FR3077239A1 - VENTILATION DEVICE FOR A HEAT EXCHANGE MODULE OF A MOTOR VEHICLE - Google Patents

Abstract

The invention relates to a ventilation system for generating at least one air flow through at least one motor vehicle heat exchanger (1; la; lb) comprising at least one propeller fan (3) and a ventilation device (2), the ventilation device (2) comprising ducts (8) intended to be supplied with air by at least one air propulsion device, distinct from the propeller fan (3), each duct (8) having at least one opening (16; 40) for ejecting an air flow passing through said duct (8), substantially towards said at least one heat exchanger (1; la; 1b).

Description

VENTILATION DEVICE FOR HEAT EXCHANGE MODULE

OF MOTOR VEHICLE

The present invention relates to a ventilation device for a heat exchange module and a heat exchange module for a motor vehicle.

A heat exchanger generally comprises tubes, in which a heat transfer fluid is intended to circulate, and heat exchange elements connected to these tubes, often designated by the term "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 heat transfer fluid and the ambient air, it is frequent that a ventilation device is used in addition to generate a flow of air directed towards the tubes and the fins.

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

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

In addition, the distribution of air ventilated by the propeller, often placed in the center of the row of heat pipes, is not uniform over the entire surface of the heat exchanger. In particular, certain regions of the heat exchanger, such as the ends of the heat transfer tubes and the corners of the heat exchanger, are not or only slightly affected by the air flow ventilated by the propeller.

Finally, when it is not necessary to start the ventilation device, in particular when the ambient air flow created by the movement of the motor vehicle is sufficient to cool the heat transfer fluid, the blades of the propeller partially mask the 'heat exchanger. 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 the 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 secondary air flow being much stronger than the primary air flow. According to this patent, the ventilation device is part of a cooling grid, arranged on the front face of the motor vehicle.

In such a motor vehicle, each annular element is supplied with a primary air flow by a single fan, disposed outside the annular element, via a conduit opening punctually into the annular element. Consequently, the flow of ejected air emitted by the annular element is not homogeneous over the contour of the annular element. On the contrary, the flow of air emitted is all the more important as it is close to the fan. It follows the creation of a secondary air flow passing 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 area delimited by the frame into cells. The frame and the spacer (s) are in fluid communication with a turbomachine supplying an air flow. The turbomachine is arranged outside the frame. The frame and possibly the spacer or spacers are further provided with an opening for ejection of the air flow passing 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 when it is ejected from the ventilation device near the turbomachine.

The invention aims to provide an improved ventilation system.

To this end, the invention provides a ventilation system intended to generate at least one air flow through at least one heat exchanger of a motor vehicle, comprising at least one propeller fan and one ventilation device, the ventilation device comprising ducts intended to be supplied with air flow by at least one air propulsion device, distinct from the propeller fan, each duct having at least one opening for ejection of a traversing air flow said conduit, substantially in the direction of said at least one heat exchanger.

Thus, the ventilation system according to the invention proposes to combine a ventilation device called "without propeller" and a conventional propeller fan, in order to best adapt the air flow emitted to the need of the cooled heat exchanger (s) by the ventilation system, while limiting the pressure losses due to the ventilation system.

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

the ventilation device further comprises at least one air intake manifold, each duct opening at one of its ends into a separate orifice of the at least one air intake manifold, the conduits being intended to be supplied with an air flow through said at least one air propulsion device, via the at least one air intake manifold, said at least one duct ejection opening being distinct from the ends of the corresponding duct, said at at least one ejection opening being located outside the at least one air intake manifold;

the ducts of the ventilation device form a row of ducts extending substantially in a foreground;

the ventilation device and the propeller fan extend substantially in the same plane as the first plane;

the ventilation device and the propeller fan extend substantially one beside the other;

the ventilation device and the propeller fan extend substantially one above the other, in the direction of alignment of the row of ducts of the ventilation device;

the ventilation device and the propeller fan extend one after the other relative to the direction of flow of the air flow generated towards said at least one heat exchanger;

the ventilation device is arranged upstream relative to the propeller fan;

the ventilation device is arranged upstream of the at least one heat exchanger and the propeller fan is arranged downstream of the at least one heat exchanger;

at least one of the conduits is mounted orientable. Therefore, the ventilation system according to the present invention provides a function for shutting off the air intake as well as a function for ventilating the exchangers in a compact space allowing better thermal management of a motor vehicle, since the grid is blowing. Depending on the orientation of the ducts, the device makes it possible to adjust the air flow which arrives at the heat exchanger, thereby optimizing thermal management. According to another characteristic of the invention, said at least one pivoting duct is mounted to be orientable between a closed position and an open position, the closed position leaving a space between said tube and an adjacent tube which is less than a space between said tube and said adjacent tube in the open position. Preferably, the ducts are positioned relative to each other so as to block an air flow in the closed position, and so as to allow a flow of air to flow in the open position.

- The conduits are substantially straight tubes, aligned so as to form a row of tubes;

the opening is a slot in an external wall of the duct, the slot extending in a direction of elongation of the duct, preferably over at least 90% of the length of the duct 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 conduit 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 part of the first profile,

said at least one opening of the first profile being delimited by an external lip and an internal lip, one end of the internal 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 conduits, is downstream of said at least one opening, in the direction of flow of said flow of air ejected through 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 includes a curved part, the apex of which defines the point of the first profile corresponding to the maximum distance, the curved part being arranged downstream of the opening in the direction of flow of said air flow ejected by said at least an opening ;

- The first profile has a first substantially straight portion, preferably downstream of the curved portion in the direction of flow of said air flow ejected from the at least one opening, in which the second profile comprises a substantially straight portion, s preferably extending over a majority of the length of the second profile, the first rectilinear part of the first profile and the rectilinear part 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 still 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 conduits and to a longitudinal direction of the conduits, greater than or equal to 30 mm, preferably greater 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 rectilinear part of the second profile, the first profile preferably comprising 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 straight portion of the second profile, the third straight portion extending substantially up to a rounded edge connecting the third straight portion of the first profile and the straight portion of the second profile, the rounded edge defining the trailing edge of the profile of the conduit;

the distance between the second straight part of the first profile and the straight 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;

the said geometric section of the conduit has a length, measured in a direction perpendicular to the direction of alignment of the conduits and to a main direction of extension of the conduits, 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 duct, the first profile of the first duct being opposite the first profile of the second duct;

- The ventilation device also comprises a third duct, such that the second profile of the second duct is opposite the second profile of the third duct, the distance between the center of the geometric section of the second duct and the center of the geometric section of the third duct preferably being less than the distance between the center of the geometric section of the first duct and the center of the geometric section of the second duct; and

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

According to another aspect, the invention relates to a cooling system for a motor vehicle, comprising at least one heat exchanger and a ventilation system as described above.

Preferably, the cooling system includes one or more of the following characteristics:

at least a first heat exchanger and at least a second heat exchanger arranged substantially in the same plane, one next to the other, the ventilation device being arranged opposite said at least one first exchanger heat and said propeller fan being disposed opposite said at least one second heat exchanger;

at least a first heat exchanger and at least a second heat exchanger arranged substantially in the same plane, one below the other, the ventilation device being arranged opposite said at least one first exchanger heat and said propeller fan being disposed opposite said at least one second heat exchanger;

at least a first heat exchanger and at least a second heat exchanger arranged substantially in two separate planes, the ventilation device being arranged opposite said at least one first heat exchanger and said propeller fan being disposed at at least partially opposite said at least one second heat exchanger, said at least one first heat exchanger being located between said at least one second heat exchanger and said ventilation device;

the ventilation device and said propeller fan are arranged upstream of the at least one heat exchanger relative to the direction of flow of the air flow generated in the direction of said at least one heat exchanger;

the ventilation device is arranged upstream of the at least one heat exchanger relative to the direction of flow of the air flow generated towards said at least one heat exchanger, said propeller fan is arranged downstream of the at least one heat exchanger relative to the direction of flow of said air flow.

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

Figure 1 is a schematic perspective view of an example of a heat exchange module;

Figure 2 is a more detailed perspective view of a detail of the heat exchange module of Figure 1;

Figure 3 is a schematic sectional view along the plane II-II of a tube of the ventilation device of Figure 2;

Figures 4 to 7 are views similar to that of Figure 3, of alternative tubes of the ventilation device of Figure 2;

Figures 8 and 9 are views similar to Figure 1, other examples of heat exchange modules;

Figures 10 and 10a are views similar to Figure 1, according to another embodiment of the invention; and

Figures 11 and 12 are perspective views of a ventilation device of Figure 2 according to a variant, in two separate positions.

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

FIG. 1 shows an example of a heat exchange module 10 intended to equip a motor vehicle, with a plurality of heat exchangers 1, la, lb and equipped with a ventilation system according to a first example of production. According to this first example, the ventilation system comprises a ventilation device 2 and a propeller fan 3.

In the example of FIG. 1, the heat exchangers 1,1a, lb, the ventilation device 2 and the propeller fan 3 extend in parallel planes. In particular, a first heat exchanger 1 is arranged parallel to a second heat exchanger la and to the propeller fan 3, such that the propeller fan 3, the first heat exchanger la and the second heat exchanger lb are arranged substantially aligned. Thus, the second heat exchanger lb is interposed between the first heat exchanger la and the propeller fan 3. The propeller fan 3 can have dimensions substantially identical to the dimensions of the first and second heat exchangers la, lb and / or be sized to allow cooling of these first and second heat exchangers 1a, 1b.

In the same plane as the propeller fan 3, the ventilation system here comprises a ventilation device 2, placed next to the propeller fan and opposite a third heat exchanger 1.

The heat exchanger 1 comprises, as is more visible in FIG. 2, heat transfer conduits 4 in which a fluid is intended to circulate. The fluid here is water, coolant or coolant. The heat transfer conduits 4 are here substantially rectilinear and extend in a longitudinal direction. The heat transfer pipes thus form heat transfer tubes 4. The heat transfer tubes 4 are mutually parallel and aligned so as to form a row. The heat transfer tubes 4 are substantially all of the same length.

The heat transfer conduits 4 each extend between a fluid intake manifold 5 and a fluid discharge manifold 6, common to all the heat transfer conduits 4. Preferably, the orifices of the fluid intake manifold 5, in which open the heat transfer conduits 4 are all included in the same foreground. Likewise, the orifices of the fluid evacuation manifold 6, into which the heat transfer conduits 4 open are all included in 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 section, and is delimited by first and second planar walls which are connected to heat exchange fins. For reasons of clarity, the fins are not shown in FIG. 2.

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 so as 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 an air flow in the direction of the heat transfer tubes 4.

The heat transfer tubes 4 and the ventilation tubes 8 can all be parallel to each other, as illustrated in FIG. 2. Thus, the rows of ventilation tubes 8 and heat transfer tubes 4 are themselves parallel. In addition, the ventilation tubes 8 can 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 can for example comprise at least ten ventilation tubes 8, preferably at least fifteen tubes ventilation 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 can 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 can be such that a minimum air passage section between the tubes of the ventilation device, defined in a plane substantially perpendicular to the flow of air through the 'heat exchanger 1, is between 25 and 50% of the surface, defined in a plane perpendicular to the air flow through the heat exchanger, between two extreme heat pipes.

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

Furthermore, in order to limit the volume occupied by the heat exchange module comprising the heat exchanger 1 and the ventilation device 2, while obtaining heat exchange performance similar to that of a ventilation device. with a propeller, the row of ventilation tubes 8 can be placed at a distance less than or equal to 150 mm from 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 mixing of the 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 drops. Too great a distance may not allow the assembly formed by the ventilation device and the heat exchange device to be put into place in a motor vehicle, without requiring an adapted design of the power unit and / or others components of the motor vehicle present in the vicinity of the heat exchange module.

Likewise, still to limit the volume occupied by the heat exchange module 10, 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 according to 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. 2, via an air intake manifold 12, preferably via two intake intake manifolds. air 12.

The air propulsion means supplying air to the ventilation device are for example a turbomachine, supplying the two air intake manifolds 12, arranged at each end of the ventilation device 1, via a respective port 13. This the turbomachine is advantageously separate from the propeller fan 3.

In the example illustrated in FIG. 2, 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 and / or at the other longitudinal end 12b of each air intake manifold 12 and / or arranged along the length of the air intake manifolds 12. Alternatively, also, a turbomachine can supply a single intake manifold 12 and not two. One or more turbomachines can also be used to supply each air intake manifold 12 or all of the air intake manifolds 12.

According to another embodiment, also, the turbomachine (s) are received in one or in each air intake manifold 12, in particular in the vicinity of one or each longitudinal end 12a, 12b of the or each manifold d air intake.

Here, however, the air propulsion means are moved away from the ventilation tubes 8, outside the air intake manifolds 12 through which the air propulsion means supply air flow the ventilation tubes 8. The or each turbomachine forming the air propulsion means may not be directly adjacent to the air intake manifolds 12. On the contrary, it may be advantageous to be able to offset the turbomachine (s) remotely ventilation tubes 8, in particular by means of the intake manifolds 12 and, optionally, of an appropriate aeraulic circuit putting the port or ports 13 of the air manifold (s) 12 into communication with one or more turbomachines .

Each air intake manifold 12 can for example be tubular. In the embodiment of Figure 2, the air intake manifolds 12 extend in the same direction, which is here perpendicular to the direction of elongation (or longitudinal direction) of the heat transfer tubes 4 and ventilation 8.

As can be seen in FIG. 2, the air intake manifold 12 comprises a plurality of air ejection orifices each produced at one end of a respective tubular portion, each ejection orifice air being connected to a single ventilation tube 8, and more particularly to the end of the ventilation tube 8.

Advantageously, each air intake manifold 12 is devoid of any other opening than the orifices and the port or ports 13 mentioned above. In particular, the manifold 12 is preferably devoid of an opening oriented in the direction of the heat exchanger 1, which would in the present case allow the ejection of part of the air flow passing through the air manifold 12, directly in the direction of the heat exchanger 1, without traversing at least a portion of a ventilation tube 8. Thus, all of the air flow created by the turbomachine (s) passing through the air collector (s) 12, can be distributed between substantially all of the ventilation tubes 8. This also allows a more homogeneous distribution of this air flow.

Each ventilation tube 8 has, according to the example of FIGS. 2 and 3, a plurality of openings 16 for the passage of an air flow F2 passing through the tube 8. The openings 16 of the ventilation tubes 8 are located at the 'exterior of the air collectors 12. More specifically, here, the openings 16 are oriented substantially in the direction of the heat exchanger 1, and more precisely still, substantially in the direction of the heat transfer tubes 4, the slots 16 being for example arranged opposite the heat transfer tubes 4 or the fins housed between the heat transfer tubes.

Each ventilation tube 8 opens into a separate orifice in each manifold 12. Thus, each air collector 12 has as many orifices as it receives ventilation tubes 8, a ventilation tube 8 being received in each of the orifices 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.

Furthermore, the air manifold (s) 12 and the ventilation tubes 8 are here configured so that an air flow passing through the air collector (s) 12 is distributed between the various ventilation tubes 8, traverses the 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 exchanger heat 1.

It should be noted, however, that the air flow F1 passing through the heat exchanger 1 can be significantly different from the air flow F2 ejected through the openings. In particular, the air flow F1 can include, in addition to the air flow F2, an ambient air flow created by the movement of the moving motor vehicle.

In the first example illustrated in FIGS. 2 and 3, and as seen more particularly in FIG. 3, apart from their ends forming an air intake inlet, which have a substantially circular cross section, the ventilation tubes 8 have a substantially oblong cross section, interrupted by the openings 16.

The choice of this shape allows 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 sheet for example, but also by molding, overmolding, or by metallic or plastic three-dimensional printing.

More specifically, in the first example shown in Figures 2 and 3, the cross section of the ventilation tubes 8 has a substantially elliptical shape, the small axis of which corresponds to the height of the ventilation tubes 8 and the large axis of the width of the ventilation tubes ventilation 8 (the terms height and width should be understood relative to the orientation of Figure 3). For example, the minor h axis of the ellipse is about 11 mm.

To increase the flow of air F2 ejected towards the heat exchanger 1 through the openings 16, the openings 16 are formed by slots made in the wall 17 of the ventilation tube 8, these slots 16 extending in the direction elongation of the ventilation tube 8. This slotted shape makes it possible to constitute an air passage of large dimensions, while maintaining a satisfactory mechanical strength of the ventilation tubes 8. Thus, to obtain a larger air passage possible, the openings 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 here delimited by guide lips 18 projecting from the wall 17 of the ventilation tube 8.

Due to the fact that they project from the wall 17 of each ventilation tube 8, the guide lips 18 make it possible to guide the air ejected through the opening 16 from the interior of the ventilation tube 8 towards the heat exchanger 1.

The guide lips 18 are preferably planar 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 made integrally with the ventilation tube 8. The guide lips 18 are for example obtained by folding the wall of the ventilation tube 8.

Furthermore, 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 keep the width of the openings 16 constant. Here , this is achieved by the fact that the reinforcing elements extending between the two guide lips 18 extend on either side of each opening 16. The reinforcing elements 20 preferably extend in a plane substantially normal to the direction of elongation of the ventilation tubes 8, this in order to maintain the largest possible, the section of the openings 16 allowing the passage of the air flow L2. The reinforcement elements 20 are advantageously distributed regularly over the length of the ventilation tubes 8. In the example illustrated in FIGS. 2 and 3, each ventilation tube 8 comprises seven reinforcement elements 20. Of course, this number is by no means limiting.

The ventilation device 2 can be provided with means adapted to selectively interrupt a fluid communication between at least certain ejection openings 16 of the ventilation tubes 8 and the air ejection device or devices supplying the ventilation tubes 8 in air flow. Such means make it possible in particular to eject or not an air flow through certain ejection openings 16, for example as a function of their position. It is thus possible to adapt the flow of air ejected by the ventilation device 2 and, by the same, the flow of air F1 passing through the heat exchanger. For example, again, an air flow F1 can be produced only opposite certain elements to be cooled. This may be more particularly advantageous when the ventilation device 2 is associated with different heat exchangers and / or different elements to be cooled, arranged in defined zones facing the ventilation device 2. By "defined zones" is meant herein zones which can advantageously be distinct, without overlapping.

Advantageously, at least one of the tubes 8 is mounted orientable, preferably pivoting about a respective longitudinal axis.

In the embodiments illustrated in FIGS. 11 and 12, all the tubes 8 are pivotally mounted around respective longitudinal axes.

As is apparent from these figures, the tubes 8 are pivotally mounted between a closed position (FIG. 11) and an open position (FIG. 12), the closed position leaving a space between two adjacent tubes 3 less than a space between two adjacent tubes 3 in the open position.

In other words, the quantity of air circulating through the blowing grid formed by the set of tubes 8 is greater in the open position than in the closed position.

In the embodiment illustrated in Figures 11 and 12, the tubes 3 are positioned relative to each other so as to block an air flow in the closed position, and so as to allow a flow of air to flow in the open position.

Of course, the invention is not limited to this configuration, and it is entirely conceivable to provide a multitude of positions according to which more or less air passes through the tubes.

Thus, the ventilation system has a function for shutting off the air intake and a function for ventilating the exchangers in a compact space allowing better thermal management of a motor vehicle, since the grille is blower.

Depending on the orientation of the tubes, the system adjusts the air flow to the heat exchanger, which also optimizes the efficiency of the heat exchanger.

The closed position is advantageous for example when the vehicle is traveling, especially at high speed, since, in this position, the coefficient of drag of the vehicle is reduced, and its aerodynamics improved.

The open position is advantageous for example when the vehicle is stationary, since in this position, the ventilation of the engine compartment is improved.

FIGS. 4 to 7 illustrate variants of the ventilation device 2 and, more precisely, ventilation tubes 8 of this ventilation device 2.

In what follows, the ventilation tubes 8 are called aerodynamic tubes 8. It can be noted here that the shape of the ventilation tubes 8 is a priori independent of the configuration of the air intake manifolds.

According to the example of FIG. 4, an aerodynamic tube 8 has on at least one portion, preferably over substantially its entire length, a cross section as illustrated with a leading edge 37, a trailing edge 38 opposite to the leading edge 37 and, here, disposed opposite the heat transfer tubes 4, and a first and a second profile 42, 44, each extending between the leading edge 37 and the trailing edge 38. The edge of attack 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 minimum. The front of the section of the aerodynamic tube 8 can in turn be defined as the portion of the section of the aerodynamic tube 8 which is opposite - that is to say which is not opposite - of the heat exchanger 1. Similarly, the trailing edge 38 can 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 is opposite 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 direction of alignment of the row of aerodynamic tubes 8 and to the longitudinal direction of the aerodynamic tubes 8

In the example of FIG. 4, the leading edge 37 is free. Also in this figure, 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. 4 also has at least one opening 40 for ejecting a flow of air passing through the aerodynamic tube 8, outside the aerodynamic tube 8 and the air intake manifold 12, in particular substantially towards the heat exchanger 1. The opening or each opening 40 is for example a slot in an external wall 41 of the aerodynamic tube 8, the slot or slots extending for example in the direction of elongation of the aerodynamic tube 8 in which they are made. The total length of the opening 40 or openings can 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 in slot makes it possible to constitute a large air passage in the direction of the heat exchanger 1 without excessively reducing the mechanical resistance of the aerodynamic tubes 8.

In the following, only an opening 40 is described, it being understood that each opening 40 of the aerodynamic tube 8 can be identical to the opening 40 described.

The opening 40 is for example arranged near the leading edge 37. In the example of FIG. 4, the opening 40 is on the first profile 42. In this example, the second profile 44 has no opening 40. The opening 40 in the first profile 42 is configured so that the air flow ejected through the opening 40 flows along at least part 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 oriented upwards. Thus, alternatively, two neighboring aerodynamic tubes 8 are such that their first profiles 42 are opposite or, on the contrary, their second profiles 44 are opposite. The distance between two neighboring aerodynamic tubes 8 whose second profiles 44 are opposite each other is less than the distance between two neighboring aerodynamic tubes 8 whose first profiles 42 are vis-à-vis. The pitch between two neighboring aerodynamic tubes or the distance between the center of the geometric section of a first aerodynamic tube 8 and the center of the geometric section of a second aerodynamic tube 8, such as the first profile 42 of the first aerodynamic tube 8 either facing 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, the openings 40 of which face each other, the air flows ejected through these openings 40 thus create an air passage in which part, called induced air, of the ambient air is entrained. by suction.

It should be noted here that the air flow 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 ambient air in the created air passage, to obtain a flow of air sent to the heat transfer tubes 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 through the slots and the 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 in the direction of 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 between the aerodynamic tubes 8, which promotes the formation of a greater induced air flow.

The opening 40 is, in FIG. 4, delimited by lips 40a, 40b. The spacing e between the lips 40a, 40b, which defines the height of the 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 2 mm, preferably less than or equal to

1.5 mm, more preferably less than 0.9 mm, more preferably still less than or equal to 0.7 mm. The height of the slit is the dimension of this slit in the direction perpendicular to its length. The lower the height of the slot 40, the greater the speed of the air flow ejected through this slot. A high speed of the ejected air flow results in a high dynamic pressure. This dynamic pressure is then converted into static pressure in the mixing zone of the air flow ejected through the slot 40 and the induced air flow. This static pressure makes it possible to overcome the pressure drops due to the presence of the heat exchanger downstream of the ventilation device, in order to ensure a suitable air flow through the heat exchanger. These pressure drops due to the heat exchanger vary in particular as a function of the pitch of the heat transfer tubes and the pitch of the fins of the heat exchanger, as well as according to the number of heat exchange modules which can be superimposed in the heat exchanger. However, a too low slot height induces high pressure losses in the ventilation device, which implies using one or more oversized air propelling device (s). This can generate an 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 part 50 of the first profile 42. One end 51 of the inner lip 40b can extend, towards 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, in the direction of the leading edge 37, beyond the plane L normal to the free end of the outer lip 40a. The end 51 can then help direct the air flow circulating 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 circulating 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 the air flow along the first profile 42 can 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 to cling to it.

To do this, here, the maximum distance h between the first 42 and the second 44 profiles, measured along an alignment direction of the aerodynamic tubes 8, is downstream of the opening 40. The maximum distance h can 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 that is too small can cause significant pressure drops in the aerodynamic tube 8, which could make it necessary to implement a more powerful and therefore more bulky turbomachine. 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 that is too large limits the passage section between the aerodynamic tubes for the induced air flow. The total air flow to the heat exchanger is 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 convex part 50 can be arranged downstream of the opening 40 in the direction of ejection of the air flow. In particular, the curved part 50 can be contiguous with the internal lip 40b delimiting the opening 40.

Downstream of the convex part 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 in FIG. 4 comprises a first part 52 which is substantially rectilinear. The second profile 44 comprises, in the example illustrated in FIG. 4, a substantially rectilinear part 48, preferably extending over a majority of the length of the second profile 44. In the example of FIG. 4, the length 1 of the first rectilinear part 52, measured in a direction perpendicular to the longitudinal direction of the aerodynamic tube 8 and to the direction of alignment 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 to ensure the guiding of the flow of air ejected from the opening 40, which makes it possible to ensure greater air intake. The length of this first rectilinear part is however limited due to the corresponding size of the ventilation device and its consequences on the packaging of the ventilation device or of the heat exchange module.

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

The first profile 42 may comprise, as illustrated in FIG. 4, 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 straight part 48 of the second profile 44. The first profile 42 can also include a third straight part 54, downstream of the second straight part 38a of the first profile 42. The third straight part 54 can form a non-flat angle with the rectilinear part 48 of the second profile 44. The third rectilinear part 54 can extend, as illustrated, substantially up to a rounded edge connecting the third rectilinear part 54 of the first profile 42 and the rectilinear part 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 rectilinear part 48 of the second profile 44 extends in the example of FIG. 4 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 direction of alignment of the row of aerodynamic tubes 8. This direction corresponds, in the example of FIG. 4, substantially to the direction of the flow of the induced air flow. In this first 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. In fact, 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 air flow ejected through the opening 40 and the induced air flow, which mixes with this ejected air flow. However, too long a length of the cross section of the aerodynamic tube 8 poses a packaging problem for the ventilation device 2. In particular, the size of the heat exchange module can then be too large compared to the space which 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.

Furthermore, as illustrated in FIG. 4, the second rectilinear part 38a of the first profile 42 and the portion 38b of the rectilinear part 48 of the second profile 44 which faces it, are parallel. For example, the distance f between this second rectilinear part 38a and the portion 38b of the rectilinear part 48 of the second profile 44 can 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.

FIG. 4 also illustrates that the cross section (or geometric section) of the aerodynamic tube 8 defines a passage section S for the air flow passing through the aerodynamic tube 8. This passage section S is here defined by the walls of the aerodynamic tube 8 and by the segment extending in the direction of alignment of the aerodynamic tubes 8 between the second profile 44 and the tip of the end 51 of the internal 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 section for the passage of the air flow in the aerodynamic tube 8 makes it possible to limit the pressure drops which would have the consequence of having to oversize the turbomachine used to obtain a flow of air ejected through the desired opening 40. However, a large passage section induces a large bulk of the aerodynamic tube 8. Thus, with fixed pitch aerodynamic tubes, a larger passage section may harm the passage section of the induced air flow between the aerodynamic tubes 8 , thus not making it possible to obtain a satisfactory total air flow rate, directed towards the heat transfer tubes 4.

In order to obstruct the flow of air to the heat transfer tubes 4 and the fins as little as possible, the ventilation device 2 provided with such aerodynamic tubes 8 is advantageously arranged so that each aerodynamic tube 8 faces each other. screw of the front face connecting the first and second flat walls of a corresponding heat transfer tube 4. More particularly, the trailing edge 38 of each aerodynamic tube 8 is included in the volume delimited by the first and second longitudinal plane walls of the corresponding heat transfer tube 4.

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

In particular, the distance f separating the second rectilinear part 38a from the first profile 42 and the portion 38b from the rectilinear part 48 of the second profile 44 which faces it, is substantially equal to the distance separating the first longitudinal wall and the second longitudinal wall of the heat transfer tube 4 opposite 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 separating the second straight portion 38a of the first profile 42 and the portion 38b of the straight 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 transfer tube opposite which the aerodynamic tube 8 is disposed.

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

In the examples of FIGS. 5, 6 and 7, the aerodynamic conduits 8 are substantially rectilinear, mutually parallel 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 chord 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 produced on the first profile 42, which is configured so that a air flow leaving the first opening 42 flows along at least part of the first profile 42. Likewise, at least one second opening 40 is present on the second profile 44, which is configured so that a air flow leaving the second opening 40 flows along at least part of the second profile 44. As for the example in FIG. 4, this can be achieved here by implementing the Coanda effect.

For the same reasons as those given for the example of FIG. 4, 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 less or equal to 80 mm. In particular, the length c can be equal to 60 mm.

The openings 40 are similar to those of the example in FIG. 4. In particular, the distance e separating the internal 40b and external 40a lips from each opening 40 can 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 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 FIG. 4, an air passage entraining the ambient air is created between each pair of neighboring aerodynamic tubes 8, produced according to one of FIGS. 5 to 7.

The pitch between two neighboring aerodynamic tubes 8 can, in this case, be greater than or equal to 15 mm, preferably greater than or equal to 20 mm, more preferably still 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 air flow does not allow an induced air flow to be created over the entire pitch between the neighboring aerodynamic tubes.

The pitch between two neighboring aerodynamic tubes 8 can in particular be defined as the distance between the center of the cross section of two neighboring 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 can in particular be one of the leading edge 37, the trailing edge 38 or the top of the convex part 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 . In fact, the speed peak of the air speed profile in the vicinity of the profile tends to reduce as it moves away from the opening 40 in the aerodynamic tube. An absence of peak indicates a homogeneous mixture of the air flow ejected through the opening 40 and the induced air flow. It is preferable that such a homogeneous mixture is produced before the air flow arrives on the aerodynamic tubes. Indeed, an incident air flow on the heat transfer tubes, heterogeneous, does not allow optimal cooling of the heat transfer tubes and induces higher pressure drops. 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. 7, 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 strictly decreases towards the edge of 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 of the air flow ejected through the opening 40. Preferably, the first and second profiles 42, 44 each form an angle of between 5 and 10 ° with the cord CC of symmetry of the cross section of the aerodynamic tube 8.

Therefore, unlike the example of Figure 4, the aerodynamic profile of Figure 7 does not include a portion delimited by first and second opposite planar walls parallel. 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. 5, the trailing edge 38 is formed by the top joining two rectilinear symmetrical portions 60 of the first profile 42 and of the second profile 44 of each aerodynamic tube 8. According to the variant of FIG. 5, the 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 °, in particular less than 90 °.

On the contrary, in the variant of FIG. 6, 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 a formed by the rectilinear portions 60 is here greater than 90 °, in particular greater than 180 °.

Figure 8 illustrates a variant 100 of the heat exchange module of Figure

1. In this variant 100, the third heat exchanger 1 is arranged below the first and second heat exchangers 1a, 1b, which are themselves arranged opposite one another. The ventilation device 2 is then placed under the propeller fan 3, in the direction of alignment of the conduits 8, in the same plane parallel to the planes of the first, second and third heat exchangers 1a, 1b, 1. More precisely, the ventilation device 2 is then placed opposite the third heat exchanger 1, while the propeller fan 3 is arranged opposite the first and second heat exchangers 1a, 1b, so the second heat exchanger lb is interposed between the first heat exchanger la and the propeller fan 3. It is thus possible to size the propeller fan according to the cooling needs of the first and second heat exchangers la, lb, while the ventilation device 2 is dimensioned as a function of the cooling needs of the only third heat exchanger.

In variant 200 of FIG. 9, the ventilation device 2 and the propeller fan are arranged substantially in the same plane, one above the other. The first, second and third heat exchangers 1a, 1b, 1 are arranged in three parallel planes so that the second heat exchanger 1b is interposed between the first heat exchanger 1a and the third heat exchanger 1. In addition, this third heat exchanger 1 is of reduced dimensions compared to the first and second heat exchangers 1a, 1b, so that it extends opposite an end portion, only, of the first and second heat exchangers la, lb. Advantageously, in this case, the ventilation device 2 is arranged opposite the third heat exchanger 1, while the propeller ventilation device 3 is arranged opposite the portion of the first and second heat exchangers 1a, 1b which are not opposite the third heat exchanger 1.

FIG. 10 shows an example of a heat exchange module 10 intended to equip a motor vehicle, according to another embodiment, particularly suitable for a hybrid or electric vehicle, in particular with very rapid mode of charging the battery. electric.

In fact, this very fast charging mode involves very high electrical powers (more than 300 kW) and a very significant heat peak (more than 10 kW) is generated at the level of the battery.

This heat peak must be evacuated in particular thanks to the front panel heat exchangers, even when the vehicle is stationary.

The system of FIG. 10 advantageously makes it possible to increase the air flow rate passing through the heat exchange surfaces without thoroughly reviewing the front face, as will be detailed.

As can be seen from this figure, the ventilation device 2 and the propeller fan 3 extend one after the other and are positioned opposite the heat exchanger 1.

In FIG. 10, the ventilation device 2 is arranged upstream of the propeller fan 3.

Of course, it is possible to provide the propeller fan 3 upstream of the ventilation device 2.

Advantageously, the surface delimited by the tubes 8, that is to say the ventilation surface of the ventilation device 2, is preferably of the same order of magnitude as the ventilation surface of the propeller fan 3.

As shown in FIG. 10, the exchange module 10 can comprise means for securing the propeller fan 3 to the ventilation device 2.

Preferably, the exchange module 10 comprises means for controlling a power supply for the ventilation device 2 and a power supply for the propeller fan 3 configured to independently control the ventilation device 2 and the propeller fan 3.

For example, when the exchange module 10 equips an electric vehicle, during the recharging of the electric battery, and in particular during a rapid recharging, it is advantageous to operate that of the ventilation device 2 and of the propeller fan 3 which is the most powerful, or both at the same time, in order to effectively cool the battery.

This may be all the more necessary when the vehicle is also occupied by passengers who demand thermal comfort, for which the heat exchanger (s) are used, for example by activating the air conditioning in the passenger compartment. vehicle.

Preferably, the ventilation device 2 is more powerful than the propeller fan 3.

When the vehicle is traveling, the air power required for the heat exchangers is lower, and, advantageously, only the propeller fan 3 operates while the ventilation device 2 is stopped.

As a variant or in addition, the angular position of the tubes 8 is chosen according to the ventilation power required for cooling the exchanger.

According to another possible variant shown in FIG. 10a, the ventilation device 2 is arranged upstream of the at least one heat exchanger 1 relative to the direction of flow of the air flow generated in the direction of said at least one heat exchanger. heat 1, and the propeller fan 3 is arranged downstream of the heat exchanger 1.

The invention is not limited to the embodiments presented and other embodiments will be apparent to those skilled in the art. In particular, the different examples can be combined, as long as they are not contradictory.

Claims (16)

1. Ventilation system intended to generate at least one air flow through at least one heat exchanger (1; la; lb) of a motor vehicle, comprising at least one propeller fan (3) and a device for ventilation (2), the ventilation device (2) comprising ducts (8) intended to be supplied with air flow by at least one air propulsion device, distinct from the propeller fan (3), each duct ( 8) having at least one opening (16; 40) for ejecting an air flow passing through said duct (8), substantially towards said at least one heat exchanger (1; la; lb). 2. Ventilation system according to claim 1, the ventilation device (2) further comprising at least one air intake manifold (12), each duct (8) opening at one of its ends in a separate orifice of the at least one air intake manifold (12), the conduits (8) being intended to be supplied with an air flow by said at least one air propulsion device, via the at least one air manifold air intake (12), said at least one ejection opening (16; 40) of the ducts (8) being distinct from the ends of the corresponding duct (8), said at least one ejection opening (16; 40) being located outside the at least one air intake manifold (12). 3. Ventilation system according to claim 1 or 2, wherein the ducts (8) of the ventilation device (2) form a row of ducts (8) extending substantially in a foreground. 4. The ventilation system according to claim 3, wherein the ventilation device (2) and the propeller fan (3) extend substantially in the same plane as the first plane. 5. Ventilation system according to claim 4, wherein the ventilation device (2) and the propeller fan (3) extend substantially one next to the other. 6. The ventilation system according to claim 4, wherein the ventilation device (2) and the propeller fan (3) extend substantially one above the other, in the direction of alignment of the row of ducts (8) of the ventilation device (2). 7. Ventilation system according to one of claims 1 to 3, wherein the ventilation device (2) and the propeller fan (3) extend one after the other relative to the direction of flow of the air flow (F) generated towards said at least one heat exchanger (1). 8. Ventilation system according to the preceding claim, wherein the ventilation device (2) is arranged upstream relative to the propeller fan (3). 9. Ventilation system according to the preceding claim, in which: the ventilation device (2) is arranged upstream of the at least one heat exchanger (1) and the propeller fan (3) is arranged downstream of the at least one heat exchanger (1). 10. Ventilation system according to one of the preceding claims, in which at least one of the conduits (8) is pivotally mounted. 11. A cooling system for a motor vehicle, comprising at least one heat exchanger (1; la; lb) and a ventilation system according to any one of the preceding claims. 12. Cooling system according to claim 11, comprising at least a first heat exchanger (1) and at least a second heat exchanger (la; lb) arranged substantially in the same plane, one next to the other , the ventilation device (2) being arranged opposite said at least one first heat exchanger (1) and said propeller fan (3) being arranged opposite said at least one second heat exchanger heat (la; lb). 13. Cooling system according to claim 11, comprising at least a first heat exchanger (1) and at least a second heat exchanger (la; lb) arranged substantially in the same plane, one below the other , the ventilation device (2) being arranged opposite said at least one first heat exchanger (1) and said propeller fan (3) being arranged opposite said at least one second heat exchanger heat (la; lb). 14. Cooling system according to claim 11, comprising at least a first heat exchanger (1) and at least a second heat exchanger (la; lb) arranged substantially in two separate planes, the ventilation device (2) being disposed facing said at least one first heat exchanger (1) and said propeller fan (3) being arranged at least partially facing said at least one second heat exchanger (la; lb), said at least one first heat exchanger (1) being located between said at least one second heat exchanger (la; lb) and said ventilation device (2). 15. The cooling system as claimed in claim 11, in which the ventilation device (2) and said propeller fan (3) are arranged upstream of the at least one heat exchanger (1) relative to the direction of flow of the air flow generated towards said at least one heat exchanger (1). 16. The cooling system according to claim 11, in which: the ventilation device (2) is arranged upstream of the at least one heat exchanger (1) relative to the direction of flow of the air flow generated in the direction of said at least one heat exchanger (1), and said propeller fan (3) is arranged downstream of the at least one heat exchanger (1) relative to the direction of flow of said air flow. 1/6 FIG. 1 12a FIG. 2 2/6 FIG. 3 FIG. 4 3/6 '50 FIG. 6 4/6 100 1b FIG. 9 5/6 6/6 FIG. 11 FIG. 12 FRENCH REPUBLIC National registration number FA 848117 FR 1850811 EPO FORM 1503 12.99 (P04C14) irai - I NATIONAL INSTITUTE PROPERTY INDUSTRIAL PRELIMINARY SEARCH REPORT based on the latest claims filed before the start of the search DOCUMENTS CONSIDERED AS RELEVANT Category Citation of the document with indication, if necessary, of the relevant parts X US 4,516,406 A (GENTRY SAMUEL H [US] ET AL) May 14, 1985 (1985-05-14) Y * figures 1-3 * W0 2017/098765 Al (SOKEN INC [JP]; DENSO CORP [JP]) June 15, 2017 (2017-06-15) * figures 1, 2 * JP 2015 001155 A (CALSONIC KANSEI CORP) January 5, 2015 (2015-01-05) * figure 1 * US 3,926,000 A (SCOFIELD CARLIE D) December 16, 1975 (1975-12-16) * figure 1 * US 5,181,554 A (MITA YOSHIYUKI [JP]) January 26, 1993 (1993-01-26) * figures 1-5 * Research completion date October 2, 2018 CATEGORY OF DOCUMENTS CITED X: particularly relevant on its own Y: particularly relevant in combination with another document in the same category A: technological background O: unwritten disclosure P: intermediate document Relevant claim (s) 1.3 to 16 1-16 1-16 Classification attributed to the invention by ΙΊΝΡΙ B60H1 / 00 B60K11 / 08 F28F9 / 24 F01P5 / 02 TECHNICAL AREAS SOUGHT (IPC) F28D F28F F01P B60K F04D Examiner Delaitre, Maxime T: theory or principle underlying the invention E: patent document with a date prior to the filing date and which was only published on that filing date or on a later date. D: cited in the request L: cited for other reasons &: member of the same family, corresponding document ANNEX TO THE PRELIMINARY RESEARCH REPORT RELATING TO THE FRENCH PATENT APPLICATION NO. FR 1850811 FA 848117 This appendix indicates the members of the patent family relating to the patent documents cited in the preliminary search report referred to above. The said members are contained in the computer file of the European Patent Office on the date of 02 - Lu ^- 2018 The information provided is given for information only and does not engage the responsibility of the European Patent Office or the French Administration