EP2810009B1 - Cooling radiator for a vehicle, particularly a motor vehicle - Google Patents

Description

The invention relates to a cooling radiator for a vehicle, in particular an automobile. It may in particular be radiators for cooling the engine of the vehicle. An exchanger according to the preamble of claim 1 is known from US 2012/0024510 . Cooling radiators are known comprising a bundle of parallel tubes and two collectors (or manifolds) in which the corresponding ends of the tubes are connected in a fixed and sealed manner. A cooling fluid can thus flow through the tubes and exchange heat with an external air flow passing between the tubes. For this, the radiators are placed on the front of the vehicle and the air flow reaches the radiator passing through the calender.

Many solutions have already been proposed to increase the thermal performance of such exchangers. It is in particular known to provide their corrugation tubes to disrupt the flow of the fluid. Indeed, having a turbulent flow improves the heat exchange.

However, such a solution increases the pressure losses generated by the exchanger. It leads in this way to oversize pumps to be used to ensure the flow of fluid in the engine cooling circuit.

At the same time, it has already been proposed heat exchangers having tube pitches, that is to say a spacing between the tubes, relatively reduced. It should be noted that such a characteristic also has the disadvantage of generating pressure drops, this time on the air.

There is thus a need for a cooling radiator having improved thermal performance while controlling the pressure losses generated on the fluid or fluids exchanging heat through the radiator.

The invention proposes for this purpose a cooling radiator for a vehicle, in particular an automobile, according to claim 1. By "flat tube" is meant a tube comprising two large parallel flat faces connected by lateral sides or radii, the total height of the tube, that is to say, its dimension in the direction perpendicular to the large flat faces, being less than the total width of the tube, that is to say its dimension in the direction perpendicular to the total height of the tube and the longitudinal axis of the tube.

A particularly advantageous embodiment of the invention is based on the link made by the applicant between the operating characteristics of the pumps used in the cooling loops and the characteristics of the radiator for optimizing their operation.

The figure 1 illustrates the overall efficiency "e" of a pump according to the flow "D" of fluid it generates. It is observed that the efficiency begins to grow until a certain flow rate before decreasing. In other words, there is a flow rate value for which the efficiency of the pump is maximum, here about 4000 liters per hour.

The figure 2 illustrates the "P" pressure of the fluid leaving the pump as a function of the flow "D" that it generates. It is observed that the pressure decreases with the flow rate.

In order to optimize the overall energy efficiency of the vehicle, it is advantageous to operate the pump in its zone of maximum efficiency. By plotting this value on the curve of the figure 2 the corresponding pressure at the outlet of the pump is then known, which makes it possible to determine an optimum overall pressure drop for the cooling circuit.

The pressure drop due to the other circuit components such as the engine or the circulation channels between the engine and the cooling radiator being known or specified, it is possible to evaluate a corresponding pressure drop for the radiator.

That being so, it has been demonstrated by the applicant that a parameter influencing in particular the pressure drop generated by a radiator as defined above is the profile of the tube and even more specifically the internal height h _T of the tube. "Internal height" means the distance between the inner walls of the flat faces of the tube or the height of the fluid circulation blade in the tube, such a distance being measured at a portion of the walls not exhibiting corrugations.

The curves 3 and 4 illustrate in this way the relationship between this parameter and, respectively, the outlet pressure of the pump and the overall efficiency of the latter.

The invention thus proposes a radiator in which the tubes have an internal height of between 0.6 and 1.5 mm, more particularly between 0.8 and 1.2 mm. In fact, we can see figure 4 that the pump operates optimally in this value range.

• une épaisseur de matière des tubes est inférieure ou égale à 270 µm, particulièrement 230 µm, encore plus particulièrement 200 µm,
• les corrugations sont configurées de façon à représenter moins de 10% du volume interne des tubes,
• les tubes présentent une largeur comprise entre 10 et 45 mm,
• les tubes présentent :
  • soit une largeur inférieure à 24 mm et une hauteur interne supérieure ou égale à 1 mm,
  • soit une largeur supérieure à 24 mm et une hauteur interne inférieure à 1 mm,
• les corrugations sont issues de matière d'une paroi des tubes,
• les corrugations présentent une extrémité libre,
• lesdits tubes sont formés par pliage d'une feuille de matière.

According to other features of the invention, which may be taken together or separately:

• a material thickness of the tubes is less than or equal to 270 μm, particularly 230 μm, more particularly 200 μm,
• the corrugations are configured to represent less than 10% of the internal volume of the tubes,
• the tubes have a width of between 10 and 45 mm,
• the tubes present:
  • a width less than 24 mm and an internal height greater than or equal to 1 mm,
  • a width greater than 24 mm and an internal height of less than 1 mm,
• the corrugations come from material of a wall of the tubes,
• the corrugations have a free end,
• said tubes are formed by folding a sheet of material.

• La figure 1 déjà évoquée illustre l'efficacité globale d'une pompe en fonction du débit de fluide générée par celle-ci.
• La figure 2 déjà évoquée illustre la pression du fluide en sortie de la pompe de la figure 1 en fonction du débit de fluide générée par celle-ci.
• La figure 3 déjà évoquée reprend la figure 2 en l'associant à la hauteur interne d'un tube d'un radiateur de refroidissement.
• La figure 4 déjà évoquée reprend la figure 1 en l'associant à la même caractéristique que celle utilisée dans la figure 3.
• La figure 5 est une vue d'ensemble d'un radiateur de refroidissement conforme à l'invention.
• La figure 6 est une vue de coupe transversale d'un tube de l'échangeur de la figure 5.

The appended figures will make it clear how the invention can be realized. In these figures, identical references designate similar elements.

• The figure 1 already mentioned illustrates the overall efficiency of a pump as a function of the flow of fluid generated by it.
• The figure 2 already mentioned illustrates the pressure of the fluid at the outlet of the pump of the figure 1 depending on the fluid flow generated by it.
• The figure 3 already mentioned takes over the figure 2 by associating it with the internal height of a tube of a cooling radiator.
• The figure 4 already mentioned takes over the figure 1 by associating it with the same characteristic used in the figure 3 .
• The figure 5 is an overview of a cooling radiator according to the invention.
• The figure 6 is a cross-sectional view of a tube of the exchanger of the figure 5 .

As illustrated in figure 5 the invention relates to a cooling radiator 1 for a vehicle, in particular an automobile, comprising a beam for exchanging heat between a first and a second fluid. The first fluid consists, for example, of a cooling fluid such as a mixture of water and glycol. The second fluid consists, for example, of air.

Said radiator may be configured to be placed on the front face of a motor vehicle so as to be swept by a flow of ambient air passing through a radiator grille of the vehicle.

Said beam comprises a row of tubes 2, parallel to each other, for the flow of the first fluid. Said tubes 2 extend in a longitudinal direction marked A in the figure. Each tube 2 here has two longitudinal ends 2A fixedly and sealingly connected to manifolds 3, 4 of the radiator for the circulation of said first fluid through said radiator.

Said manifolds 3, 4 comprise, for example, a header plate and a lid defining an interior volume of the box. The tubes 2, in particular the longitudinal ends 2A of the tubes 2, open into said interior volume through orifices provided in the collector plates. To these manifolds 3, 4 can be reported fastening flanges, not shown. They may also comprise, respectively, inlet and outlet pipes 5 and 6.

The collector plates of said collector boxes 3, 4 are, for example metal, including aluminum or aluminum alloys. The covers are, for example, plastic and crimped on the collector plates. Alternatively, the collector plates and lids are both metal, especially aluminum or aluminum alloys.

Between the tubes 2 may be arranged interlayers 7 increasing the heat exchange surface between the fluid flowing in the tubes 2 and the air flowing between said tubes 2. The tubes 2 and the spacers 7 are here stacked alternatively in the direction B, perpendicular to the axis A in the plane of the figure.

The radiator may also include lateral cheeks 8 protecting the beam on either side of the stack of tubes 2 and tabs 7.

As illustrated in figure 6 said tubes 2 are flat. As already said, this means that the tubes 2 comprise two large flat faces 10a, 10b, parallel, connected by lateral sides or radii 12. It is still understood that the height of the tubes 2, that is to say that is, their dimension in the direction perpendicular to the planar faces 10a, 10b, which corresponds to the stacking direction B of the tubes 2 and the spacers 7, is smaller than the width L _{T of} said tubes 2, that is to say their dimension in the direction perpendicular to the direction B and the longitudinal axis A of the tubes 2, the latter being orthogonal to the plane of the figure.

The tubes 2 are, for example, of the type comprising a strip 14, folded on itself so as to define a plurality of channels 16a, 16b for circulating the fluid.

Said tubes 2 may in particular have a configuration in which said strip 14 has legs 18a, 18b joining a first 10a to the second 10b of said flat faces of the tube so as to define said channels 16a, 16b. By this is meant that the free ends of said legs 18a, 18b are in contact with said second planar face 10b.

As this is more easily seen at the figure 6 , said legs 18a, 18b have, for example, a base formed of a bent portion 20 of the strip 14 connecting them to the first planar face 10a. They are extended here against each other to finish against the second flat face 10b, especially via their edge. Here they define two channels 16a, 16b of substantially equal section. In other words, said legs 18a, 18b are located along a median plane of the tubes 2. The latter substantially have a substantially B-shaped profile in this way.

Such tubes 2 are sealed, for example, by soldering, the brazing of the tubes 2 of the same exchanger taking place, in particular, simultaneously with the brazing of all the metal parts of the exchanger. In this regard, said sheet of material 14 is, for example, aluminum or aluminum alloy.

That said, according to the invention, said tubes 2 are provided with corrugations 22 configured to disrupt the flow of said first fluid. Corrugations 22 means shapes having a protruding profile towards the channel or channels 16a, 16b defined by said tubes 2. At the figure 6 , some of said corrugations 22 are in the cutting plane while others are located behind.

The corrugations 22 may be derived from material of a wall of the tube, that is to say, here the strip 14. They are formed, for example, by stamping said strip 14. They are located, in particular, at the planar faces 10a, 10b of the tubes. Said corrugations 22 have, for example, a free end (26). By this is meant that they are not in contact with the opposite planar face 10a, 10b or with any other of said corrugations 22.

• Sfd la section frontale des corrugations, c'est-à-dire, la surface de la partie de la section du ou des canaux de circulation 16a, 16b du tube obstruée par les corrugations 22,
• Stl la section interne du tube lisse (Stl), c'est-à-dire, la section qu'aurait le tube sans ses corrugations 22,

le ratio Sfd / Stl est compris entre 20 et 40%. Une telle relation est vérifiée, par exemple, tout au long du tube ou à tout le moins pour toutes sections du tube coupant une ou des corrugations.For each tube, said corrugations 22 are configured, for example, to represent 10 to 50% of the section of the tube. In other words, either:

• Sfd the frontal section of the corrugations, that is to say, the surface of the part of the section of the circulation channel (s) 16a, 16b of the tube obstructed by the corrugations 22,
• Stl the internal section of the smooth tube (Stl), that is to say, the section that would have the tube without its corrugations 22,

the Sfd / Stl ratio is between 20 and 40%. Such a relationship is verified, for example, throughout the tube or at least for all sections of the tube cutting one or corrugations.

• Vtd, le volume total des corrugations 22 à l'intérieur du tube,
• Vtl, le volume interne total du tube,

le ratio Vtd / Vtl est inférieure à 0,1, de préférence à 0,05.For each tube, said corrugations 22 may still be configured to represent less than 10% of the internal volume of the tube. In other words, either:

• Vtd, the total volume of corrugations 22 inside the tube,
• Vtl, the total internal volume of the tube,

the ratio Vtd / Vt1 is less than 0.1, preferably 0.05.

Still according to the invention, said tubes 2 are furthermore spaced apart in the direction B by a pitch Tp (visible at figure 5 ), said no tubes, between 5 and 8 mm. Said tube pitch is between 6 and 7 mm.

By using tubes 2 provided with such corrugations 22 and having such a pitch of tubes, the performance of the radiator is already optimized.

To further improve this result, it will further be possible to choose tubes 2 having an internal height h _T of between 0.6 and 1.5 mm, more particularly between 0.8 and 1.2 mm.

By internal height is meant as already said the distance between the inner walls 24a, 24b of the flat faces 10a, 10b of the tubes 2 or the blade height of circulation of the first fluid in said tubes 2, such a distance being measured at the part of the walls showing no corrugations 22.

Said tubes 2 may have a material thickness e _T less than 270 μm, more particularly 230 μm, more particularly 200 μm.

• soit une largeur L_T inférieure à 24 mm et une hauteur interne e_T supérieure à 1 mm,
• soit une largeur L_T supérieure à 24 mm et une hauteur interne e_T inférieure à 1 mm.

Different beam widths can be used. The tubes 2 thus have, for example, a width L _T of between 10 and 40 mm, in particular between 14 and 34 mm. More particularly, the tubes 2 may have:

• a width L _T less than 24 mm and an internal height e _T greater than 1 mm,
• a width L _T greater than 24 mm and an internal height e _T less than 1 mm.

It should be noted that said corrugations 22 may have on the surface of the tube 2 any possible distributions or shapes. They may thus, for example, be arranged in rows or staggered on the same flat face 10a, 10b and / or a flat face 10a, 10b to another. They may also be circular or elongated sections, forming or not at the same angle or different angles relative to the longitudinal axis A of the tubes.

Claims (9)

1. Cooling radiator for a vehicle, in particular a motor vehicle, comprising a bundle allowing heat exchange between a first and a second fluid, the said bundle comprising at least one row of parallel tubes (2) for the flow of the first fluid, the said tubes (2) being provided flat and spaced from one another by a spacing Tp, termed tube spacing, in a first direction, the said tubes (2) being provided with corrugations (22) configured to disturb the flow of the said first fluid, and the said tube spacing being between 6 and 7 mm, characterized in that the corrugations (22) are configured so as to represent 20 to 40% of the cross section of the tubes (2).
2. Radiator according to Claim 1, in which the tubes (2) have an internal height between 0.6 and 1.5 mm.
3. Radiator according to either one of the preceding claims, in which the tubes (2) have a width L_T of between 10 and 45 mm.
4. Radiator according to any one of the preceding claims, in which the tubes have:

   - either a width L_T which is less than 24 mm and an internal height h_T which is greater than or equal to 1 mm,

   - or a width L_T which is greater than 24 mm and an internal height h_T which is less than 1 mm.
5. Radiator according to any one of the preceding claims, in which the corrugations (22) are formed integrally from a wall of the tubes (2).
6. Radiator according to any one of the preceding claims, in which the corrugations (22) have a free end (26).
7. Radiator according to any one of the preceding claims, in which the said tubes (2) are formed by folding a sheet of material (14).
8. Radiator according to any one of the preceding claims, in which a thickness of material e_T of the tubes (2) is less than or equal to 270 µm.
9. Radiator according to any one of the preceding claims, in which the corrugations (22) are configured so as to represent less than 10% of the internal volume of the tubes (2).

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