WO2019063946A1 - Ventilation device for a motor vehicle heat exchange module with air guides for guiding the air flow passing through the air manifolds - Google Patents

Ventilation device for a motor vehicle heat exchange module with air guides for guiding the air flow passing through the air manifolds Download PDF

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Publication number
WO2019063946A1
WO2019063946A1 PCT/FR2018/052382 FR2018052382W WO2019063946A1 WO 2019063946 A1 WO2019063946 A1 WO 2019063946A1 FR 2018052382 W FR2018052382 W FR 2018052382W WO 2019063946 A1 WO2019063946 A1 WO 2019063946A1
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WO
WIPO (PCT)
Prior art keywords
air
ventilation device
flow
profile
opening
Prior art date
Application number
PCT/FR2018/052382
Other languages
French (fr)
Inventor
Michael LISSNER
Amrid MAMMERI
Kamel Azzouz
Original Assignee
Valeo Systemes Thermiques
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
Priority to FR1759160A priority Critical patent/FR3071875A1/en
Priority to FR1759160 priority
Priority to FR1759159 priority
Priority to FR1759159A priority patent/FR3071873A1/en
Application filed by Valeo Systemes Thermiques filed Critical Valeo Systemes Thermiques
Publication of WO2019063946A1 publication Critical patent/WO2019063946A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/10Guiding or ducting cooling-air, to, or from, liquid-to-air heat exchangers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00Pumping cooling-air or liquid coolants
    • F01P5/02Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/06Guiding or ducting air to, or from, ducted fans
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F04F5/16Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46Arrangements of nozzles

Abstract

The invention relates to a ventilation device (2) for generating an air flow through a motor vehicle heat exchanger (1), the ventilation device (2) comprising: a plurality of ducts (8), - at least one air manifold (12) comprising at least one air flow inlet (131; 132) and ports, each duct (8) opening at one of the ends thereof into a port (14) separate from the air manifold (12), wherein the at least one air manifold (12; 100; 200; 300; 400; 500) is provided with air guides (104, 402) configured to guide the air flow passing through the air manifold (12; 100; 200; 300; 400; 500).

Description

 VENTILATION DEVICE FOR AUTOMOTIVE AIR HEAT EXCHANGE MODULE WITH AIR FLOW AIR GUIDES

 CROSSING THE AIR COLLECTORS

The present invention relates to a motor vehicle heat exchange module.

 A motor vehicle heat exchanger generally comprises tubes, in which a coolant is intended to circulate, and heat exchange elements connected to these tubes, often referred to as "fins" or "spacers".

 The fins increase the exchange surface between the tubes and the ambient air. However, in order to increase the heat exchange between the coolant and the ambient air, it is common that a ventilation device is used in addition to generate a flow of air directed to the tubes and fins.

 Such a ventilation device most often comprises a propeller fan, which has many disadvantages.

 First, the assembly formed by the propeller fan and its motorization system occupies a large volume.

 In addition, the distribution of the air ventilated by the propeller, often placed in the center of the heat pipe row, is not homogeneous over the entire surface of the heat exchanger. In particular, some regions of heat exchanger, such as the ends of the heat pipes and the heat exchanger corners, are not or hardly reached by the air flow ventilated by the propeller.

 Finally, when the start of the ventilation device is not necessary, especially when the ambient air flow created by the movement of the motor vehicle is sufficient to cool the coolant, the blades of the propeller partially mask exchanger heat. Thus, part of the heat exchanger is not or only slightly ventilated by the ambient air flow in this case, which limits the heat exchange between the heat exchanger and the ambient air flow.

Furthermore, it is known from German patent DE 10 2011 120 865 a motor vehicle having a ventilation device and a heat exchanger, the ventilation device being adapted to generate a flow of air through heat exchanger. The ventilation device is adapted to create a secondary air flow from a primary flow emitted from one or more annular elements, the air flow secondary being much stronger than the primary airflow. According to this patent, the ventilation device is part of a cooling grid disposed on the front face of the motor vehicle.

 In such a motor vehicle, each annular element is supplied with primary air flow by a single fan, disposed outside the annular element, via a duct opening punctually in the annular element. Consequently, the ejected air flow emitted by the annular element is not homogeneous on the contour of the annular element. On the contrary, the air flow emitted is all the more important as it is close to the fan. It follows the creation of a secondary air flow through the heat exchanger which is also inhomogeneous.

 Finally, it is known from the application DE 10 2015 205 415 a ventilation device intended to generate an air flow through a heat exchanger comprising a hollow frame and at least one hollow spacer, dividing the surface delimited by the frame. cells. The frame and the spacer (s) are in fluid communication with a feed turbine engine in a flow of air. The turbomachine is disposed outside the frame. The frame and possibly the spacer or spacers are further provided with an ejection opening of the flow of air flowing through them.

 Again, the ventilation device does not generate a homogeneous air flow through the heat exchanger. On the contrary, the air flow emitted by the device is all the more important that it is ejected from the ventilation device near the turbomachine.

 The invention aims to provide an improved ventilation device does not have at least some of the aforementioned disadvantages.

 For this purpose, the invention proposes a ventilation device for generating an air flow through a motor vehicle heat exchanger, the ventilation device comprising:

 a plurality of conduits,

at least one air collector comprising at least one air flow inlet and orifices, each duct opening at one of its ends into a hole distinct from the air collector, each duct having at least one passage opening; a flow of air passing through said duct, the opening being distinct from the ends of the corresponding duct, the opening being situated outside the at least one air collector, in which the at least one air collector is equipped with air guides configured to guide the flow of air passing through the air collector. Advantageously, the air guides of the air flow make it possible to feed more homogeneously the different ducts of the ventilation device, thus allowing a more homogeneous effect of the ventilation device on its entire surface. The air guides also limit the pressure drop of the air flow in the ventilation device, which improves the efficiency of this ventilation device.

 Preferably, the ventilation device comprises one or more of the following features, taken alone or in combination:

 the air guides comprise means for distributing the flow of air entering the manifold through said at least one airflow inlet, towards the orifices,

 the distribution means comprise partitions inside the at least one air collector,

 - for each air manifold:

 o the number of partitions is zero if the ratio of the area of the inlet of the collector to the total area of the orifices is greater than 1.5 and / or where the number of partitions is equal to three if the ratio of the area of the collector inlet over the total area of the orifices is between 1 and 1.5; and or

 the number of partitions is equal to 5 or more if the ratio of the area of the inlet of the collector to the total area of the orifices is less than 1, where the or each partition is rectilinear, rectilinear in pieces or curve.

 at least one partition extends, in the vicinity of the airflow inlet, in a first direction, said at least one partition extends, in the vicinity of the orifices, in a second direction, and the first and second directions are substantially perpendicular,

 the air guides comprise, in the vicinity of the orifices, deflectors adapted to deflect the flow of air in the vicinity of the orifices, so that the flow of air passing through the orifices is directed substantially in a direction normal to the section of the orifices,

each deflector is rectilinear, rectilinear in pieces or curved, the deflectors are integral with the at least one air collector,

 at least one partition and / or at least one deflector comprises an electrically conductive material,

each duct has, on at least one section, a geometric section comprising: o a leading edge;

 o a trailing edge opposite the leading edge;

 a first and a second profile, each extending between the leading edge and the trailing edge,

 said at least one opening of the duct being on the first profile, said at least one opening being configured so that the flow of ejected air flows along at least a portion of the first profile,

 each duct has, on at least one section, a geometric section comprising:

 o a leading edge;

 o a trailing edge opposite the leading edge;

 a first and a second profile, each extending between the leading edge and the trailing edge,

 at least one opening of the duct being configured on the first profile so that the flow of ejected air flows along at least a portion of the first profile and at least one opening of the duct being configured on the second profile so the ejected airflow flows along at least a portion of the second profile.

 the ducts are substantially rectilinear tubes, aligned so as to form a row of tubes;

 the opening is a slot in an outer wall of the duct, the slot extending in a direction of elongation of the duct, preferably on at least 90% of the duct length and / or the height of said at least one opening is greater than or equal to 0.5 mm, preferably greater than or equal to 0.7 mm, and / or less than or equal to 2 mm, preferably less than or equal to 1.5 mm;

 each duct has, on at least one section, a geometric section comprising:

 - a leading edge;

 - a trailing edge opposite the leading edge;

 a first and a second profile, each extending between the leading edge and the trailing edge,

said at least one opening of the duct being on the first profile, said at least one opening being configured so that the flow of ejected air flows along at least a portion of the first profile, said at least one opening of the first profile being delimited by an outer lip and an inner lip, an end of the inner lip extends, in the direction of the second profile, beyond a plane normal to the free end of the outer lip, the passage section then being defined as the portion of the section of the tube disposed between said end of the inner lip and the trailing edge, on the one hand, and between the first and second profiles, on the other hand;

 the maximum distance between the first and the second profiles, in a direction of alignment of the ducts, is downstream of the said at least one opening, in the direction of flow of the said flow of air ejected by the said at least one opening, the maximum distance preferably being greater than or equal to 5 mm, preferably greater than or equal to 10 mm, and / or less than or equal to 20 mm, preferably less than or equal to 15 mm, the maximum distance being even more preferably equal to 11.5 mm;

 the first profile comprises a curved portion whose apex defines the point of the first profile corresponding to the maximum distance, the curved portion being disposed downstream of the opening in the direction of flow of said air flow ejected by said at least one an opening ;

 the first profile comprises a first substantially rectilinear portion, preferably downstream of the curved portion in the direction of flow of said air flow ejected by the at least one opening, in which the second profile comprises a substantially rectilinear part, extending preferably over a majority of the length of the second profile, the first rectilinear portion of the first profile and the rectilinear portion of the second profile forming a non-flat angle, the angle preferably being greater than or equal to 5 °, and / or less than or equal to 20 °, more preferably substantially equal to 10 °;

 the first rectilinear part extends over a section of the first profile corresponding to a length, measured in a direction perpendicular to the direction of alignment of the ducts and to a longitudinal direction of the ducts, greater than or equal to 30 mm, preferably greater than or equal to 40 mm, and / or less than or equal to 50 mm;

the first profile comprises a second rectilinear part, downstream of the first rectilinear part in the direction of flow of the air flow ejected by the at least one opening, the second rectilinear part extending substantially parallel to the straight part of the second profile, the first profile preferably having a third straight portion, downstream of the second straight portion of the first profile, the third straight portion forming a non-flat angle with the rectilinear portion of the second profile, the third straight portion extending substantially to a rounded edge connecting the third straight portion of the first profile and the rectilinear portion of the second profile, the rounded edge defining the trailing edge of the profile of the conduit;

 the distance between the second rectilinear part of the first profile and the rectilinear part of the second profile is greater than or equal to 2 mm and / or less than or equal to

10 mm, preferably less than or equal to 5 mm;

 said geometrical section of the duct has a length, measured in a direction perpendicular to the direction of alignment of the ducts and at a principal direction of extension of the ducts, greater than or equal to 50 mm and / or less than or equal to 70 mm, preferably substantially equal to 60 mm;

 - The ventilation device comprises at least a first and a second ducts, the first profile of the first duct being vis-à-vis the first profile of the second duct;

 - The ventilation device further comprises a third conduit, such that the second profile of the second conduit is vis-à-vis the second profile of the third conduit, the distance between the center of the geometric section of the second conduit and the center of the geometrical section of the third duct preferably being smaller than the distance between the center of the geometrical section of the first duct and the center of the geometrical section of the second duct; and

 each duct is symmetrical with respect to the plane containing the leading edge and the trailing edge, so that each duct has two symmetrical openings, respectively on the first profile and on the second profile.

 Advantageously, the deflectors of the air flow can guide the flow of air in the ducts of the ventilation device by limiting the pressure losses and guiding it in a preferred direction.

 The invention also relates to a motor vehicle heat exchange module comprising:

 a heat exchanger, the heat exchanger having a plurality of tubes, called heat-transfer tubes, in which a fluid is intended to circulate, and

 - A ventilation device as described above, adapted to generate a flow of air to the heat pipes.

 The invention will be better understood on reading the description which follows, given solely by way of example and with reference to the drawings in which:

FIG. 1 is a perspective view of an exemplary exchange module of FIG. heat with a heat exchanger provided with a part of a ventilation device;

 Figure 2 is a schematic sectional view along the plane II-II of an aerodynamic tube of the ventilation device of Figure 1;

 - Figures 3 to 7 schematically illustrate in section examples of air intake manifold that can be implemented in the ventilation device of Figure 1; and

 Figures 8 to 11 are views similar to that of Figure 2, the tube variants of the ventilation device of Figure 1.

 In the various figures, the identical or similar elements, having an identical function or the like, bear the same references. The description of their structure and function is therefore not systematically repeated.

 FIG. 1 shows an example of a heat exchange module 10 with a heat exchanger 1 intended to equip a motor vehicle, equipped with a ventilation device 2 according to a first exemplary embodiment.

 The heat exchanger 1 comprises heat-transfer ducts 4 in which a fluid is intended to circulate, in this case water or cooling liquid. Heat transfer ducts 4 are here substantially rectilinear and extend in a longitudinal direction. The heat-transfer ducts thus form heat-transfer tubes 4. The heat-transfer tubes 4 are parallel to each other and aligned so as to form a row. The heat pipes 4 are substantially all of the same length.

 The heat-transfer ducts 4 each extend between a fluid intake manifold 5 and a fluid evacuation manifold 6, common to all the heat-transfer ducts 4. Preferably, the orifices of the fluid intake manifold 5, in which open the heat pipes 4 are all included in the same foreground. Likewise, the orifices of the fluid evacuation manifold 6 into which the heat transfer ducts 4 open are all included in one and the same second plane, preferably parallel to said first plane.

 More particularly, and conventionally in motor vehicle heat exchangers, each heat transfer tube 4 has a substantially oblong cross section, and is delimited by first and second planar walls which are connected to heat exchange fins. For the sake of clarity, the fins are not shown in FIG.

The heat exchange module 10 is equipped with a ventilation device 2 comprising a plurality of ventilation ducts 8. The ventilation ducts 8, in the same way as the heat-transfer ducts 4, are substantially rectilinear, so as to form ventilation tubes 8. The ventilation tubes 8 are also parallel to each other and aligned to form a row of ventilation tubes 8. The ventilation tubes 8 are also of the same length. The length of the ventilation tubes 8 is for example substantially equal to the length of the heat-transfer tubes 4.

 The ventilation device 2 is intended to generate a flow of air towards the heat-transfer tubes 4.

 The heat-transfer tubes 4 and the ventilation tubes 8 may all be parallel to each other, as illustrated in FIG. 1. Thus, the rows of ventilation tubes 8 and of heat-transfer tubes 4 are themselves parallel. In addition, the ventilation tubes 8 may be arranged so that each of them is opposite a heat-transfer tube 4.

 The number of ventilation tubes 8 is adapted to the number of heat-transfer tubes 4. For example, for a conventional heat exchanger 1, the ventilation device 2 may comprise, for example, at least ten ventilation tubes 8, preferably at least 15 tubes. 8, more preferably at least twenty-four ventilation tubes 8 and / or at most fifty ventilation tubes 8, preferably at most thirty-six ventilation tubes 8, more preferably at most thirty ventilation tubes 8. The heat exchanger 1 may for example comprise between sixty and seventy heat transfer tubes 4.

 The tubes and the number of ventilation tubes 8 of the ventilation device 2 may be such that a minimum air passage section between the tubes of the ventilation device, defined in a plane substantially perpendicular to the air flow through the exchanger 1, is between 25 and 50% of the surface, defined in a plane perpendicular to the flow of air through heat exchanger, between two extreme heat transfer tubes.

 Preferably, the front surface of the ventilation tubes 8, measured in a plane substantially perpendicular to the heat exchanger through air flow 1, is less than 85% of the front surface occupied by the heat-transfer tubes 4.

Moreover, in order to limit the volume occupied by the heat exchange module comprising heat exchanger 1 and the ventilation device 2, while obtaining heat exchange performance similar to that of a propeller ventilation device , the row of ventilation tubes 8 can be arranged at a lower distance or equal to 150 mm of the row of heat transfer tubes 4, preferably less than or equal to 100 mm. This distance is preferably greater than or equal to 5 mm, preferably greater than 40 mm. Indeed, a too short distance between the ventilation tubes 8 and the heat-transfer tubes 4 may not allow a homogeneous mixture of air flow ejected from the ventilation tubes 8 with the induced air flow. An inhomogeneous mixture does not allow homogeneous cooling of the heat transfer tubes 4 and induces high pressure losses. Too great a distance may not allow to set up the assembly formed by the ventilation device and the heat exchange device in a motor vehicle without requiring a suitable design of the power unit and / or other motor vehicle bodies present in the vicinity of the heat exchange module.

 Similarly, again to limit the volume occupied by the heat exchange module, it can be ensured that the height of the row of ventilation tubes 8 (the term height here referring to the dimension corresponding to the direction in which the ventilation tubes 8 are aligned) is substantially equal to or less than that of the height of the row of heat transfer tubes 4. For example, the height of the row of heat transfer tubes 4 being 431 mm, it can be ensured that the height of the row of ventilation tubes 8 is substantially equal to or less than this value.

 The ventilation device 2 further comprises a supply device supplying air to the ventilation tubes 8, not visible in FIG. 1, via an air intake manifold 12, preferably via two intake manifolds. air 12.

 The air propulsion means are for example a turbomachine, supplying the two air intake manifolds 12, disposed at each of the ends of the ventilation device 1, via a respective port 13. In the example illustrated in FIG. 1, the ports 13 are substantially in the middle of the air intake manifolds 12. Alternatively or in addition, the ports 13 are at a longitudinal end 12a, 12b of each air intake manifold 12. Alternatively, a turbomachine can feed a single intake manifold 12 and not two. Also, one or more turbomachines can be implemented to supply each air intake manifold 12 or all the air intake manifolds 12.

 According to another embodiment, also, the turbine engine or turbomachines are received in one or in each air intake manifold 12.

Here, however, the air propulsion means are remote from the ventilation tubes 8 via the air intake manifolds 12. The or each turbomachine may not be directly adjacent to the air intake manifolds 12.

 Each air intake manifold 12 may for example be tubular. In the embodiment of Figure 1, the air intake manifolds 12 extend in the same direction, which is here perpendicular to the elongation direction (or longitudinal direction) of the heat transfer tubes 4 and ventilation 8.

 As can be seen in FIG. 1, the air intake manifold 12 comprises a plurality of air ejection orifices 14 each made at one end of a respective tubular portion, each ejection port of air 14 being connected to a single ventilation tube 8, and more particularly to the end of the ventilation tube 8.

 Each ventilation tube 8 has, according to the example of Figures 1 and 2, a plurality of openings 16 for passage of a flow of air F2 through the tube 8. The openings 16 of the ventilation tubes 8 are located at 12 More precisely, here, the openings 16 are oriented substantially in the direction of the heat exchanger 1, and even more precisely, substantially in the direction of the heat-transfer tubes 4, the slots 16 being for example arranged vis-à-vis the heat pipes 4 or fins housed between the heat pipes.

 Each ventilation tube 8 opens into a hole 14 separate from each manifold 12. Thus, each air manifold 12 has as many orifices 14 as it receives ventilation tubes 8, a ventilation tube 8 being received in each the openings 14 of the air collector 12. This allows a more homogeneous distribution of the air flow passing through each air collector 12, in the various ventilation tubes 8.

In this case, each air manifold 12 has a hollow shape, for example a substantially cylindrical shape, more particularly still substantially cylindrical rectilinear axis. In addition to the orifices 14 in which the ventilation tubes 8 open at their ends, each air manifold 12 also has one or more mouths 13 intended to be in fluid communication with a turbomachine (not shown in the figures) to create a Each collector 12 then makes it possible to distribute this flow of air in the various ventilation tubes 8. In different variants, each air collector 12 may be in fluid communication with one or more turbomachines. clean (that is to say that are in fluid communication only with one of the two air collectors 12) or, conversely, the air collectors 12 can be in fluid communication with the same turbomachine or several, common (that is to say that each turbine engine is in communication with fluid with each of the collectors 12).

 Advantageously, each air manifold 12 is devoid of any other opening than the orifices 14 and the mouths 13 mentioned above. In particular, the collector 12 is preferably devoid of an opening directed towards the heat exchanger 1, which in this case would make it possible to eject a part of the air flow passing through the air collector 12, directly in the direction of the heat exchanger 1, without traversing at least a portion of a ventilation tube 8. Thus, all the air flow created by the turbine engine or turbomachines traversing the or the air collectors 12, is distributed between substantially all ventilation tubes 8. This also allows a more homogeneous distribution of this air flow.

 It should be noted here that an advantage of the cooling module 10 of Figure 1 is to be able to move the turbine engine or turbomachines away from the ventilation tubes 8, in particular through the intake manifolds 12 and, optionally, a suitable air flow circuit putting in fluid communication the mouth or mouths 13 of the air collector (s) 12 to one or more turbomachines.

 Moreover, the air collector (s) 12 and the ventilation tubes (8) are here configured so that an air flow passing through the at least one air collector (12) is distributed between the different ventilation tubes (8), flows through them. different ventilation tubes 8 and is ejected through the openings 16. Thus, the openings 16 being disposed opposite the heat exchanger 1, an air flow F2 is ejected through the openings 16, and passes through the heat exchanger. heat 1.

 It should be noted, however, that the air flow Fl passing through the heat exchanger 1 may be substantially different from the air flow F2 ejected through the openings. In particular, the air flow Fl can comprise, in addition to the air flow F2, a flow of ambient air created by the movement of the motor vehicle running.

 Preferably, except at their air intake inlet ends, which have a substantially circular cross section, the ventilation tubes 8 have a substantially oblong constant cross-section, interrupted by the openings 16, as illustrated in FIG. 2.

The choice of this form allows an easy manufacture of the ventilation tubes 8 and gives good mechanical strength to the ventilation tubes 8. In particular, such ventilation tubes 8 can be obtained by folding an aluminum foil for example, but also by molding, overmolding, or by printing in three dimensions metal or plastic. More specifically, in the example of Figures 1 and 2, the cross section of the ventilation tubes 8 has a substantially elliptical shape whose small axis corresponds to the height of the ventilation tubes 8 and the major axis to the width of the ventilation tubes 8 (the terms height and width to be understood in relation to the orientation of Figure 2). For example, the small axis h of the ellipse is about 11 mm.

 To increase the flow of air F2 ejected to the heat exchanger 1 through the openings 16, the openings 16 are constituted by slots in the wall 17 of the ventilation tube 8, these slots 16 extending in the direction This slot shape makes it possible to constitute a large air passage, while maintaining a satisfactory mechanical strength of the ventilation tubes 8. Thus, to obtain the largest air passage possible, the openings

16 extend over a large part of the length of the ventilation tube 8, preferably over a total length corresponding to at least 90% of the length of the ventilation tube 8.

 The openings 16 are delimited by guide lips 18 protruding from the wall 17 of the ventilation tube 8.

 Because they protrude from the wall 17 of each ventilation tube 8, the guide lips 18 guide the air ejected through the opening 16 from the inside of the ventilation tube 8 towards the heat exchanger 1.

 The guide lips 18 are preferably flat and substantially parallel. For example, they are spaced from each other by a distance of about 5 mm and have a width (the term width to be considered in view of the orientation of Figure 4), between 2 and 5 mm. The guide lips 18 advantageously extend over the entire length of each opening 16.

 The guide lips 18 are preferably integral with the ventilation tube 8. The guide lips 18 are for example obtained by folding the wall

17 of the ventilation tube 8.

Moreover, the openings 16 are also delimited, in the direction of the length of the ventilation tubes 8, by reinforcing elements 20 of the ventilation tubes 8. The reinforcing elements 20 make it possible to maintain the width of the openings 16 constant. this is achieved because the reinforcing elements extend between the two guide lips 18 extending on either side of each opening 16. The reinforcing elements 20 preferably extend in a substantially normal plane the direction of elongation of the ventilation tubes 8, this in order to maintain the greatest possible, the section of the openings 16 allowing the passage of the air flow F2. The reinforcement elements 20 are advantageously evenly distributed along the length of the ventilation tubes 8. In the example illustrated in FIG. 3, each ventilation tube 8 comprises seven reinforcing elements 20. Of course, this number is in no way limiting. .

 Alternatively, the cross section of the ventilation tubes 8 is substantially circular, interrupted by the openings 16. For example, the diameter of the circle interrupted by the openings 16 is about 11 mm.

 Moreover, FIG. 3 schematically illustrates a first example of an air intake manifold 12 of the ventilation device 2 illustrated in FIG.

 This first example 100 air intake manifold has a substantially T-shaped with an inlet port 13 for being in fluid communication with an air propulsion device for supplying air flow, through the air intake manifold, the different ventilation tubes 8. The first example 100 of air intake manifold is substantially constant circular section.

 Remarkably, the air intake manifold 200 according to the second example illustrated in FIG. 4, comprise air guides in the form of means 104 for distributing the flow of air entering the manifold through the port d. inlet 13, towards the outlet orifices 14. These distribution means 104 make it possible to distribute more homogeneously the flow of air entering the manifold 12 between the different outlet orifices 14.

 Here, these distribution means 104 essentially comprise five divergent rectilinear walls 106, in the direction from the inlet port 13 to the outlet orifices 14. These rectilinear walls 106 guiding the flow of incoming air, they make it possible to limit the losses. charging the flow of air through the collector 12, and also reduce the passage section.

In Figure 5, the intake manifold 12 is a dual intake manifold having two halves 12i, 12 2 , separated. Here these two halves 12i, 12 2 are identical. The two halves 12i, 12 2, are substantially identical to the manifold 200 of Figure 4. Here, however, each half l5 12 12 2 manifold 300 has only three walls 106 divergent rectilinear as means 104 for distributing the flow of air entering the manifold 300 through the ports 131, 13 2 to the outlet ports 14.

The collector 400 according to the example of FIG. 6 is also a double collector comprising two halves 12 15 12 2 . Here, these halves are symmetrical. The ports 13 1 , 13 2 are here arranged at the longitudinal ends 12a, 12b of the intake manifold 400. This allows for a more compact heat exchange module. Therefore, each half 12i, 12 2 of the air intake manifold 400 is bent. Each half 12 15 12 2 of the air intake manifold 400 is provided with means 104 for distributing the flow of air entering the air intake manifold 400 through the inlet ports 131, 13 2 , to Here, these means 104 take the form of two walls 106. Here, the walls are not rectilinear. On the contrary, the two walls 106 are curved. The walls 106 thus make it possible to improve the guiding of the flow of air entering through the inlet port 13i, 13 2 , towards the outlet orifices 14.

 In addition, the collector 400 of FIG. 6 is provided with air guides in the form of deflectors 402, in the vicinity of the orifices 14. These deflectors 402 are made by curved walls which extend in the vicinity of the orifices 14 in such a manner that perpendicular to these orifices 14. These deflectors 402 and can better guide the flow of air towards the orifices 14, thereby limiting the pressure losses. Advantageously, the deflectors 402 deflect the flow of air in a direction substantially normal to the section of the orifices 14, in the vicinity of these orifices 14. The deflectors 402 are for example straight, curved or folded walls (i.e. say straight in pieces).

The collector 500 of Figure 7 is also a dual air intake manifold, comprising two halves 12i, 12 2 , symmetrical. The input ports 13i, 13 2 , are also located at the longitudinal ends 12a, 12b of the air intake manifold 500 in order to limit the overall width. The air intake manifold 500 is bent.

The collector 500 is provided with nine walls 106 by half 12i, 12 2 as means 104 for distributing the flow of air entering the air intake manifold 500 through the inlet ports 13i, 13 2 , to the outlets 14. In the vicinity of the ports 13i,

13 2 , these walls 106 extend substantially in the direction of extension of the port 13i, 13 2 . On the contrary, near the orifices 14, the walls 106 extend perpendicular to the section of the orifices 14. Thus, the walls 106 extend in two directions perpendicular to the vicinity of the inlet port 131, 13 2 and in the vicinity of the orifices 14. The walls 106 thus form means 104 for distributing the air flow but also deflectors 402.

Other forms of air flow distribution means 104 are accessible to those skilled in the art. The shape of the walls can thus be different. In particular, the walls 106 may be rectilinear, rectilinear in pieces or curves. Similarly, in the examples of FIGS. 4 to 7, the walls 106 may be integral with the air intake manifold or the walls 106 may be made separately from the air intake manifold and then be fixed thereto. .

 The walls 106 and / or the deflectors 402 may advantageously be made of an electrically conductive material. It is thus possible to pass an electric current in the walls 106 and / or in the deflectors 402 and, by joule effect, to produce heat. The heat produced can be used in particular to heat the air flow.

 Moreover, the number of walls 106 described is not limiting. However, it was found that the best results were obtained when the number of walls 106 per intake manifold or half of the air intake manifold was chosen according to the ratio of the total area of the air intake manifold. air flow inlet, on the total area of the airflow outlets. The total inflow area refers to the cross-sectional area of the port of entry or the sum of the cross-sectional areas of the ports of entry. The total area of the exits is the sum of the areas of the cross-sections of the outlets. In particular, the number of partitions can be zero if the ratio of the total input area of the collector to the total area of the outputs is greater than 1.5. The number of partitions can be equal to three if the ratio of the total entrance area of the collector to the total area of the outlets is between 1 and 1.5. And the number of partitions can be equal to 5 or more if the ratio of the total entrance area of the collector to the total area of the outlets is less than 1.

 The use of air guides in the form of air flow distribution means and / or deflectors is independent of the shape of the ventilation tubes 8. In the following, examples of the shape of the ventilation tubes are described. 8 can be implemented in the ventilation device 2.

 In the following, the ventilation tubes 8 are called aerodynamic tubes 8.

It may be noted here that the shape of the ventilation tubes 8 is a priori independent of the configuration of the air intake manifolds.

An aerodynamic tube 8 has on at least a portion, preferably over substantially its entire length, a cross section as illustrated in Figure 8 with a leading edge 37, a trailing edge 38 opposite the leading edge 37 and, here, disposed facing the heat pipes 4, and a first and a second profiles 42, 44, each extending between the leading edge 37 and the trailing edge 38. The leading edge 37 is for example defined as the point at the front of the section of the aerodynamic tube 8 where the radius of curvature of the section is minimal. The front of the tube section aerodynamic 8 can be defined as the portion of the section of the aerodynamic tube 8 which is opposite - that is to say, which is not vis-à-vis - of the heat exchanger 1. From Similarly, the trailing edge 38 may be defined as the point at the rear of the section of the aerodynamic tube 8 where the radius of curvature of the section is minimal. The rear of the section of the aerodynamic tube 8 can be defined, for example, as the portion of the section of the aerodynamic tube 8 which faces the heat exchanger 1.

 The distance c between the leading edge 37 and the trailing edge 38 is for example between 16 mm and 26 mm. This distance is here measured in a direction perpendicular to the alignment direction of the row of aerodynamic tubes 8 and the longitudinal direction of the aerodynamic tubes 8

 In the example of Figure 8, the leading edge 37 is free. In this figure also, the leading edge 37 is defined on a parabolic portion of the section of the aerodynamic tube 8.

 The aerodynamic tube 8 illustrated in FIG. 8 also comprises at least one opening 40 for ejecting a stream of air passing through the aerodynamic tube 8, outside the aerodynamic tube 8 and the air intake manifold 12, in particular substantially in the direction of the heat exchanger 1. The opening or each opening 40 is for example a slot in an outer wall 41 of the aerodynamic tube 8, the slot or slots extending for example in the direction of extension of the aerodynamic tube 8 in which they are made. The total length of the opening 40 or openings may be greater than 90% of the length of the aerodynamic tube. Each opening 40 is distinct from the ends of the aerodynamic tube 8, through which the aerodynamic tube 8 opens into an air manifold 12. Each opening 40 is also outside the air intake manifold 12. The shape slot makes it possible to constitute a large air passage in the direction of the heat exchanger 1 without greatly reducing the mechanical strength of the aerodynamic tubes 8.

 In the following only describes an opening 40 being understood that each opening 40 of the aerodynamic tube 8 may be identical to the opening 40 described.

The opening 40 is for example disposed near the leading edge 37. In the example of Figure 8, the opening 40 is on the first profile 42. In this example, the second profile 44 is devoid of opening 40. The opening 40 in the first profile 42 is configured so that the flow of air ejected through the opening 40 flows along at least a portion of the first profile 42. The aerodynamic tubes 8 of the ventilation device 2 can be oriented alternately with the first profile 42 or the second profile 44 facing upwards. Thus, alternatively, two adjacent aerodynamic tubes 8 are such that their first profiles 42 are vis-à-vis or, conversely, their second profiles 44 are vis-à-vis. The distance between two aerodynamic tubes 8 neighbors whose second profiles 44 are vis-à-vis is less than the distance between two aerodynamic tubes 8 neighbors whose first profiles 42 are vis-à-vis. The pitch between two adjacent aerodynamic tubes or the distance between the center of the geometrical section of a first aerodynamic tube 8 and the center of the geometrical section of a second aerodynamic tube 8, such as the first profile 42 of the first aerodynamic tube 8 either vis-à-vis the first profile 42 of the second aerodynamic tube 8, measured in the direction of alignment of the aerodynamic tubes 8 is greater than or equal to 15 mm, preferably greater than or equal to 20 mm, and / or less or equal to 30 mm, preferably less than or equal to 25 mm.

 For each pair of aerodynamic tubes 8 whose openings 40 are in facing relation, the air flows ejected by these openings 40 thus create an air passage in which a part, called induced air, of the ambient air is driven by aspiration.

 It should be noted here that the flow of air ejected through the openings 40 runs along at least part of the first profile 42 of the aerodynamic tube 8, for example by Coanda effect. Taking advantage of this phenomenon, it is possible, thanks to the entrainment of the ambient air in the created air passage, to obtain a flow of air sent to the heat pipes identical to that generated by a propeller fan. while consuming less energy.

 Indeed, the air flow sent to the row of heat transfer tubes 4 is the sum of the air flow ejected by the slots and induced air. Thus, it is possible to implement a turbomachine of reduced power compared to a conventional propeller fan, generally implemented in the context of such a heat exchange module.

 A first profile 42 having a Coanda surface also makes it possible not to have to orient the openings 40 directly towards the heat-transfer tubes 4, and thus to limit the size of the aerodynamic tubes 8. It is thus possible to maintain a passage section. more important between the aerodynamic tubes 8, which promotes the formation of a greater induced air flow.

The opening 40 is, in Figure 8, delimited by lips 40a, 40b. The distance e between the lips 40a, 40b, which defines the height of the opening 40, can be greater or equal to 0.3 mm, preferably greater than or equal to 0.5 mm, more preferably greater than or equal to 0.7 mm and / or less than 2 mm, preferably less than or equal to 1.5 mm, preferably still less than 0.9 mm, more preferably still less than or equal to 0.7 mm. The height of the slot is the size of this slot in the direction perpendicular to its length. The lower the height of the slot 40, the greater the speed of the air flow ejected by this slot. A high speed of ejected airflow results in a high dynamic pressure. This dynamic pressure is then converted into static pressure in the mixing zone of the air flow ejected by the slot 40 and the induced air flow. This static pressure makes it possible to overcome the pressure losses due to the presence of the heat exchanger downstream of the ventilation device, in order to ensure a suitable flow of air through the heat exchanger. These pressure losses due to the heat exchanger vary in particular as a function of the heat pipe pitch and the pitch of the fins of the heat exchanger, as well as the number of heat exchange modules that can be superimposed. in the heat exchanger. However, a slot height too low induces high pressure losses in the ventilation device, which involves using an air propulsion device or several oversized (s). This can lead to additional cost and / or create a space incompatible with the space available in the vicinity of the heat exchange module in the motor vehicle.

 The outer lip 40a here consists of the extension of the wall of the aerodynamic tube 8 defining the leading edge 37. The inner lip 40b is constituted by a curved portion 50 of the first profile 42. An end 51 of the inner lip 40b can extend, as illustrated in Figure 11, in the direction of the second profile 44, beyond a plane L normal to the free end of the outer lip 40a. In other words, the end 51 of the inner lip 40b can extend, towards the leading edge 37, beyond the normal plane L at the free end of the outer lip 40a. The end 51 can then contribute to directing the flow of air flowing in the aerodynamic tube 8 towards the opening 40.

The opening 40 of the aerodynamic tube 8 can be configured so that a flow of air flowing in this aerodynamic tube 8 is ejected through this opening 40, flowing along the first profile 42 substantially to the trailing edge 38 of the aerodynamic tube 8. The flow of airflow along the first profile 42 may result from the Coanda effect. It is recalled that the Coanda effect is an aerodynamic phenomenon resulting in the fact that a fluid flowing along a surface at a short distance from it tends to be flush with it, or even cling to it.

 To do this, here the maximum distance h between the first 42 and the second 44 profiles, measured according to an alignment direction of the aerodynamic tubes 8, is downstream of the opening 40. The maximum distance h may be greater than 10 mm, preferably greater than 11 mm and / or less than 20 mm, preferably less than 15 mm. Here, by way of example, the maximum distance h is substantially equal to 11.5 mm. A height h too low can cause significant pressure losses in the aerodynamic tube 8 which could require to implement a turbomachine more powerful and therefore more voluminous. For the same value of the distance between the aerodynamic tubes 8, measured according to the direction of alignment of the aerodynamic tubes, a height h too large limits the passage section between the aerodynamic tubes for the induced air flow. The total air flow directed to the heat exchanger is then also reduced.

 The first profile 42 here comprises a curved portion 50 whose apex defines the point of the first profile 42 corresponding to the maximum distance h. The curved portion 50 may be disposed downstream of the opening 40 in the direction of ejection of the air flow. In particular, the convex portion 50 may be contiguous with the inner lip 40b delimiting the opening 40.

 Downstream of the curved portion 50 in the direction of ejection of said air flow through the opening 40, the first profile 42 of the aerodynamic tube 8 of the example of Figure 8 comprises a first portion 52 substantially straight. The second profile 44 comprises, in the example illustrated in FIG. 8, a substantially rectilinear portion 48, preferably extending over a majority of the length of the second profile 44. In the example of FIG. 8, the length 1 of the first rectilinear part 52, measured in a direction perpendicular to the longitudinal direction of the aerodynamic tube 8 and the alignment direction of the row of aerodynamic tubes, may be greater than or equal to 30 mm, preferably greater than or equal to 40 mm, and / or less than or equal to 50 mm. A relatively large length of this first rectilinear part is desired in particular for guiding the air flow ejected from the opening 40, which makes it possible to ensure greater suction of air. The length of this first rectilinear part is however limited because of the corresponding size of the ventilation device and its consequences on the packaging of the ventilation device or the heat exchange module.

In this case, the first rectilinear portion 52 of the first profile 42 and the portion rectilinear 48 of the second profile 44 may form a non-flat angle Θ. The angle Θ thus formed may in particular be greater than or equal to 5 °, and / or less than or equal to 20 °, more preferably substantially equal to 10 °. This angle of the first rectilinear portion 52 with respect to the rectilinear portion 48 of the second profile 44 makes it possible to accentuate the expansion of the flow of air ejected by the opening 40 and undergoing the Coanda effect forcing it to follow the first profile 42 , this accentuated relaxation to increase the induced air flow. An angle Θ too great, however, may prevent the realization of the Coanda effect, so that the flow of air ejected through the opening 40 may not follow the first profile 42 and, therefore, not to be oriented correctly towards the heat exchanger 2.

 The first profile 42 may comprise, as illustrated in FIG. 8, a second rectilinear part 38a, downstream of the first rectilinear part 52, in the direction of ejection of the air flow, the second rectilinear part 38a extending substantially parallel to the rectilinear portion 48 of the second profile 44. The first profile 42 may also include a third straight portion 54, downstream of the second straight portion 38a of the first profile 42. The third straight portion 54 may form a non-flat angle with the rectilinear portion 48 of the second profile 44. The third rectilinear portion 54 may extend, as illustrated, substantially to a rounded edge connecting the third rectilinear portion 54 of the first profile 42 and the straight portion 48 of the second profile 44. The edge rounded can define the trailing edge 38 of the cross section of the aerodynamic tube 8.

The straight portion 48 of the second profile 44 extends in the example of Figure 8 over the majority of the length c of the cross section. This length c is measured in a direction perpendicular to the longitudinal direction of the aerodynamic tubes 8 and to the alignment direction of the row of aerodynamic tubes 8. This direction corresponds, in the example of FIG. 11, substantially to the direction of the flow of the induced air flow. In this first exemplary embodiment, the length c of the cross section (or width of the aerodynamic tube 8) may be greater than or equal to 50 mm and / or less than or equal to 70 mm, preferably substantially equal to 60 mm. Indeed, the inventors have found that a relatively large length of the cross section of the aerodynamic tube makes it possible to more effectively guide the flow of air ejected through the opening 40 and the induced air flow, which mixes with this flow of air ejected. However, too great a length of the cross section of the aerodynamic tube 8 poses a problem of packaging of the ventilation device 2. In particular, the size of the heat exchange module can then be too much important compared to the place that is available in the motor vehicle in which it is intended to be mounted. The packaging of the heat exchange module or the ventilation device can also be problematic in this case.

 Moreover, as illustrated in FIG. 8, the second rectilinear portion 38a of the first profile 42 and the portion 38b of the rectilinear portion 48 of the second profile 44 facing it are parallel. For example, the distance f between this second rectilinear portion 38a and the portion 38b of the rectilinear portion 48 of the second profile 44 may be greater than or equal to 2 mm and / or less than or equal to 10 mm, preferably less than or equal to 5 mm. mm.

FIG. 8 further illustrates that the cross section (or geometrical section) of the aerodynamic tube 8 delimits a passage section S for the flow of air passing through the aerodynamic tube 8. This passage section S is here defined by the walls of the aerodynamic tube 8 and the segment extending in the alignment direction of the aerodynamic tubes 8 between the second profile 44 and the end of the end 51 of the inner lip 40b. This passage section may have an area greater than or equal to 150 mm 2 , preferably greater than or equal to 200 mm 2 , and / or less than or equal to 700 mm 2 , preferably less than or equal to 650 mm 2 . A passage section of the air flow in the aerodynamic tube 8 limits the pressure losses which would have the consequence of having to oversize the turbomachine used to obtain an air flow ejected by the desired opening 40. However, a large passage section induces a large size of the aerodynamic tube 8. Thus, with fixed pitch aerodynamic tubes, a larger passage section may affect the passage section of the induced air flow between the aerodynamic tubes 8 , thus not making it possible to obtain a satisfactory total flow of air directed towards the heat-transfer tubes 4.

 In order to block as little as possible the flow of air towards the heat-transfer tubes 4 and the fins, the ventilation device 2 provided with such aerodynamic tubes 8 is advantageously arranged so that each aerodynamic tube 8 is vis-à-vis 4f of the front face connecting the first 4a and second 4b planar walls of a heat pipe 4 corresponding. More particularly, the trailing edge 38 of each aerodynamic tube 8 is included in the volume defined by the first and second longitudinal plane walls of the heat pipe 4 corresponding.

Preferably, the second rectilinear portion 38a of the first profile and the rectilinear portion 48 of the second profile 44 are respectively contained in the same plane as the first longitudinal plane wall and the second longitudinal plane wall of the tube. coolant 4 corresponding.

 In particular, the distance f between the second straight portion 38a of the first profile 42 and the portion 38b of the rectilinear portion 48 of the second profile 44 facing it is substantially equal to the distance separating the first longitudinal wall and the second longitudinal wall. heat transport tube 4 vis-à-vis which the aerodynamic tube 8 is disposed. For example, this distance f is greater than or equal to 2 mm and / or less than or equal to 10 mm, preferably less than or equal to 5 mm.

 In other embodiments, the distance f between the second rectilinear portion 38a of the first profile 42 and the portion 38b of the rectilinear portion 48 of the second profile 44, which faces it, may, however, be less than the distance separating the first longitudinal wall and the second longitudinal wall of the heat transport tube vis-à-vis the aerodynamic tube 8 is disposed.

 Two heat transfer tubes 4 may be contained in the volume defined by the air passage defined by two aerodynamic tubes 8 neighbors. However, it can be envisaged that a single heat-transfer tube 4, or three or four heat-transfer tubes 4 are contained in this volume. Conversely, it can be envisaged that an aerodynamic tube 8 is disposed opposite each heat-carrying tube 4.

 In the examples of FIGS. 9, 10 and 11, the aerodynamic ducts 8 are substantially rectilinear, parallel to each other and aligned so as to form a row of aerodynamic tubes 8. However, the first and second profiles 42, 44 of each aerodynamic tube 8 are, according to these examples, symmetrical with respect to a plane CC, or rope plane, passing through the leading edge 37 and the trailing edge 38 of each aerodynamic tube 8.

 As the first and second profiles 42, 44 are symmetrical, each of these profiles 42, 44 is provided with an opening 40. Thus, at least a first opening 40 is formed on the first profile 42, which is configured so that a the air flow exiting the first opening 42 flows along at least a portion of the first profile 42. Likewise, at least a second opening 40 is present on the second profile 44, which is configured so that a airflow exiting the second opening 40 flows along at least a portion of the second profile 44. As for the example of Figure 8, this can be achieved here by implementing the Coanda effect.

For the same reasons as those given for the example of FIG. 8, the distance c between the leading edge 37 and the trailing edge 38 can also, in these examples, be greater than or equal to 50 mm and / or lower. or equal to 80 mm. In particular, the length c may be equal to 60 mm.

 The openings 40 are similar to those of the example of FIG. 8. In particular, the distance e between the inner and outer lips 40b and 40a of each opening 40 may be greater than or equal to 0.3 mm, preferably greater than or equal to 0.5 mm, more preferably greater than or equal to 0.7 mm, and / or less than or equal to 2 mm, preferably less than or equal to 1.5 mm, more preferably less than or equal to 0.9 mm and more preferably still less than or equal to 0.7 mm.

 The fact that the profiles 42, 44 are symmetrical with respect to the chord plane CC passing through the leading edge 37 and the trailing edge 38 of the aerodynamic tube 8 makes it possible to limit the obstruction to the air flow between the device of FIG. ventilation 2 and the heat pipes 4, while creating more air passages in the volume available in front of the heat pipes 4.

 In other words, unlike the embodiment of Figure 8, an air passage leading to ambient air is created between each pair of aerodynamic tubes 8 neighbors, made according to one of Figures 9 to 11.

 The pitch between two adjacent aerodynamic tubes 8 may, in this case, be greater than or equal to 15 mm, preferably greater than or equal to 20 mm, more preferably greater than or equal to 23 mm and / or less than or equal to 30 mm, preferably less than or equal to 25 mm, more preferably less than or equal to 27 mm. Indeed, if the pitch between the aerodynamic tubes 8 is lower, the induced air flow is limited by a passage section between the weak aerodynamic tubes. On the contrary, if the pitch is too large, the ejected airflow does not create an induced air flow over the entire pitch between the neighboring aerodynamic tubes.

 The pitch between two adjacent aerodynamic tubes 8 can in particular be defined as the distance between the center of the cross section of two adjacent aerodynamic tubes 8 or, more generally, as the distance between a reference point on a first aerodynamic tube 8 and the point corresponding to the reference point, on the nearest aerodynamic tube 8. The reference point may especially be one of the leading edge 37, the trailing edge 38 or the top of the curved portion 50.

The distance between the aerodynamic tubes 8 and the heat-transfer tubes 4 can in particular be chosen greater than or equal to 5 mm, preferably greater than or equal to 40 mm, and / or less than or equal to 150 mm, preferably less than or equal to 100 mm. . Indeed, the speed peak of the air velocity profile in the vicinity of the profile, tends to be reduce away from the opening 40 in the aerodynamic tube. An absence of peak reflects a homogeneous mixture of the air flow ejected by the opening 40 and the induced air flow. It is preferable that such a homogeneous mixture is made before the airflow reaches the aerodynamic tubes. Indeed, a flow of air incident on the heat transfer tubes, heterogeneous, does not allow optimal cooling of the heat pipes and induces greater pressure losses. However, the distance between the aerodynamic tubes and the heat transfer tubes is preferably contained to limit the size of the cooling module.

 In the example illustrated in FIG. 9, the first and second profiles 42, 44 of the aerodynamic tube 8 converge towards the trailing edge 38 so that the distance separating the first and second profiles 42, 44 decreases strictly towards the leak 38 from a point of these first and second profiles 42, 44 corresponding to the maximum distance h between these two profiles, these points of the first and second profiles 42, 44 being downstream of the openings 40 in the direction of flow the flow of air ejected through the opening 40. Preferably, the first and second profiles 42, 44 each form an angle of between 5 and 10 ° with the symmetry rope CC of the cross section of the aerodynamic tube 8.

 Therefore, unlike the example of Figure 8, the aerodynamic profile of Figure 9 does not include a portion defined by first and second parallel opposed planar walls. This has the advantage of limiting the drag along the aerodynamic profile of the aerodynamic tube 8.

 For example, the maximum distance h between the first profile 42 and the second profile 44 may be greater than or equal to 10 mm and / or less than or equal to 30 mm. In particular, this maximum distance h can be equal to 11.5 mm. In the example shown in FIGS. 12 to 14, this distance becomes zero at the trailing edge 38.

 In the example illustrated in FIG. 10, the trailing edge 38 is formed by the apex joining two straight symmetrical portions 60 of the first profile 42 and the second profile 44 of each aerodynamic tube 8. According to the variant of FIG. trailing edge 38 is the point of the cross section of the aerodynamic tube 8 located closest to the heat exchanger. In other words, the angle formed by the two rectilinear portions 60 is less than 180 °, especially less than 90 °.

In contrast, in the variant of FIG. 11, the trailing edge 38 is disposed between the two rectilinear portions 38a, 38b of the first and second profiles 42, 44. in other words, the angle formed by the rectilinear portions 60 is here greater than 90 °, in particular greater than 180 °.

 The invention is not limited to the exemplary embodiments presented and other embodiments will become clear to those skilled in the art. In particular, the different examples can be combined, as long as they are not contradictory. For example, the air guides may comprise the air flow distribution means and / or deflectors, independently or complementary.

Claims

Ventilation device (2) for generating a flow of air through a motor vehicle heat exchanger (1), the ventilation device (2) comprising:
 a plurality of ducts (8),
at least one air collector (12; 100; 200; 300; 400; 500) having at least one inlet (13i; 13 2 ) of air flow and orifices, each duct (8) opening through one of its ends in an orifice (14) separate from the air collector (12; 100; 200; 300; 400; 500), each duct (8) having at least one opening (16; air passing through said conduit (8), the opening (16; 40) being distinct from the ends of the corresponding conduit (8), the opening (16; 40) being located outside the at least one air manifold (12; 100; 200; 300; 400; 500)
wherein the at least one air manifold (12; 100; 200; 300; 400; 500) is provided with air guides (104,402) configured to guide the flow of air through the air manifold (12; 100; 200; 300; 400; 500).
2. Ventilation device according to the preceding claim, wherein the air guides comprise distribution means (104) of the air flow entering the manifold (12; 100; 200; 300; 400; 500) by said at least one inlet (13i; 13 2 ) of air flow to the orifices.
3. Ventilation device according to the preceding claim, wherein the distribution means (104) comprise partitions (106) inside the at least one air collector (12; 100; 200; 300; 400; 500). .
4. Ventilation device according to the preceding claim, wherein, for each air manifold (12; 100; 200; 300; 400; 500):
the number of partitions (106) is zero if the ratio of the area of the inlet (13i; 13 2 ) of the collector (12; 100; 200; 300; 400; 500) to the total area of the orifices is greater than 1.5 and / or
the number of partitions (106) is equal to three if the ratio of the area of the inlet (13i; 13 2 ) of the collector (12; 100; 200; 300; 400; 500) to the total area of the orifices is between 1 and 1.5; and or the number of partitions (106) is equal to 5 or more if the ratio of the area of the inlet (131; 13 2 ) of the collector to the total area of the orifices is less than 1.
5. Ventilation device according to one of claims 2 to 4, wherein at least one partition (106) extends in the vicinity of the inlet (13i; 13 2 ) of air flow, in a first direction said at least one partition (106) extends, in the vicinity of the orifices, in a second direction, and the first and second directions are substantially perpendicular.
6. Ventilation device according to any one of the preceding claims, wherein the air guides comprise, in the vicinity of the orifices, baffles (402) adapted to deflect the flow of air in the vicinity of the orifices, so that the flow of air passing through the orifices is directed substantially in a direction normal to the section of the orifices.
7. Ventilation device according to the preceding claim, wherein each deflector is rectilinear, straight in pieces or curve.
8. Ventilation device according to any one of claims 6 or 7, wherein the baffles are integral with the at least one air collector (12; 100;
200; 300; 400; 500).
9. Ventilation device according to any one of claims 2 to 8, wherein at least one partition (106) and / or at least one deflector (402) comprises an electrically conductive material.
10. Ventilation device according to any one of the preceding claims, wherein each duct (8) has, on at least one section, a geometric section comprising:
 a leading edge (37);
 - an opposite trailing edge (38) to the leading edge (37);
 first and second profiles (42; 44), each extending between the leading edge (37) and the trailing edge (38),
said at least one opening (40) of the conduit (8) being on the first profile (42), said at least one opening (40) being configured such that ejected airflow flows along at least a portion of the first profile (42).
11. Ventilation device according to any one of the preceding claims, wherein each duct has, on at least one section, a geometric section comprising:
 a leading edge (37);
 - a trailing edge (38) opposite to the leading edge (37);
 first and second profiles (42; 44), each extending between the leading edge (37) and the trailing edge (38),
 at least one opening (40) of the duct (8) being configured on the first profile (42) so that the flow of ejected air flows along at least a portion of the first profile (42) and at least an opening (40) of the conduit (8) being configured on the second profile (44) so that the ejected airflow flows along at least a portion of the second profile (44).
A heat exchange module (10) for a motor vehicle comprising:
 - a heat exchanger (1), the heat exchanger (1) having a plurality of tubes (4), said heat-transfer tubes, in which a fluid is intended to circulate, and
 - A ventilation device (2) according to any one of the preceding claims, adapted to generate a flow of air to the heat transfer tubes (4).
PCT/FR2018/052382 2017-09-29 2018-09-27 Ventilation device for a motor vehicle heat exchange module with air guides for guiding the air flow passing through the air manifolds WO2019063946A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
FR1759160A FR3071875A1 (en) 2017-09-29 2017-09-29 Tube ventilation device for automotive vehicle heat exchange module with air flow deflectors in air collectors
FR1759160 2017-09-29
FR1759159 2017-09-29
FR1759159A FR3071873A1 (en) 2017-09-29 2017-09-29 Tube ventilation device for a motor vehicle heat exchange module with air flow distribution partitions in air collectors

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WO2010100453A1 (en) * 2009-03-04 2010-09-10 Dyson Technology Limited A fan assembly
EP2256450A2 (en) * 2009-05-28 2010-12-01 Behr GmbH & Co. KG Heat exchanger
DE102011120865B3 (en) 2011-12-12 2012-11-15 Audi Ag Vehicle, has fan assembly generating airflow through heat exchanger and including fan, which generates strong adjacent airflow using primary airflow from annular element, where fan assembly is designed as component of radiator grill
JP2015001155A (en) * 2013-06-13 2015-01-05 カルソニックカンセイ株式会社 Cooling device
JP2015124748A (en) * 2013-12-27 2015-07-06 カルソニックカンセイ株式会社 Cooling device
DE102015205415A1 (en) 2015-03-25 2016-09-29 Ford Global Technologies, Llc Cooling fan arrangement for a cooling system of a liquid-cooled engine of a vehicle
WO2017098765A1 (en) * 2015-12-09 2017-06-15 株式会社Soken Cooling device
EP3184776A1 (en) * 2015-12-23 2017-06-28 Audi Ag Charged air cooler for a combustion engine and method for operating same

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010100453A1 (en) * 2009-03-04 2010-09-10 Dyson Technology Limited A fan assembly
EP2256450A2 (en) * 2009-05-28 2010-12-01 Behr GmbH & Co. KG Heat exchanger
DE102011120865B3 (en) 2011-12-12 2012-11-15 Audi Ag Vehicle, has fan assembly generating airflow through heat exchanger and including fan, which generates strong adjacent airflow using primary airflow from annular element, where fan assembly is designed as component of radiator grill
JP2015001155A (en) * 2013-06-13 2015-01-05 カルソニックカンセイ株式会社 Cooling device
JP2015124748A (en) * 2013-12-27 2015-07-06 カルソニックカンセイ株式会社 Cooling device
DE102015205415A1 (en) 2015-03-25 2016-09-29 Ford Global Technologies, Llc Cooling fan arrangement for a cooling system of a liquid-cooled engine of a vehicle
WO2017098765A1 (en) * 2015-12-09 2017-06-15 株式会社Soken Cooling device
EP3184776A1 (en) * 2015-12-23 2017-06-28 Audi Ag Charged air cooler for a combustion engine and method for operating same

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