EP1779054A1 - Heat exchanger with tube core, in particular for a supercharged internal combustion engine - Google Patents

Heat exchanger with tube core, in particular for a supercharged internal combustion engine

Info

Publication number
EP1779054A1
EP1779054A1 EP05791964A EP05791964A EP1779054A1 EP 1779054 A1 EP1779054 A1 EP 1779054A1 EP 05791964 A EP05791964 A EP 05791964A EP 05791964 A EP05791964 A EP 05791964A EP 1779054 A1 EP1779054 A1 EP 1779054A1
Authority
EP
European Patent Office
Prior art keywords
tubes
series
turbulators
heat exchanger
air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05791964A
Other languages
German (de)
French (fr)
Other versions
EP1779054B1 (en
Inventor
Jean-Yves Rohellec
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
RENAULT TECHNOCENTRE
Original Assignee
RENAULT TECHNOCENTRE
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by RENAULT TECHNOCENTRE filed Critical RENAULT TECHNOCENTRE
Publication of EP1779054A1 publication Critical patent/EP1779054A1/en
Application granted granted Critical
Publication of EP1779054B1 publication Critical patent/EP1779054B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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 with tubular bundle, in particular for cooling the supercharging 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 or "coolers” such as a heat exchanger or heat exchanger, to cool the charge air to reduce the thermal load of the engine, the temperature of the exhaust gases, 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 cooler - typically an air-water type exchanger - can be chosen freely, which is very advantageous in view of the extreme compactness of the water-cooled chillers. 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.
  • Such a solution is therefore rarely implemented for reasons of cost, weight and size.
  • 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.
  • solutions are particularly sought to implement supercharging air exchangers (or coolers) above or below the water radiator.
  • 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 invention proposes a heat exchanger of the type described above, characterized in that the bundle of tubes comprises at least:
  • a first part comprising a first series of tubes with turbulators having a total passage section and a second series of tubes without turbulators having a total passage section generally equivalent to the total passage section,
  • a second part comprising a first series of tubes without turbulators having a total passage section and a second series of tubes with turbulators having a total passage section generally equivalent to the total passage section, and a distribution box of the internal air flow to be cooled comprising means for connecting the outlet of the first series of tubes with turbulators of the first part with the inlet of the first series of tubes without turbulators of the second part. and connecting the output of the second series of tubes without turbulators of the first part with the inlet of the second series of tubes with turbulators of the second part.
  • 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.
  • the first series of tubes with turbulators of the first part comprises an upper group of tubes and a lower group of tubes and in that the second series of tubes without turbulators of the first part is arranged vertically between the upper and lower groups of tubes of the first series of tubes with turbulators of the first part;
  • the second series of tubes without turbulators of the second part comprises an upper group of tubes and a lower group of tubes and in that the first series of tubes with turbulators of the second part is arranged vertically between the upper and lower groups of tubes. the second series of tubes without turbulators of the second part;
  • the exchanger comprises at least one flow passage of the flow (Fe) coolant between at least a portion of the tubes of the first and second series with turbulators and / or first and second series without turbulators;
  • the tubes of the first series and the second series of each of the parts have, according to a sectional plane vertical, a longitudinal parallelepipedal section, in particular rectangular;
  • the first manifold and the second manifold constitute respectively an inlet air box and an outlet air box of the interior air stream to be cooled;
  • the cooling fluid of the internal air flow is constituted by an external air flow, such as an air flow resulting from the dynamic pressure of the air caused by the displacement of the vehicle and / or by a group motorcycle fan;
  • the exchanger has a generally oblong transverse shape so as to allow in particular its implantation above or below the engine cooling radiator;
  • the exchanger is generally of parallelepipedal shape / rectangle.
  • FIG. 1 is a partial side view of the front part of a vehicle in which is shown schematically the implementation of the internal combustion engine, the cooling radiator and the heat exchanger according to the teachings of the invention;
  • FIG. 2 is a front view of the heat exchanger according to the invention arranged below the engine cooling radiator;
  • FIG. 3 is a view from above of the heat exchanger according to the invention
  • FIG. 4 is a cross-sectional and vertical sectional view of the heat exchanger according to the corresponding plane IV-IV shown in FIG. 3, which illustrates an exemplary embodiment of an exchanger comprising a first and second part; respectively equipped with series of tubes with and without turbulators;
  • 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 circuit and a turbo-compressor (not shown) which comprises a compressor for pressurizing fresh atmospheric air and a turbine to provide the atmosphere. mechanical energy required 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 that is engine speed function 12.
  • the intake circuit therefore comprises a cooling device, also known as a cooler, which generally consists, as explained above, in a heat exchanger 14 through which a cooling coolant passes so as to cool the internal air flow Fi of supercharging of 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. It will be noted that the dimensions of the heat exchanger
  • the heat exchanger 14 comprises a first collector
  • 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.
  • such 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 heat exchanger 14 is characterized in that the bundle 20 of tubes comprises at least:
  • the first part P1 comprising a first series S1 P1 of tubes provided with turbulators 34 having a total section or passage area A1 1 and a second series S2P1 of tubes without turbulators having a total section or passage area A12 generally equivalent to the section of passage A1 1,
  • a second part P2 comprising a first series S1 P2 of tubes without turbulators having a total section or passage area A21 and a second series S2P2 of tubes provided with turbulators 34 having a total section or passage area A22 generally equivalent to the total section; passage A21, and the central intermediate distribution box 24 of the internal air flow to be cooled, comprising means for connecting the output of the first series S1 P1 of tubes with turbulators of the first part P1 with the input of the first series S1 P2 of tubes without turbulators of the second part P2 and connection of 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 with turbulators 34 of the second part P2.
  • the first series S1 P1 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 S1 P1 of tubes with turbulators 34 of the first part P1.
  • the second series S2P2 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 first series S1 P2 of tubes with turbulators 34 of the second part P2 is arranged vertically between the upper and lower groups 32 of tubes of the second series S2P2 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 S1 P2 without turbulators of the second part P2 comprises an upper tube 30 and a tube lower 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 comprises circulation passages 38 for the external cooling air flow Fe, preferably between each of the tubes of the first series S1 P1 and the second series S2P1 so as to optimize the heat exchanges between the flow Indoor Fi and the outside 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 outlet of the first series S1 P1 of tubes provided with turbulators 34 of the first part P1 with the inlet of the first series S1 P2 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 upper transverse plate 42 and an inclined lower transverse plate 44 which vertically delimit between them a divergent inner section. 46 connecting the output of the central tube 36 without turbulators of the first portion P1 and the inputs of each of the tubes of the second series of tubes S2P2 comprising turbulators 34.
  • the upper plate 42 defines vertically with the upper horizontal wall 48 of the body 50 of the housing 24 an upper convergent section 52 connecting the outputs of each tube of the upper group 26 of the first series of tubes S1 P1 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 outputs of each tube of the lower group 28 of the first series of tubes S1 P1 comprising turbulators 34 and 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 inlet orifice OE1 which it emerges through the orifice OS1 to first pass through the first portion P1 of the heat exchanger 14.
  • the internal air flow Fi is distributed to circulate respectively in the first series S1 P1 of tubes with turbulators total passage section A1 1 and the second S2P1 series 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 A1 1 and A12 respectively of the first series S1 P1 and the second series S2P1 so that the internal air flow Fi is divided in two parts Fi 1 and Fi 2 and is distributed here also between the first series S1 P1 and the second series S2P1.
  • the part Fi 1 of the internal air flow Fi is cooled during its passage through the first series S1 P1 of tubes whose turbulators 34 make it possible to increase the heat dissipation by the outside air flow Fe of cooling circulating in passages 38.
  • the internal air flow Fi undergoes a first pressure drop which is essentially caused by the first series S1 P1 of turbulent tubes.
  • the internal air flow Fi to be cooled corresponding respectively to the parts Fi 1 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 of the second part P2 to be cooled in turn.
  • the second portion P2 of the heat exchanger 14 comprises, as the first portion P1, circulation passages 38 of the external air flow Fe cooling between each of the tubes of the first series S 1 P2 and the second series S2P2 so as 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 S1 P2 and S2P2 of tubes opens in at minus one inlet port OE2 of the second manifold 18, forming the outlet air box, then continues its course in a downstream element of the duct of the engine intake circuit 12 which is connected at least one outlet port OS2 of the second collector 18.
  • the first series of tubes S1 P1 and S1 P2 have a total passage section A1 1 and A21 which are respectively substantially equivalent to the total passage sections A12 and A22 of the first and second series of S2P1 and S2P2 tubes.
  • the tubes of the first series S 1 P1 and S 1 P2 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 S 1 P1 and S1 P2 and 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 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 (I) .
  • each part of the flow Fi through a series of tubes provided with turbulators 34 actually runs between the inlet port OE 1 and the OE2 outlet orifice that half of this length, so "L / 2", is in the first part P1 or in the second part P2 which provides 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.
  • 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.
  • the concepts of "input” and “output” are relative and therefore are not limiting the possible embodiments, in particular depending on the applications.
  • 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)

Abstract

A heat exchanger including at least a first manifold and a second manifold connected by a bundle of horizontal tubes. An air flow circulates to be cooled by a cooling air flow. The bundle includes at least: a first portion including a first series of tubes with turbulators of passage section corresponding to the section; a second portion including a first series of tubes with no turbulators of passage section and a second series of tubes with turbulators of passage section corresponding to the section; and a distribution box of internal air flow to be cooled including a connection mechanism between the first portion and the second portion.

Description

"Echangeur thermique à faisceau tubulaire, notamment pour un moteur à combustion interne suralimenté" "Tube bundle heat exchanger, in particular for a supercharged internal combustion engine"
L'invention concerne un echangeur thermique à faisceau tubulaire, notamment destiné à refroidir l'air de suralimentation dans un moteur à combustion interne suralimenté de véhicule automobile.The invention relates to a heat exchanger with tubular bundle, in particular for cooling the supercharging air in a supercharged internal combustion engine of a motor vehicle.
L'invention concerne plus particulièrement un echangeur thermique, notamment du type air-air, pour un moteur à combustion interne suralimenté, du type comportant au moins un premier collecteur et un second collecteur qui sont reliés transversalement par un faisceau de tubes horizontaux dans lesquels circule un flux intérieur d'air à refroidir par un flux de fluide de refroidissement circulant à l'extérieur du faisceau de tubes. Dans les moteurs à combustion interne suralimentés, il est connu d'utiliser des dispositifs de refroidissement ou "refroid isseurs", tels qu'un echangeur thermique ou de chaleur, pour refroidir l'air de suralimentation afin de réduire la charge thermique du moteur, la température des gaz d'échappement, et par conséquent les émissions de NOx et la consommation de carburant.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. In supercharged internal combustion engines, it is known to use cooling devices or "coolers", such as a heat exchanger or heat exchanger, to cool the charge air to reduce the thermal load of the engine, the temperature of the exhaust gases, and therefore NOx emissions and fuel consumption.
L'air de suralimentation peut essentiellement être refroidi de deux façons, à savoir soit par le liquide de refroid issement du moteur, soit par l'air ambiant extérieur. Dans le cas du refroidissement par eau, la position de montage du refroidisseur - typiquement un echangeur d u type air-eau - peut être choisie librement, ce qui est très avantageux vu l'extrême compacité des refroidisseurs refroidis par eau. Néanmoins, il n'est pas possible d'abaisser la température de l'air de suralimentation à la valeur souhaitée qui est en général en dessous de celle du liquide de refroidissement.The charge air can essentially be cooled in two ways, either by the engine coolant or by the ambient air outside. In the case of water cooling, the mounting position of the cooler - typically an air-water type exchanger - can be chosen freely, which is very advantageous in view of the extreme compactness of the water-cooled chillers. 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.
C'est la raison pour laquelle, les véhicules automobiles comportant des moteurs à combustion interne suralimentés ou turbocompressés sont presque exclusivement équipés de refroidisseurs d'air de suralimentation refroidis par air, généralement au moins un échangeur thermique du type air-air.This is the reason why motor vehicles with supercharged or turbocharged internal combustion engines are almost exclusively equipped with air-cooled charge air coolers, generally at least one air-to-air type heat exchanger.
Le document US-A-4.702.079 décrit un exemple d'échangeur thermique du type air-air qui, comme on peut notamment le voir sur la figure 2 de ce document, est le plus souvent monté à l'avant du véhicule de manière à être ventilé par la pression dynamique de l'air extérieur lorsque le véhicule se déplace.Document US-A-4,702,079 describes an example of an air-to-air type heat exchanger which, as can be seen in particular in FIG. 2 of this document, is most often mounted at the front of the vehicle in such a way that to be ventilated by the dynamic pressure of the outside air when the vehicle is moving.
Bien entendu, l'échangeur air-air peut aussi être placé à un autre endroit du compartiment moteur du véhicule, mais il doit alors être ventilé au moyen d'une soufflante séparée, telle qu'un groupe moto-ventilateur. Une telle solution est donc rarement mise en œuvre pour des raisons de coûts, de poids et d'encombrement. Dans le cas d'une implantation de l'échangeur à l'avant du véhicule, il est aussi nécessaire de prendre en considération d'autres contraintes, plus particulièrement des contraintes relatives à la sécurité telles que le respect des normes relatives au choc avec un piéton. Ainsi, l'échangeur air-air est généralement placé devant le radiateur d'eau avec l'avantage de toujours avoir un refroidissement suffisant à petite vitesse du fait de la présence du ventilateur du radiateur d'eau.Of course, 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. Such a solution is therefore rarely implemented for reasons of cost, weight and size. In the case of an implantation of the exchanger at the front of the vehicle, it is also necessary to take into consideration other constraints, more particularly safety constraints such as compliance with the standards relating to impact with a vehicle. pedestrian. Thus, 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.
Cependant, une telle implantation présente en contrepartie le risque d'entraver la circulation et l'arrivée de l'air extérieur de refroid issement, et l'inconvénient de "préchauffer" l'air de refroidissement, et donc de devoir surdimensionner le radiateur d'eau.However, such an implementation has the counterpart the risk of impeding the circulation and the arrival of external air cooling, and the disadvantage of "preheating" the cooling air, and therefore having to oversize the radiator d 'water.
Afin de remédier à ces inconvénients, on recherche notamment des solutions permettant d'implanter les échangeurs (ou refroidisseurs) d'air de suralimentation au dessus ou au dessous du rad iateur d'eau.In order to overcome these drawbacks, solutions are particularly sought to implement supercharging air exchangers (or coolers) above or below the water radiator.
Néanmoins, une telle implantation nécessite d'utiliser, en particulier pour des raisons d'encombrement, un échangeur thermique présentant des dimensions en longueur, en largeur et en hauteur appropriées, c'est-à-dire un échangeur globalement en forme de "barre" dont le faisceau de tubes soit de grande longueur par comparaison à ses largeur et hauteur respectives. Dans un échangeur thermique, plus la longueur des tubes du faisceau parcourus par le flux d'air de suralimentation est importante pour un même nombre de tubes, plus la perte de charge augmente.However, such an implementation requires the use, particularly for reasons of space, an exchanger thermal having length dimensions, width and height appropriate, that is to say a generally "bar" -shaped exchanger whose tube bundle is of great length compared to its respective width and height. In a heat exchanger, the greater the length of the tubes of the bundle traversed by the supercharging air flow is important for the same number of tubes, the greater the pressure loss increases.
De plus, les tubes du faisceau comportent généralement des moyens tels que des "turbulateurs" ainsi appelés parce qu'ils provoquent un écoulement de l'air à refroidir de type turbulent ou non laminaire et cela afin d'accroître les échanges thermiques entre l'air à refroidir et le fluide de refroidissement.In addition, the 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.
Ainsi, l'importance des pertes de charge dans de tels échangeurs a jusqu'à présent compromis leur utilisation dans des applications de refroidissement de l'air de suralimentation d'un moteur à combustion interne.Thus, the importance of the pressure drop in such exchangers has so far compromised their use in charge air cooling applications of an internal combustion engine.
Pour remédier à ces inconvénients, l'invention propose un échangeur thermique, notamment du type air-air, dont la perte de charge interne est particulièrement réduite.To overcome these drawbacks, the invention proposes a heat exchanger, in particular of the air-air type, whose internal pressure drop is particularly reduced.
Dans ce but, l'invention propose un échangeur thermique du type décrit précédemment, caractérisé en ce que le faisceau de tubes comporte au moins :For this purpose, the invention proposes a heat exchanger of the type described above, characterized in that the bundle of tubes comprises at least:
- une première partie comportant une première série de tubes avec turbulateurs présentant une section totale de passage et une deuxième série de tubes sans turbulateurs présentant une section totale de passage globalement équivalente à la section totale de passage,a first part comprising a first series of tubes with turbulators having a total passage section and a second series of tubes without turbulators having a total passage section generally equivalent to the total passage section,
- une seconde partie comportant une première série de tubes sans turbulateurs présentant une section totale de passage et une deuxième série de tubes avec turbulateurs présentant une section totale de passage globalement équivalente à la section totale de passage, - et une boîte de répartition du flux intérieur d'air à refroidir comportant des moyens de raccordement de la sortie de la première série de tubes avec turbulateurs de la première partie avec l'entrée de la première série de tubes sans turbulateurs de la seconde partie et de raccordement de la sortie de la deuxième série de tubes sans turbulateurs de la première partie avec l'entrée de la deuxième série de tubes avec turbulateurs de la seconde partie.- a second part comprising a first series of tubes without turbulators having a total passage section and a second series of tubes with turbulators having a total passage section generally equivalent to the total passage section, and a distribution box of the internal air flow to be cooled comprising means for connecting the outlet of the first series of tubes with turbulators of the first part with the inlet of the first series of tubes without turbulators of the second part. and connecting the output of the second series of tubes without turbulators of the first part with the inlet of the second series of tubes with turbulators of the second part.
Avantageusement, l'échangeur thermique selon l'invention présente, à capacité de refroidissement et à perte de charge équivalentes par rapport aux échangeurs de l'état de la technique, un encombrement réduit permettant notamment de l'implanter en dessous du radiateur d'eau du moteur.Advantageously, 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.
Selon d'autres caractéristiques de l'invention : - la première série de tubes avec turbulateurs de la première partie comporte un groupe supérieur de tubes et un groupe inférieur de tubes et en ce que la deuxième série de tubes sans turbulateurs de la première partie est agencée verticalement entre les groupes supérieur et inférieur de tubes de la première série de tubes avec turbulateurs de la première partie ;According to other characteristics of the invention: the first series of tubes with turbulators of the first part comprises an upper group of tubes and a lower group of tubes and in that the second series of tubes without turbulators of the first part is arranged vertically between the upper and lower groups of tubes of the first series of tubes with turbulators of the first part;
- la deuxième série de tubes sans turbulateurs de la seconde partie comporte un groupe supérieur de tubes et un groupe inférieur de tubes et en ce que la première série de tubes avec turbulateurs de la seconde partie est agencée verticalement entre les groupes supérieur et inférieur de tubes de la deuxième série de tubes sans turbulateurs de la seconde partie ;the second series of tubes without turbulators of the second part comprises an upper group of tubes and a lower group of tubes and in that the first series of tubes with turbulators of the second part is arranged vertically between the upper and lower groups of tubes. the second series of tubes without turbulators of the second part;
- l'échangeur comporte au moins un passage de circulation du flux (Fe) de fluide de refroidissement entre au moins une partie des tubes des première et deuxième séries avec turbulateurs et/ou des première et deuxième séries sans turbulateurs ;- The exchanger comprises at least one flow passage of the flow (Fe) coolant between at least a portion of the tubes of the first and second series with turbulators and / or first and second series without turbulators;
- les tubes des premières séries et des deuxièmes séries de chacune des parties présentent, suivant un plan de coupe vertical, une section longitudinale parallélépipédique, notamment rectangulaire ;the tubes of the first series and the second series of each of the parts have, according to a sectional plane vertical, a longitudinal parallelepipedal section, in particular rectangular;
- le premier collecteur et le second collecteur constituent respectivement une boîte à air d'entrée et une boîte à air de sortie du flux d'air intérieur à refroidir ;the first manifold and the second manifold constitute respectively an inlet air box and an outlet air box of the interior air stream to be cooled;
- le fluide de refroidissement du flux intérieur d'air est constitué par un flux extérieur d'air, tel qu'un flux d'air résultant de la pression dynamique de l'air provoqué par le déplacement du véhicule et/ou par un groupe moto-ventilateur ; - l'échangeur présente transversalement une forme générale oblongue de manière à permettre notamment son implantation au dessus ou en dessous du radiateur de refroidissement du moteur ; l'échangeur est globalement de forme parallélépipédique/rectangle.the cooling fluid of the internal air flow is constituted by an external air flow, such as an air flow resulting from the dynamic pressure of the air caused by the displacement of the vehicle and / or by a group motorcycle fan; the exchanger has a generally oblong transverse shape so as to allow in particular its implantation above or below the engine cooling radiator; the exchanger is generally of parallelepipedal shape / rectangle.
D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la description détaillée qui suit pour la compréhension de laquelle on se reportera aux figures annexées parmi lesquelles : - la figure 1 est une vue partielle de côté de la partie avant d'un véhicule dans laquelle on a représenté schématiquement l'implantation du moteur à combustion interne, du radiateur de refroidissement et de l'échangeur thermique conforme aux enseignements de l'invention ; - la figure 2 est une vue de face de l'échangeur thermique selon l'invention agencé en dessous du radiateur de refroidissement du moteur ;Other features and advantages of the invention will appear on reading the detailed description which follows for the understanding of which reference will be made to the appended figures among which: - Figure 1 is a partial side view of the front part of a vehicle in which is shown schematically the implementation of the internal combustion engine, the cooling radiator and the heat exchanger according to the teachings of the invention; - Figure 2 is a front view of the heat exchanger according to the invention arranged below the engine cooling radiator;
- la figure 3 est une vue de dessus de l'échangeur thermique selon l'invention ; - la figure 4 est une vue en coupe transversale et verticale de l'échangeur thermique selon le plan IV-IV correspondant ind iqué à la figure 3, qui illustre un exemple de réalisation d'un échangeur comportant une première et seconde partie respectivement munis de séries de tubes avec et sans turbulateurs ;FIG. 3 is a view from above of the heat exchanger according to the invention; FIG. 4 is a cross-sectional and vertical sectional view of the heat exchanger according to the corresponding plane IV-IV shown in FIG. 3, which illustrates an exemplary embodiment of an exchanger comprising a first and second part; respectively equipped with series of tubes with and without turbulators;
- les figures 5 à 7 sont respectivement des vues en coupe longitudinale et verticale de la première partie, de la boîte de répartition et de la seconde partie selon les plans de coupe verticaux V-V à VI I-VII correspondants indiqués sur la figure 3.- Figures 5 to 7 are respectively longitudinal and vertical sectional views of the first part, the distribution box and the second part according to the vertical sectional planes V-V to VI I-VII corresponding indicated in Figure 3.
Par convention, on utilisera à titre non limitatif dans la description et les revendications les termes "premier" ou "second/deuxième", "inférieur" ou "supérieur" et les directions "longitudinale", "transversale" ou "verticale" pour désigner respectivement des éléments ou des positions selon les définitions données dans la description et selon le trièdre (L, V, T) représenté sur les figures.By convention, the terms "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.
On a représenté schématiquement à la figure 1 , la partie avant d'un véhicule automobile 10 comportant un groupe motopropulseur à moteur à combustion interne 12, qui est ici du type suralimenté.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.
De manière connue, un tel moteur suralimenté 12 comporte un circuit d'admission, un circuit d'échappement et un turbo- compresseur (non représentés) qui comprend un compresseur pour mettre sous pression de l'air frais atmosphérique et une turbine pour fournir l'énergie mécanique nécessaire à l'entraînement du compresseur.In a known manner, such a supercharged engine 12 comprises an intake circuit, an exhaust circuit and a turbo-compressor (not shown) which comprises a compressor for pressurizing fresh atmospheric air and a turbine to provide the atmosphere. mechanical energy required to drive the compressor.
On rappellera succinctement que, lors du fonctionnement du moteur 12, l'air frais provenant de l'atmosphère est admis dans un partie d'entrée du circuit d'admission, après avoir traversé le filtre à air destiné à retenir les particules présentes dans l'air frais et qu'il est alors aspiré, puis comprimé par le compresseur.It will be briefly recalled that, during the operation of the engine 12, the fresh air from the atmosphere is admitted into an inlet portion of the intake circuit, after passing through the air filter for retaining the particles present in the air. fresh air and that it is then sucked, then compressed by the compressor.
La compression de l'air provoque son échauffement de sorte qu'il est nécessaire que l'air frais comprimé, dit de suralimentation, soit ensuite refroidi avant de parvenir au collecteur d'admission et d'alimenter cycliquement les cylindres selon une fréquence qui est fonction du régime du moteur 12. Le circuit d'admission comporte par conséquent un dispositif de refroid issement, encore appelé refroidisseur, lequel consiste généralement comme expliqué précédemment en un échangeur thermique 14 que traverse un fluide caloporteur de refroidissement de manière à refroidir le flux intérieur d'air Fi de suralimentation venant du compresseur.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 that is engine speed function 12. The intake circuit therefore comprises a cooling device, also known as a cooler, which generally consists, as explained above, in a heat exchanger 14 through which a cooling coolant passes so as to cool the internal air flow Fi of supercharging of the compressor.
Après la combustion, les gaz d'échappement sous pression sont rejetés, par l'intermédiaire d'un collecteur d'échappement (non représenté), dans une conduite d'échappement (non représentée) qui alimente sélectivement la turbine du turbocompresseur avant que ces gaz ne soient rejetés dans l'atmosphère.After combustion, 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.
Dans l'exemple de réalisation illustré aux figures, l'échangeur thermique 14 est un échangeur du type air-air de sorte que le fluide de refroidissement est constitué par un flux extérieur d'air Fe.In the embodiment illustrated in the figures, the heat exchanger 14 is an air-air type exchanger so that the cooling fluid is constituted by an external air flow Fe.
Comme on peut le voir sur la figure 1 , le flux extérieur d'air Fe correspond notamment au flux d'air résultant de la pression dynamique de l'air provoqué par le déplacement du véhicule. Le flux extérieur d'air Fe est ici représenté schématiquement par des flèches à hampe ondulée de manière à les distinguer des autres flèches que comportent les figures, notamment des flèches à hampe rectiligne représentant schématiquement le flux intérieur d'air Fi. On notera que les dimensions de l'échangeur thermiqueAs can be seen in Figure 1, 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. It will be noted that the dimensions of the heat exchanger
14, c'est à dire sa largeur ou profondeur (I), sa hauteur (h) et sa longueur (L), correspondent ici respectivement à ses dimensions selon les directions longitudinale, verticale et transversale du trièdre (L, V, T). L'échangeur thermique 14 comporte un premier collecteur14, that is to say its width or depth (I), its height (h) and its length (L), respectively correspond to its dimensions in the longitudinal, vertical and transverse directions of the trihedron (L, V, T) . The heat exchanger 14 comprises a first collector
16 et un second collecteur 18 qui sont reliés transversalement par un faisceau 20 de tubes dans lesquels circule un flux intérieur d'air Fi à refroidir par le flux extérieur d'air Fe de refroidissement circulant à l'extérieur du faisceau 20 de tubes. Comme on peut le voir sur la figure 3, le premier collecteur 16 et le second collecteur 18 constituent ici respectivement une boîte à air d'entrée et une boîte à air de sortie du flux d'air intérieur Fi à refroidir. Avantageusement, les boîtes à air d'entrée et de sortie sont identiques ce qui permet notamment d'en réduire le coût de production.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 outside flow of cooling air Fe circulating outside the bundle 20 of tubes. As can be seen in FIG. 3, 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. Advantageously, the inlet and outlet air boxes are identical, which makes it possible in particular to reduce the cost of production.
Le flux intérieur d'air Fi circule de gauche à droite suivant les flèches illustrées sur les figures 2 et 3, c'est à dire suivant la direction transversale (T).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).
Le flux extérieur d'air Fe de refroidissement circule, comme l'illustrent les flèches sur les figures 1 et 3, suivant la direction longitudinale (L), c'est à dire orthogonalement à la direction transversale (T). Le faisceau 20 de tubes comporte principalement une première partie P1 , une seconde partie P2 et une boîte intermédiaire de répartition 24 interposée transversalement, ici centralement, entre les première et seconde parties P1 , P2.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.
L'échangeur thermique 14 a sensiblement une forme de "barre", c'est-à-dire qu'il présente transversalement une forme générale oblongue, ici globalement parallélépipédique-rectangle.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.
Avantageusement, un tel échangeur thermique 14 est donc susceptible d'être implanté en dessous du radiateur de refroidissement 22 du circuit de refroidissement du moteur 12, comme cela est illustré sur les figures 1 et 2.Advantageously, such 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.
En variante, l'échangeur thermique 14 est implanté au dessus du radiateur de refroidissement 22 du circuit de refroidissement du moteur 12.Alternatively, the heat exchanger 14 is located above the cooling radiator 22 of the engine cooling circuit 12.
Une telle implantation est désormais rendue possible avec un échangeur thermique 14 réalisé conformément à l'invention qui permet notamment de réduire la perte de charge interne par comparaison aux échangeurs de forme oblongue selon l'état de la technique. L'échangeur thermique 14 selon l'invention est caractérisé par le fait que le faisceau 20 de tubes comporte au moins :Such an implantation is now made possible with a heat exchanger 14 made in accordance with the invention which in particular makes it possible to reduce the internal pressure drop as compared with the oblong-shaped heat exchangers according to the state of the art. The heat exchanger 14 according to the invention is characterized in that the bundle 20 of tubes comprises at least:
- la première partie P1 comportant une première série S1 P1 de tubes munis de turbulateurs 34 présentant une section totale ou aire de passage A1 1 et une deuxième série S2P1 de tubes sans turbulateurs présentant une section totale ou aire de passage A12 globalement équivalente à la section de passage A1 1 ,the first part P1 comprising a first series S1 P1 of tubes provided with turbulators 34 having a total section or passage area A1 1 and a second series S2P1 of tubes without turbulators having a total section or passage area A12 generally equivalent to the section of passage A1 1,
- une seconde partie P2 comportant une première série S1 P2 de tubes sans turbulateurs présentant une section totale ou aire de passage A21 et une deuxième série S2P2 de tubes munis de turbulateurs 34 présentant une section totale ou aire de passage A22 globalement équivalente à la section totale de passage A21 , - et la boîte intermédiaire centrale de répartition 24 du flux intérieur d'air à refroidir comportant des moyens pour raccorder la sortie de la première série S1 P1 de tubes avec turbulateurs de la première partie P1 avec l'entrée de la première série S1 P2 de tubes sans turbulateurs de la seconde partie P2 et de raccordement de la sortie de la deuxième série S2P1 de tubes sans turbulateurs de la première partie P1 avec l'entrée de la deuxième série S2P2 de tubes avec turbulateurs 34 de la seconde partie P2.a second part P2 comprising a first series S1 P2 of tubes without turbulators having a total section or passage area A21 and a second series S2P2 of tubes provided with turbulators 34 having a total section or passage area A22 generally equivalent to the total section; passage A21, and the central intermediate distribution box 24 of the internal air flow to be cooled, comprising means for connecting the output of the first series S1 P1 of tubes with turbulators of the first part P1 with the input of the first series S1 P2 of tubes without turbulators of the second part P2 and connection of 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 with turbulators 34 of the second part P2.
Selon l'exemple de réalisation de l'échangeur thermique 14 illustré à la figure 4, la première série S1 P1 de tubes avec turbulateurs 34 de la première partie P1 de l'échangeur thermique 14 comporte un groupe supérieur 26 de tubes et un groupe inférieur 28 de tubes, et la deuxième série S2P1 de tubes sans turbulateurs de la première partie P1 est agencée verticalement entre les groupes supérieur 26 et inférieur 28 de tubes de la première série S1 P1 de tubes avec turbulateurs 34 de la première partie P1 .According to the embodiment of the heat exchanger 14 illustrated in FIG. 4, the first series S1 P1 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, and 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 S1 P1 of tubes with turbulators 34 of the first part P1.
De même, la deuxième série S2P2 de tubes sans turbulateurs de la seconde partie P2 de l'échangeur thermique 14 comporte un groupe supérieur 30 de tubes et un groupe inférieur 32 de tubes et la première série S1 P2 de tubes avec turbulateurs 34 de la seconde partie P2 est agencée verticalement entre les groupes supérieur 30 et inférieur 32 de tubes de la deuxième série S2P2 de tubes sans turbulateurs de la seconde partie P2.Similarly, the second series S2P2 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 first series S1 P2 of tubes with turbulators 34 of the second part P2 is arranged vertically between the upper and lower groups 32 of tubes of the second series S2P2 of tubes without turbulators of the second part P2.
Dans l'exemple de réalisation illustré à la figure 4, la deuxième série S2P1 sans turbulateurs de la première partie P1 comporte un seul tube 36 central et la première série S1 P2 sans turbulateurs de la seconde partie P2 comporte un tube supérieur 30 et un tube inférieur 32 formant ici respectivement les groupes supérieur et inférieur.In the embodiment illustrated in FIG. 4, the second series S2P1 without turbulators of the first part P1 comprises a single central tube 36 and the first series S1 P2 without turbulators of the second part P2 comprises an upper tube 30 and a tube lower 32 forming here respectively the upper and lower groups.
Les tubes comportant des turbulateurs 34 ont été représentés sur la figure 4 en "grisé" ou "tramé" afin de les différencier et sont par ailleurs mieux visibles sur les coupes des figures 5 et 7.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.
L'échangeur thermique 14 comporte des passages 38 de circulation pour le flux extérieur d'air Fe de refroidissement, de préférence entre chacun des tubes de la première série S1 P1 et de la deuxième série S2P1 de manière à optimiser les échanges thermiques entre le flux intérieur Fi et le flux extérieur d'air Fe.The heat exchanger 14 comprises circulation passages 38 for the external cooling air flow Fe, preferably between each of the tubes of the first series S1 P1 and the second series S2P1 so as to optimize the heat exchanges between the flow Indoor Fi and the outside air flow Fe.
Les passages 38 sont notamment visibles sur la vue de face de la figure 2 et sur la vue en coupe de la figure 4.The passages 38 are in particular visible in the front view of FIG. 2 and in the sectional view of FIG. 4.
La boîte intermédiaire de répartition 24 comporte des moyens de raccordement 40 de la sortie de la première série S1 P1 de tubes munis de turbulateurs 34 de la première partie P1 avec l'entrée de la première série S1 P2 de tubes sans turbulateurs de la seconde partie P2 et de raccordement de la sortie de la deuxième série S2P1 de tubes sans turbulateurs de la première partie P1 avec l'entrée de la deuxième série S2P2 de tubes munis de turbulateurs 34 de la seconde partie P2.The intermediate distribution box 24 comprises connection means 40 of the outlet of the first series S1 P1 of tubes provided with turbulators 34 of the first part P1 with the inlet of the first series S1 P2 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.
Les moyens de raccordement 40 de la boîte de répartition 24 sont constitués par une plaque transversale supérieure inclinée 42 et une plaque transversale inférieure inclinée 44 qui délimitent verticalement entre elles un tronçon intérieur divergent 46 de raccordement entre la sortie du tube central 36 sans turbulateurs de la première partie P1 et les entrées de chacun des tubes de la deuxième série de tubes S2P2 comportant des turbulateurs 34. La plaque supérieure 42 délimite verticalement avec la paroi horizontale supérieure 48 du corps 50 du boîtier 24 un tronçon convergent supérieur 52 de raccordement entre les sorties de chaque tube du groupe supérieur 26 de la première série de tubes S1 P1 comportant des turbulateurs 34 et l'entrée du tube supérieur 30.The connection means 40 of the distribution box 24 are constituted by an inclined upper transverse plate 42 and an inclined lower transverse plate 44 which vertically delimit between them a divergent inner section. 46 connecting the output of the central tube 36 without turbulators of the first portion P1 and the inputs of each of the tubes of the second series of tubes S2P2 comprising turbulators 34. The upper plate 42 defines vertically with the upper horizontal wall 48 of the body 50 of the housing 24 an upper convergent section 52 connecting the outputs of each tube of the upper group 26 of the first series of tubes S1 P1 comprising turbulators 34 and the inlet of the upper tube 30.
La plaque inférieure 44 délimite verticalement avec la paroi horizontale inférieure 54 du corps 50 du boîtier 24 un tronçon convergent inférieur 56 de raccordement entre les sorties de chaque tube du groupe inférieur 28 de la première série de tubes S1 P1 comportant des turbulateurs 34 et l'entrée du tube inférieur 32.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 outputs of each tube of the lower group 28 of the first series of tubes S1 P1 comprising turbulators 34 and inlet of the lower tube 32.
Comme illustré sur la figure 6, les tronçons de raccordement 46, 52 et 56 sont aussi délimités longitudinalement par les parois transversales opposées 58 du corps 50 du boîtier 24.As illustrated in FIG. 6, the connection sections 46, 52 and 56 are also delimited longitudinally by the opposite transverse walls 58 of the body 50 of the housing 24.
On décrira ci-après le fonctionnement de l'échangeur thermique 14 selon l'invention et le refroidissement du flux intérieur d'air Fi par le flux extérieur d'air Fe.Hereinafter will be described the operation of the heat exchanger 14 according to the invention and the cooling of the internal air flow Fi by the external air flow Fe.
Le premier collecteur 16 formant la boîte à air d'entrée comporte un orifice d'entrée OE1 qui est raccordé à un élément amont du conduit d'admission du circuit d'admission du moteur 12 et un orifice de sortie OS1 qui débouche dans le faisceau 20.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.
Ainsi, le flux intérieur d'air Fi à refroidir provenant du compresseur pénètre dans le premier collecteur 16 par l'orifice d'entrée OE1 dont il ressort par l'orifice OS1 pour traverser d'abord la première partie P1 de l'échangeur thermique 14.Thus, the internal air flow Fi to be cooled from the compressor enters the first manifold 16 through the inlet orifice OE1 which it emerges through the orifice OS1 to first pass through the first portion P1 of the heat exchanger 14.
Le flux intérieur d'air Fi se repartit pour circuler respectivement dans la première série S1 P1 de tubes avec turbulateurs de section totale de passage A1 1 et la deuxième série S2P1 de tubes sans turbulateurs de section totale de passage A12.The internal air flow Fi is distributed to circulate respectively in the first series S1 P1 of tubes with turbulators total passage section A1 1 and the second S2P1 series of tubes without turbulators of total passage section A12.
La section globale A1 de passage de la première partie P1 correspond globalement à la somme des sections totales de passage A1 1 et A12 respectivement de la première série S1 P1 et de la deuxième série S2P1 de sorte que le flux intérieur d'air Fi se divise en deux parties Fi 1 et Fi 2 et se répartit ici également entre la première série S1 P1 et de la deuxième série S2P1 .The overall passage A1 section of the first portion P1 corresponds globally to the sum of the total passage sections A1 1 and A12 respectively of the first series S1 P1 and the second series S2P1 so that the internal air flow Fi is divided in two parts Fi 1 and Fi 2 and is distributed here also between the first series S1 P1 and the second series S2P1.
La partie Fi 1 du flux intérieur d'air Fi est refroidi lors de son passage à travers la première série S1 P1 de tubes dont les turbulateurs 34 permettent d'augmenter la dissipation de chaleur par le flux extérieur d'air Fe de refroidissement circulant dans les passages 38.The part Fi 1 of the internal air flow Fi is cooled during its passage through the first series S1 P1 of tubes whose turbulators 34 make it possible to increase the heat dissipation by the outside air flow Fe of cooling circulating in passages 38.
L'autre partie Fi2 du flux intérieur d'air Fi traversant la deuxième série S2P1 de tubes sans turbulateurs n'est que peu refroidie mais ne subit, à contrario, que peu ou pas de perte de charges.The other part Fi2 of the internal air flow Fi through the second series S2P1 of tubes without turbulators is only slightly cooled but undergoes, conversely, little or no loss of charge.
Ainsi, lors de son passage à travers la première partie P1 , le flux intérieur d'air Fi subit une première perte de charge qui est essentiellement provoquée par la première série S1 P1 de tubes turbulés.Thus, during its passage through the first part P1, the internal air flow Fi undergoes a first pressure drop which is essentially caused by the first series S1 P1 of turbulent tubes.
Après avoir traversé la première partie P1 , le flux intérieur d'air Fi à refroidir correspondant respectivement aux parties Fi 1 et Fi2 traverse ensuite la boîte de répartition 24 avant de traverser la seconde partie P2 de l'échangeur thermique 14.After passing through the first part P1, the internal air flow Fi to be cooled corresponding respectively to the parts Fi 1 and Fi2 then passes through the distribution box 24 before passing through the second portion P2 of the heat exchanger 14.
Ainsi, la partie Fi 1 du flux intérieur d'air Fi ayant traversé la première série de tubes avec turbulateurs S1 P1 de la première partie P1 pour y être refroidi, traverse donc ensuite, dans la seconde partie P2, la première série de tubes sans turbulateurs S1 P2 en ne subissant que peu ou pas de perte de charges.Thus, the part Fi 1 of the internal air flow Fi having passed through the first series of tubes with turbulators S1 P1 of the first part P1 to be cooled, then passes through, in the second part P2, the first series of tubes without turbulators S1 P2 undergoing little or no loss of charge.
Réciproquement, l'autre partie Fi2 du flux intérieur d'air Fi ayant traversé la deuxième série S2P1 de tubes sans turbulateurs de la première partie P1 avec peu ou pas de perte de charges, traverse ensuite la deuxième série S2P2 de tubes avec turbulateurs 34 de la seconde partie P2 afin d'y être à son tour refroidi.Conversely, 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 of the second part P2 to be cooled in turn.
Avantageusement, la seconde partie P2 de l'échangeur thermique 14 comporte, comme la première partie P1 , des passages de circulation 38 du flux extérieur d'air Fe de refroidissement entre chacun des tubes de la première série S 1 P2 et de la deuxième série S2P2 de manière à optimiser les échanges thermiques entre le flux intérieur Fi et le flux extérieur d'air Fe. Le flux intérieur d'air Fi issue des sorties respectives de la première et de la deuxième séries S1 P2 et S2P2 de tubes débouche dans au moins un orifice d'entrée OE2 du second collecteur 18, formant la boîte à air de sortie, puis poursuit son parcours dans un élément aval du conduit du circuit d'admission du moteur 12 auquel est relié au moins un orifice de sortie OS2 du second collecteur 18.Advantageously, the second portion P2 of the heat exchanger 14 comprises, as the first portion P1, circulation passages 38 of the external air flow Fe cooling between each of the tubes of the first series S 1 P2 and the second series S2P2 so as 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 S1 P2 and S2P2 of tubes opens in at minus one inlet port OE2 of the second manifold 18, forming the outlet air box, then continues its course in a downstream element of the duct of the engine intake circuit 12 which is connected at least one outlet port OS2 of the second collector 18.
De préférence, dans les première et seconde parties P1 , P2, les premières séries de tubes S1 P1 et S1 P2 présentent une section totale de passage A1 1 et A21 qui sont respectivement globalement équivalente aux sections totales de passage A12 et A22 des première et deuxième séries de tubes S2P1 et S2P2.Preferably, in the first and second portions P1, P2, the first series of tubes S1 P1 and S1 P2 have a total passage section A1 1 and A21 which are respectively substantially equivalent to the total passage sections A12 and A22 of the first and second series of S2P1 and S2P2 tubes.
Comme illustré aux figures 5 à 7, les tubes des premières séries S 1 P1 et S 1 P2 ainsi que les tubes des deuxièmes séries S2P1 et S2P2 de chacune des première et seconde parties P1 , P2 présentent, suivant un plan de coupe vertical, une section longitudinale parallélépipédique, ici rectangulaire.As illustrated in FIGS. 5 to 7, the tubes of the first series S 1 P1 and S 1 P2 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.
En variante (non représentée), les tubes des premières séries S 1 P1 et S1 P2 ainsi que les tubes des deuxièmes séries S2P1 et S2P2 de chacune des première et seconde parties P1 , P2 présentent suivant un plan de coupe vertical une section longitudinale globalement circulaire.Alternatively (not shown), the tubes of the first series S 1 P1 and S1 P2 and 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 generally circular longitudinal section. .
Grâce à l'invention, il est possible de réaliser un échangeur thermique 14 de forme oblongue, c'est-à-dire de grande longueur (L) et de faible hauteur (h), qui est ainsi susceptible d'être implanté en dessous ou au dessus du radiateur 22.Thanks to the invention, it is possible to produce a heat exchanger 14 of oblong shape, that is to say of great length (L) and low height (h), which is thus likely to be implanted below or above the radiator 22.
Les dimensions du faisceau 20 de l'échangeur thermique 14 sont par exemple comprises entre 500 et 800 mm pour la longueur (L), entre 40 et 200 mm pour la hauteur (h) et entre 50 et 120 mm pour la largeur (I).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 (I) .
Par comparaison avec un échangeur thermique de l'état de la technique comportant un faisceau tubes horizontaux de longueur "L", chaque partie du flux Fi traversant une série de tubes munis de turbulateurs 34 ne parcourt en réalité entre l'orifice d'entrée OE 1 et l'orifice de sortie OE2 que la moitié de cette longueur, donc "L/2", soit dans la première partie P1 soit dans la seconde partie P2 ce qui permet d'obtenir une réduction de la perte de charge. De plus, par comparaison avec un échangeur thermique de l'état de la technique, le nombre de tubes horizontaux du faisceau est avantageusement augmenté.In comparison with a heat exchanger of the state of the art comprising a horizontal tube bundle of length "L", each part of the flow Fi through a series of tubes provided with turbulators 34 actually runs between the inlet port OE 1 and the OE2 outlet orifice that half of this length, so "L / 2", is in the first part P1 or in the second part P2 which provides a reduction of the pressure drop. In addition, by comparison with a heat exchanger of the state of the art, the number of horizontal tubes of the beam is advantageously increased.
Avantageusement, un tel agencement d'un échangeur thermique 14 permet de supprimer des problèmes tels que "l'effet de masque" que provoque un premier échangeur qui, agencé devant un deuxième échangeur comme le radiateur de refroidissement, constitue alors un "écran" pour le deuxième échangeur et qui est notamment susceptible de perturber la circulation du flux extérieur d'air de refroidissement. De plus, une telle implantation de l'échangeur thermiqueAdvantageously, 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. In addition, such an implantation of the heat exchanger
14 facilite le raccordement des orifices d'entrée et de sortie de l'échangeur avec les conduits respectifs du circuit d'admission, en améliorant notamment l'accessibilité à l'échangeur 14 et en permettant de surcroît une simplification des parcours des conduits auparavant tortueux et de plus grande longueur.14 facilitates the connection of the inlet and outlet ports of the heat exchanger with the respective ducts of the intake circuit, in particular improving the accessibility to the exchanger 14 and furthermore allowing a simplification of the paths previously tortuous ducts and of greater length.
Bien entendu, les notions d'"entrée" et de "sortie" sont relatives et ne sont par conséquent pas limitatives des variantes de réalisation possibles, notamment en fonction des applications. Ainsi, sans sortir du cadre de l'invention, le flux intérieur d'air Fi peut notamment circuler dans le faisceau 20 de tubes en sens inverse, c'est-à-dire de droite vers la gauche en traversant d'abord la seconde partie P2 puis la boîte de répartition 24 et enfin la première partie P1 .Of course, the concepts of "input" and "output" are relative and therefore are not limiting the possible embodiments, in particular depending on the applications. Thus, without departing from the scope of the invention, 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.
Dans ce cas, le second collecteur 18 constitue une boîte à air d'entrée du flux intérieur d'air Fi et le premier collecteur 16 une boîte à air de sortie.In this case, the second manifold 18 constitutes an air inlet box of the internal air flow Fi and the first manifold 16 an outlet air box.
Avantageusement, un groupe moto-ventilateur, tel que le groupe moto-ventilateur associé au radiateur du circuit de refroidissement du moteur, est susceptible d'amener à l'échangeur thermique 14 suffisamment d'air de refroidissement lorsque le flux extérieur d'air créé par la marche du véhicule est insuffisant, en particulier lorsque le véhicule roule doucement ou est arrêté alors que le moteur 12 continue de fonctionner.Advantageously, 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.
Bien entendu, l'invention trouve à s'appliquer à tous types d'échangeur thermique et l'échangeur thermique de type air-air illustré par les figures n'est donné qu'à titre d'exemple non limitatif, ainsi en variante les tubes du faisceau 20 peuvent être verticaux.Of course, the invention is applicable to all types of heat exchanger and the air-air type heat exchanger illustrated in the figures is given by way of non-limiting example, thus alternatively Beam tubes 20 may be vertical.
En variante, l'échangeur thermique 14 est du type air-liquide dans lequel le liquide de refroidissement est par exemple constitué par de l'eau ou de l'huile. Alternatively, the heat exchanger 14 is of the air-liquid type in which the cooling liquid is for example constituted by water or oil.

Claims

REVENDICATIONS
1 . Echangeur thermique (14), notamment du type air-air pour un moteur (12) à combustion interne suralimenté, du type comportant au moins un premier collecteur (16) et un second collecteur (18) qui sont reliés par un faisceau (20) de tubes horizontaux dans lesquels circule un flux intérieur d'air (Fi) à refroidir par un flux (Fe) de fluide de refroidissement circulant à l'extérieur des tubes du faisceau (20), caractérisé en ce que le faisceau (20) de tubes comporte au moins : - une première partie (P1 ) comportant une première série de tubes (S1 P1 ) avec turbulateurs (34) présentant une section totale de passage (S1 1 ) et une deuxième série de tubes sans turbulateurs (S2P1 ) présentant une section totale de passage (S12) globalement équivalente à la section totale de passage (S 1 1 ),1. Heat exchanger (14), in particular of the air-air type for a supercharged internal combustion engine (12), of the type comprising at least a first collector (16) and a second collector (18) which are connected by a bundle (20) of horizontal tubes in which circulates an internal flow of air (Fi) to be cooled by a flow (Fe) of cooling fluid flowing outside the tubes of the bundle (20), characterized in that the bundle (20) of tubes comprises at least: a first part (P1) comprising a first series of tubes (S1 P1) with turbulators (34) having a total passage section (S1 1) and a second series of tubes without turbulators (S2P1) having a total passage section (S12) substantially equivalent to the total passage section (S 1 1),
- une seconde partie (P2) comportant une première série de tubes sans turbulateurs (S1 P2) présentant une section totale de passage (S21 ) et une deuxième série de tubes (S2P2) avec turbulateurs (34) présentant une section totale de passage (S22) globalement équivalente à la section totale de passage (S21 ),- a second part (P2) comprising a first series of tubes without turbulators (S1 P2) having a total passage section (S21) and a second series of tubes (S2P2) with turbulators (34) having a total passage section (S22 ) substantially equivalent to the total passage section (S21),
- et une boîte de répartition (24) du flux intérieur d'air (Fi) à refroidir comportant des moyens de raccordement (40) de la sortie de la première série de tubes avec turbulateurs (S1 P1 ) de la première partie (P1 ) avec l'entrée de la première série de tubes sans turbulateurs (S1 P2) de la seconde partie (P2) et de raccordement de la sortie de la deuxième série de tubes sans turbulateurs (S2P1 ) de la première partie (P1 ) avec l'entrée de la deuxième série de tubes avec turbulateurs (S2P2) de la seconde partie (P2). and a distribution box (24) for the internal air flow (Fi) to be cooled, comprising connection means (40) for the output of the first series of tubes with turbulators (S1 P1) of the first part (P1). with the entry of the first series of tubes without turbulators (S1 P2) of the second part (P2) and connection of the output of the second series of tubes without turbulators (S2P1) of the first part (P1) with the inlet of the second series of tubes with turbulators (S2P2) of the second part (P2).
2. Echangeur thermique (14) selon la revendication 1 , caractérisé en ce que la première série de tubes avec turbulateurs (S 1 P1 ) de la première partie (P1 ) comporte un groupe supérieur (26) de tubes et un groupe inférieur (28) de tubes et en ce que la deuxième série de tubes sans turbulateurs (S2P1 ) de la première partie est agencée verticalement entre les groupes supérieur (26) et inférieur (28) de tubes de la première série de tubes avec turbulateurs (S1 P1 ) de la première partie (P1 ). 2. Heat exchanger (14) according to claim 1, characterized in that the first series of tubes with turbulators (S 1 P1) of the first part (P1) comprises an upper group (26) of tubes and a lower group (28). ) of tubes and in that the second series of tubes without turbulators (S2P1) of the first part is arranged vertically between the upper (26) and lower (28) groups of tubes of the first series of tubes with turbulators (S1 P1) of the first part (P1).
3. Echangeur thermique ( 14) selon l'une des revendications 1 ou 2, caractérisé en ce que la deuxième série de tubes sans turbulateurs (S2P2) de la seconde partie (P2) comporte un groupe supérieur (30) de tubes et un groupe inférieur (32) de tubes et en ce que la première série de tubes avec turbulateurs (S1 P2) de la seconde partie (P2) est agencée verticalement entre les groupes supérieur (30) et inférieur (32) de tubes de la deuxième série de tubes sans turbulateurs (S2P2) de la seconde partie (P2).3. Heat exchanger (14) according to one of claims 1 or 2, characterized in that the second series of tubes without turbulators (S2P2) of the second part (P2) comprises an upper group (30) of tubes and a group lower part (32) of tubes and in that the first series of tubes with turbulators (S1 P2) of the second part (P2) is arranged vertically between the upper (30) and lower (32) groups of tubes of the second series of tubes without turbulators (S2P2) of the second part (P2).
4. Echangeur thermique ( 14) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il comporte au moins un passage (38) de circulation du flux (Fe) de fluide de refroidissement entre au moins une partie des tubes des première et deuxième séries avec turbulateurs (S1 P1 , S2P2) et/ou des première et deuxième séries sans turbulateurs (S1 P2, S2P1 ). 4. heat exchanger (14) according to any one of the preceding claims, characterized in that it comprises at least one passage (38) for circulating the flow (Fe) of cooling fluid between at least a portion of the tubes of the first and second series with turbulators (S1 P1, S2P2) and / or first and second series without turbulators (S1 P2, S2P1).
5. Echangeur thermique (14) selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes des premières séries (S 1 P1 , S1 P2) et des deuxièmes séries (S2P1 , S2P2) de chacune des parties (P1 , P2) présentent, suivant un plan de coupe vertical, une section longitudinale parallélépi- pédique, notamment rectangulaire.5. Heat exchanger (14) according to any one of the preceding claims, characterized in that the tubes of the first series (S 1 P1, S1 P2) and the second series (S2P1, S2P2) of each of the parts (P1, P2 ) have, in a vertical sectional plane, a parallelepipedal longitudinal section, in particular rectangular.
6. Echangeur thermique (14) selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier collecteur ( 16) et le second collecteur (18) constituent respectivement une boîte à air d'entrée et une boîte à air de sortie du flux d'air intérieur (Fi) à refroidir.6. Heat exchanger (14) according to any one of the preceding claims, characterized in that the first collector (16) and the second collector (18) constitute respectively an inlet air box and an air outlet box of the indoor air flow (Fi) to cool.
7. Echangeur thermique (14) selon l'une quelconque des revendications précédentes, caractérisé en ce que le fluide de refroidissement du flux intérieur d'air (Fi) est constitué par un flux extérieur d'air (Fe), tel qu'un flux d'air résultant de la pression dynamique de l'air provoqué par le déplacement du véhicule et/ou par un groupe moto-ventilateur.7. heat exchanger (14) according to any one of the preceding claims, characterized in that the cooling fluid of the inner air flow (Fi) is constituted by an external flow of air (Fe), such as a air flow resulting from the pressure air dynamics caused by the movement of the vehicle and / or by a motor-fan unit.
8. Echangeur thermique (14) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il présente transversalement une forme générale oblongue de manière à permettre notamment son implantation au dessus ou en dessous du radiateur (22) de refroidissement du moteur (12).8. heat exchanger (14) according to any one of the preceding claims, characterized in that it has a generally oblong transverse general shape so as to allow its implementation above or below the radiator (22) of the engine cooling ( 12).
9. Echangeur thermique selon la revendication 8, caractérisé en ce qu'il est globalement de forme parallélépipédique-rectangle. 9. Heat exchanger according to claim 8, characterized in that it is generally rectangular parallelepiped-shaped.
EP05791964A 2004-08-02 2005-07-13 Heat exchanger with tube core, in particular for a supercharged internal combustion engine Not-in-force EP1779054B1 (en)

Applications Claiming Priority (2)

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FR0408507A FR2873798B1 (en) 2004-08-02 2004-08-02 THERMAL HEAT EXCHANGER WITH TUBULAR BEAM, IN PARTICULAR FOR A SUPERIOR INTERNAL COMBUSTION ENGINE
PCT/FR2005/050580 WO2006021704A1 (en) 2004-08-02 2005-07-13 Heat exchanger with tube core, in particular for a supercharged internal combustion engine

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JP2008508472A (en) 2008-03-21
US20070209783A1 (en) 2007-09-13
KR20070048179A (en) 2007-05-08
ES2297757T3 (en) 2008-05-01
FR2873798A1 (en) 2006-02-03
DE602005004160D1 (en) 2008-02-14
US7748437B2 (en) 2010-07-06
EP1779054B1 (en) 2008-01-02
DE602005004160T2 (en) 2008-12-24
WO2006021704A1 (en) 2006-03-02
ATE382840T1 (en) 2008-01-15
JP4543083B2 (en) 2010-09-15
FR2873798B1 (en) 2006-09-29

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