic lip opposite the inlet nozzle. Here, too, results in an increased axial depth due to the installation of the sealing lip.

Durch die DE 40 15 259 A1 wurde eine Kühlvorrichtung mit einem über eine Flüssigkeitsreibungskupplung vom Motor des Kraftfahrzeuges angetriebenen Axiallüfter bekannt, welcher von einem auf der Lüfterantriebswelle gelagerten Mantel bzw. Zargenring umgeben ist, sodass sich ein minimaler Radialspalt zwischen den Lüfterblattspitzen und dem Lüftermantel ergibt. Eine am Kühler befestigte Kühlerzarge ist über eine Gummimanschette mit dem Lüftermantel verbunden, um Relativbewegungen zwischen Lüftermantel und Kühler auszugleichen. Nachteilig bei der bekannten Kühlvorrichtung ist die erhebliche Vergrößerung der axialen Bautiefe und die Beeinträchtigung der Lüftetströmung durch die Manschette, was einen erhöhten Druckabfall bzw. einen erhöhte Lüfterleistung zur Folge hat.By the DE 40 15 259 A1 a cooling device with a via a fluid friction clutch driven by the engine of the motor vehicle axial fan was known, which is surrounded by a mounted on the fan drive shaft shroud or ring so that there is a minimum radial gap between the fan blade tips and the fan shroud. A radiator frame attached to the radiator is connected via a rubber sleeve to the fan shroud to compensate for relative movements between fan shroud and radiator. A disadvantage of the known cooling device is the considerable increase in the axial depth and the impairment of the Lüftetströmung through the cuff, which has an increased pressure drop or increased fan performance.

Es ist Aufgabe der vorliegenden Erfindung, bei einer Kühlvorrichtung der eingangs genannten Art die axiale Bautiefe zu verkürzen, die Strömungsführung der Luft zu verbessern und die Herstellkosten zu senken.It is an object of the present invention to shorten the axial depth in a cooling device of the type mentioned, to improve the flow guidance of the air and to reduce the manufacturing costs.

Diese Aufgabe wird durch die Merkmale des Patentanspruches 1 gelöst. Erfindungsgemäß ist vorgesehen, dass die zumindest eine Bewegungsausgleichseinrichtung bzw. das zumindest eine Dichtelement direkt an dem zumindest einen Kühlmittelkühler angeordnet, dort befestigt und/oder abgedichtet ist. Das andere Ende der zumindest einen Bewegungsausgleichseinrichtung schließt an das kühlerseitige Ende der zumindest einen Kühler- bzw. Lüfterzarge an. Damit wird der Spalt zwischen dem zumindest einen Kühlmittelkühler und den motorfesten Teilen wie Zarge oder Zargenring direkt an den zumindest einen Kühlmittelkühler verlagert, und die zumindest eine Zarge muss nicht mehr geteilt, sondern kann vielmehr einstückig ausgebildet werden. Damit entfällt auch ein zusätzliches Bauteil (Teil der Zarge). Es ergeben sich somit als Vorteile, dass die axiale Bautiefe verkürzt, die Strömungsführung an der zumindest einen Zarge verbessert, d. h. der Druckverlust vermindert und auch die Herstellkosten verringert werden. Durch das Verschieben des zumindest einen Bewegungsausgleichselementes an den Umfang des zumindest einen Kühlers entfällt auch eine Befestigungsstelle (Zargenteil gegenüber Kühler), sodass axialer Bauraum gewonnen wird. Die Zargentiefe (Lüfterhaubentiefe) kann somit entweder vergrößert werden, was eine bessere Kühlleistung ergibt, oder der Bauraum kann reduziert werden.This object is solved by the features of claim 1. According to the invention, it is provided that the at least one movement compensating device or the at least one sealing element is arranged, fixed and / or sealed directly to the at least one coolant radiator. The other end of the at least one motion compensation device connects to the radiator-side end of the at least one radiator or fan cowl. Thus, the gap between the at least one coolant radiator and the engine-fixed parts such as frame or Zargenring is displaced directly to the at least one coolant radiator, and the at least one frame no longer needs to be divided, but rather can be integrally formed. This eliminates an additional component (part of the frame). It thus results as advantages that the axial depth is shortened, improves the flow guidance on the at least one frame, ie the pressure loss is reduced and also the production costs are reduced. By moving the at least one motion compensation element to the circumference of the at least one radiator, an attachment point (frame part opposite the radiator) is also eliminated, so that axial space is obtained. The Camber depth (fan cowl depth) can thus be either increased, resulting in a better cooling performance, or the space can be reduced.

Vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen. So kann das Bewegungsausgleichselement als Manschette aus einem Elastomer ausgebildet sein, welche einerseits am Kühlmittelkühler und andererseits an der Stirnseite der Zarge befestigt bzw. abgedichtet wird. Damit wird der Spalt zwischen Kühler und Zarge überbrückt. Vorteilhaft ist auch eine Ausbildung des Bewegungsausgleichselementes als elastisch verformbarer Streifen, der ebenfalls beiderseits befestigbar ist. Durch die relativ glatte Ausbildung - gegenüber einer ziehharmonikaartigen Manschette - ergeben sich geringere Strömungsverluste.Advantageous embodiments of the invention will become apparent from the dependent claims. Thus, the movement compensation element may be formed as a sleeve made of an elastomer, which is fastened or sealed on the one hand to the coolant radiator and on the other hand to the front side of the frame. This bridges the gap between the radiator and the frame. Also advantageous is an embodiment of the motion compensation element as an elastically deformable strip, which is also fastened on both sides. The relatively smooth design - compared to a concertina-like cuff - results in lower flow losses.

Möglich ist auch, das Bewegungsausgleichselement nur an einer Seite, z. B. an der Zarge zu befestigen; die andere Seite liegt mit einer elastischen Vorspannung am Umfang des Kühlmittelkühlers an. Die Dichtwirkung bleibt bei Auftreten von Relativbewegungen erhalten, weil die Dichtfläche den Bewegungen des Kühlmittelkühlers aufgrund der elastischen Vorspannung folgen kann. Bei dieser Lösung entfällt die zweite Befestigung, die durch eine gleitende Dichtung ersetzt wird.It is also possible, the motion compensation element only on one side, z. B. to attach to the frame; the other side abuts with an elastic bias on the circumference of the coolant radiator. The sealing effect is maintained when relative movements occur because the sealing surface can follow the movements of the coolant radiator due to the elastic prestressing. In this solution eliminates the second attachment, which is replaced by a sliding seal.

Der Lüfter kann vorteilhaft als Axiallüfter, vorzugsweise als Mantellüfter ausgebildet sein, der darüber hinaus mit einer Einlaufdüse ausgestattet ist. Durch die erfindungsgemäße Verschiebung des Bewegungsausgleichselements an den Umfang des Kühlmittelkühlers kann die gesamte Zarge einschließlich Zargenring und Einlaufdüse einstückig, insbesondere als Kunststoffspritzteil hergestellt werden. Von Vorteil sind hierbei die geringen Herstellkosten und die deutlich verbesserten Strömungsverhältnisse infolge der glatten Wand der Zarge, die nicht durch einen Spalt unterbrochen wird.The fan can advantageously be designed as an axial fan, preferably as a shell fan, which is also equipped with an inlet nozzle. By the inventive displacement of the motion compensation element to the periphery of the coolant radiator, the entire frame including Zargenring and inlet nozzle can be made in one piece, in particular as a plastic injection molded part. The advantage here are the low production costs and the significantly improved flow conditions due to the smooth wall of the frame, which is not interrupted by a gap.

Aufgrund der erfindungsgemäßen Anordnung von Lüfter und Zarge ergibt sich für den Radialspalt zwischen Lüfteraußen- und Zargenringinnendurchmesser sich ein äußerst geringes Maß. Vorzugsweise ist das Maß für den Radialspalt kleiner als 9 mm, vorzugsweise kleiner als 6 mm, wobei die Untergrenze bevorzugt oberhalb von 3,5 mm liegt. Diese Spaltmaße im Bereich von 3,5 bis 9 mm gelten für Lüfteraußendurchmesser im Bereich von 400 bis 900 mm, bevorzugt im Bereich von 500 bis 800 mm, wobei kein festes Verhältnis von Radialspalt zu Lüfteraußendurchmesser vorliegt. Als Vorteil des minimalen Radialspaltes ergibt sich eine höhere Lüfterleistung und eine geringere Geräuschentwicklung.Due to the inventive arrangement of the fan and frame results in an extremely small measure for the radial gap between Lüfteraußen- and Zargenringinnendurchmesser. Preferably, the dimension for the radial gap is less than 9 mm, preferably less than 6 mm, wherein the lower limit is preferably above 3.5 mm. These gaps in the area from 3.5 to 9 mm apply to fan outer diameter in the range of 400 to 900 mm, preferably in the range of 500 to 800 mm, wherein there is no fixed ratio of radial gap to fan outer diameter. As an advantage of the minimum radial gap results in a higher fan performance and lower noise.

Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im Folgenden näher erläutert. Es zeigen

Fig. 1
eine erfindungsgemäße Kühlvorrichtung mit Mantellüfter und Einlaufdüse,
Fig. 2
eine Kühlvorrichtung mit Axiallüfter und Zargenring,
Fig. 3
eine erste Ausführungsform eines Bewegungsausgleichselementes,
Fig. 4
eine zweite Ausführungsform des Bewegungsausgleichselementes und
Fig. 5
eine dritte Ausführungsform des Bewegungsausgleichselementes.
Embodiments of the invention are illustrated in the drawings and will be explained in more detail below. Show it
Fig. 1
a cooling device according to the invention with jacket fan and inlet nozzle,
Fig. 2
a cooling device with axial fan and frame ring,
Fig. 3
a first embodiment of a motion compensation element,
Fig. 4
a second embodiment of the motion compensation element and
Fig. 5
a third embodiment of the motion compensation element.

Fig. 1 zeigt eine teilweise dargestellte Kühlvorrichtung 1, welche aus einem Kühlmittelkühler 2, einem Mantellüfter 3 und einer Zarge 4 besteht. Der Kühlmittelkühler ist an einen nicht dargestellten Kühlmittelkreislauf einer Brennkraftmaschine angeschlossen und wird einerseits vom Kühlmittel und andererseits von Umgebungsluft in Richtung des Pfeiles L durchströmt. Der Mantellüfter 3 weist eine Axialbeschaufelung 3a und einen mit der Beschaufelung 3a verbundenen Mantel 3b auf. Die Zarge 4 ist über ein Bewegungsausgleichselement 5 mit dem Umfang des Kühlers 2 verbunden und abgedichtet, sodass aus dem Kühlmittelkühler 2 austretende Luft durch die Zarge 4 kanalisiert und dem Lüfter 3 zugeführt wird. Die Zarge 4 weist einen Zargenring 4a, welcher den rotierenden Lüftermantel 3b umgibt, sowie eine Einlaufdüse 4b auf, in welche der stirnseitige, überstehende Teil des Mantels 3b hineinragt. Zur Funktion des Mantellüfters in Verbindung mit einer Einlaufdüse wird auf den eingangs genannten Stand der Technik verwiesen. Die Zarge 4 einschließlich Zargenring 4a und Einlaufdüse 4b ist einstückig als Kunststoffspitzteil ausgebildet. Der Lüfter 3 ist - was nicht dargestellt ist - gegenüber einem nicht dargestellten Motorblock einer Brennkraftmaschine des Kraftfahrzeuges gelagert und wird von der Brennkraftmaschine angetrieben. Auch die Zarge 4 mit Zargenring 4a und Einlaufdüse 4b ist - was ebenfalls nicht dargestellt ist - motorfest angeordnet, sodass sich zwischen dem Mantel 3b und dem Zargenring 4a ein minimaler Radialspalt 6 ergibt. Der Kühlmittelkühler 2 ist - wie aus dem Stand der Technik bekannt - gegenüber dem nicht dargestellten Fahrzeugrahmen (Karosserie) abgestützt. Damit ergeben sich die bekannten Relativbewegungen zwischen Zarge 4 und Kühlmittelkühler 2, welche durch das hier nur schematisch dargestellte Bewegungsausgleichselement 5 kompensiert werden. Erfindungsgemäß ist das Bewegungsausgleichselement 5 direkt am Kühler 2 und am kühlerseitigen Stirnende der Zarge 4 angeordnet. Ausführungsformen des Bewegungsausgleichselementes 5 sind als Einzelheit X in den Figuren 3, 4, 5 dargestellt. Fig. 1 shows a partially illustrated cooling device 1, which consists of a coolant radiator 2, a jacket fan 3 and a frame 4. The coolant radiator is connected to a coolant circuit, not shown, of an internal combustion engine and on the one hand by the coolant and on the other hand by ambient air in the direction of the arrow L flows through. The jacket fan 3 has an axial blading 3a and a jacket 3b connected to the blading 3a. The frame 4 is connected via a motion compensation element 5 with the circumference of the radiator 2 and sealed, so that from the coolant radiator 2 exiting air channeled through the frame 4 and the fan 3 is supplied. The frame 4 has a Zargenring 4a, which surrounds the rotating fan casing 3b, and an inlet nozzle 4b, in which the frontal, protruding part of the shell 3b protrudes. For the function of the shroud fan in conjunction with an inlet nozzle, reference is made to the above-mentioned prior art. The frame 4 including the frame ring 4a and inlet nozzle 4b is integrally formed as a plastic tip part. The fan 3 is - which is not shown - compared to an engine block of an internal combustion engine, not shown Motor vehicle stored and is driven by the internal combustion engine. Also, the frame 4 with Zargenring 4a and inlet nozzle 4b is - which is also not shown - motor-mounted, so that there is a minimum radial gap 6 between the casing 3b and the ring frame 4a. The coolant radiator 2 is - as known from the prior art - compared to the vehicle frame (body), not shown supported. This results in the known relative movements between frame 4 and coolant radiator 2, which are compensated by the motion compensation element 5 shown here only schematically. According to the invention, the movement compensation element 5 is arranged directly on the radiator 2 and on the radiator-side front end of the frame 4. Embodiments of the motion compensation element 5 are as a detail X in the FIGS. 3, 4, 5 shown.

Fig. 2 zeigt eine weitere Kühlvorrichtung 7 mit einem Kühlmittelkühler 2 (wie in Fig. 1), einer Zarge 8 mit Zargenring 8a und einem Axiallüfter 9 (hier ohne Mantel), welcher im Zargenring 8a unter Belassung eines geringen Radialspaltes 10 umläuft. Auch hier sind der Axiallüfter 9 und die Zarge 8 motorfest angeordnet, sodass ebenfalls Relativbewegungen auftreten, welche über das am Kühler 2 angeordnete Ausgleichselement 5 (analog Fig. 1) kompensiert werden. Fig. 2 shows a further cooling device 7 with a coolant radiator 2 (as in Fig. 1 ), a frame 8 with Zargenring 8a and an axial fan 9 (here without coat), which rotates in the Zargenring 8a, leaving a small radial gap 10. Again, the axial fan 9 and the frame 8 are arranged fixed to the motor, so that also relative movements occur, which via the arranged on the radiator 2 compensation element 5 (analog Fig. 1 ) are compensated.

Nach einem bevorzugten Ausführungsbeispiel liegen die in Fig. 1 und Fig. 2 dargestellten minimalen Radialspalte 6, 10 in einem Bereich zwischen 3,5 und 9 mm, vorzugsweise in einem Bereich zwischen 4 und 8,5 mm. Der Radialspalt ergibt sich aus der halben Differenz zwischen Lüfteraußendurchmesser und Zargenringinnendurchmesser. Mit anderen Worten ist der Radialspalt das Maß, um welches der Lüfter 3 oder 9 verschoben wird, bevor er an der Zarge 4a oder 8a streift. Die angegebenen Bereiche für das Spaltmaß gelten für Lüfterdurchmesser im Bereich von 400 bis 900 mm, was die Anmelderin durch Messungen festgestellt hat. Dabei besteht kein festes Verhältnis zwischen Radialspalt und Lüfterdurchmesser, vielmehr wurden für einen größeren Durchmesserbereich konstante Spaltmaße gemessen. Es handelt sich somit um absolute Spaltmaße, die nicht oder zumindest in einem größeren Bereich nicht vom Lüfterdurchmesser abhängig sind.According to a preferred embodiment, the in Fig. 1 and Fig. 2 illustrated minimum radial gaps 6, 10 in a range between 3.5 and 9 mm, preferably in a range between 4 and 8.5 mm. The radial gap results from half the difference between the outer diameter of the fan and the inner ring diameter of the inner ring. In other words, the radial gap is the extent to which the fan 3 or 9 is displaced before it touches the frame 4a or 8a. The specified ranges for the gap size apply to fan diameters in the range of 400 to 900 mm, which the Applicant has determined by measurements. There is no fixed ratio between radial gap and fan diameter, but constant gap dimensions were measured for a larger diameter range. These are therefore absolute gap dimensions that are not or at least in a larger area not dependent on the fan diameter.

Fig. 3 zeigt eine erste Ausführungsform des Bewegungsausgleichselementes 5 gemäß Fig. 1 und 2, welches hier mit der Bezugszahl 11 versehen ist. Das Bewegungsausgleichselement 11 ist als ziehharmonikaartige Manschette, vorzugsweise aus einem Elastomer ausgebildet und weist zwei Stirnseiten 11a, 11b auf, welche einerseits am Umfang 2b des Kühlmittelkühlers 2 und andererseits an der Stirnseite 4a der Zarge 4 befestigt sind. Die Art der Befestigung der Manschette 11 an der Zarge 4, 4a und am Kühler 2 sind nicht näher dargestellt, sie entsprechen dem bekannten Stand der Technik. Zwischen der Stirnseite 4a der Zarge 4 und der rückseitigen Stirnfläche 2a des Kühlers 2 befindet sich ein Spalt 12, welcher in Verbindung mit der Manschette 11 die auftretenden Relativbewegungen zwischen Zarge 4 und Kühler 2 zulässt. Fig. 3 shows a first embodiment of the motion compensation element 5 according to Fig. 1 and 2 , which is provided here with the reference numeral 11. The movement compensation element 11 is formed as a concertina-like cuff, preferably made of an elastomer and has two end faces 11a, 11b which are fastened on the one hand to the circumference 2b of the coolant cooler 2 and on the other hand to the end face 4a of the frame 4. The type of attachment of the sleeve 11 to the frame 4, 4a and the radiator 2 are not shown in detail, they correspond to the known prior art. Between the end face 4 a of the frame 4 and the rear end face 2 a of the radiator 2 there is a gap 12 which, in conjunction with the sleeve 11, permits the occurring relative movements between the frame 4 and the radiator 2.

Fig. 4 zeigt eine weitere Ausführungsform des Bewegungsausgleichselementes 5, welches als leicht gewölbter Dichtstreifen 13 mit zwei stirnseitigen Befestigungsrändern 13a, 13b ausgebildet ist. Der vorzugsweise aus einem Elastomer bestehende Streifen 13 ist ebenfalls mit der Stirnseite 4a der Zarge 4 und mit dem Umfang 2b des Kühlers 2 verbunden. Der Spalt 12 zwischen Kühlmittelkühler 2 und Stirnseite 4a der Zarge 4 ist damit überbrückt und abgedichtet. Aufgrund der flexiblen Ausbildung des Streifenelementes 13 sind Relativbewegungen möglich. Im Unterschied zum Ausführungsbeispiel gemäß Fig. 3, d. h. der Manschette 11 liegt hier ein glatter Übergang zwischen Kühler 2 und Zarge 4, d. h. ohne wesentliche Störung der an der Zarge anliegenden Strömung vor. Fig. 4 shows a further embodiment of the motion compensation element 5, which is formed as a slightly curved sealing strip 13 with two frontal mounting edges 13a, 13b. The preferably made of an elastomer strip 13 is also connected to the front side 4a of the frame 4 and the circumference 2b of the radiator 2. The gap 12 between coolant radiator 2 and end face 4 a of the frame 4 is thus bridged and sealed. Due to the flexible design of the strip element 13 relative movements are possible. In contrast to the embodiment according to Fig. 3 , ie, the sleeve 11 is here a smooth transition between the radiator 2 and frame 4, ie without substantial disturbance of the voltage applied to the frame flow.

Fig. 5 zeigt ein weiteres Ausführungsbeispiel für das Bewegungsausgleichselement 5, nämlich eine vorgespannte, gleitende Dichtung 14, welche zargenseitig einen Befestigungsrand 14a und kühlerseitig einen Dichtbereich 14b aufweist, welcher unter Vorspannung am Umfang 2b des Kühlers 2 anliegt und somit eine Abdichtung bewirkt. Der Befestigungsrand 14a ist mit der Zarge 4 fest verbunden, sodass eine Einspannung der elastischen Dichtung 14 gegeben ist. Daher liegt der Dichtbereich 14b, der beispielsweise als Bürstendichtung ausgebildet sein kann, ständig am Umfang 2b des Kühlers 2 an. Wenn Relativbewegungen zwischen Kühler 2 und Zarge 4 auftreten, folgt der Dichtbereich 14b aufgrund seiner Vorspannung dem Umfang 2b des Kühlers 2. Fig. 5 shows a further embodiment of the movement compensation element 5, namely a prestressed, sliding seal 14, which has a fastening edge 14a on the frame side and a sealing region 14b on the radiator side, which bears under pretension on the circumference 2b of the radiator 2 and thus effects a seal. The attachment edge 14a is firmly connected to the frame 4, so that a clamping of the elastic seal 14 is given. Therefore, the sealing region 14b, which may be formed, for example, as a brush seal, is constantly on the circumference 2b of the radiator 2. If relative movements between radiator 2 and frame 4 occur, follows the sealing region 14b due to its bias to the circumference 2b of the radiator second

Durch die Bewegungsausgleichselemente 11, 13, 14 werden also keine bzw. nur geringe Kräfte zwischen Kühler 2 und Zarge 4 übertragen; vielmehr besteht die primäre Funktion in der Abdichtung bei gleichzeitigem Bewegungsausgleich. Dementsprechend sind Abweichungen von den oben beschriebenen Ausführungsbeispielen möglich, soweit sie erfindungsgemäß am Kühlmittelkühler angeordnet sind.By the motion compensation elements 11, 13, 14 so no or only small forces between radiator 2 and frame 4 are transmitted; Rather, the primary function is the seal with simultaneous motion compensation. Accordingly, deviations from the embodiments described above are possible, as long as they are arranged according to the invention on the coolant radiator.

Claims (15)

  1. Cooling device for a motor vehicle with an internal combustion engine comprising at least one coolant cooler (2) through which air is able to flow, at least one fan (3, 9) positioned downstream of the coolant cooler (2) in the direction of air flow (L) and at last one frame (4, 8) which is positioned between the coolant cooler (2) and the at least one fan (3, 9) and has at least one frame ring (4a, 8a) which encases the fan, at least one motion compensation element (5) being provided in the region of the at least one frame (4, 8),
    characterised in that
    the at least one motion compensation element (5, 11, 13, 14) is attached on one side to the at least one frame (4, 8) and on the other side to the at least one coolant cooler (2).
  2. Cooling device in accordance with claim 1,
    characterised in that
    the at least one motion compensation element (5, 11, 13, 14) is sealed.
  3. Cooling device in accordance with claim 1 or 2,
    characterised in that
    the at least one motion compensation element (5) is designed as a sleeve (11, 11a, 11b).
  4. Cooling device in accordance with one of the preceding claims,
    characterised in that
    the at least one motion compensation element (5) is designed as an elastic strip (13, 13a, 13b).
  5. Cooling device in accordance with one of the preceding claims,
    characterised in that
    the at least one motion compensation element (5) is designed as at least one elastic sealing strip (14, 14a) which is fixed on one side and has at least one free sealing face (14b) which lies adjacent to the coolant cooler forming a seal.
  6. Cooling device in accordance with claim 5,
    characterised in that
    the at least one free sealing face (14b) is designed as at least one brush seal which is pre-stressed and lies adjacent to the circumference (2b) of the coolant cooler (2).
  7. Cooling device in accordance with one of the preceding claims,
    characterised in that
    the at least one fan is designed as an axial fan (3, 9).
  8. Cooling device in accordance with one of the preceding claims,
    characterised in that
    the at least one fan is designed as a ring fan (3, 3a, 3b).
  9. Cooling device in accordance with claim 8,
    characterised in that
    at least one intake nozzle (4b) is assigned to the at least one ring fan (3, 3a, 3b).
  10. Cooling device in accordance with one of the preceding claims,
    characterised in that
    the at least one frame (4, 8) and the at least one frame ring (4a, 8a) are designed in one piece as a moulded plastic part.
  11. Cooling device in accordance with claim 9 or 10,
    characterised in that
    the at least one intake nozzle (4b) is designed in one piece with the at least one frame (4) and the at least one frame ring (4a).
  12. Cooling device in accordance with one of the preceding claims,
    characterised in that
    a minimal radial gap (6, 10) is left between the at least one fan (3, 9) and the at least one frame ring (4a, 8a).
  13. Cooling device in accordance with claim 12,
    characterised in that
    the radial gap (6, 10) is less than 9.0 mm and preferably less than 6.0 mm.
  14. Cooling device in accordance with claim 13,
    characterised in that
    the radial gap (6, 10) is greater than 3.5 mm.
  15. Cooling device in accordance with claim 13 or 14,
    characterised in that
    the at least one fan (3, 9) has an external diameter and the external diameter lies within a range of 400 to 900 mm, and preferably within a range of 500 to 800 mm.
EP07013151A 2006-07-06 2007-07-05 Cooling device for a motor vehicle Active EP1876407B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006031609 2006-07-06

Publications (2)

Publication Number Publication Date
EP1876407A1 EP1876407A1 (en) 2008-01-09
EP1876407B1 true EP1876407B1 (en) 2009-01-07

Family

ID=38508816

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07013151A Active EP1876407B1 (en) 2006-07-06 2007-07-05 Cooling device for a motor vehicle

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Country Link
EP (1) EP1876407B1 (en)
AT (1) ATE420335T1 (en)
DE (2) DE502007000363D1 (en)

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Publication number Priority date Publication date Assignee Title
DE102008046508A1 (en) * 2008-09-09 2010-03-11 Behr Gmbh & Co. Kg Ventilating device for ventilating internal combustion engine of motor vehicle, has wheel cover section and fan shroud section between which gap is formed, where gap runs towards centrifugal force occurring during rotation of fan wheel
DE102009050347B4 (en) 2008-11-27 2019-04-04 Schaeffler Technologies AG & Co. KG Switchable friction clutch with protected sliding toothing
DE102009012025A1 (en) 2009-03-10 2010-09-16 Behr Gmbh & Co. Kg Cooling device for a motor vehicle
DE202010010913U1 (en) 2010-07-31 2011-11-03 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Shroud
DE102011105451A1 (en) 2011-06-22 2012-12-27 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Fan of a motor vehicle
DE102013015835A1 (en) 2013-09-24 2015-04-16 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Fan
CN103742250A (en) * 2013-10-29 2014-04-23 广西玉柴重工有限公司 Adjustable air director
USD860427S1 (en) 2017-09-18 2019-09-17 Horton, Inc. Ring fan

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Publication number Priority date Publication date Assignee Title
IT8353039V0 (en) * 1982-03-15 1983-03-10 Sueddeutsche Kuehler Behr AXIAL FAN PARTICULARLY FOR WATER COOLED THERMAL ENGINE COOLING RADIATORS
DE3304297A1 (en) * 1982-03-15 1984-03-15 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Axial fan, especially for a cooler of a water-cooled internal combustion engine
DE8207204U1 (en) * 1982-03-15 1982-08-19 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart AXIAL BLOWER, ESPECIALLY FOR RADIATOR OF A WATER-COOLED INTERNAL COMBUSTION ENGINE
DE3446732C2 (en) * 1984-12-21 1986-10-23 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Fan wheel
DE3737391A1 (en) * 1987-11-04 1989-05-18 Kloeckner Humboldt Deutz Ag Air guiding device for a radiator/fan arrangement
DE4015259A1 (en) * 1990-05-12 1991-11-14 Behr Gmbh & Co Ventilator casing for coolant blower in motor vehicle - has roller bearing between belt-driven pulley and tightly enclosed fan secured against rotation w.r.t. engine
DE9016496U1 (en) * 1990-12-05 1991-03-14 Behr Gmbh & Co, 7000 Stuttgart, De
DE4438184C1 (en) * 1994-10-26 1996-04-11 Behr Gmbh & Co Axial air fan for heavy goods vehicle radiator

Also Published As

Publication number Publication date
DE102007031462A1 (en) 2008-01-10
EP1876407A1 (en) 2008-01-09
ATE420335T1 (en) 2009-01-15
DE502007000363D1 (en) 2009-02-26

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