WO2022171687A1

WO2022171687A1 - Cooling module for a motor vehicle, with additional evaporative cooling device

Info

Publication number: WO2022171687A1
Application number: PCT/EP2022/053150
Authority: WO
Inventors: Amrid MAMMERI; Kamel Azzouz; Sebastien Garnier; Issiaka Traore
Original assignee: Valeo Systemes Thermiques
Priority date: 2021-02-11
Filing date: 2022-02-09
Publication date: 2022-08-18
Also published as: FR3119645B1; FR3119645A1

Abstract

Cooling module (22) for an electric or hybrid motor vehicle (10), said cooling module (22) being designed to be traversed by an air flow (F) and comprising at least one heat exchanger (24, 26, 28, 29), said cooling module (22) further comprising an evaporative cooling device (90), said evaporative cooling device (90) comprising: – a meshed surface (91) arranged upstream of at least one heat exchanger (24, 26, 28, 29) and designed to be traversed by the air flow (F), – a device (92) for distributing by gravity a cooling fluid onto the meshed surface (91), said distribution device (92) being arranged on an edge of said meshed surface (91).

Description

Motor vehicle cooling module with additional evaporative cooling device

The present invention relates to a cooling module for a motor vehicle, in particular for an electric or hybrid vehicle.

A cooling module (or heat exchange module) of a motor vehicle conventionally comprises at least one heat exchanger and a ventilation device adapted to generate an air flow in contact with the at least one heat exchanger. The ventilation device thus makes it possible, for example, to generate a flow of air in contact with the heat exchanger, when the vehicle is stationary or at low driving speed.

In electric or hybrid motor vehicles, it is common to have several heat exchangers arranged in cascade, i.e. arranged one behind the other in the air flow. This arrangement makes it possible to limit the space necessary for these heat exchangers, in particular at the level of the front face of the motor vehicle. However, this arrangement has the counterpart that the most downstream heat exchangers are crossed by an air flow having already crossed at least one heat exchanger further upstream. The air flow passing through these downstream heat exchangers is thus, for example, hotter and thus their cooling performance is reduced. This is for example the most impactful for heat exchangers such as condensers connected within an air conditioning type cooling circuit to cool an air flow to the passenger compartment.

A known solution to remedy this drop in cooling performance is to increase the size and therefore the cooling surface of the heat exchangers. However, this solution is expensive, increases the weight of the cooling module and can be difficult to apply due to the reduced space, for example at the front face of the motor vehicle.

One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose an improved cooling module.

The present invention therefore relates to a cooling module for an electric or hybrid motor vehicle, said cooling module being intended to be traversed by a flow of air and comprising at least one heat exchanger, said cooling module further comprising a device for evaporative cooling, said evaporative cooling device comprising:

- a meshed surface arranged upstream of at least one heat exchanger and intended to be crossed by the air flow,

- A device for distributing a cooling fluid by gravity on the mesh surface, said distribution device being arranged on an edge of said mesh surface. According to one aspect of the invention, one of the heat exchangers is a condenser connected to a cooling circuit, the mesh surface being arranged within the cooling module upstream of said condenser.

According to another aspect of the invention, the evaporative cooling device further comprises:

- a coolant manifold arranged on an edge of the mesh surface opposite the distribution device,

- a coolant reservoir connected on the one hand to the distribution device and on the other hand to the coolant manifold, and

- A pump so as to bring the cooling fluid from the cooling fluid collector to the reservoir.

According to another aspect of the invention, the meshes of the meshed surface have an opening comprised between 1 and 3mm.

According to another aspect of the invention, the mesh surface is a flexible surface.

According to another aspect of the invention, the mesh surface is a textile fabric.

According to another aspect of the invention, the fibers of the textile fabric have a diameter of between 0.5mm and 1.5mm.

According to another aspect of the invention, the mesh surface is a burlap.

According to another aspect of the invention, the mesh surface is a canvas of coconut fiber.

According to another aspect of the invention, the evaporative cooling device comprises a mesh surface retraction system so that said mesh surface is movable between a retracted position and a deployed position upstream of the at least one heat exchanger heat.

According to another aspect of the invention, the retraction system comprises:

- a winding roller attached to an edge of the mesh surface and arranged on the periphery of the at least one heat exchanger, in the retracted position, said mesh surface being wound around the winding roller,

- an actuator for rotating the winding roller.

According to another aspect of the invention, the retraction system comprises at least one mesh surface guide so as to guide said mesh surface when passing from one position to another. Other characteristics and advantages of the present invention will appear more clearly on reading the following description, provided by way of illustration and not limitation, and the appended drawings in which:

[Fig 1] Figure 1 shows a schematic representation of the front of a motor vehicle in side view, [Fig 2] Figure 2 shows a schematic representation in perspective and in partial section of the front of a motor vehicle and a cooling module,

[Fig 3] Figure 3 shows a schematic representation of thermal management circuits,

[Fig 4] Figure 4 shows a schematic representation in semi-transparent perspective of a cooling module according to a first embodiment,

[Fig 5] Figure 5 shows a schematic representation of a cooling device,

[Fig 6] Figure 6 shows a schematic representation in semi-transparent perspective of a cooling module according to a second embodiment in the retracted position,

[Fig 7] Figure 7 shows a schematic representation in semi-transparent perspective of a cooling module according to the second embodiment in the deployed position,

[Fig 8] Figure 8 shows a schematic representation in semi-transparent perspective of a cooling module according to the second embodiment in the intermediate position.

In the various figures, identical elements bear the same reference numbers.

The following achievements are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference is to the same embodiment, or that the features apply only to a single embodiment. Simple features of different embodiments may also be combined and/or interchanged to provide other embodiments.

In the present description, it is possible to index certain elements or parameters, such as for example first element or second element as well as first parameter and second parameter or else first criterion and second criterion, etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria that are close, but not identical. This indexing does not imply a priority of one element, parameter or criterion over another and such denominations can easily be interchanged without departing from the scope of the present description. Nor does this indexing imply an order in time, for example, to assess such and such a criterion.

In the present description, the term “placed upstream” means that one element is placed before another with respect to the direction of circulation of an air flow. Conversely, “placed downstream” means that one element is placed after another in relation to the direction of circulation of a flow.

In FIGS. 1, 2, 4, 6, 7 and 8, an XYZ trihedron is represented in order to define the orientation of the various elements with respect to each other. A first direction, denoted X, corresponds to a longitudinal direction of the vehicle. It also corresponds to the direction opposite to the direction of travel of the vehicle. A second direction, denoted Y, is a lateral or transverse direction. Finally, a third direction, denoted Z, is vertical. The directions, X, Y, Z are orthogonal two by two. In the present description, “low” or “low” means the position of one element relative to another in the direction Z determined above.

In Figures 1 and 2, the cooling module according to the present invention is illustrated in a functional position, that is to say when it is arranged within a motor vehicle.

FIG. 1 schematically illustrates the front part of an electric or hybrid motor vehicle 10 which may comprise an electric motor 12. The vehicle 10 notably comprises a body 14 and a bumper 16 carried by a chassis (not shown) of the vehicle automobile 10. The body 14 defines a cooling bay 18, that is to say an opening through the body 14. The cooling bay 18 is unique here. This cooling bay 18 is preferably located in the lower part of the front face 14a of the bodywork 14. In the example illustrated, the cooling bay 18 is located under the bumper 16. A grille 20 can be arranged in the cooling bay 18 to prevent projectiles from passing through the cooling bay 18. A cooling module 22 is arranged opposite the cooling bay 18. The grid 20 makes it possible in particular to protect this cooling module 22.

As shown in Figure 2, the cooling module 22 is intended to be traversed by an air flow F parallel to the direction X and going from the front to the rear of the vehicle 10. This direction X corresponds more particularly to a longitudinal direction X running from the front to the rear of the cooling module 22. In the present application, an element is referred to as "upstream" or "downstream" according to the longitudinal direction X of the cooling module 22 , an element that is respectively arranged further forward or backward than another element. The front corresponds to the front of the motor vehicle 10 in the assembled state or else the face of the cooling module 22 through which the air flow F is intended to enter the cooling module 22. to him at the rear of the motor vehicle 10 or else to the face of the cooling module 22 through which the air flow F is intended to come out of the cooling module 22.

The cooling module 22 includes at least one heat exchanger 24, 26, 28, 29 as shown in Fig.2. The at least one heat exchanger 24, 26, 28, 29 is more particularly arranged within a set of heat exchangers 23. This set of heat exchangers 23 may more particularly comprise a first heat exchanger 24 , a second heat exchanger 26 and a third heat exchanger 28.

The first heat exchanger 24 is in particular configured to dissipate heat energy in the air flow F. This first heat exchanger 24 can more particularly be a condenser of a cooling circuit A (visible in FIG. 3) allowing the cooling of the batteries of the vehicle 10. This cooling circuit A can also be configured to allow the thermal management of an air flow intended for the passenger compartment. In this case, the cooling circuit A may be a particularly reversible air conditioning circuit. The first heat exchanger 24 can thus be an evapo-condenser as part of a reversible air conditioning circuit (not shown). The second heat exchanger 26 is also configured to release heat energy into the air flow F. This second heat exchanger 26 can more particularly be a radiator connected to a thermal management circuit C (visible in FIG. 3 ) of electrical elements such as the electric motor 12.

The third heat exchanger 28 is itself configured to be a sub-cooler connected within the cooling circuit A. This third heat exchanger 28 is thus also configured to dissipate heat energy in the air flow. f.

In the example illustrated in FIG. 2, the set of heat exchangers 23 comprises a fourth heat exchanger 29, also configured to release heat energy into the air flow F. This fourth heat exchanger 29 can more particularly also be a low temperature radiator. This fourth heat exchanger 29 can be connected to the thermal management circuit C in parallel with the second heat exchanger 26 as illustrated in FIG. 3. However, it is quite possible to imagine an embodiment (not shown) wherein the fourth heat exchanger 29 is connected to another thermal management circuit dedicated for example to cooling the power electronics.

Still according to FIG. 2, the cooling module 22 essentially comprises a casing or shroud 40 forming an internal channel between two opposite ends 40a, 40b and inside which the set of heat exchangers 23 is arranged. is preferably oriented parallel to the longitudinal direction X so that the upstream end 40a is oriented towards the front of the vehicle 10 facing the cooling bay 18 and so that the downstream end 40b is oriented rearward of the vehicle 10.

The cooling module 22 also comprises a first manifold housing 41 disposed downstream of the set of heat exchangers 23 in the longitudinal direction X of the cooling module 22. This first manifold housing 41 comprises an outlet 45 of the air flow F, This first collector box 41 thus makes it possible to recover the flow of air passing through the set of heat exchangers 23 and to direct this flow of air towards the outlet 45. The first collector box 41 can come from material with the fairing 40 or else be an added part fixed to the downstream end 40b of said fairing 40.

The cooling module 22 can also comprise at least one tangential fan, also called tangential turbomachine 30, configured so as to generate the air flow F intended for the set of heat exchangers 23. The tangential turbomachine 30 comprises a rotor or turbine (or tangential propeller) not shown. The turbine has a substantially cylindrical shape. The turbine advantageously comprises several stages of blades (or blades). The turbine is mounted rotating around an axis of rotation A, for example parallel to the direction Y. The diameter of the turbine is for example between 35 mm and 200 mm to limit its size. The turbomachine 30 is thus compact.

The tangential turbomachine 30 can also comprise a motor 31 configured to set the turbine in rotation. The motor 31 is for example adapted to drive the turbine in rotation, at a speed of between 200 revolutions/min and 14,000 revolutions/min. This makes it possible in particular to limit the noise generated by the tangential turbomachine 30.

The tangential turbomachine 30 is preferably arranged in the first manifold housing 4L. The tangential turbomachine 30 is then configured to suck in air in order to generate the air flow F passing through the set of heat exchangers 23. The first housing collector 41 then forms a volute in the center of which is arranged the turbine and whose air evacuation at the outlet 45 of the first collector box 41 allows the outlet of the air flow F.

In the example illustrated in FIG. 2, the tangential turbomachine 30 is in a high position, in particular in the upper third of the first manifold housing 41, preferably in the upper quarter of the first manifold housing 4L. This makes it possible in particular to protect the turbomachine tangential 30 in the event of submersion and/or to limit the size of the cooling module 22 in its lower part.

It is nevertheless possible to imagine that the tangential turbomachine 30 is in a low position, in particular in the lower third of the first collector box 4L. This would make it possible to limit the size of the cooling module 22 in its upper part. Alternatively, the tangential turbomachine 30 can be in a middle position, in particular in the middle third of the height of the first manifold box 41, for example for reasons of integration of the cooling module 22 in its environment.

In addition, in the example illustrated in Figure 2, the tangential turbomachine 30 operates in suction, that is to say it sucks in the ambient air so that it passes through the set of heat exchangers 23 Alternatively, the tangential turbomachine 30 can operate by blowing, blowing the air towards the set of heat exchangers 23. For this, the tangential turbomachine 30 will be arranged upstream of the set of heat exchangers 23.

The cooling module 22 may also include a second manifold box 42 arranged upstream of the set of heat exchangers 23. This second manifold box 42 includes an inlet 42a for the flow of air F coming from outside the vehicle 10. The inlet 42a may in particular be arranged opposite the cooling bay 18. This inlet 42a may also comprise the protective grid 20. The second collector box 42 can be made in one piece with the fairing 40 or else be an attached part fixed to the upstream end 40a of said fairing 40. In addition, the inlet 42a of the second collector box 42 may include a front face shutter device (not shown) configured to allow the flow of air F coming from outside the vehicle 10 to pass through said first inlet 42a in an open state and closing off said first airflow inlet 42a in a closed state. The front face closure device can be in different forms, such as for example in the form of a plurality of flaps mounted to pivot between an open position and a closed position within a frame. The shutters can be flag type shutters but other types of shutters such as butterfly shutters are quite possible.

FIG. 3 shows a schematic representation of the cooling circuit A and of the thermal management circuit C to which the first 24, second 26 and third 28 heat exchangers are connected.

Inside the thermal management circuit C, shown in dotted lines, is intended to circulate a heat transfer fluid. The thermal management circuit C can thus comprise, in the direction of circulation of a heat transfer fluid, a pump 80, a first cooler 82 and the second heat exchanger 26. The first cooler 82 can in particular be a heat exchange interface by example arranged at the level of electrical elements such as the electric motor 12 and/or power electronics in order to manage their temperature.

As stated above, in the example illustrated in Figure 3, the thermal management circuit C may also include the third heat exchanger 29. The third heat exchanger 29 is here connected to the thermal management circuit C in parallel with the second heat exchanger 26. In Figure 3, the cooling circuit A is shown for its part in solid lines. Within this cooling circuit A is intended to circulate a refrigerant fluid. The cooling circuit A comprises, in the direction of circulation of the refrigerant fluid, a compressor 60 and the first heat exchanger 24, configured to be a condenser intended to be traversed by the flow of air F. Downstream of the first heat exchanger 24, the cooling circuit A includes the third heat exchanger 28 configured to be a sub-cooler. Downstream of the third heat exchanger 28, the cooling circuit A comprises a first expansion device 63 and a second cooler 64 in particular dedicated to the thermal management of the batteries. The second cooler 64 can be an evaporator for direct cooling of the batteries or else, as illustrated in FIG. 3, a two-fluid heat exchanger arranged jointly on an annex loop B for indirect cooling of the batteries.

This annex loop B may in particular comprise a pump 70 and a thermal management interface 72, for example a cold plate, in contact with the batteries. The annex loop B may also include a bypass B' for bypassing the fifth heat exchanger 67 comprising a valve 74 in order, for example, to achieve homogenization of the temperature of the batteries. The cooling circuit A may comprise a bypass branch A' connected in parallel with the first expansion device 63 and the first cooler 64. This bypass branch A' comprises a second expansion device 66 disposed upstream of a third cooler 67 This third cooler 67 may in particular be an evaporator intended to be traversed by a flow of air intended for the passenger compartment.

Between the first 24 and the third 28 heat exchanger, the cooling circuit A comprises a dehydrating bottle 61. This dehydrating bottle 61 is in particular connected within the cooling circuit A downstream of the first heat exchanger 24, between said first exchanger heat exchanger 24 and the third heat exchanger 28, in the direction of circulation of the refrigerant fluid circulating in said cooling circuit A.

As shown in Figures 2 and 3, the third heat exchanger 28 is arranged, within the set of heat exchangers 23, the most upstream in the longitudinal direction X of said cooling module 22. This allows this last to benefit from the “freshest” air of the air flow F. The third heat exchanger 28 can thus perform its function of sub-cooling the refrigerant fluid circulating in the cooling circuit A efficiently. The coefficient of performance of the cooling circuit A is thus high and its cooling power is sufficient to ensure, for example, both the cooling of an air flow intended for the passenger compartment and the cooling of the batteries.

Still as illustrated in Figures 2 and 3, the second heat exchanger 26 is arranged, within the set of heat exchangers 23, upstream of the first heat exchanger 24 in the longitudinal direction X of the cooling module 22, within the set of heat exchangers 23. More particularly, the second heat exchanger 26 and the third heat exchanger 28 can be arranged on the same plane within the set of heat exchangers 23, in upstream of the first heat exchanger 24 in the longitudinal direction X of the cooling module 22. This thus allows the second 26 and the third 28 heat exchanger to be both furthest upstream in the longitudinal direction X of the cooling module 22 Thus, both the second 26 and the third 28 heat exchanger benefit from the “freshest” air in order to dissipate heat energy as efficiently as possible.

Preferably, the cumulative height of the second 26 and of the third 28 heat exchanger is substantially equal to that of the first heat exchanger 24. This thus makes it possible to maintain a set of heat exchangers 23 in which each layer or stratum of of heat has similar dimensions. This also makes it possible to limit the number of heat exchangers that the air flow F passes through and therefore this limits the pressure drops. It is thus for example possible to add the fourth heat exchanger 29 downstream of the first heat exchanger 24 in the air flow F. Still according to FIGS. 2 and 3, the third heat exchanger 28 is preferably arranged under the second heat exchanger 26. By “arranged under” is meant here that in the mounted state within the motor vehicle 10, the third heat exchanger 28 is located closer to the ground relative to the second heat exchanger 26.

As illustrated in Figure 4, within the cooling module, the dehydrating bottle 61 is arranged in an upstream part of the cooling module 22 in the longitudinal direction X from the front to the rear of said cooling module 22. More Specifically, the dehydrating bottle 61 extends along an axis perpendicular to the longitudinal direction X of the cooling module 22.

As illustrated in Figure 4, Tat least one heat exchanger 24, 26, 28, 29 arranged furthest upstream in the longitudinal direction X of said cooling module 22, here the second heat exchanger 26, and the dehydrating bottle 61 can be arranged on the same plane. This allows in particular that the cooling module 22 has a reduced size.

More particularly, the dehydrating bottle 61 can be arranged so that its axis, here transverse axis Y, is perpendicular to the axis Z of the height of said at least one heat exchanger 24, 26, 28, 39. The dehydrating bottle 61 is then "lying" below or above said at least one heat exchanger 24, 26, 28, 39.

In the case where the cooling module 22 comprises two heat exchangers, here the second 26 and the third 28 heat exchanger, arranged on the same plane and arranged furthest upstream in the longitudinal direction X of said cooling module 22, the dehydrating bottle 61 can be arranged between said heat exchangers 26, 28, or else below or above the assembly formed by these two heat exchangers 26, 28.

Still as illustrated in FIG. 4, the cooling module 22 also comprises a device for cooling 90 by evaporation. This cooling device 90 by evaporation comprises in particular a mesh surface 91 as well as a device 92 for distributing a cooling fluid by gravity.

The mesh surface 91 is more particularly arranged within the cooling module 22 at the level of the set of heat exchangers 23 upstream of at least one heat exchanger 24, 26, 28,29. The mesh surface 91 is also arranged in a plane substantially parallel to the heat exchangers 24, 26, 28, 29 so that the latter is intended to be traversed by the flow of air F. The mesh surface 91 can thus have a shape rectangular complementary to the shape of the heat exchangers 24, 26, 28, 29.

The distribution device 92 by gravity is placed on an edge of said mesh surface 91. More particularly, the distribution device 92 is placed on the upper edge of the mesh surface 91 so that the cooling fluid, generally of water, either driven by gravity and capillarity over the whole of the mesh surface 91. The dispensing device 92 can in particular be connected to a reservoir (not shown) in which the cooling fluid is stored. According to a particular mode, the dispensing device 92 and the reservoir can form a single piece. In order to allow the cooling fluid to flow over the whole of the mesh surface 91, the distribution device 92 can extend over the entire upper edge of the mesh surface 91. The distribution device 92 can for example be a regularly perforated pipe in which the cooling fluid passes and arranged along the upper edge of the mesh surface 91.

The presence of this cooling device 90 makes it possible to cool the air flow F before the latter passes through the heat exchanger 24, 26, 28, 29 disposed downstream of the mesh surface 91. Indeed, the evaporation cooling fluid absorbs heat energy from the airflow F as it passes through the mesh surface 91.

This is more particularly advantageous when the heat exchanger 24 is a condenser connected to the cooling circuit A. Indeed, such a condenser 24 requires the most "cool" air flow possible in order to be the most efficient and therefore example allow good thermal comfort within the passenger compartment. Thus, as illustrated in Figure 4, the mesh surface 91 is arranged within the cooling module 22 upstream of said condenser 24.

As shown in FIG. 5, the evaporative cooling device 90 may also comprise a cooling fluid collector 93. This cooling fluid collector 93 is more particularly arranged on an edge of the mesh surface 91 opposite the distribution device 92 in order to recover the non-evaporated cooling fluid. The coolant manifold 93 is also connected to the coolant reservoir (not shown). The cooling fluid reservoir is thus connected on the one hand to the distribution device 92 and on the other hand to the cooling fluid collector 93. The cooling device 90 also comprises a pump 94 so as to bring the cooling fluid from the coolant manifold 93 to the reservoir. This saves coolant and recycles unevaporated coolant.

So that the cooling fluid can evaporate within the meshed surface 91, the meshes of the latter may in particular have an opening comprised between 1 mm and 3 mm. The mesh surface 91 can more particularly be a flexible surface such as for example a textile fabric. This textile fabric may in particular comprise fibers having a diameter of between 0.5 mm and 1.5 mm. These fibers may in particular be permeable to the cooling fluid to improve the efficiency of the cooling device 90. The mesh surface 91 may thus be a burlap or even a coconut fiber canvas. As shown in Figures 6 to 8, the evaporative cooling device 90 may also include a system 95 for retracting the mesh surface 91. The mesh surface 91 is then movable between a retracted position (Figure 6) and an extended position. (Figure 7) upstream of the at least one heat exchanger 24, 26, 28,29. This thus makes it possible, during cooling of the air flow F by the cooling device 90, to limit the pressure drops of said air flow F. The mesh surface 91 can also be in an intermediate position, illustrated in Figure 8 in which the mesh surface 91 does not cover the entire surface of the heat exchanger 24, 26, 28, 29 disposed downstream. This is particularly useful for cooling the airflow locally and partially as needed while limiting the increase in pressure drops.

Still as illustrated in Figures 6 to 8, when the mesh surface 91 is flexible, the retraction system 95 may in particular comprise a winding roller integral with an edge of the mesh surface 91 and arranged on the periphery of the at least one heat exchanger heat 24, 26, 28,29. In the retracted position, the mesh surface 91 is wound around the winding roller as shown in Figure 6. The retraction system 95 then also includes an actuator (not shown) for rotating the winding roller.

Because the mesh surface 91 is mobile, the retraction system 95 may comprise at least one guide of the mesh surface 91 so as to guide said mesh surface 91 when passing from one position to another. This guide can for example be one or more guide rails in which the mesh surface 91 slides. Another example of a guide can be one or more tensioned cables, the mesh surface 91 comprising one or more eyelets through which said cables pass. .

Thus, it is clear that the cooling device 90 allows cooling of the air flow F before the latter passes through a heat exchanger 24, 26, 28, 29. This cooling of the air flow makes it possible to increase the temperature difference between the air flow F and the heat exchanger 24, 26, 28, 29 and thus increase the performance of said heat exchanger 24, 26, 28, 29.

Claims

[Claim 1] Cooling module (22) for an electric or hybrid motor vehicle (10), said cooling module (22) being intended to be traversed by a flow of air (F) and comprising at least one heat exchanger ( 24, 26, 28, 29), characterized in that it further comprises an evaporative cooling device (90), said evaporative cooling device (90) comprising:

- a mesh surface (91) arranged upstream of at least one heat exchanger (24, 26, 28,29) and intended to be crossed by the air flow (F),

- a distribution device (92) by gravity of a cooling fluid on the mesh surface (91), said distribution device (92) being arranged on an edge of said mesh surface (91).

[Claim 2] Cooling module (22) according to the preceding claim, characterized in that one of the heat exchangers (24) is a condenser connected to a cooling circuit (A), the mesh surface (91) being arranged within the cooling module (22) upstream of said condenser (24).

[Claim 3] Cooling module (22) according to any one of the preceding claims, characterized in that the evaporative cooling device (90) further comprises:

- a coolant manifold (93) arranged on an edge of the mesh surface (91) opposite the distribution device (92),

- a coolant reservoir connected on the one hand to the distribution device (92) and on the other hand to the coolant manifold (93), and

- a pump (94) so as to bring the cooling fluid from the cooling fluid manifold (93) to the reservoir.

[Claim 4] Cooling module (22) according to one of the preceding claims, characterized in that the meshes of the mesh surface (91) have an opening of between 1 and 3 mm.

[Claim 5] Cooling module (22) according to any one of the preceding claims, characterized in that the mesh surface (91) is a flexible surface.

[Claim 6] Cooling module (22) according to the preceding claim, characterized in that the mesh surface (91) is a textile fabric.

[Claim 7] Cooling module (22) according to the preceding claim, characterized in that the fibers of the textile fabric have a diameter of between 0.5mm and 1.5mm.

[Claim 8] Cooling module (22) according to any one of the preceding claims, characterized in that the evaporative cooling device (90) comprises a system (95) for retracting the mesh surface (91) so that said mesh surface (91) is movable between a retracted position and a deployed position upstream of the at least one heat exchanger (24,

26, 28,29).

[Claim 9] Cooling module (22) according to the preceding claim with any one of Claims 5 to 7, characterized in that the retraction system (95) comprises:

- a winding roller secured to an edge of the mesh surface (91) and arranged on the periphery of the at least one heat exchanger (24, 26, 28,29), in the retracted position, said mesh surface (91) being wrapped around the winding roller,

- an actuator for rotating the winding roller.

[Claim 10] Cooling module (22) according to any one of claims 8 or 9, characterized in that the retraction system (95) comprises at least one mesh surface guide so as to guide said mesh surface ( 91) when moving from one position to another.