EP1779054B1 - Wärmetauscher mit rohrkern, besonders für einen turboverbrennungsmotor - Google Patents

Wärmetauscher mit rohrkern, besonders für einen turboverbrennungsmotor Download PDF

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Publication number
EP1779054B1
EP1779054B1 EP05791964A EP05791964A EP1779054B1 EP 1779054 B1 EP1779054 B1 EP 1779054B1 EP 05791964 A EP05791964 A EP 05791964A EP 05791964 A EP05791964 A EP 05791964A EP 1779054 B1 EP1779054 B1 EP 1779054B1
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EP
European Patent Office
Prior art keywords
tubes
series
turbulators
heat exchanger
air
Prior art date
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Not-in-force
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EP05791964A
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English (en)
French (fr)
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EP1779054A1 (de
Inventor
Jean-Yves Rohellec
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RENAULT TECHNOCENTRE
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RENAULT TECHNOCENTRE
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Publication of EP1779054A1 publication Critical patent/EP1779054A1/de
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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
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F28D2021/0082—Charged air coolers

Definitions

  • the invention relates to a heat exchanger tube bundle, in particular for cooling the charge air in a supercharged internal combustion engine of a motor vehicle.
  • the invention relates more particularly to a heat exchanger, in particular of the air-air type, for a supercharged internal combustion engine, of the type comprising at least a first collector and a second collector which are connected transversely by a bundle of horizontal tubes in which circulates an internal flow of air to be cooled by a flow of cooling fluid flowing outside the tube bundle.
  • cooling devices such as a heat exchanger or heat exchanger, to cool the charge air in order to reduce the thermal load of the engine, the Exhaust gas temperature, and therefore NOx emissions and fuel consumption.
  • the charge air can essentially be cooled in two ways, either by the engine coolant or by the ambient air outside.
  • the mounting position of the chiller - typically an air-water type exchanger - can be chosen freely, which is very advantageous due to the extreme compactness of the chillers cooled by water. Nevertheless, it is not possible to lower the temperature of the charge air to the desired value which is generally below that of the coolant.
  • the air-air exchanger can also be placed at another location in the engine compartment of the vehicle, but it must then be ventilated by means of a separate fan, such as a motor-fan unit.
  • a separate fan such as a motor-fan unit.
  • the air-air heat exchanger is generally placed in front of the water radiator with the advantage of always having sufficient cooling at low speed because of the presence of the water radiator fan.
  • tubes of the bundle generally comprise means such as "turbulators” so called because they cause a flow of air to be cooled turbulent or non-laminar type and to increase the heat exchange between the air to cool and the coolant.
  • the invention proposes a heat exchanger, in particular of the air-air type, whose internal pressure drop is particularly reduced.
  • the heat exchanger according to the invention has, with equivalent cooling capacity and pressure drop compared to the exchangers of the state of the art, a reduced bulk allowing notably to implant it below the water radiator. of the motor.
  • first or “second / second”, “lower” or “upper” and the “longitudinal”, “transverse” or “vertical” directions will be used in a nonlimiting manner in the description and in the claims. respectively elements or positions according to the definitions given in the description and according to the trihedron (L, V, T) shown in the figures.
  • FIG. 1 shows diagrammatically the front part of a motor vehicle 10 comprising a power unit with an internal combustion engine 12, which is here of the supercharged type.
  • such a supercharged engine 12 comprises an intake circuit, an exhaust system and a turbocharger (not shown) which comprises a compressor for pressurizing fresh atmospheric air and a turbine to provide the energy mechanical necessary to drive the compressor.
  • the compression of the air causes its heating so that it is necessary that the compressed fresh air, called supercharging, is then cooled before reaching the intake manifold and cyclically feed the cylinders at a frequency which is a function of the engine speed 12.
  • the intake circuit therefore comprises a cooling device, also known as a cooler, which generally consists, as previously explained, in a heat exchanger 14 through which a cooling coolant fluid passes so as to cool the internal air flow Fi of supercharging coming from the compressor.
  • a cooling device also known as a cooler
  • a heat exchanger 14 through which a cooling coolant fluid passes so as to cool the internal air flow Fi of supercharging coming from the compressor.
  • the pressurized exhaust gas is discharged via an exhaust manifold (not shown) into an exhaust duct (not shown) which selectively powers the turbine of the turbocharger before these exhaust gases are exhausted. gases are released into the atmosphere.
  • the heat exchanger 14 is an air-air type exchanger so that the cooling fluid is constituted by an external air flow Fe.
  • the external air flow Fe corresponds in particular to the air flow resulting from the dynamic pressure of the air caused by the movement of the vehicle.
  • the external air flow Fe is here schematically represented by arrows with a corrugated shaft so as to distinguish them from the other arrows in the figures, in particular arrows with a straight shaft schematically representing the internal air flow Fi.
  • the heat exchanger 14 comprises a first collector 16 and a second collector 18 which are connected transversely by a bundle 20 of tubes in which circulates an internal air flow Fi to be cooled by the external flow of cooling air Fe circulating outside the bundle 20 of tubes.
  • the first collector 16 and the second collector 18 constitute here respectively an inlet air box and an outlet air box of the interior air flow Fi to be cooled.
  • the inlet and outlet air boxes are identical, which makes it possible in particular to reduce the cost of production.
  • the inside air flow Fi circulates from left to right along the arrows illustrated in FIGS. 2 and 3, ie in the transverse direction (T).
  • the external flow of air Fe cooling circulates, as illustrated by the arrows in Figures 1 and 3, in the longitudinal direction (L), ie orthogonal to the transverse direction (T).
  • the bundle 20 of tubes mainly comprises a first portion P1, a second portion P2 and an intermediate distribution box 24 interposed transversely, here centrally, between the first and second portions P1, P2.
  • the heat exchanger 14 has substantially a shape of "bar”, that is to say, it has a generally oblong transverse shape, here generally parallelepiped-rectangle.
  • a heat exchanger 14 is therefore likely to be implanted below the cooling radiator 22 of the engine cooling circuit 12, as illustrated in FIGS. 1 and 2.
  • the heat exchanger 14 is located above the cooling radiator 22 of the engine cooling circuit 12.
  • the first series S1P1 of tubes with turbulators 34 of the first part P1 of the heat exchanger 14 comprises an upper group 26 of tubes and a lower group 28 of tubes
  • the second series S2P1 of tubes without turbulators of the first part P1 is arranged vertically between the upper groups 26 and lower 28 of tubes of the first series S1P1 of tubes with turbulators 34 of the first part P1.
  • the first series S1P2 of tubes without turbulators of the second part P2 of the heat exchanger 14 comprises an upper group 30 of tubes and a lower group 32 of tubes and the second series S2P2 of tubes with turbulators 34 of the second part P2 is arranged vertically between the upper and lower groups 32 of tubes of the first series S1P2 of tubes without turbulators of the second part P2.
  • the second series S2P1 without turbulators of the first part P1 comprises a single central tube 36 and the first series S1P2 without turbulators of the second part P2 comprises an upper tube 30 and a lower tube 32 forming here respectively the upper and lower groups.
  • the tubes comprising turbulators 34 have been shown in FIG. 4 in "grayed” or “halftone” in order to differentiate them and are also better visible on the sections of FIGS. 5 and 7.
  • the heat exchanger 14 has circulation passages 38 for the external air flow Fe of cooling, preferably between each of the tubes of the first series S1P1 and the second series S2P1 so as to optimize the heat exchange between the internal flow. Fi and the external air flow Fe.
  • the passages 38 are in particular visible in the front view of FIG. 2 and in the sectional view of FIG. 4.
  • the intermediate distribution box 24 comprises connection means 40 of the output of the first series S1P1 of tubes provided with turbulators 34 of the first part P1 with the inlet of the first series S1P2 of tubes without turbulators of the second part P2 and connecting the output of the second series S2P1 of tubes without turbulators of the first part P1 with the input of the second series S2P2 of tubes equipped with turbulators 34 of the second part P2.
  • connection means 40 of the distribution box 24 are constituted by an inclined top transverse plate 42 and an inclined lower transverse plate 44 which vertically delimit between them a divergent inner section 46 of connection between the outlet of the central tube 36 without turbulators of the first part P1 and the entries of each of the tubes of the second series of tubes S2P2 comprising turbulators 34.
  • the upper plate 42 delimits vertically with the upper horizontal wall 48 of the body 50 of the housing 24, an upper convergent section 52 for connection between the outlets of each tube of the upper group 26 of the first series of tubes S1P1 comprising turbulators 34 and the inlet of the upper tube 30.
  • the lower plate 44 delimits vertically with the lower horizontal wall 54 of the body 50 of the housing 24, a lower convergent section 56 connecting the outlets of each tube of the lower group 28 of the first series of tubes S1P1 comprising turbulators 34 and the inlet of the lower tube 32.
  • connection sections 46, 52 and 56 are also delimited longitudinally by the opposite transverse walls 58 of the body 50 of the housing 24.
  • the first manifold 16 forming the inlet air box comprises an inlet port OE1 which is connected to an upstream element of the intake duct of the engine intake circuit 12 and an outlet orifice OS1 which opens into the beam 20.
  • the internal air flow Fi to be cooled from the compressor enters the first manifold 16 through the orifice input OE1 which emerges through the opening OS1 to first cross the first portion P1 of the heat exchanger 14.
  • the internal air flow Fi is distributed to circulate respectively in the first series S1P1 of tubes with turbulators of total passage section A11 and the second series S2P1 of tubes without turbulators of total passage section A12.
  • the overall passage A1 section of the first portion P1 corresponds globally to the sum of the total passage sections A11 and A12 respectively of the first series S1P1 and the second series S2P1 so that the internal air flow Fi is divided into two parts. parts Fi1 and Fi 2 and is distributed here also between the first series S1P1 and the second series S2P1.
  • the portion Fi1 of the internal air flow Fi is cooled during its passage through the first series S1P1 of tubes whose turbulators 34 make it possible to increase the heat dissipation by the external flow of air Fe cooling circulating in the passages 38.
  • the internal air flow Fi undergoes a first pressure drop which is essentially caused by the first series S1P1 of turbulent tubes.
  • the internal air flow Fi to be cooled corresponding respectively to the parts Fi1 and Fi2 then passes through the distribution box 24 before passing through the second portion P2 of the heat exchanger 14.
  • the other part Fi2 of the internal air flow Fi having passed through the second series S2P1 of tubes without turbulators of the first part P1 with little or no loss of charge, then passes through the second series S2P2 of tubes with turbulators 34. the second part P2 to be cooled in turn.
  • the second portion P2 of the heat exchanger 14 comprises, as the first part P1, circulation passages 38 of the external air flow Fe cooling between each of the tubes of the first series S1P2 and the second series S2P2 of in order to optimize the heat exchange between the internal flow Fi and the external air flow Fe.
  • the internal air flow Fi issuing from the respective outlets of the first and second series S1P2 and S2P2 of tubes opens into at least one inlet port OE2 of the second manifold 18, forming the outlet air box, then continues its in a downstream element of the conduit of the engine intake circuit 12 to which is connected at least one outlet port OS2 of the second manifold 18.
  • the first series of tubes S1P1 and S1P2 have a total passage section A11 and A21 which are respectively substantially equivalent to the total passage sections A12 and A22 of the first and second series of tubes S2P1 and S2P2.
  • the tubes of the first series S1P1 and S1P2 as well as the tubes of the second series S2P1 and S2P2 of each of the first and second parts P1, P2 have, in a vertical sectional plane, a parallelepipedal longitudinal section, here rectangular.
  • the tubes of the first series S1P1 and S1P2 as well as the tubes of the second series S2P1 and S2P2 of each of the first and second portions P1, P2 have in a vertical sectional plane a generally circular longitudinal section.
  • the dimensions of the bundle 20 of the heat exchanger 14 are, for example, between 500 and 800 mm for the length (L), between 40 and 200 mm for the height (h) and between 50 and 120 mm for the width (1). .
  • each part of the flow Fi passing through a series of tubes provided with turbulators 34 does not actually travel between the inlet orifice OE1 and the outlet orifice OE2 that half of this length, therefore "L / 2", is in the first part P1 or in the second part P2 which makes it possible to obtain a reduction of the pressure drop.
  • the number of horizontal tubes of the beam is advantageously increased.
  • such an arrangement of a heat exchanger 14 makes it possible to eliminate problems such as the "mask effect" caused by a first heat exchanger which, arranged in front of a second heat exchanger such as the cooling radiator, then constitutes a "screen” for the second heat exchanger and which is particularly likely to disturb the circulation of the external flow of cooling air.
  • such an implantation of the heat exchanger 14 facilitates the connection of the inlet and outlet ports of the exchanger with the respective ducts of the intake circuit, in particular improving accessibility to the exchanger 14 and furthermore, simplifying the routes of the previously tortuous conduits and of greater length.
  • the internal air flow Fi can in particular circulate in the tube bundle in opposite directions, that is to say from right to left crossing first the second part P2 then the distribution box 24 and finally the first part P1.
  • the second manifold 18 constitutes an air inlet box of the internal air flow Fi and the first manifold 16 an outlet air box.
  • a motor-fan unit such as the motor-fan unit associated with the radiator of the engine cooling circuit, is capable of supplying the heat exchanger 14 with sufficient cooling air when the external air flow created when the vehicle is running is insufficient, especially when the vehicle rolls slowly or is stopped while the engine 12 continues to operate.
  • Beam tubes 20 may be vertical.
  • the heat exchanger 14 is of the air-liquid type in which the cooling liquid is for example constituted by water or oil.

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

Claims (9)

  1. Wärmetauscher (14), insbesondere vom Typ Luft-Luft für einen aufgeladenen Verbrennungsmotor (12) von dem Typ, der mindestens einen ersten Kollektor (16) und einen zweiten Kollektor (18) aufweist, die durch ein Bündel (20) von waagrechten Rohren verbunden sind, in denen ein innerer Luftstrom (Fi) zirkuliert, der von einem Kühlfluidstrom (Fe) gekühlt werden soll, der außerhalb der Rohre des Bündels (20) zirkuliert, dadurch gekennzeichnet, dass das Bündel (20) von Rohren mindestens aufweist :
    - einen ersten Teil (P1), der eine erste Reihe von Rohren (S1P1) mit Turbulenzerzeugern (34) mit einem Gesamtdurchlassquerschnitt (S11) und eine zweite Reihe von Rohren (S2P1) ohne Turbulenzerzeuger mit einem Gesamtdurchlassquerschnitt (S12) aufweist, der global gleich dem Gesamtdurchlassquerschnitt (S11) ist,
    - einen zweiten Teil (P2), der eine erste Reihe von Rohren (S1P2) ohne Turbulenzerzeuger mit einem Gesamtdurchlassquerschnitt (S21) und eine zweite Reihe von Rohren (S2P2) mit Turbulenzerzeugern (34) mit einem Gesamtdurchlassquerschnitt (S22) aufweist, der global gleich dem Gesamtdurchlassquerschnitt (S21) ist,
    - und einen Verteilerkasten (24) des zu kühlenden inneren Luftstroms (Fi), der Mittel (40) zur Verbindung des Ausgangs der ersten Reihe von Rohren (S1P1) mit Turbulenzerzeugern des ersten Teils (P1) mit dem Eingang der ersten Reihe von Rohren (S1P2) ohne Turbulenzerzeuger des zweiten Teils (P2) und zur Verbindung des Ausgangs der zweiten Reihe von Rohren (S2P1) ohne Turbulenzerzeuger des ersten Teils (P1) mit dem Eingang der zweiten Reihe von Rohren (S2P2) mit Turbulenzerzeugern des zweiten Teils (P2) aufweist.
  2. Wärmetauscher (14) nach Anspruch 1, dadurch gekennzeichnet, dass die erste Reihe von Rohren (S1P1) mit Turbulenzerzeugern des ersten Teils (P1) eine obere Gruppe von Rohren (26) und eine untere Gruppe von Rohren (28) aufweist, und dass die zweite Reihe von Rohren (S2P1) ohne Turbulenzerzeuger des ersten Teils senkrecht zwischen der oberen (26) und unteren Gruppe (28) von Rohren der ersten Reihe von Rohren (S1P1) mit Turbulenzerzeugern des ersten Teils (P1) angeordnet ist.
  3. Wärmetauscher (14) nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass die erste Reihe von Rohren (S1P2) ohne Turbulenzerzeuger des zweiten Teils (P2) eine obere Gruppe von Rohren (30) und eine untere Gruppe von Rohren (32) aufweist, und dass die zweite Reihe von Rohren (S2P2) mit Turbulenzerzeugern des zweiten Teils (P2) senkrecht zwischen der oberen Gruppe (30) und der unteren Gruppe (32) von Rohren der ersten Reihe von Rohren (S1P2) ohne Turbulenzerzeuger des zweiten Teils (P2) angeordnet ist.
  4. Wärmetauscher (14) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass er mindestens einen Durchlass (38) für die Zirkulation des Kühlfluidstroms (Fe) zwischen mindestens einem Teil der Rohre der ersten und der zweiten Reihe von Rohren mit Turbulenzerzeugern (S1P1, S2P2) und/oder der ersten und der zweiten Reihe ohne Turbulenzerzeuger (S1P2, S2P1) aufweist.
  5. Wärmetauscher (14) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Rohre der ersten Reihen (S1P1, S1P2) und der zweiten Reihen (S2P1, S2P2) jedes der Teile (P1, P2) gemäß einer senkrechten Schnittebene einen parallelepipedischen, insbesondere rechteckigen Längsquerschnitt aufweisen.
  6. Wärmetauscher (14) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der erste Kollektor (16) und der zweite Kollektor (18) einen Lufteingangskasten bzw. einen Luftausgangskasten des zu kühlenden inneren Luftstroms (Fi) bilden.
  7. Wärmetauscher (14) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Kühlfluid des inneren Luftstroms (Fi) aus einem äußeren Luftstrom (Fe) besteht, wie einem Luftstrom, der aus dem dynamischen Druck der Luft resultiert, der durch die Bewegung des Fahrzeugs und/oder von einem Kühlerventilator verursacht wird.
  8. Wärmetauscher (14) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass er in Querrichtung eine im Wesentlichen längliche Form aufweist, um insbesondere seinen Einbau über oder unter dem Kühler (22) des Motors (12) zu erlauben.
  9. Wärmetauscher (14) nach Anspruch 8, dadurch gekennzeichnet, dass er global von parallelepipedischer rechteckiger Form ist.
EP05791964A 2004-08-02 2005-07-13 Wärmetauscher mit rohrkern, besonders für einen turboverbrennungsmotor Not-in-force EP1779054B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0408507A FR2873798B1 (fr) 2004-08-02 2004-08-02 Echangeur thermique a faisceau tubulaire, notamment pour un moteur a combustion interne suralimente
PCT/FR2005/050580 WO2006021704A1 (fr) 2004-08-02 2005-07-13 Echangeur thermique a faisceau tubulaire, notamment pour un moteur a combustion interne suralimente

Publications (2)

Publication Number Publication Date
EP1779054A1 EP1779054A1 (de) 2007-05-02
EP1779054B1 true EP1779054B1 (de) 2008-01-02

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EP05791964A Not-in-force EP1779054B1 (de) 2004-08-02 2005-07-13 Wärmetauscher mit rohrkern, besonders für einen turboverbrennungsmotor

Country Status (9)

Country Link
US (1) US7748437B2 (de)
EP (1) EP1779054B1 (de)
JP (1) JP4543083B2 (de)
KR (1) KR20070048179A (de)
AT (1) ATE382840T1 (de)
DE (1) DE602005004160T2 (de)
ES (1) ES2297757T3 (de)
FR (1) FR2873798B1 (de)
WO (1) WO2006021704A1 (de)

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Publication number Priority date Publication date Assignee Title
US7726285B1 (en) * 2005-04-01 2010-06-01 Hansen Craig N Diesel engine and supercharger
JP5133531B2 (ja) * 2006-07-25 2013-01-30 富士通株式会社 液冷ユニット用熱交換器および液冷ユニット並びに電子機器
DE102006048667A1 (de) * 2006-10-14 2008-04-17 Modine Manufacturing Co., Racine Wärmeübertrageranordnung und Verfahren zur Wärmeübertragung
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ES2297757T3 (es) 2008-05-01
ATE382840T1 (de) 2008-01-15
US20070209783A1 (en) 2007-09-13
DE602005004160T2 (de) 2008-12-24
FR2873798A1 (fr) 2006-02-03
KR20070048179A (ko) 2007-05-08
US7748437B2 (en) 2010-07-06
WO2006021704A1 (fr) 2006-03-02
EP1779054A1 (de) 2007-05-02
FR2873798B1 (fr) 2006-09-29
JP2008508472A (ja) 2008-03-21
JP4543083B2 (ja) 2010-09-15
DE602005004160D1 (de) 2008-02-14

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