FR3111977A1 - Heat exchanger comprising a section reduction member of a manifold. - Google Patents

Abstract

Title: Heat exchanger comprising a section reduction member of a collector. The present invention relates to a heat exchanger (1) for a motor vehicle comprising at least one heat exchange bundle (2) consisting of a plurality of plates (3) nested one inside the other in a stacking direction (E ), the heat exchange bundle (2) comprising a first circuit (20) intended to be traversed by a heat transfer liquid and comprising at least a first inlet manifold (44a) and a second circuit intended to be traversed by a refrigerant fluid and comprising a second inlet manifold, at least one reduction member (48) extends in the volume defined by the first inlet manifold (44a). [figure 4]

Description

Heat exchanger comprising a member for reducing the section of a collector.

The present invention relates to the field of heat exchangers, in particular intended to equip air conditioning systems and/or motor vehicle cooling systems.

In the automotive field, it is common to have to modify the temperature of a component, such as an electric motor, a battery, a calorie and/or cold storage device or the like. To this end, the motor vehicle is equipped with a heat exchanger which comprises a heat exchange bundle within which is arranged a refrigerant circuit, within which a refrigerant fluid circulates, and a liquid circuit coolant, inside which circulates a coolant liquid. In order to circulate the refrigerant fluid and the heat transfer liquid in the heat exchange bundle, the refrigerant fluid circuit and the heat transfer liquid circuit respectively comprise a plurality of chambers and a plurality of channels. The plurality of chambers is then supplied with heat transfer liquid, by means of a first inlet manifold, while the plurality of channels is supplied with refrigerant fluid, by means of a second inlet manifold.

In order to carry out the heat exchanges between the heat transfer liquid and the refrigerant, each of the channels is arranged alternately with each of the chambers, so that a chamber is framed on either side by a channel.

A problem with such a heat exchanger is that the flow of the heat transfer liquid in the plurality of chambers is not distributed evenly. Indeed, it has been observed by the inventors that the flow of coolant liquid is not distributed identically in each of the chambers of the heat exchange bundle. This effect of the distribution of the heat transfer liquid in each of the chambers tends to reduce the heat exchanges with the refrigerant fluid, in the least supplied chambers.

The object of the present invention is to respond at least in part to the problem set out above by optimizing the distribution of the flow of the heat transfer liquid in each of the chambers of the first circuit of the heat exchange bundle.

The invention relates to a heat exchanger for a motor vehicle comprising at least one heat exchange bundle consisting of a plurality of plates nested one inside the other in a stacking direction E, the heat exchange bundle comprising :

• a first circuit intended to be traversed by a heat transfer liquid and comprising a first inlet manifold through which the heat transfer liquid is admitted into the heat exchanger and a first outlet manifold through which the heat transfer liquid leaves the heat exchanger, the first circuit comprising a plurality of chambers hydraulically connected to the first inlet manifold and to the first outlet manifold,
• a second circuit intended to be traversed by a refrigerant fluid and comprising a second inlet manifold through which the refrigerant fluid is admitted into the heat exchanger and a second outlet manifold through which the refrigerant fluid leaves the heat exchanger, the second circuit comprising a plurality of channels hydraulically connected to the second inlet manifold and second outlet manifold,

the heat exchanger being configured to implement a heat exchange between the heat transfer liquid circulating in the plurality of chambers and the refrigerant fluid circulating in the plurality of channels,

characterized in that the heat exchanger comprises at least one section reduction member of the first inlet manifold along the stacking direction.

The heat exchanger can be a heat exchanger configured for cooling at least one component of a motor vehicle, such as an electrical storage device and can also equip an air conditioning system of said motor vehicle. In order to implement the heat exchanges between the heat transfer liquid and the coolant, the plurality of chambers and the plurality of channels are arranged, in the heat exchange bundle, alternately. In other words, each of the chambers is arranged alternately with each of the channels in the stacking direction of the plates.

The section reduction member of the first inlet manifold is arranged in such a way that it decreases the volume defined by the first inlet manifold, and this for example in a progressive manner along the stacking direction of the plates . More specifically, the purpose of the reduction member is to reduce the section of the first inlet manifold as one advances in said first inlet manifold along the stacking direction of the plates, from the entry of the first inlet manifold, that is to say the arrival of the heat transfer liquid, to a closed end of the first inlet manifold, delimited by at least one plate. Advantage is taken of such a reduction member in that it makes it possible to homogenize the flow of heat transfer liquid in each of the chambers of the heat exchange bundle, in the sense that the chambers formed at the level of the inlet of the first inlet manifold require a greater quantity of heat transfer liquid than the chambers provided at a distance from the inlet of the first inlet manifold, in order to be supplied in a similar manner with the latter.

According to an exemplary embodiment of the invention, the reduction member is a conical part. Advantage is taken of such a structure of the reduction member in that its profiled shape allows a regular and progressive reduction of the sections which define the first inlet collector.

According to an example of the invention, the conical piece comprises a base and an apex opposite each other along a main direction of elongation of the reduction member and between which extends a peripheral wall of the piece conical.

According to an example of the invention, a main direction of elongation of the reduction member is parallel to the stacking direction of the plurality of plates of the heat exchange bundle.

According to an example of the invention, each of the plurality of plates of the heat exchange bundle comprises a bottom wall surrounded by a raised edge and the plurality of plates are distributed into a bundle body which is comprised between a first end plate and a second end plate opposed to each other along the stacking direction of the plates, each of the bottom walls of the plates of the bundle body comprises at least one opening which delimits at least in part the volume of the first inlet manifold, the bottom wall of the first end plate comprising at least one opening for inlet of the heat transfer liquid in the first inlet manifold and the second end plate presenting its wall bottom which extends in line with the openings of the plates of the bundle body, the reduction member being integral with the bottom wall of the second end plate.

It is understood from such a characteristic that the reduction member is arranged in the first inlet manifold such that its top faces the first inlet opening of the first end plate. Thus, when using the heat exchanger, the coolant entering the first inlet manifold through the inlet opening is first in contact with the top of the reduction member, then licks the peripheral wall of the reduction member down to its base, secured to the bottom wall of the second end plate.

According to an example of the invention, the first inlet manifold extends over a length parallel to the stacking direction of the plates and the reduction member extends over an axial dimension measured along its direction of main elongation, the axial dimension of the reduction member being at most equal to the length of the first inlet manifold. Section reduction member and first inlet manifold are thus aligned along the same direction, the reduction member being housed inside the first inlet manifold.

According to an example of the invention, the axial dimension of the conical part is equal to plus or minus 2% to the length of the first inlet manifold, axial dimension and length being measured along the same direction.

According to an example of the invention, the axial dimension of the conical piece is strictly less than the length of the first inlet manifold.

It is understood from the preceding characteristics that the reduction member is limited to the first inlet manifold in its main direction of elongation.

According to an example of the invention, the first inlet manifold has a section of the first inlet manifold and the base of the conical part has a section of the base strictly less than the section of the first inlet manifold. This ensures that the conical part can easily be installed in the manifold. It is also guaranteed that the heat transfer liquid can penetrate into the chambers which are close to this base, the latter not obstructing the entire first inlet manifold.

The section of the first inlet collector and the section of the base are taken along a direction perpendicular to the stacking direction of the plates of the heat exchange bundle.

According to an example of the invention, the section of the base of the conical piece is between 20% and 80% of the section of the first inlet manifold.

According to an example of the invention, at least one of the section of the first inlet manifold or the section of the base of the conical piece is a circular section. Advantageously, the section of the first inlet manifold and the section of the base are circular sections.

According to an example of the invention, the peripheral wall of the conical part extends at an angle relative to a central axis of the conical part, the angle being between 10° and 60°.

According to an example of the invention, the conical part is provided with at least one member which protrudes from the peripheral wall of the conical part.

According to an example of the invention, the member which protrudes from the conical part is configured to change the direction of the heat transfer liquid circulating within the first inlet manifold.

More specifically, the heat-transfer liquid enters the first inlet manifold along a first direction that is substantially rectilinear and parallel to the stacking direction of the plates. The member which emerges from the peripheral wall then has the function of modifying this first direction of the heat-transfer liquid into a second direction of the secant heat-transfer liquid from the first direction.

It is understood that such a characteristic of the reduction member comprising the member which projects from the conical part makes it possible to optimize the distribution of the heat transfer liquid in each of the chambers of the heat exchange bundle, along the direction stacking plates.

According to an example of the invention, the member is a spiral helix which extends over at least part of the axial dimension of the conical piece. It is then understood that the spiral helix modifies the first direction of circulation of the heat transfer liquid in the second direction of circulation, substantially spiral.

According to an example of the invention, the member extends from the base of the conical part to the top of said conical part. This guarantees a change in the direction of the flow of coolant from one end of the conical part to the other.

According to an example of the invention, the section reduction member of the first inlet manifold along the stacking direction is made of aluminum or an aluminum alloy.

According to an example of the invention, the section reduction member of the first inlet manifold along the stacking direction is brazed simultaneously with the heat exchange bundle.

According to an example of the invention, the section reduction member of the first inlet manifold along the stacking direction is made of a synthetic material.

The invention also relates to a system for thermal management of at least one passenger compartment of a motor vehicle and/or of an electrical energy storage device of the motor vehicle and/or of control means of an electric motor propelling the motor vehicle, comprising at least one heat exchanger according to any one of the preceding characteristics.

According to an example of the thermal management system, the heat transfer liquid is glycol water.

Other characteristics and advantages of the invention will become apparent through the description which follows on the one hand, and several embodiments given by way of indication and not limiting with reference to the appended diagrammatic drawings on the other hand, on which :

is a schematic perspective view of a heat exchanger according to the invention;

is a view in section along a vertical and longitudinal plane of the heat exchange bundle of FIG. 1 comprising at least one member for reducing the section of the first inlet manifold;

is a schematic perspective view of a plate of a heat exchange bundle of the heat exchanger of FIG. 1;

is a close-up sectional view along a vertical and longitudinal plane of the first inlet manifold comprising the reduction member according to a first embodiment of the invention;

is a close-up sectional view along a vertical and longitudinal plane of the first inlet manifold comprising the reduction member according to a second embodiment of the invention;

is a close-up view in vertical section of the first inlet manifold comprising the reduction member according to a third embodiment of the invention.

represents a thermal management installation which is capable of modifying a temperature of a passenger compartment of a motor vehicle and/or of an electrical energy storage device of the motor vehicle and/or of control means of an electric motor propelling the motor vehicle, the installation comprising a heat exchanger shown in the preceding figures.

It should first be noted that if the figures expose the invention in detail for its implementation, they can of course be used to better define the invention if necessary. It should also be noted that, in all the figures, similar elements and/or fulfilling the same function are indicated by the same numbering.

In the following description, a direction of a longitudinal axis L, a direction of a transverse axis T, and a direction of a vertical axis V are represented by a trihedron (L, V, T) in the figures. We define a horizontal plane as being a plane perpendicular to the vertical axis, a longitudinal plane as being a plane perpendicular to the transverse axis, and a transverse plane as being a plane perpendicular to the longitudinal axis.

Figure 1 shows in perspective a heat exchanger 1 according to the invention, used in particular to cool in particular the cells of an electric battery. This heat exchanger 1 could also be used to cool and/or heat other components located in a motor vehicle.

The heat exchanger 1 implements an exchange of calories between a coolant 7 and a coolant 5, the coolant 7 then being cooled by the coolant 5. The coolant 7 is glycol water.

The refrigerant 5 is for example carbon dioxide or a refrigerant known by the acronym R134A or 1234YF.

Referring to Figure 1, the heat exchanger 1 comprises a heat exchange bundle 2 formed by a stack of plates 3, superimposed on each other along a stacking direction E, parallel to the axis vertical V. The heat exchanger 1, and therefore the bundle 2, comprises a first longitudinal end 4 and a second longitudinal end 6 opposite the first longitudinal end 4 along the longitudinal axis L. The first longitudinal end 4 and the second end longitudinal 6 are opposite with respect to a center 8 of the heat exchanger 1.

The heat exchanger 1, and therefore the bundle 2, comprises a first transverse end 10 and a second transverse end 12 opposite the first transverse end 10 along the transverse axis T. The first transverse end 10 and the second transverse end 12 are opposite with respect to the center 8 of the heat exchanger 1.

The beam 2 comprises a first end plate 14 and a second end plate 16 which delimit the beam 2 along the stacking axis E. Between these two end plates 14, 16 are arranged the plates 3 which forms a beam body 18 and which delimit two separate circulation circuits: a first circulation circuit 20 configured to be traversed by the heat transfer liquid 7 and a second circulation circuit 22 configured to be traversed by the refrigerant fluid 5.

As seen in Figure 2, illustrating a sectional view along the vertical plane A-A visible in Figure 1, two immediately adjacent plates 3 define a chamber 24 or a channel 26, where the heat transfer liquid and the fluid can circulate respectively. refrigerant 5. The chambers 24 arranged for the circulation of the coolant fluid, alternate with the channels 26 arranged for the circulation of the refrigerant fluid. Thus, a first plate 3 can be arranged for the circulation of the heat transfer liquid in collaboration with a second adjacent plate 3, and be arranged for the circulation of the refrigerant fluid in collaboration with a third adjacent plate 3. The same plate 3 is thus licked on one side by the heat transfer liquid and on the other by the refrigerant.

All of the chambers 24 participate in forming at least in part the first circuit 20. All of the channels 26 participate in forming at least in part the second circuit 22.

As visible in Figure 3, each plate 3 has the shape of a bathtub, that is to say it comprises a bottom wall 28 surrounded by a raised edge 30. The bottom wall 28 has a shape rectangle with rounded corners. The raised edge 30 surrounding the bottom wall 28 extends continuously all around the plate 3.

Plates 3 are stacked on top of each other, an upper face 32 of a first plate 3 facing a lower face of an adjacent second plate. Similarly, a lower face of the first plate 3 faces an upper face of an adjacent third plate.

The plates 3 are manufactured by stamping, stamping or rolling a strip of material designed to allow sufficient heat exchange to allow the heat exchanger 1 to fulfill its role. It may in particular be aluminum or an aluminum alloy.

According to an example of the invention, the plates 3 can comprise at least one disturbance device 36 illustrated in FIG. 3 and arranged to disturb the circulation of the liquid circulating along the plates 3. This makes it possible to improve the heat exchanges between the heat transfer liquid and the refrigerant. The disturbance device 36 is for example made from material with the plates 3, that is to say they form a single block of material with the plate 3 on which it is formed. The disturbance device 36 can therefore be derived from the manufacturing process of the plate 3, and is for example stamped at the same time as the plate 3.

The disturbance device 36 is provided on the upper face 32 and on the lower face of the bottom wall 28 of the plate 3 along the vertical axis V and extends between the first longitudinal end 4 and the second longitudinal end 6 of the plate 3. In the example illustrated in Figure 3, the disturbance device 36 takes the form of chevrons, that is to say a succession of V-shaped grooves seen in a plane perpendicular to the vertical axis V , i.e. in the horizontal plane.

Each plate 3 of the harness body 18 further comprises openings 38. In the example of the invention, the plates 3 of the harness body 18 each comprise four openings, arranged at each of the corners of the plate 3 and arranged in the bottom wall 28. Plates 3 thus have a first opening 38a, a second opening 38b, a third opening 38c and a fourth opening 38d. The openings 38 have a circular shape and are through.

The first end plate 14 also comprises at least a first inlet opening 40 for the heat transfer liquid 7, visible in FIG. 2, a second refrigerant inlet opening, not visible, while the second end plate 16 comprises at least a first outlet opening 43 of the heat transfer liquid, visible in Figure 2, and a second outlet opening of the coolant.

All of the openings 38 of the plates 3 of the body of the bundle 18, of the first end plate 14 and of the second end plate 16 are arranged to allow the passage of the heat transfer liquid and of the refrigerant fluid into the bundle 2 d heat exchange.

Referring to Figure 3, the first opening 38a is arranged at the angle of the first longitudinal end 4 and the first transverse end 10 of the heat exchanger. When the plates 3 are stacked and form the bundle 2, the first openings 38a are then aligned with each other and form a first inlet collector 44a for the coolant liquid in the first circuit 20, visible in FIG. 2. The first collector of inlet 44a is bordered by the contour of the first openings 38a, the first end plate 14 and the second end plate 16. The first inlet manifold 44a therefore has the shape of a right cylinder of circular section. The first inlet manifold 44a makes it possible to distribute the heat transfer liquid in the chambers 24 partly forming the first circuit 20.

As illustrated in Figure 3, the second opening 38b is arranged at the angle of the first longitudinal end 4 and the second transverse end 12 of the heat exchanger. When the plates 3 are stacked and form the bundle 2, the second openings 38b are then aligned with each other and form the second inlet manifold 44b of the refrigerant fluid of the second circuit 22, visible in FIG. 1. The second inlet manifold 44b is bordered by the outline of the second openings 38b, the first end plate 14 and the second end plate 16. The second inlet manifold 44b therefore has the shape of a right cylinder of circular section and makes it possible to distribute the fluid refrigerant in the channels 26 forming part of the second circuit 22.

Referring to Figure 3, the third opening 38c is arranged at the angle of the second longitudinal end 6 and the second transverse end 12 of the heat exchanger. When the plates 3 are stacked and form the bundle 2, the third openings 38c are then aligned with each other and form a second outlet manifold 46b, visible in FIG. 1, of the refrigerant fluid in the second circuit 22. The second outlet manifold 46b is bordered by the contour of the third openings 38c, the first end plate 14 and the second end plate 16. It therefore has the shape of a right cylinder of circular section. The second outlet manifold 46b collects the coolant distributed in the plurality of channels 26 and sends it outside the second circuit 22 of the heat exchange beam 2.

As shown in Figure 3, the fourth opening 38d is arranged at the angle of the second longitudinal end 6 and the first transverse end 10 of the heat exchanger. When the plates 3 are stacked and form the beam 2, the fourth openings 38d are then aligned with each other and form a first outlet manifold 46a for the heat transfer liquid, visible in FIG. 2. The first outlet manifold 46a is bordered by the contour fourth openings 38d, the first end plate 14 and the second end plate 16. It therefore has the shape of a right cylinder of circular section and makes it possible to collect the heat transfer liquid distributed in the plurality of chambers 24 and from the send outside the first circuit 20 of the heat exchange beam 2.

It is then understood that the inlet manifolds 44a, 44b ensure the entry of the coolant liquid and of the refrigerant fluid respectively into the chambers 24 and into the channels 26 of the heat exchange bundle 2 and that the outlet manifolds 46a, 46b ensure the exit of said heat transfer liquid and of said coolant from said chambers 24 and said channels 26.

In order to ensure a homogeneous distribution of the heat transfer liquid within each of the chambers 24 which make up the heat exchange bundle 2, at least one reduction member 48, visible in FIG. 2, of section of the first inlet collector 44a along the stacking direction E of the plates 3 is formed in said first inlet manifold 44a. Indeed, it has been noticed by the inventors that the distribution of the flow of heat transfer liquid from the first inlet manifold 44a to each of the chambers 24 was not homogeneous, in the sense that the quantity of heat transfer liquid is greater at as one moves away from the input of said first input collector 44a. The reduction member 48 will be detailed later in the following detailed description, in particular in Figures 4 to 6.

To obtain the bundle 2 of plates 3, the various plates 3 are stacked in the stacking direction E. All of the plates 3 are then brazed using a process of brazing by passing through an oven. This step secures the different plates 3 together.

In the example of the invention, the inlet openings 40 and the outlet openings 43 formed at the level of the first end plate 14 and of the second end plate 16 are arranged in line with the openings 38 of the plates 3 of the beam body 18. The first end plate 14 thus comprises the first inlet opening 40 arranged in line with the first openings 38a and the second inlet opening, not visible, arranged in line with the second openings 38b. The second end plate 16 comprises the second outlet opening arranged in line with the third openings 38c and the first outlet opening 43 arranged in line with the fourth openings 38d. The inlet openings 40 and the outlet openings 43 have a substantially circular shape in the horizontal plane and are through.

It is then understood that the first inlet opening 40 and the second inlet opening 43 form the inlet orifices respectively for the heat transfer liquid and the refrigerant fluid in the first inlet manifold 44a and in the second inlet manifold 44b . Likewise, the first outlet opening 43 and the second outlet opening form the outlet orifices respectively for the heat transfer liquid and the refrigerant fluid from the first outlet manifold 46a and the second outlet manifold 46b.

According to an example of the invention, the heat exchanger 1 comprises several interfaces 52 to connect the first circuit 20 and the second circuit 22 of the heat exchange bundle 2 with external circulation ducts.

In the example of the invention illustrated in FIG. 1, the heat exchanger 1 comprises a first interface 52a so that the heat transfer liquid can enter the heat exchanger 1 through the first inlet opening 40 and the first intake manifold. entrance 44a.

The heat exchanger 1 further comprises a second interface 52b so that the refrigerant fluid can enter the heat exchanger 1 through the second inlet opening and the second inlet manifold 44b.

The heat exchanger 1 also comprises a third interface 52c, through which the refrigerant fluid can leave the heat exchanger 1 via the second outlet manifold 46b and the second outlet opening.

The heat exchanger 1 also comprises a fourth interface 52d, visible in Figure 2, through which the coolant can exit the heat exchanger 1 through the first outlet manifold 46a and the first outlet opening 43.

It is then understood that each of the interfaces 52 comprises at least one passage 20 which extends in said interface 52 along the vertical direction V. Each of the passages 20 of the interfaces 52 is therefore in line with the inlet opening or the the output opening with which the interface 52 is associated, as previously mentioned above. In this way, the fluidic connection is ensured between the interfaces 52 and the inlet manifolds 44a, 44b or the outlet manifolds 46a, 46b with which each is associated. The interfaces 52 can then take, in a non-limiting way, the shape of a sleeve or of a square base cylinder.

The section reduction member 48 of the first inlet manifold 44a along the stacking direction will now be described in relation to FIGS. 4 to 6 showing sectional views, along the vertical and longitudinal plane A-A, visible in Figure 1, parallel to the vertical direction V of the heat exchanger, the plane A-A passing through the first inlet manifold 44a and the first outlet manifold 46a.

The section reduction member 48 of the first inlet manifold 44a has the function of reducing the volume defined by the first inlet manifold 44a, for example progressively along the stacking direction E of the plates 3. In other words, reduction member 48 tends to reduce the section of first inlet manifold 44a progressively from first inlet opening 40 to bottom wall 28 of second end plate 16. thus understands that the volume defined by the first inlet manifold 44a is less important as one moves away from the first inlet opening 40. In this way, a greater quantity of heat transfer liquid circulates in the first inlet manifold 44a at the level of the first inlet opening 40 than at the level of the bottom wall 28 of the second end plate 16 and thus the flow of heat transfer liquid which circulates in each of the chambers 24 of the swap beam 2 heat.

According to the invention, the reduction member 48 is for example a conical piece 54 which extends along a main direction of elongation C. The reduction member 48 then comprises at least one base 56 and one vertex 58 opposite the to each other along the main direction of elongation C of the reduction member 48. A peripheral wall 60 extends between the base 56 and the top 58 of the reduction member 48.

Still according to the invention, a central axis T of the reduction member 48 is defined, parallel to the main direction of elongation C of the said reduction member 48. The peripheral wall 60 of the reduction member 48 extends between the top 58 and the base 56 at an angle G, relative to the central axis T of the reduction member 58, comprised between 10° and 60°.

The reduction member 48 can be in a non-limiting way in aluminum, or in an aluminum alloy, or even in a synthetic material.

According to the invention, the reduction member 48 is arranged in the volume defined by the first inlet manifold 44a such that its main direction of elongation C is parallel to the stacking direction E of the plates 3 and therefore also parallel to the vertical direction V of the heat exchanger.

Still according to the invention, the reduction member 48 extends in the volume defined by the first inlet manifold 44a, such that its top 58 is closer to the first inlet opening 40 of the first plate. end 14, than is its base 56. In other words, the base 56 of the reduction member 48 is arranged in the vicinity of the bottom wall 28 of the second end plate 16, while the top 58 of the reduction member 48 is provided in the vicinity of the first inlet opening 40 of the first end plate 14.

The base 56 of the reduction member 48 is then integral with the bottom wall 28 of the second end plate 16. In other words, a fixing means 62 is provided between the base 56 of the reduction member 48 and the bottom wall 28 of the second end plate 16 so that they are secured to one another. According to an example of the invention and in a non-limiting way, the fixing means 62 can be a brazing operation carried out during the manufacture of the heat exchange bundle.

A length L of the first inlet collector 44a is defined corresponding to a distance along the stacking direction E of the plates 3, along which said first inlet collector 44a extends. It is then understood that the length L of the first inlet manifold 44a is taken between the bottom wall 28 of the second end plate 16 and the first intake opening 42 of the first end plate 16.

Similarly, an axial dimension H of reduction member 48 is defined corresponding to a distance, along the main direction of elongation C of reduction member 48, along which said reduction member 48 extends. According to the invention, the axial dimension H of the reduction member 48 is at most equal to the length L of the first inlet manifold 44a.

According to the two embodiments of the invention visible in Figures 4 and 6, the axial dimension H of the reduction member 48 is equal to plus or minus 2% to the length L of the first inlet manifold 44a. According to the embodiment of the invention visible in Figure 5, the axial dimension H of the reduction member 48 is less than the length L of the first inlet manifold 44a, said axial dimension H corresponding to two-thirds of said length L.

A section S1 of the first inlet collector 44a is defined, perpendicular to the stacking direction E of the plates of the heat exchange bundle 2, the section S1 of the first inlet collector 44a being circular as mentioned previously. A section S2 of the base 56 of the reduction member 48 is also defined, perpendicular to the main direction of elongation C of the reduction member 48. It is understood from what has been previously described, that the section S2 of base 56 of reduction member 48 is circular.

According to the invention, the section S2 of the base 56 of the reduction member 48 is strictly lower than the section S1 of the first inlet collector 44a. More precisely, the section S2 of the base 56 of the reduction member 48 is between 20% and 80% of the section S1 of the first inlet collector 44a.

It is understood from the foregoing that the reduction member 48 acts on the flow of distribution of the coolant liquid towards each of the chambers 24 of the bundle 2 of heat exchange by means of its conical shape, the top 58 of which is turned in the direction of the first inlet opening 40 of the first end plate 14. In other words, the section of the first inlet manifold 44a is reduced progressively from the first inlet opening 40 to the bottom wall 28 of the second end plate 16, so that a quantity of heat transfer liquid is greater at the level of the inlet of the first inlet manifold 44a than at the level of the end of the first inlet manifold 44a located towards the bottom wall 28 of the second end plate 16. In this way, an equalization of the flow of the coolant liquid is ensured within each of the chambers 24 of the bundle 2 of heat exchange.

The reduction member 48 thus occupies more and more space within the first inlet manifold 44a as one moves from the first inlet opening 40 towards the bottom wall 28.

According to the second embodiment of the invention, visible in FIG. 5, the reduction member 48 comprises an intermediate section S3 taken between the top 58 and the base 56 of the said reduction member 48 and a section S4 of the top 58 of the reduction member 48. The intermediate section S3 is then strictly lower than the section S2 of the base 56 and strictly greater than the section S4 of the top 58 of the reduction member 48. In other words, the section S4 of the top 58 of the reduction member 48 is strictly lower than the section S2 of the base 56 and of the intermediate section S3 of the reduction member 48.

It is understood from all the characteristics of the second embodiment of the reduction member 48 which have just been detailed, that the latter concentrates the reduction in section of the first inlet manifold 44a at the level of the chambers 24 which are away from the first inlet opening 40 of the first end plate 14. This allows the general reduction in the size of the reduction member 48 and thus reduces the production costs associated with the manufacture of said reduction member 48 while maintaining an optimization of the distribution of the flow of heat transfer liquid in each of the chambers 24 of the bundle 2 of heat exchange.

According to the third embodiment of the invention, visible in Figure 6, the peripheral wall 60 of the conical piece 54 is provided with at least one member 64 which projects from said peripheral wall 60. The member 64 has in particular the effect of amplifying the homogeneous distribution of the flow of heat transfer liquid within each of the chambers 24 of the heat exchange bundle 2, in particular by changing the direction of initial circulation of the heat transfer liquid within the first inlet manifold 44a. In other words, the heat transfer liquid enters the first inlet manifold 44a along a first direction I1 parallel to the vertical direction V and changes direction to go towards the chambers of the heat transfer liquid circuit, along a second direction I2. In other words, the heat transfer liquid enters the first inlet manifold 44a along the first direction I1 then comes into contact with the member 62 which causes it to deviate along the second direction I2.

According to an example of the third embodiment of the invention, is in a non-limiting way, the member 62 can be a spiral helix 66 which extends at least over a portion of the peripheral wall 60. Advantageously, the spiral helix 66 extends from the base 56 of the conical piece 54 to its top 58.

A first turn of the spiral helix 66 located at the level of the top 58 of the conical part 54 and a last turn of the spiral helix 66 located at the level of the base 56 of the said conical part 54 are also defined. visible in the illustrated example of the invention, the first turn of the spiral helix 66 has a diameter smaller than the diameter of the last turn of the spiral helix 66. In other words, the diameter of the turns of the spiral helix 66 increases progressively as one advances in the first inlet manifold 44a, from the first inlet opening 40 to the bottom wall 28 of the second end plate 16. Such a configuration of the the spiral helix 66 increases the diffusion of the heat transfer liquid along the second direction I2 as described previously.

In FIG. 7, the heat exchanger 1 which has just been described finds a particular and advantageous application in a thermal management installation 70 which is capable of modifying a temperature of a passenger compartment of a motor vehicle and/or of an electrical energy storage device 72 of the motor vehicle and/or control means 74 of an electric motor propelling the motor vehicle. To this end, the heat exchanger 1 can be connected to a first external loop 200 of the control means 74 of the electric motor and to a second external loop 220 configured to modify the temperature of the electrical energy storage device 72 and/or a pulsed air 80 intended to be admitted inside the passenger compartment of the motor vehicle.

The first external loop 200 is then connected to the first circuit of the heat exchanger 1 and comprises at least one pump 82 for circulating the heat transfer liquid 7, for example consisting of glycol water or the like, between the heat exchanger 1 and the control means 74 of the electric motor.

The second outer loop 220 is connected to the second circuit of the heat exchanger 1 and comprises at least one compressor 84 to compress the refrigerant fluid 5, for example formed of carbon dioxide or the like, the heat exchanger 1 to transfer calories to the air flow 80, an expansion member 86 inside which the refrigerant fluid 5 undergoes expansion, a first heat exchanger 88 which is arranged to cool the electrical energy storage device 72 and a second heat exchanger 90 which is arranged to cool the forced air 80.

Such a thermal management installation 70 is more particularly dedicated to a motor vehicle provided with at least one electric motor forming a means of propulsion of the motor vehicle, this electric motor being supplied with electrical energy via the heat storage device. electrical energy 72.

Of course, the invention is not limited to the examples which have just been described and many adjustments can be made to these examples without departing from the scope of the invention.

The invention thus successfully achieves the aim it had set itself by optimizing the flow of the heat transfer liquid within the plurality of chambers of the heat exchange bundle by means of the section reduction member of the first collector of entry along the stacking direction.

Claims (10)

Heat exchanger (1) for a motor vehicle comprising at least one heat exchange bundle (2) consisting of a plurality of plates (3) nested one inside the other in a stacking direction (E), the bundle ( 2) heat exchange including:

• a first circuit (20) intended to be traversed by a heat transfer liquid (7) and comprising a first inlet manifold (44a), through which the heat transfer liquid (7) is admitted into the heat exchanger (1), and a first outlet manifold (46a) through which the heat transfer liquid (7) leaves the heat exchanger (1), the first circuit (20) comprising a plurality of chambers (24) hydraulically connected to the first inlet manifold (44a) and to the first output collector (46a),
• a second circuit (22) intended to be traversed by a refrigerant fluid (5) and comprising a second inlet manifold (44b), through which the refrigerant fluid (5) is admitted into the heat exchanger (1), and a second outlet manifold (46b) through which the refrigerant fluid (5) leaves the heat exchanger (1), the second circuit (22) comprising a plurality of channels (26) hydraulically connected to the second inlet manifold (44b) and second output collector (46b),

the heat exchanger (1) being configured to implement a heat exchange between the heat transfer liquid (7) circulating in the plurality of chambers (24) and the refrigerant fluid (5) circulating in the plurality of channels (26),
characterized in that the heat exchanger (1) comprises at least one section reduction member (48) of the first inlet manifold (44a) along the stacking direction (E). Heat exchanger (1) according to the preceding claim, in which the reduction member (48) is a conical piece (54). Heat exchanger (1) according to the preceding claim, in which the conical part (54) comprises a base (56) and an apex (58) opposite to each other along a main direction of elongation (C) of the reduction member (48) and between which extends a peripheral wall (60) of the conical piece (54). Heat exchanger (1) according to any one of the preceding claims, in which a main direction of elongation (C) of the reduction member (48) is parallel to the direction of stacking (E) of the plurality of plates (3) of the heat exchange beam (2). Heat exchanger (1) according to any one of claims 2 to 4, in which each of the plates (3) of the plurality of plates (3) of the heat exchange bundle (2) comprises a bottom wall (28) surrounded by a raised edge (30) and the plurality of plates (3) are divided into a beam body (18) which is included between a first end plate (14) and a second end plate (16) opposite each other along the stacking direction (E) of the plates (3), each of the bottom walls (28) of the plates (3) of the harness body (18) comprises at least one opening (38 ) which at least partially delimits the volume of the first inlet manifold (44a), the bottom wall (28) of the first end plate (14) comprising at least one inlet opening (40) for the heat transfer liquid (7) in the first inlet manifold (44a) and the second end plate (16) having its bottom wall (28) which extends in line with the openings (38) of the plates (3) of the body s beam (18), the reduction member (48) being integral with the bottom wall (28) of the second end plate (16). Heat exchanger (1) according to any one of Claims 2 to 5, in which the first inlet collector (44a) extends over a length (L) parallel to the stacking direction (E) of the plates (3 ) and the reduction member (48) extends over an axial dimension (H) measured along its main direction of elongation (C), the axial dimension (H) of the reduction member (48) being at most equal to the length (L) of the first inlet manifold (44a). Heat exchanger (1) according to any one of the preceding claims in combination with claim 3, in which the first inlet manifold (44a) has a section (S1) of the first inlet manifold (44a) and the base ( 56) of the conical piece (54) has a section (S2) of the base (56) strictly smaller than the section (S1) of the first inlet manifold (44a). Heat exchanger (1) according to any one of claims 3 or 7, in which the conical part (54) is provided with at least one member (64) which projects from the peripheral wall (60) of the conical part ( 54). Heat exchanger (1) according to the preceding claim, in which the member (64) which projects from the conical part (54) is configured to change the direction of the heat transfer liquid (7) circulating within the first inlet manifold ( 44a). Thermal management system (70) of at least one passenger compartment of a motor vehicle and/or of an electrical energy storage device (72) of the motor vehicle and/or of control means (74) of a electric motor propelling the motor vehicle, comprising at least one heat exchanger (1) according to any one of the preceding claims.