HEAT EXCHANGER FOR AN ELECTRICAL COMPONENT AND ASSEMBLY OF THE HEAT EXCHANGER AND THE COMPONENT

Description

[0001] The present invention relates to a heat exchanger for an electrical component, typically for battery cells. This component may also be a power electronic component. The heat exchanger can be used to both cool and heat the electrical component. The invention is particularly relevant to motor vehicles, especially electric or hybrid vehicles. More specifically, the invention relates to heat exchangers conforming to the preamble of claim 1, and as disclosed by US 2013 / 040 175A1.

[0002] The applicant has already proposed in a patent application not published at the date of this application a heat exchanger comprising a body defining parallel and contiguous primary and secondary channels, in which a fluid circulates in series from the primary channels to the secondary channels, according to a U-shaped circulation. Cells of a battery to be cooled or heated are arranged on each face of the body at the level of heat exchange surfaces between the fluid circulating in said channels and said cells.

[0003] Such a configuration is advantageous in that it allows a large number of cells to be cooled or heated in an optimized footprint.

[0004] For the battery to function properly, the temperature difference between the coldest cell and the hottest cell must be less than 5°C.

[0005] To achieve this, in the patent application mentioned above, each cell is positioned opposite one of the primary channels and one of the secondary channels. Indeed, if we consider the case of cell cooling, the fluid heats up along these channels, exchanging heat with the cells, such that its temperature is a priori minimal at the inlet of the primary channels and maximal at the outlet of the secondary channels. Thus, by positioning each cell opposite both a primary and a secondary channel, the entire system of cells is a priori cooled by a portion of cooler fluid and a portion of warmer fluid, so that it could be expected that the heat exchange with the fluid would tend towards a uniform average for all the cells.

[0006] However, with the channel configuration illustrated in this patent application, with the primary and secondary channels being of identical width, it was found that the heat exchange did not occur as predicted, to the detriment of limiting the temperature difference between the coldest and hottest cells.

[0007] More specifically, the applicant was able to establish that, due to an excessive temperature rise in the fluid within the primary channels, heat exchange occurred between the fluid circulating in the primary channels and the fluid, which had become too hot, circulating in the secondary channels. The expected average temperature effect was therefore limited.

[0008] The invention is based on these findings and aims to solve at least part of the problems mentioned above by proposing an exchanger as defined in claim 1.

[0009] By "exchange surface" we mean a surface opposite which the component to be cooled or heated is intended to extend.

[0010] By limiting the width of the primary channels, heat exchange between the component and the fluid circulating within them is restricted. This promotes a gradual temperature increase for the fluid throughout its circulation, from the primary channel inlet to the secondary channel outlet. This allows for the creation of zones on the body's surface that offer a relatively stable average heat exchange with the fluid across all zones.

[0011] Depending on specific embodiments, the heat exchanger comprises one or more of the following characteristics, taken alone or in any technically feasible combination: said primary and secondary channels have a constant width, a width ratio between the secondary channel(s) and the primary channel(s) is between 1.5 and 4, preferably 2, said primary and secondary channels are arranged alternately, the heat transfer fluid is preferably glycol water, and / or a refrigerant, said primary and secondary channels are arranged opposite each other across the entire heat exchange surface, the first body has two longitudinal edges, each bordered by two half-primary channels, said heat exchange surface is substantially rectangular, the heat exchanger includes a manifold allowing circulation of the fluid towards the primary channels and / or from the secondary channels, said manifold has an inlet and / or an outlet for the passage of the fluid,The first body comprises a connection zone located between the manifold and an inlet of the primary channels and / or between an outlet of the secondary channels and the manifold; said connection zone comprises first convergent sections for the passage of fluid between the manifold and the inlet of the primary channels; said first convergent sections comprise a primary throat in communication with the inlet of the primary channels; said primary throats extend along a longitudinal extension of said primary channels; the width of the primary throats differs according to the proximity of said primary throats to the fluid inlet of the manifold, one of the primary throats, closer to said inlet of the manifold, having a narrower width than one of the primary throats, further from said inlet of the manifold; said connection zone comprises second convergent sections for the passage of fluid between the manifold and the outlet of the secondary channels.said second convergents include a secondary throat in communication with the manifold; the secondary throats are between the first convergents; said secondary throats extend along a longitudinal extension of said secondary channels; the width of the secondary throats differs according to the proximity of said secondary throats to the fluid outlet of the manifold; one of the secondary throats, closer to said outlet of the manifold, has a narrower width than one of the secondary throats, further from said outlet of the manifold; said manifold includes primary indentations to control the flow of fluid between the inlet of the manifold and the primary channels and / or secondary indentations to control the flow of fluid between the secondary channels and the outlet of the manifold; said manifold includes an inlet indentation creating a fluid distribution chamber in the vicinity of the inlet of the manifold.said inlet stamping is oriented identically to the secondary stampings, said inlet stamping has an annular configuration, said inlet stamping and the convergent associated with one of the primary channels, located near said inlet of the manifold, are continuous with each other, the exchanger includes a second body symmetrical to the first body with respect to the manifold, the exchanger includes a stack of plates, the stack of plates defines said manifold, said first body and / or said second body, the stack includes an intermediate plate, said intermediate plate is stamped, the intermediate plate has undulations allowing the definition of a bottom and side walls of the primary and / or secondary channels, of the first and second convergents, of the primary and / or secondary necks and / or of the primary, secondary and / or inlet stampings, the side walls of the channels are substantially straight,said intermediate plate defines a base and side walls of collecting boxes for the passage of fluid from the primary channels to the secondary channels, said collecting box has cavities forming deflecting surfaces to guide the fluid in said box from one of the primary channels to the adjacent secondary channels, said intermediate plate has slots at the level of said collecting boxes, each slot being located opposite an opening end of one of the secondary channels, said stack of plates further includes a first outer plate opposite which a first part of the cells are intended to be positioned, on a first face of said exchanger, said stack of plates further includes a second outer plate opposite which another part of the cells are intended to be positioned, on a second face of said exchanger, opposite the first face,The first outer plate has a flat bottom and raised edges; the second outer plate is flat; the intermediate plate has a flat peripheral edge, sandwiched between the raised edges of the first outer plate and a peripheral edge of the second outer plate; said exchanger has inlet and outlet connections, respectively related to the inlet and outlet of the manifold.

[0012] The invention also relates to an assembly of an electrical component and an exchanger as described above.

[0013] In particular embodiments, said assembly comprises one or more of the following characteristics, taken alone or in any technically feasible combination: the component is in contact with said first body and / or said second body opposite said primary and secondary channels, the component includes cells of an electricity storage battery, the cells are opposite both one of the primary channels and one of the secondary channels, the cells are located on each side of said first body and / or said second body.

[0014] For purely illustrative purposes, a detailed example will now be described, based on the figures, in which: [ Fig.1 ] there figure 1 is a perspective view of a heat exchanger according to an embodiment of the invention, equipped on both sides with electric battery cells; [ Fig.2 ] there figure 2 is a front view of an intermediate plate of said exchanger; [ Fig.3 ] there figure 3 is a perspective view of a central part of the intermediate plate of the figure 2 , top view; [ Fig.4 ] there figure 4 is a perspective view of the central part of the intermediate plate of the figure 2 , view from below; [ Fig.5 ] there figure 5 is a perspective view of a portion of the longitudinal end of the intermediate plate of the figure 2 , top view; [ Fig.6 ] there figure 6 is a perspective view of the longitudinal end portion of the figure 5 , view from below, [ Fig.7 ] there figure 7 illustrates in top view and by transparency the relative positioning of the electrical cells and fluid circulation channels of an exchanger, according to a configuration conforming to the invention.

[0015] As illustrated in the figure 1 The invention relates to a heat exchanger 1 for an electrical component 4, in particular for an electrical component of a motor vehicle.

[0016] Component 4 here consists of an electricity storage battery comprising electrical cells 6. These cells are electrically connected to each other in series and / or in parallel, for example at one of their ends. These cells are, for example, cylindrical, with a circular cross-section.

[0017] We observe that the cells are here divided into four groups, two upper groups 7, 7' and two lower groups 9, 9'.

[0018] The said cells 6 are preferentially distributed in a regular manner according to rows oriented along a first direction X, the different rows succeeding one another along a second direction Y, perpendicular to the direction X. The cells are arranged in a staggered pattern from one row to the next.

[0019] Component 4 is in contact with said heat exchanger 1. In other words, here, the cells 6 are in contact with said heat exchanger 1, for example, at one of their ends, namely the end opposite to the one by which they are electrically connected. Put another way, the cells 6 are in contact with the heat exchanger via a disc-shaped surface.

[0020] The said exchanger defines one or more exchange surfaces 8, here four, each corresponding to one of the groups 7, 7', 9, 9' of cells 6. By "exchange surface," we mean a surface opposite which the component 4 to be cooled or heated is intended to extend. It can be seen that here, the exchange surfaces are essentially rectangular.

[0021] The heat exchanger preferably comprises a contact layer 10 between the cells 6 and the heat exchange surfaces 8. This contact layer 10 is made of a thermally conductive material. This material is advantageously deformable so as to absorb manufacturing variations in the individual cells 6 and / or material deformation resulting from differential thermal expansion. It is preferably a thermal adhesive that provides mechanical support for the individual cells 6 on the heat exchange surfaces 8.

[0022] The heat exchanger preferably comprises a stack of plates, the plates being stacked along a Z direction orthogonal to the X and Y directions. In other words, the plates extend substantially along the X and Y directions. The heat exchanger has a thickness, along the Z direction, much less than its length, along the Y direction, and its width, along the X direction.

[0023] These plates are, for example, made of aluminum and / or aluminum alloy. They are assembled, in particular, by brazing.

[0024] The stack here comprises a first outer plate 12 opposite which a first portion of the cells 6 is positioned on a first face 14 of said exchanger. Said first outer plate 12 here defines two of the exchange surfaces 8, corresponding to the upper groups 7, 7' of the cells 6.

[0025] The stack further includes a second, non-visible, outer plate, opposite which another portion of the cells 6 is positioned, on a second face of the exchanger, opposite the first face 14 of the exchanger. This second outer plate defines two further exchange surfaces 8, corresponding to the lower groups 9, 9' of the cells 6.

[0026] The first outer plate 12 has a substantially flat bottom 16 and raised edges 18. The exchange surfaces 8, corresponding to the upper groups 7, 7' of the cells 6 are positioned at the level of said bottom 16 of the first outer plate 12 and the corresponding contact layers 10 are located between said bottom 16 of the first outer plate 12 and each of the upper groups 7,7' of cells 6.

[0027] The second outer plate is flat. The contact layers 10 corresponding to the other exchange surfaces 8 are located between the second outer plate and each of the lower groups 9,9' of cells 6.

[0028] The first external plate 12 and the second external flat plate define between them a volume within which a heat exchange fluid, in particular a heat transfer fluid, such as glycol water, and / or refrigerant, passing through the exchanger is intended to circulate.

[0029] For the circulation of said fluid, said heat exchanger further presents inlet connections 20 and outlet connections 22 related to the internal volume defined between the first outer plate 12 and the second outer plate. These inlet connections 20 and outlet connections 22 are substantially on the same straight line oriented along the X direction.

[0030] Preferably, the heat exchanger also includes 90 flanges for attaching to a support.

[0031] As illustrated in the figure 2 , the stack of plates includes an intermediate plate 20, preferably stamped.

[0032] The intermediate plate 24 has a flat peripheral edge 26, sandwiched between the raised edges 18 of the first outer plate 12 and a peripheral edge of the second outer plate. In other words, said intermediate plate 24 extends into the internal volume defined between the first outer plate 12 and the second outer plate. Such characteristics promote a good seal of the plate stack.

[0033] The circulation of the fluid through the exchanger will now be described.

[0034] The said exchanger comprises a first body 28 defined here by a part of the plate stack, in this case a part located on the right of the figures 1 et 2 .

[0035] The body 28 defines at least one primary channel 30 and one secondary channel 32, parallel and contiguous. The channels extend along the second direction Y.

[0036] In said primary and secondary channels, fluid flows in series from the primary channel 30 to the secondary channel 32, in opposite directions, as represented by the arrows 34, corresponding to the direction of fluid flow in the primary channels 30, and by the arrows 36, corresponding to the direction of fluid flow in the secondary channels 32. The arrows 34 are shown as dashed lines because the primary channels are defined at the level of a lower face of the intermediate plate 24 and are therefore not visible from the front. figure 2 The arrows 36 are shown in solid lines because the secondary channels are located on one upper face of the intermediate plate 24 and are therefore visible at the figure 2 The same convention is maintained in figures 3 à 6 It is understood that the primary channels 30 and the secondary channels 32 are located on either side of the said intermediate plate 24.

[0037] The said primary channels 30 and the said secondary channels 32 are arranged alternately, preferably over the entire extent of each of the exchange surfaces 8. The heat exchange surfaces 8 thus allow heat exchange between the fluid circulating in the said primary and secondary channels, on the one hand, and, on the other hand, the said component 6.

[0038] The intermediate plate 24 has undulations that define the base and lateral walls of the primary canals, not visible at the figure 2 , as well as a bottom 38 and side walls 40 of the secondary channels 32.

[0039] The primary channels 30 are closed by said second outer plate. On the side opposite to the fluid passage, the bottom of the primary channels is fixed to the bottom 16 of said first outer plate 12. The secondary channels 32 are closed by the bottom 16 of said first outer plate 12. On the side opposite to the fluid passage, the bottom of the secondary channels is fixed to said second outer plate.

[0040] The lateral walls of the primary and secondary canals are preferentially substantially straight.

[0041] The first body 28 further comprises a collector box for the passage of fluid from the primary channels 30 to the secondary channels 32, as indicated by the arrows 37. In said collector boxes, the fluid reverses direction and, as illustrated, passes from one side of the intermediate plate 24 to the other. The configuration of the intermediate plate 24 in this respect will be detailed later.

[0042] According to the invention, a width I1 of the primary channels 30 is less than a width I2 of the secondary channels 32. As already explained above, this promotes a uniform heat exchange between the fluid circulating in the primary and secondary channels, on the one hand, and, on the other hand, the component 6, over the entire extent of each of the heat exchange surfaces 8.

[0043] The primary channels 30 and secondary channels 32 advantageously have a constant width, I1 and I2 respectively, with respect to the exchange surfaces 8. It should be noted, however, that in the exchanger according to the invention, a portion of the surface of the cell row located at each end of the groups, along the second direction Y, may extend beyond the exchange surfaces 8 (see figure 7 ).

[0044] A preferred width ratio (I2 / I1) between the secondary channel(s) 32 and the primary channel(s) 30' is between 1.5 and 4, preferably around 2. It was observed that below 2, the uniformity of heat exchange across the heat exchanger surface remained limited. It was also observed that above 4, the heat exchanger exhibited problems with resistance to internal pressure. Furthermore, the advantage in terms of uniform surface heat exchange reached a limit as pressure losses became too high.

[0045] In the illustrated example, the first body 28 has two longitudinal edges 42, each bordered by two primary half-channels 30. They ensure the uniformity of heat exchange up to the edge of the exchange surfaces 8.

[0046] As detailed in figures 3 et 4 The heat exchanger 1 includes a manifold 44 allowing fluid circulation towards the primary channels 30 and / or from the secondary channels 32. Said manifold 44 has an inlet 46 and / or an outlet 48 for the passage of the fluid, respectively in communication with the inlet 20 and outlet 22 connections. Said inlet 46 is provided both through the first outer plate 12 and the intermediate plate 24. Said outlet 48 is provided through the first outer plate 12 only.

[0047] The intermediate plate 24 has a central portion 80 which, in combination with the first and second outer plates, defines two fluid circulation chambers. A first 82 of the chambers, visible figure 4 , forms an inlet chamber in communication with the primary channels 30. It is located between the aforementioned median portion 80 and the second outer plate. It is fed by the inlet 46 of the aforementioned collector 44. A second 84 of the chambers, visible figure 3 forms an outlet chamber in communication with the secondary channels 32. It is located between the median portion 80 and the bottom of the first outer plate. It is in communication with the outlet 48 of the collector 44. The median portion 80 is preferably located, along the Z-axis, equidistant from the first and second outer plates.

[0048] As will be detailed later, the exchanger is configured to promote good distribution of the fluid in each of the primary 30 and secondary 32 channels, depending on the positioning of said inlet / outlet 46, 48.

[0049] For this purpose the first body 28 includes here a connection zone 50, located between the collector 44 and an inlet 52 of the primary channels 30 and / or between an outlet 54 of the secondary channels 32 and the collector 44.

[0050] As this stands out more figure 4 The said connection zone 50 includes first convergent sections 56 for the passage of fluid between the manifold 44 and the inlet 52 of the primary channels 30. A "convergent section" is understood to be a portion whose cross-section, in particular its width, decreases according to the direction of fluid flow. These first convergent sections 56 extend into a primary throat 58 in communication with the inlet 52 of the primary channels 30. These primary throats 58 extend along the longitudinal extension direction Y of the primary channels 30, each primary throat 58 maintaining a constant width.

[0051] However, the width of the primary necks 58 varies depending on their proximity to the fluid inlet 46 of the manifold. The primary neck(s) closest to the inlet 46 of the manifold 44 have a narrower width than the primary neck(s) 58 furthest from the inlet 46 of the manifold 44. Here, the three primary necks 58 closest to the inlet 46 of the manifold 44 have approximately the same width, while the furthest primary neck 58, on the right in the figure, has a greater width.

[0052] As this stands out more figure 3 , said connection zone 50 further includes second convergents 60 for the passage of the fluid between the manifold 44 and the outlet 54 of the secondary channels 32. Said second convergents extend by a secondary neck 62 in communication with the manifold 44.

[0053] The said secondary necks 62 extend along the Y direction of longitudinal extension of the said secondary channels 32, each of the secondary necks 62 maintaining a constant width.

[0054] That being said, the width of the secondary necks 62 differs depending on the proximity of said secondary necks to the fluid outlet 48 of the manifold 44. The secondary neck(s) closest to said outlet 48 of the manifold 44 have a smaller width than the secondary neck(s) 62 furthest from said outlet 48 of the manifold 44. Here, the secondary necks 62 have an increasing width as they move away from said outlet 48 of the manifold 44, the location of which, in projection, is marked S on the figure.

[0055] The secondary necks 62 are between the first convergents 56. This also has the effect of modifying the size of an inlet width of said first convergents 56, the first convergent(s) 56 located near the inlet 46 of the collector 44 having a smaller mouth than the first convergent(s) 56 further away.

[0056] The intermediate plate 24 has undulations that define the bottom and lateral walls of the first and second convergents 56, 60, as well as the primary and / or secondary necks 58, 62. The bottom of the first convergents 56 and the primary necks 58 is located at the same level, along the Z direction, as the bottom 41 of the primary channels 30. The bottom 40 of the second convergents 60 and the secondary necks 62 is located at the same level, along the Z direction, as the bottom 40 of the secondary channels 32. The lateral walls of the first and second convergents 56, 60 and the primary and secondary necks 58, 62 are respectively continuous with the longitudinal walls 41, 40 of the primary and secondary channels 30, 32.

[0057] Said collector 44 includes primary stampings 64, projecting figure 4 , to control the flow of fluid between the inlet 46 of the manifold 44 and the primary channels 30 and secondary stampings 66, protruding figure 3 , to control the flow of fluid between the secondary channels 32 and the outlet 48 of the manifold 44.

[0058] The said primary and secondary stampings 64, 66 have various shapes depending on their positioning in the collector 44, for example a substantially circular, elongated, chevron or three-pointed star shape.

[0059] To the figure 4 We can see that some of the primary indentations 64 are located at the inlet of the first convergent sections 56. Those closest to the inlet 46 of the collector 44 are chevron-shaped, while those furthest away are elongated. Others are located on the same line, along the X direction, as the inlet 46 of the collector 44. The closest one has a three-pointed star shape, while the others are elongated or circular.

[0060] To the figure 3 We can see that some of the secondary stampings 66 are located at the outlet of the second converging sections 60. Those closest to the outlet 48 of the manifold 44 are chevron-shaped, while those further away are elongated. Others are located on the same line, along the X direction, as the outlet 48 of the manifold 44. The closest one has a three-pointed star shape, while the others are elongated or circular.

[0061] Back at the figure 4 It can be seen that the manifold 44 includes a stamped inlet 68, creating a fluid distribution chamber 70 in the vicinity of the fluid inlet 46. This inlet stamped inlet 68 is oriented identically to the secondary stamped inlets 66. The inlet stamped inlet 68 has an annular configuration. This prevents the occurrence of overspeed phenomena for the fluid entering the manifold 44, given the low height of the inlet chamber 82.

[0062] In the variant not shown, said inlet stamping and the first convergent associated with one of the primary channels, located near said inlet of the collector, are continuous with each other.

[0063] The intermediate plate 24 has undulations that define the primary 64 and / or secondary 66 indentations. A crest of the primary indentations 64 is located at the same level, along the Z direction, as the bottom of the secondary channels 32. A crest of the secondary indentations 66 is located at the same level, along the Z direction, as the bottom of the primary channels 30.

[0064] As illustrated in figures 5 et 6 , said intermediate plate 24 defines a bottom 92 and side walls 94 of the collecting boxes for the passage of fluid from the primary channels 30 to the secondary channels 32.

[0065] The said collecting box has alveoli 72 forming deflecting surfaces 74 to guide the fluid in said box from one of the primary channels 30 to the neighboring secondary channels 32.

[0066] The intermediate plate 24 has slots 76 at the level of the collector boxes, each slot 76 being located opposite an open end of one of the secondary channels 32 to allow the fluid to pass from one side of the plate to the other. The slots 76 are formed, for example, by removing material before stamping the intermediate plate 24 or by punching during stamping.

[0067] In the variant not shown, the intermediate plate is made of a corrugated interlayer defining the said primary and secondary channels, the collector box, or even the connection area being defined by stamping the said first and / or second external plates.

[0068] By referring again figure 1 As will be understood, the exchanger here includes a second body 78, symmetrical to the first body 28 with respect to the collector 44.

[0069] The stacking of plates defines said collector 44, said first body 28 and said second body 78.

[0070] As can be seen from the above, component 4 is in contact with said first body 28 and / or said second body 78 opposite said primary and secondary channels 30, 32. More specifically, the cells 6 are located on each side of said first body 28 and said second body 78. They are preferentially attached to said first and / or second body 28, 78.

[0071] As this appears more clearly to the figure 7 , each of the cells 6 is opposite both one of the primary channels 30, 30' and one of the secondary channels 32, with a majority of the end surface of the cells being opposite one of the secondary channels 32.

[0072] It can also be seen from this figure that the said connection zone has an extension, along the Y axis, substantially identical to the diameter of cells 6.

Claims

1. Heat exchanger (1) for an electrical component (4), said exchanger comprising a first body (28) defining at least one primary channel (30) and at least one secondary channel (32), parallel contiguous, in which fluid circulation occurs in series from the primary channel (30) to the secondary channel (32), in opposite directions, said first body (28) having at least one heat exchange surface (8) between the fluid circulating in said channels (30, 32) and said component (4), a width of the primary channels (30) being less than a width of the secondary channels (32), the exchanger is characterized in that it further comprises a stack of plates comprising a first external plate opposite which a first portion of the cells are intended to be positioned, on a first face of said exchanger, and comprising a second external plate opposite which another portion of the cells are intended to be positioned, on a second face of said exchanger, opposite to the first face, the stack further comprising an intermediate plate, the primary channels (30) and the secondary channels (32) being located on either side of said intermediate plate (24)2. Exchanger according to claim 1 in which a width ratio between the secondary channel(s) (32) and the primary channel(s) (2) is between 1.5 and 4, preferably 2.

3. Exchanger according to any one of the preceding claims in which the exchanger comprises a manifold (44) allowing circulation of the fluid to the primary channels (30) and / or from the secondary channels (32), said manifold (44) having an inlet (46) and / or an outlet (48) for the passage of the fluid.

4. Exchanger according to the preceding claim in which the first body (28) comprises a connection zone (50) located between the manifold (44) and an inlet (52) of the primary channels (30) and / or between an outlet (54) of the secondary channels (32) and the manifold (44).

5. Exchanger according to the preceding claim in which said connection zone (50) comprises first convergents (56) for the passage of the fluid between the manifold (44) and the inlet (52) of the primary channels (30), said first convergents (56) comprising a primary throat (58) in communication with the inlet (52) of the primary channels (30).

6. Exchanger according to the preceding claim in which said connection zone (50) comprises second convergents (60) for the passage of the fluid between the manifold (44) and the outlet (54) of the secondary channels (32), said second convergents (60) comprising a secondary throat (62) in communication with the manifold (44).

7. Exchanger according to the preceding claim in which the secondary throats (62) are located between the first convergents (56).

8. Exchanger according to any one of claims 3 to 7 in which said manifold (44) comprises primary embossments (64) to control the flow of fluid between the inlet (46) of the manifold (44) and the primary channels (30) and / or secondary embossments (66) to control the flow of fluid between the secondary channels (32) and the outlet (48) of the manifold (44).

9. Exchanger according to any one of claims 3 to 8 in which said manifold (44) comprises an embossment (68), called inlet embossment, creating a distribution chamber (70) for the fluid in the vicinity of the inlet (46) of the manifold (44).

10. Assembly of an electrical component (4) and an exchanger according to any one of the preceding claims.