Fin architecture for promoting heat transfer fluid stirring

Abstract

The invention relates to a cooling device (1) having a thermal exchange surface (10) configured to allow thermal exchange with a heat carrier fluid (2) along the thermal exchange surface in the first direction (D1), the thermal exchange takes place by convection between the thermal exchange surface (10) and the heat carrier fluid (2), the cooling device (1) includes at least one cooling fin (12), the thermal exchange surface (10) is configured to receive the heat intended to be discharged by the cooling fin (12) by conduction, the cooling fin (12) includes at least one fluid mixing guide (14) fixed and distanced relative to the thermal exchange surface (10), at least one fluid mixing guide (14) has a distorted surface, at least one fluid mixing guide (14) is arranged to create the redirection of the heat carrier fluid (2) in the second direction (D2) intersecting with the first direction (D1).

Description

[0001] The invention relates to the cooling of a heat-producing component. The invention finds application in the field of electrical machines and power electronics. Indeed, it is known that electronic equipment, computers, and electronics in general generate losses that result in heat production, which must be dissipated. Dissipating this heat, ensuring the proper functioning of the aforementioned components, thus becomes a priority. The invention finds particular application in the field of embedded electronics, where the trend is to increase the number of electrical devices and therefore the embedded electrical power. Specifically, the present invention relates to a cooling device as defined in the preamble to claim 1, and as illustrated in document DE 20 2004 020 294U.

[0002] The invention relates more particularly to a cooling fin architecture for such a heat exchanger.

[0003] Currently, a large number of electronic systems are equipped with heat exchangers, allowing heat to be removed from the elements dissipating thermal energy to a source of heat removal, in order to allow this electronic system to operate under optimal conditions.

[0004] Today, heat exchangers are known to include a set of fins arranged along the direction of movement of a heat transfer fluid, for which heat exchange with a second fluid or the thermal element itself is desired, for example, straight fins in the direction of an airflow passing through the heat exchanger using the fins to extract thermal energy to a fluid at a lower temperature, or a fluid using the fins to extract thermal energy generated by an electronic component.

[0005] The function of the fins is to facilitate heat exchange between two fluids, or between a fluid and a heat-conducting solid element, when these two elements are at different temperatures. More precisely, the fins act as interfaces to improve the efficiency of heat exchange between the aforementioned elements, namely the two heat transfer fluids or the fluid and the solid element.

[0006] The use of a single heat transfer fluid circulating through the heat exchanger is preferred for reasons of compactness and weight. Indeed, adding a second heat transfer fluid and the entire circuit for its circulation often generates excess mass and volume that must be taken into account, especially in the aeronautical field where the main issue is managing vehicle mass.

[0007] Therefore, the cooling of an electrical machine is currently limited by mass and size constraints that the state of the art is not able to overcome.

[0008] Thus, in a cooling configuration between a heat transfer fluid operating a direct extraction of heat from the fins of the heat exchanger, an exchange surface in contact with the heat exchanger and with the heat transfer fluid, at the level of the cooling fins, can be identified to allow this thermal extraction.

[0009] However, this direct heat extraction depends on the temperature difference between the heat exchanger surface temperature, or more broadly, the cooling fin temperature, and the temperature of the heat transfer fluid flowing over this heat exchange surface and the cooling system. Indeed, the greater the temperature difference between the heat exchange surface and the heat transfer fluid, the greater the heat exchange. Thus, a heat exchange surface temperature that is high relative to the heat transfer fluid temperature, or conversely, a heat transfer fluid temperature that is low relative to the heat exchange surface temperature, significantly improves heat exchange.

[0010] However, the temperature of the heat transfer fluid varies as it flows across the heat exchange surface and the cooling fins of the cooling system. Indeed, the heat exchange that occurs between the heat exchange surface and the heat transfer fluid causes an increase in the temperature of the heat transfer fluid as it flows across the surface of the cooling system. This increase in the heat transfer fluid's temperature, and therefore the resulting decrease in the temperature difference between the hot body (the heat exchange surface) and the cold body (the heat transfer fluid), reduces the efficiency of heat extraction between these two bodies.

[0011] The invention aims to overcome all or part of the problems mentioned above by proposing a cooling fin architecture which allows, on the one hand, the mixing of the heat transfer fluid sweeping the fin, thus homogenizing the temperature of the heat transfer fluid exchanging heat with the heat exchange surface and, on the other hand, evacuating the high-temperature heat transfer fluid and replacing it with a lower-temperature heat transfer fluid, thereby improving heat extraction.

[0012] The invention advantageously makes it possible to increase the exchange time between a hot body and the heat transfer fluid by lengthening the distance traveled by the heat transfer fluid along the hot body.

[0013] To this end, the invention relates to a cooling device having a heat exchange surface configured to allow heat exchange with a heat transfer fluid along the heat exchange surface in a first direction, the heat exchange occurring by convection between the heat exchange surface and the heat transfer fluid, the cooling device comprising at least one cooling fin, the heat exchange surface being configured to receive by conduction heat intended to be evacuated by the cooling fin, the cooling fin comprising at least one fluid mixing guide fixed and at a distance from the heat exchange surface, the at least one fluid mixing guide having a slanted surface, the at least one fluid mixing guide being arranged so as to generate a redirection of the heat transfer fluid in a second direction secant to the first direction.

[0014] According to one aspect of the invention, the second direction is oriented towards the heat exchange surface, the second direction having a component substantially perpendicular to the heat exchange surface.

[0015] According to one aspect of the invention, at least one mixing guide is arranged so as to generate a redirection of the heat transfer fluid along a third direction secant to the first direction and the second direction, the third direction having the same origin as the second direction along a first plane perpendicular to the heat exchange surface, the third direction having a component substantially perpendicular to the heat exchange surface opposite to the component substantially perpendicular to the heat exchange surface of the second direction along the first plane.

[0016] According to one aspect of the invention, the cooling fin comprises: a first wall extending along a second plane substantially parallel to the first direction and parallel to the first plane, the first wall being configured to receive by conduction heat intended to be evacuated by the cooling fin, at least one mixing guide being connected to the first wall by means of a first fixing support.

[0017] According to one aspect of the invention, the cooling fin comprises: a second wall extending along a third plane parallel to the first plane and distinct from the second plane, the mixing guide being connected to the second wall by means of a second fixing support.

[0018] According to one aspect of the invention, the second plane is parallel to the first plane and / or the third plane is parallel to the first plane.

[0019] According to one aspect of the invention, the heat transfer fluid contained between the first wall and the second wall comprises a first volume of heat transfer fluid disposed between the heat exchange surface and a first guide surface of at least one mixing guide for the heat transfer fluid and a second volume of heat transfer fluid disposed in contact with a second guide surface of at least one mixing guide for the fluid, the first guide surface having a concave shape and the second guide surface having a concave shape with respect to a first segment substantially coinciding with at least one mixing guide for the fluid and parallel to the first direction.

[0020] According to one aspect of the invention, at least one fluid mixing guide includes a heat transfer fluid reversal interface configured to redirect the heat transfer fluid contained in the second volume of heat transfer fluid towards the first volume of heat transfer fluid.

[0021] According to one aspect of the invention, the heat transfer fluid reversal interface is configured to redirect the heat transfer fluid contained in the first volume of heat transfer fluid towards the second volume of heat transfer fluid.

[0022] According to one aspect of the invention, the heat transfer fluid reversal interface comprises a first flow reversal zone connected to the first wall and / or the second wall and a second flow reversal zone connected to the first wall and / or the second wall, the first guide surface in the first reversal zone being concave in shape with respect to the heat exchange zone and the second guide surface in the second reversal zone being convex in shape with respect to the heat exchange surface.

[0023] According to one aspect of the invention, the first guide surface in the first inversion zone is concave in shape between two terminals of the first segment and the second guide surface in the second inversion zone is concave in shape between the two terminals of the first segment.

[0024] According to one aspect of the invention, the first inversion zone is capable of inducing a first rotation of the heat transfer fluid of the first volume of heat transfer fluid and in which the second inversion zone is capable of inducing a second rotation of the heat transfer fluid of the second volume of heat transfer fluid along an axis of rotation parallel to the first direction.

[0025] According to one aspect of the invention, at least one mixing guide comprises an additional guide extending perpendicularly to the first wall and the second wall, the additional guide comprising a first additional guide surface opposite the first wall and a second additional guide surface opposite the second wall, the first additional guide surface and the second additional guide surface having a convex shape along a second segment substantially coinciding with the additional guide and parallel to the first direction.

[0026] According to one aspect of the invention, the first guide surface in the first inversion zone and the second guide surface in the second inversion zone are defined according to the following mathematical equation: D = f 1 X ⋅ sin f 2 X in which Drepresents the displacement of the heat transfer fluid relative to the first direction between an inlet of the reversing interface and an outlet of the reversing interface along the first direction, X represents a position of the heat transfer fluid along the first direction between the inlet of the reversing interface and the outlet of the reversing interface, X being arbitrarily set to 0 upon entry into the inversion interface, f x represent any mathematical functions.

[0027] According to one aspect of the invention, the first guide surface in the first inversion zone and the second guide surface in the second inversion zone are defined according to the following mathematical equation: D = ∑ 0 n α n ⋅ X n in which Drepresents the displacement of the heat transfer fluid relative to the first direction between an inlet of the reversing interface and an outlet of the reversing interface along the first direction, X represents a position of the heat transfer fluid along the first direction between the inlet of the reversing interface and the outlet of the reversing interface, X being arbitrarily set to 0 upon entry into the inversion interface, α n represents a parameter such as a real coefficient.

[0028] The invention will be better understood and other advantages will become apparent upon reading the detailed description of an embodiment given by way of example, a description illustrated by the accompanying drawing in which: [ Fig.1 ] there figure 1 represents a schematic view of a mixing guide and a heat exchange surface of a cooling fin according to the invention; [ Fig.2 ] there figure 2 represents a schematic view of a preferred configuration of a cooling fin including the mixing guide; [ Fig.3 ] there figure 3 represents a top view of the cooling fin's mixing guide figure 2 ; Fig.4 ] there figure 4 represents a flow reversal interface according to the invention; [ Fig.5 ] there figure 5 represents a top view of the flow inversion interface of the figure 4 ; Fig.6 ] there figure 6 represents a schematic view of a first positioning configuration of the mixing guide according to the invention; [ Fig.7 ] there figure 7 represents a schematic view of a second positioning configuration of the mixing guide according to the invention; [ Fig.8 ] there figure 8 represents a schematic view of a third positioning configuration of the mixing guide according to the invention; [ Fig.9 ] there figure 9 represents a schematic view of a fourth positioning configuration of the mixing guide according to the invention; [ Fig.10 ] there figure 10 represents a schematic view of a fifth positioning configuration of the mixing guide according to the invention; [ Fig.11 ] there figure 11 represents a schematic view of the flow reversal interface generating a flow rotation; [ Fig.12 ] there figure 12 is a spatial representation of the movement of two heat transfer fluids passing through the cooling fin according to a first model; [ Fig.13 ] there figure 13 is a spatial representation of the movement of the two heat transfer fluids passing through the cooling fin according to a second model; [ Fig.14 ] there figure 14 is a spatial representation of the movement of two heat transfer fluids passing through the cooling fin according to a third model; [ Fig.15 ] there figure 15 is a spatial representation of the movement of two heat transfer fluids passing through the cooling fin according to a fourth model.

[0029] For the sake of clarity, the same elements will carry the same markers in the different figures.

[0030] THE figure 1 This represents an enlarged schematic view of a cooling fin 12 of a cooling device 1. The cooling device 1 therefore comprises a multitude of cooling fins 12. Each cooling fin 12 is swept by a heat transfer fluid 2 in a first direction D1. The cooling device has a heat exchange surface 10 which is also the base of the cooling fin 12. The cooling device 1 is thus configured to allow heat exchange with the heat transfer fluid 2 along the heat exchange surface 10 in the first direction D1, the heat exchange occurring by convection between the heat exchange surface 10 and the heat transfer fluid 2. In addition, the heat exchange surface 10 is also configured to receive, by conduction, heat intended to be dissipated by the cooling fin 12.In other words, the heat exchange surface 10 is designed to receive heat from a hot source by conduction. Advantageously, the heat exchange surface 10 comprises a thermally conductive material. This heat is then transferred from the heat exchange surface 10 to the heat transfer fluid 2, which flows through the cooling fin 12 by convection, thereby removing heat from the cooling device 1. This heat exchange occurs primarily along and near the heat exchange surface 10.

[0031] However, the heat transfer from the heat exchange surface 10 to the heat transfer fluid 2 locally increases the temperature of the heat transfer fluid 2 near the heat exchange surface 10. And, since heat exchange is efficient when the two bodies exchanging heat are at different temperatures, the increase in the temperature of the heat transfer fluid 2 locally and near the heat exchange surface 10 impairs the efficiency of this heat extraction throughout the sweep of the heat transfer fluid 2 in the cooling fin 12.

[0032] Thus, advantageously, the cooling fin 12 includes at least one fluid mixing guide 14 fixed relative to the heat exchange surface 10. In other words, at least one mixing guide 14 is fixed and embedded relative to the heat exchange surface 10. At least one mixing guide 14 is also at a distance from the heat exchange surface 10. The cooling fin 12 can thus include a multitude of mixing guides 14 arranged randomly in the cooling fin 12, or aligned parallel to each other with respect to the first direction D1, or even aligned with each other along any direction.

[0033] At least one fluid mixing guide 14 also has a skew surface. In other words, at least one fluid mixing guide 14 has a ruled, non-developable surface, that is, a surface generated by the movement of a straight line, two successive positions of which are generally not in the same plane. Thus, the skew surface of the fluid mixing guide 14 does not conform to a development rule.

[0034] Thus, through this left surface, at least one fluid mixing guide 14 is arranged so as to generate a redirection of the heat transfer fluid 2 along a second direction D2 secant to the first direction D1.

[0035] At least one fluid mixing guide 14 then redirects a portion of the heat transfer fluid 2 flowing through the cooling fin 12, thereby generating mixing of the heat transfer fluid 2 between a hot heat transfer fluid 2' near the heat exchange surface 10 and a heat transfer fluid 2" that is cooler relative to the heat transfer fluid 2'. This fluid mixing then homogenizes the overall temperature of the heat transfer fluid 2, thus cooling the heat transfer fluid 2' located near the heat exchange surface 10 and improving heat exchange between the heat exchange surface 10, or the hot body, and the heat transfer fluid 2' located near the heat exchange surface 10.

[0036] The fluid mixing guide 14 also allows for the generation of local turbulence, improving heat exchange.

[0037] As previously stated, the fluid mixing guide 14 is integral with the heat exchange surface 10. Therefore, it is possible to secure the fluid mixing guide 14 to the heat exchange surface 10 by means of a fixing pin 15 or by means of several fixing pins 15, as shown in figure 1 .

[0038] Furthermore, as represented in figure 1 The second direction D2 is oriented towards the heat exchange surface 10. Indeed, the second direction D2 can be defined by an origin D2' and an endpoint D2". The endpoint D2" of the second direction D2 is at a shorter distance than the origin D2' of the second direction D2. In other words, the second direction D2 includes a component D2"' that is substantially perpendicular to the heat exchange surface 10.

[0039] Therefore, at least one fluid mixing guide 14 allows the heat transfer fluid 2 to be deflected near the heat exchange surface, thereby generating an oscillation in the path of the heat transfer fluid 2 along the heat exchange surface 10. This oscillation in the path of the heat transfer fluid 2 along the heat exchange surface 10 has the advantage of increasing the distance traveled by the heat transfer fluid 2 along the heat exchange surface 10 and thus increasing the heat exchange time between the heat transfer fluid 2 and the heat exchange surface 10, thereby improving heat extraction. Furthermore, at least one fluid mixing guide 14 also has the advantage of not affecting the velocity of the heat transfer fluid 2.Indeed, accelerating the heat transfer fluid 2 along the heat exchange surface reduces the heat exchange time and limits heat extraction, while slowing the speed of the heat transfer fluid in the cooling fin 12 greatly limits the convection effect between the heat exchange surface 10 and the slow-moving heat transfer fluid 2. Therefore, at least one mixing guide 14 has the advantage of increasing the distance traveled by the heat transfer fluid near the heat exchange surface 10 without impacting the heat extraction capacity of the heat transfer fluid 2.

[0040] In addition, at least one fluid mixing guide 14 has the advantage of generating areas of overpressure and areas of depression which promote the movement of the heat transfer fluid 2 relative to the heat exchange surface 10 in the cooling fin 12.

[0041] Furthermore, at least one mixing guide 14 is arranged to generate a redirection of the heat transfer fluid 2 along a third direction D3 that intersects the first direction D1 and the second direction D2. The third direction D3 also includes an origin D3' and an end D3'. And, the origin D3' of the third direction D3 is superimposed on the origin D2' of the second direction D2 along a first plane P1 parallel to the first direction D1 and perpendicular to the heat exchange surface 10. In other words, in the first plane P1, the second direction D2 and the third direction D3 have the same origin; that is, the origin D2' of the second direction D2 and the origin D3' of the third direction coincide.

[0042] And, similarly to the second direction D2, the third direction D3 has a component D3'' substantially perpendicular to the heat exchange surface 10 and opposite to the component D2'' substantially perpendicular to the heat exchange surface 10 of the second direction D2 in the first plane P1. In other words, the origin D3' of the third direction D3 is at a shorter distance than the end D3' of the third direction D3', so that the third direction D3 is oriented so as not to face the heat exchange surface 10.

[0043] Thus, at least one fluid mixing guide 14 has the advantage of allowing the heat transfer fluid 2 to be redirected in two intersecting, or even opposite, directions, via the second direction D2 and the third direction D3 simultaneously for the heat transfer fluid 2 in contact with at least one fluid mixing guide 14.More specifically, at least one fluid mixing guide 14 is capable of redirecting the hot heat transfer fluid 2' which is near the heat exchange surface 10 along the third direction D3 so as to move the hot heat transfer fluid 2' away from the heat exchange surface 10 and of redirecting the cold heat transfer fluid 2" away from the heat exchange surface 10 along the second direction D2 so as to move it closer to the heat exchange surface 10, these two redirections being done simultaneously, i.e. that for a fluid coming into contact with at least one fluid mixing guide 14, the redirection along the second direction D2 and along the third direction D3 does not happen successively but at the same time.

[0044] According to a configuration represented in figure 2 The cooling fin 12 may also include a first wall 120 extending along a second plane P2 substantially parallel to the first direction D1 and the first plane P1. The first wall 120 is configured to receive heat by conduction from the heat exchange surface 10 intended to be dissipated by the cooling fin 12. In addition, the first wall 120 comprises a thermally conductive material.

[0045] At least one fluid mixing guide 14 is connected to the first wall 120 by means of a first fixing support 120'. The first wall 120 also becomes heat conductive so as to distribute the heat to be evacuated over a larger surface, namely the heat exchange surface 10 and the first wall 120 while improving the connection of at least one mixing guide 14 with respect to the heat exchange surface 10.

[0046] It can also be envisaged that the cooling fin 12 includes a second wall 122 extending along a third plane P3 substantially parallel to the first direction D1 and the first plane P1. The third plane P3 is distinct from and parallel to the second plane P2. The second wall 122 is configured to receive heat by conduction from the heat exchange surface 10 intended to be dissipated by the cooling fin 12. Furthermore, the second wall 122 comprises a thermally conductive material.

[0047] At least one fluid mixing guide 14 is connected to the second wall 122 by means of a second fixing support 122'. The second wall 122 also becomes heat conductive so as to distribute the heat to be evacuated over a larger surface, namely the heat exchange surface 10, the first wall 120 and the second wall 122 while improving the connection of at least one mixing guide 14 with respect to the heat exchange surface 10.

[0048] The first wall 120 and the second wall 122 then form a cavity 16 into which the heat transfer fluid 2 enters and in which at least one fluid mixing guide 14 develops.

[0049] Alternatively, it can also be envisaged that the first wall 120 or the second wall 122 do not extend perpendicularly with respect to the heat exchange surface 10. More precisely, it can be envisaged that the second plane P2 and / or the third plane P3 extend along a plane secant with respect to the first plane P1 so as to generate a cooling fin shape 12 in triangle or inverted triangle.

[0050] The heat transfer fluid 2 is thus contained between the first wall 120 and the second wall 122 and, more precisely, can be contained within a first volume v1 of heat transfer fluid located between the heat exchange surface 10 and a first guide surface 140 of at least one mixing guide 14 of the heat transfer fluid, and a second volume v2 of heat transfer fluid located in contact with a second guide surface 142 of at least one mixing guide 14. The first guide surface 140 of at least one mixing guide 14 faces the heat exchange surface 10, while the second guide surface 142 of at least one mixing guide 14 faces the first guide surface 140 along a fourth direction D4 perpendicular to the first direction D1 and parallel to the first plane P1. The cavity 16 is therefore composed of the first volume v1 and the second volume v2.The first volume v1 therefore represents a volume of hot heat transfer fluid 2' close to the heat exchange surface 10, while the volume v2 represents a volume of cold heat transfer fluid 2" located at a distance from the heat exchange surface 10 compared to the heat transfer fluid 2'.

[0051] As depicted in figure 3 The first guide surface 140 has a concave shape relative to a first segment S1, which essentially coincides with at least one fluid mixing guide 14, parallel to the first direction D1 and contained within the first plane P1. The second guide surface 142 also has a concave shape relative to the first segment S1. Thus, relative to the heat exchange surface 10, the first guide surface 140 has a convex shape, while the second guide surface 142 has a concave shape. Therefore, the concave shape of the first guide surface 140 directs the hot heat transfer fluid 2' from the first volume v1 towards the third direction D3, while the concave shape of the second guide surface 142 directs the cold heat transfer fluid 2' from the second volume v2 towards the second direction D2.

[0052] Alternatively, it can also be envisaged that the first guide surface 140 and the second guide surface 142 have an substantially planar shape, the planar shape of the first guide surface 140 being parallel to the third direction D3 and the planar shape of the second guide surface 142 is parallel to the second direction D2.

[0053] Thus, through its unadjusted left surface, the fluid mixing guide 14 allows the heat transfer fluid 2 to be redirected in at least two directions, namely the second direction D2 and the third direction D3, and thus mixes the hot heat transfer fluid 2' with the cold heat transfer fluid 2" so as to reduce the local temperature of the heat transfer fluid 2 near the heat exchange surface 10.

[0054] More specifically, the fluid mixing guide 14 includes a heat transfer fluid reversal interface 15 configured to redirect the cold heat transfer fluid 2" contained in the second volume v2 of heat transfer fluid towards the first volume v1 of heat transfer fluid. The reversal interface 15 allows for a reversal of the position of the heat transfer fluid 2 passing through the cooling fin 12. In effect, the reversal interface 15 allows for the simultaneous movement of the cold heat transfer fluid 2" from the second volume v2 into the first volume v1. In other words, the fluid reversal interface 15 allows the cold heat transfer fluid 2" to be moved away from the heat exchange surface 10 contained in the second volume v2 into the first volume v1, and thus brings the cold heat transfer fluid 2" closer to the heat exchange surface 10.Indeed, at the level of the fluid inversion interface 15, the concave shape of the second guide surface 142 allows the cold heat transfer fluid 2" to be directed towards the second direction D2 which is oriented towards the heat exchange surface 10 and therefore towards the first volume v1.

[0055] Furthermore, the heat transfer fluid reversing interface 15 can also be configured to redirect the hot heat transfer fluid 2' contained in the first volume v1 of the heat transfer fluid towards the second volume v2 of the heat transfer fluid. As stated previously, the reversing interface 15 allows the hot heat transfer fluid 2' to be moved simultaneously from the first volume v1 into the second volume v2. In other words, the fluid reversing interface 15 allows the hot heat transfer fluid 2' to be moved from near the heat exchange surface 10 contained in the first volume v1 into the second volume v2, and thus to be moved away from the heat exchange surface 10.Indeed, at the level of the fluid inversion interface 15, the concave shape of the first guide surface 140 allows the hot heat transfer fluid 2' to be directed towards the third direction D3 which is oriented substantially opposite to the heat exchange surface 10 and therefore towards the second volume v2.

[0056] Thus, the inversion interface 15 allows the simultaneous movement of two superimposed volumes relative to the heat exchange surface 10, namely the first volume v1 and the second volume v2, and the reversal of the position of the two volumes relative to the heat exchange surface 10 so that the volume of heat transfer fluid furthest from the exchange surface, namely the second volume v2, according to the configuration shown in figure 3 , is located near the heat exchange surface 10 and the volume closest to the heat exchange surface 10, namely the first volume, and initially included between the heat exchange surface 10 and the volume furthest from the heat exchange surface 10 is located far from the heat exchange surface 10. Therefore, after the passage of the heat transfer fluid 2 through the inversion interface 15, it is the second volume of heat transfer fluid v2 that is located between the heat exchange surface 10 and the first volume of heat transfer fluid v1.

[0057] Indeed, the exchange of heat from the heat transfer surface 10 towards the heat transfer fluid 2 near the heat transfer surface 10 increases the temperature of the heat transfer fluid 2 contained in the first volume v1. Therefore, the inversion interface 15 allows the hot heat transfer fluid 2' contained in the first volume v1, which has a low heat extraction capacity, to be replaced by the cooler heat transfer fluid 2' contained in the second volume v2 in order to improve the heat exchange between the heat transfer fluid 2 and the heat transfer surface 10.

[0058] Reversing the two volumes of heat transfer fluid, namely the first volume v1 and the second volume v2, has the advantage of allowing the coldest available heat transfer fluid 2 to be positioned near the heat exchange surface throughout the entire heat exchange process between the heat exchange surface 10 and the heat transfer fluid 2. This is achieved by replacing a hot heat transfer fluid 2' with a comparatively colder one 2', as the convective heat exchange occurs primarily near the heat exchange surface. Consequently, the temperature gradient between the heat exchange surface 10 and the heat transfer fluid 2 located near the heat exchange surface remains high, thus improving heat extraction.

[0059] Furthermore, moving the hot heat transfer fluid 2' initially contained in the first volume v1, and whose thermal extraction capacity is then low, also allows this heat transfer fluid to cool down in contact with a cooler environment compared to the heat exchange surface 10. It is then possible to consider repeatedly and regularly reversing the heat transfer fluid 2 contained in the first volume v1 and in the second volume v2 so as to improve the heat extraction during the passage of the heat transfer fluid 2 through the cooling fin in the first direction D1.

[0060] There figure 4 Figure 15 represents an enlarged view of the fluid reversal interface and the first wall of the cooling fin. The reversal interface allows the position of the heat transfer fluid contained in the first volume v1 and the second volume v2 to be reversed by simultaneously orienting the heat transfer fluid along the second direction D2 and the third direction D3. The heat transfer fluid reversal interface comprises a first flow reversal zone 150 connected to the first wall 120 and a second flow reversal zone 152 also connected to the first wall 120.

[0061] It can be envisaged, in a cooling fin configuration 12 also including the second wall 122, that the first inversion zone 150 and / or the second inversion zone 152 are only connected to the second wall or that the first inversion zone 150 and / or the second inversion zone 152 are connected to the first wall 120 and to the second wall 122.

[0062] Thus, in the first inversion zone 150, the first guide surface 140 is convex with respect to the heat exchange zone 10 and concave with respect to the first segment S1. And, in the second inversion zone 152, the second guide surface 142 is concave with respect to the first segment S1 and with respect to the heat exchange surface 10.

[0063] In other words, the first guide surface 140 in the first inversion zone 150 is concave between two terminals S1' and S1" of the first segment S1 and the second guide surface 142 in the second inversion zone 152 is concave between the two terminals S1' and S1" of the first segment S1 obtained by the left and unadjusted shape of the mixing guide 14.

[0064] Thus, the mixing guide 14 allows the generation of two superimposed straight channels parallel to the heat exchange surface 10 and the inversion interface 15 allows the position of these two straight channels, namely the first volume v1 and the second volume v2, to be reversed with respect to the heat exchange surface 10 without the heat transfer fluid contained in one of the volumes between the first volume v1 or the second volume v2 being in contact with the heat transfer fluid contained in the other volume between the first volume v1 or the second volume v2, like a redirection baffle.

[0065] The inversion interface 15 thus has the advantage of allowing inversion in a single movement, the deflection of the heat transfer fluid in the first volume v1 and the deflection of the heat transfer fluid in the second fluid v2 taking place simultaneously, and not successively along the heat exchange surface 10.

[0066] In other words, the inversion interface 15 allows the position of the first volume v1 and the second volume v2 to be reversed at a single point A with respect to the heat exchange surface 10, thus limiting the number of components or shapes needed to reverse the position of the heat transfer flows 2 in the cooling fin 12.

[0067] There figure 5 represents an enlarged view of the inversion interface 15 from a top angle.

[0068] Thus, as stated previously, the reversing interface 15 allows the position of these two straight channels, namely the first volume v1 and the second volume v2, to be reversed relative to the heat exchange surface 10 without the heat transfer fluid contained in one of the volumes (v1 or v2) coming into contact with the heat transfer fluid contained in the other volume (v1 or v2), similar to a redirection baffle. This baffle directs the cooled heat transfer fluid 2" along the second direction D2 near the heat exchange surface 10 and the hot heat transfer fluid 2' along the third direction D3, thus moving it away from the heat exchange surface 10.In order to generate this redirection of the heat transfer fluid 2 along the second direction D2 or along the third direction D3, the reversing interface 15 of the fluid may include a slewing stop 153 allowing to block the heat transfer fluid and direct the heat transfer fluid in the third direction D3 as shown in . figure 5 Furthermore, a directional stop can also be considered to direct the heat transfer fluid contained in the second volume v2 in the second direction D2. The directional stop 153 thus allows for further orientation of the heat transfer fluid 2 by adding an additional means beyond the first guide surface 140 in the first inversion zone 150.

[0069] Furthermore, several configurations can be considered.

[0070] It can be considered, as represented in figure 6 that the inversion interface 15 and the mixing guide 14 are arranged parallel to the heat exchange surface 10. Therefore, the first wall 120 is connected to the first inversion zone 150, which is also connected to the second inversion zone 152. And, the second inversion zone 152 is connected to the second wall 122.

[0071] According to another architectural configuration, it can also be envisaged that the fluid mixing guide 14 and the inversion interface 15 are connected to the heat exchange surface 10. Therefore, the first inversion zone 150 can be connected to the heat exchange surface 10 and to the second inversion zone 152.

[0072] This configuration has the advantage of allowing the fluid mixing guide 14 to also conduct heat. Therefore, the heat transfer fluid 2 in contact with the mixing guide 14 and the reversing interface 15 can also exchange heat with the heat transfer fluid 2.

[0073] According to a configuration represented in figure 8 It is possible to consider connecting the fluid mixing guide 14 and the inversion interface 15 to the heat exchange surface 10 and the walls 120 and 122 of the cooling fin. Therefore, the first inversion zone 150 can be connected to the thermal inversion surface 10, while the second inversion zone 152 can be connected to the second wall 122. This configuration has the advantage of allowing good thermal conduction in the mixing guide 14 while also ensuring secure attachment of the soldering guide 14 to the cooling fin. Alternatively, it can be envisaged that the first inversion zone 150 is connected to the first wall 120 and at a short distance from the heat exchange surface 10. According to another variant, the second inversion zone 152 can be connected to the heat exchange surface 10 and the first inversion zone 150 is connected to the first wall 120.

[0074] According to another configuration represented in figure 7 It is also possible for the inversion interface 15 to include more than two inversion zones. For example, the inversion interface 15 may include a first inversion zone 150, a second inversion zone 152, and a third inversion zone 152', allowing the heat transfer fluid to be directed along a direction D2' oriented towards the heat exchange surface 10. Furthermore, the first inversion zone 150 may be located between the second inversion zone 152 and the third inversion zone 152', thus allowing for a more homogeneous distribution of the cold heat transfer fluid 2" near the heat exchange surface 10.

[0075] According to another configuration represented in figure 10 It may also be possible to consider connecting the inversion interface 15 of the figure 9 directly to the heat exchange surface 10 so that the fluid mixing guide 14 is heat conductive. Furthermore, according to this configuration of the mixing guide 14 parallel to the walls of the cooling fin 12, it can be envisaged that the second inversion zone 152 is located between the first inversion zone 150 and the third inversion zone 152'. Unlike the configuration of the figure 9 The third inversion zone 152' is arranged so that the direction D2' intersects the third direction D3. Therefore, the heat transfer fluid 2, reoriented by the third inversion zone 152', comes into contact with the hot heat transfer fluid 2', reoriented by the first inversion zone 150, thus cooling the hot heat transfer fluid 2'. This results in an exchange of heat transfer fluids via the first inversion zone 150 and the second inversion zone 152, and also a mixing of the heat transfer fluid to cool the hot heat transfer fluid that was initially near the heat exchange surface 10, in order to cool it as efficiently as possible.

[0076] Furthermore, it can be considered, as represented in figure 11 that the first inversion zone 150 is capable of inducing a first rotation of the hot heat transfer fluid 2' in the first volume v1 of heat transfer fluid about an axis of rotation A1 parallel to the first direction D1, and that the second inversion zone 152 is capable of inducing a second rotation of the cold heat transfer fluid 2' in the second volume v2 of heat transfer fluid 2 about an axis of rotation A2 parallel to the first direction D1. Therefore, generating a rotation or helical movement around the axis of rotation A2 has the advantage of improving the mixing of the heat transfer fluid near the heat exchange surface 10, thus ensuring a homogeneous temperature in the first volume v1. Furthermore, this type of helical movement also has the advantage of increasing the distance traveled by the heat transfer fluid 2 along the heat exchange surface 10, and therefore increasing the heat exchange time per convection.

[0077] The configuration of the figure 11 represents a preferred configuration of flux reversal between a flux which is far from the heat exchange surface 10 and a flux which is close to the heat exchange surface, then which reverse through the action of the reversal interface 15.

[0078] Furthermore, according to a configuration where the first wall 120 and / or the second wall 122 is heat conductive, generating a rotation of the heat transfer fluid allows the heat transfer fluid to be directed near the heat exchange surface 10 and towards the first wall 120 and / or the second wall 122.

[0079] According to one variant, the at least one mixing guide 14 may also include an additional guide extending perpendicularly to the first wall 120 and the second wall 122. The additional guide then includes a first additional guiding surface opposite the first wall 120 and / or a second additional guiding surface opposite the second wall 122. The first additional guiding surface and the second additional guiding surface may then have a convex shape with respect to the first segment S1 substantially parallel to the first direction D1.The additional guide thus has the form of an outgrowth of material extending from at least one mixing guide 14 towards the first wall 120 or the second wall 122 and thus allows a part of the heat transfer fluid 2 contained in the first volume v1 or in the second volume v2 to be directed respectively towards the first wall 120 or towards the second wall 122 in order to increase the contacts and the heat exchange between the heat transfer fluid 2 and the first wall 120 and / or the second wall 122. Alternatively, the first additional guiding surface and the second additional guiding surface can then have a convex shape with respect to the first segment S1.

[0080] In order to generate this rotational movement of the heat transfer fluid 2 in the first volume v1 and in the second volume v2, the first guide surface 140 in the first inversion zone 150 and the second guide surface 142 in the second inversion zone 152 can be defined according to the following mathematical equation: D = f 1 X ⋅ sin f 2 X

[0081] Or D represents the displacement of the heat transfer fluid 2 relative to the first direction D1 between an inlet 154 of the reversing interface 15 and an outlet 155 of the reversing interface 15 along the first direction D1, X represents a position of the heat transfer fluid 2 along the first direction D1 between the inlet 154 of the reversing interface 15 and the outlet 155 of the reversing interface 15, X being arbitrarily set to 0 at input 154 in the inversion interface 15, f x represent any mathematical functions.

[0082] Therefore, it is possible to obtain two rotational or helical movements along the axes of rotation A1 and A2, as shown in figure 12 .

[0083] Furthermore, it may also be considered to add an oscillation curve to the helical motion of the heat transfer fluid of the first and second volumes v1 and v2.

[0084] For example, using the previous equation, it is possible to obtain a carrier wave as represented in figure 12 according to the following formula: Porteuse = Amplitude ⋅ sin 2 ⋅ π ⋅ Fr é quence ⋅ t

[0085] Where t represents time and Amplitude represents the Amplitude of the carrier and therefore of the helical motion.

[0086] More specifically, it is possible to define the movement of a first heat transfer fluid, for example the heat transfer fluid of the first volume v1 redirected towards the second volume v2, according to the following equations: x = α ⋅ cos t y = β ⋅ sin t z = γ ⋅ t

[0087] Or αβγ represent real coefficients, and x And y represent the Cartesian coordinates of the first heat transfer fluid in a plane perpendicular to the first direction D1 of the heat transfer fluid in the cooling fin 12 and z represents the Cartesian coordinate of the first heat transfer fluid parallel to the first direction D1.

[0088] And, it is possible to define the movement of a second heat transfer fluid, for example the heat transfer fluid of the second volume v2 redirected towards the first volume v2, according to the following equations: x ′ = α ⋅ cos t + π y ′ = β ⋅ sin t + π z ′ = γ ⋅ t

[0089] With a difference of π between the position of the first heat transfer fluid and the second heat transfer fluid in the plane perpendicular to the first direction D1 and where x' And y'represent the Cartesian coordinates of the second heat transfer fluid in a plane perpendicular to the first direction D1 of the heat transfer fluid in the cooling fin 12 and z' represents the Cartesian coordinate of the second heat transfer fluid parallel to the first direction D1.

[0090] And, by adding frequency overmodulation, it is possible to obtain a helical oscillatory motion as shown in figure 13 As an indicative example, this overmodulation can be obtained by multiplying the previous formula by a modulator: PorteuseModulée = Amplitude + amplitude modulation ⋅ sin 2 ⋅ π ⋅ fr é quence modulation ⋅ t + φ × sin 2 ⋅ π ⋅ Fr é quence ⋅ t + φ

[0091] amplitude modulation represents the amplitude of the modulation applied to the carrier, that is, the amplitude variation in the helicoid and fréquence modulation represents the frequency of the modulation applied to the helicoid.

[0092] Therefore, the movement of the first heat transfer fluid can be defined according to the following equations: x = A + a ∗ cos 2 ∗ pi ∗ f ∗ t + φ . ∗ cos 2 ∗ pi ∗ F ∗ t + φ ; y = A + a ∗ sin 2 ∗ pi ∗ f ∗ t + φ . ∗ sin 2 ∗ pi ∗ F ∗ t + φ ; z = γ ∗ t ;

[0093] Or A represents the amplitude of the helical motion of the first heat transfer fluid as shown in figure 12 and a represents the amplitude of the modulation applied to the carrier. f represents the frequency of the modulation applied to the helicoid and F represents the carrier frequency, that is, the helical motion of the first heat transfer fluid as shown in figure 12 .

[0094] And, the movement of the second heat transfer fluid can be defined according to the following equations: x ′ = A + a ∗ cos 2 ∗ pi ∗ f ∗ t + φ + π . ∗ cos 2 ∗ pi ∗ F ∗ t + φ + π ; y ′ = A + a ∗ sin 2 ∗ pi ∗ f ∗ t + φ + π . ∗ sin 2 ∗ pi ∗ F ∗ t + φ + π ; z ′ = γ ∗ t ;

[0095] With a difference of π between the position of the first heat transfer fluid and the second heat transfer fluid in the plane perpendicular to the first direction D1.

[0096] This over-modulation has the advantage of allowing the heat transfer fluid to oscillate near the heat exchange surface, i.e., increasing the distance traveled by the heat transfer fluid 2 along the heat exchange surface and thus improving the exchange with the heat exchange surface 10. This helical movement around an axis of rotation accompanied by an oscillation around an axis radial to the axis of rotation also has the advantage of making better use of the available volume in the cooling fin for mixing, which improves temperature homogeneity.

[0097] Furthermore, the oscillation is in the plane of the helix. It can also be considered to add a complementary oscillation in the direction of the heat transfer fluid flow, parallel to the first direction D1 as shown in figure 14 , by combining a modulation in the plane of the first direction D1 with the formula for obtaining the carrier stated previously.

[0098] Therefore, the movement of the first heat transfer fluid can be defined according to the following equations: x = cos 2 ∗ pi ∗ F ∗ t + φ ; y = sin 2 ∗ pi ∗ F ∗ t + φ ; z = A + a ∗ cos 2 ∗ pi ∗ f ∗ t + φ + π ∗ γ ∗ t ;

[0099] And, the movement of the second heat transfer fluid can be defined according to the following equations: x ′ = cos 2 ∗ pi ∗ F ∗ t + φ + π ; y ′ = sin 2 ∗ pi ∗ F ∗ t + φ + π ; z ′ = A + a ∗ sin 2 ∗ pi ∗ f ∗ t + φ + π . ∗ 20 ∗ t ;

[0100] We then obtain a helical motion coupled with a sinusoidal motion.

[0101] Alternatively, it is also possible to generate a polynomial-type motion via the inversion interface 15. The first guide surface 140 in the first inversion zone 150 and the second guide surface 142 in the second inversion zone 152 can be defined according to the following mathematical equation: D = ∑ 0 n α n ⋅ X n

[0102] in which Drepresents the displacement of the heat transfer fluid relative to the first direction D1 between the inlet 154 of the reversing interface 15 and the outlet 155 of the reversing interface 15 along the first direction D1, X represents a position of the heat transfer fluid 2 along the first direction D1 between the inlet 154 of the reversing interface 15 and the outlet 155 of the reversing interface 15, X being arbitrarily set to 0 at the input to the inversion interface 15, α n represents a parameter such as a real coefficient.

[0103] Therefore, it is possible to consider inducing a hybrid motion relative to the rotational motion induced in the first heat transfer fluid and the second heat transfer fluid as indicated in figures 12 à 14 .

[0104] Thus, as represented in figure 15 The movement of the first heat transfer fluid can be defined according to the following equations: x = A ∗ cos π ∗ t ; y = A ∗ sin π ∗ t ; z = H ∗ t ;

[0105] The movement of the second heat transfer fluid can be defined according to the following equations: x ′ = A ∗ cos π ∗ t + π ; y ′ = A ∗ sin π ∗ t + π ; z ′ = H ∗ t ;

[0106] With a shift of π in the plane perpendicular to the first direction D1.

[0107] This movement can then be likened to a DNA-like architecture.

[0108] According to one aspect of the invention, the heat transfer fluid 2 can advantageously be air. However, any heat transfer fluid with good heat extraction capacity can be considered as the heat transfer fluid 2 passing through the cooling fin 12.

[0109] The present invention therefore aims to propose a cooling fin shape 12 allowing mixing of the heat transfer fluid 2 in the direction of the heat transfer fluid for which heat exchange is desired.

[0110] The purpose of this mixing is to allow the heat transfer fluid entering the exchanger in an area far from the heat exchange surface 10, to find itself, at any level of the exchanger in the direction of the flow of said heat transfer fluid, at the level of an area close to this heat exchange surface 10.

[0111] This same mixing causes, reciprocally, the heat transfer fluid entering the exchanger in an area close to the heat exchange surface, to pass into an area far from this same heat exchange surface along the thermal surface in the direction of the flow of this fluid.

[0112] This concept of brazing the incoming fluid allows the thermal gradient between the fluid entering the exchanger and the conductive parts used for said exchange to be changed.

[0113] The purpose of the shape is to allow a regeneration of a heat transfer fluid 2 such as air which has not been in contact with the heat exchange surface 10 at the inlet of the exchanger along the first direction D1 to allow it to be further along the first direction D1 in said exchanger in its trajectory through the heat exchanger.

[0114] The shape defined by a double curvature guide allows for efficient mixing while limiting pressure losses that can be induced by overly abrupt shapes.

[0115] The goal is to optimize heat exchange by increasing the thermal gradient along the fluid flow in the heat exchanger. This is achieved by the fact that the temperature of the fluid in contact with the exchange surface varies along the flow, reducing its gradient with the second thermal element. Having a shape that allows mixing of the flow brings fluid that has not had, or has had to a lesser extent, heat exchange with the heat exchange surface back to the heat exchange surface in order to increase the temperature gradient, and therefore the heat exchange efficiency.

[0116] The cooling fin 12 may be continuous or discontinuous in places, have communication ports and / or protruding shapes that can be used to modify the flow of the fluid and generate mixing or even a reversal of the position of the heat transfer fluid with respect to the heat exchange surface 10.

[0117] This type of fluid mixing guide 14 and fluid reversal interface 15 is advantageously manufactured using a metal 3D printing process that operates by material addition. Alternatively, any 3D printing process that operates by material addition can be considered.

Claims

1. A cooling device (1) having a heat exchange surface (10) configured to allow a heat exchange with a heat transfer fluid (2) along the heat exchange surface in a first direction (D1), wherein the heat exchange occurs by convection between the heat exchange surface (10) and the heat transfer fluid (2), the cooling device (1) comprising at least one cooling fin (12), the heat exchange surface (10) being configured to receive, by conduction, heat intended to be dissipated by the cooling fin (12), the cooling fin (12) comprising at least one fluid mixing guide (14) fixed and spaced apart from the heat exchange surface (10), the at least one fluid mixing guide (14) being disposed so as to generate a redirection of the heat-transfer fluid (2) in a second direction (D2) intersecting the first direction (D1), the cooling device being characterized in that the at least one fluid mixing guide (14) has a left surface.

2. The cooling device (1) according to claim 1, wherein the second direction (D2) is oriented toward the heat exchange surface (10), the second direction (D2) having a component substantially perpendicular to the heat exchange surface (10).

3. The cooling device (1) according to claim 2, wherein the at least one mixing guide (14) is disposed such that it generates a redirection of the heat transfer fluid (2) in a third direction (D3) intersecting the first direction (D1) and the second direction (D2), the third direction (D3) having the same origin as the second direction (D2) along a first plane (P1) perpendicular to the heat exchange surface (10), the third direction (D3) having a component substantially perpendicular to the heat exchange surface (10) opposite to the component substantially perpendicular to the heat exchange surface (10) of the second direction (D2) along the first plane (P1).

4. The cooling device (1) according to claim 3, wherein the cooling fin comprises: - a first wall (120) extending along a second plane (P2) substantially parallel to the first direction (D1) and parallel to the first plane (P1), the first wall being configured to receive, by conduction, heat intended to be dissipated by the cooling fin (12), the at least one mixing guide (14) being linked to the first wall (120) via a first mounting bracket (120').

5. The cooling device (1) according to claim 4, wherein the cooling fin comprises: - a second wall (122) extending along a third plane (P3) parallel to the first plane (P1) and distinct from the second plane (P2), the mixing guide (14) being linked to the second wall (122) via a second mounting bracket (122').

6. The cooling device (1) according to claim 5, wherein the second plane (P2) is parallel to the first plane (P1) and / or the third plane (P3) is parallel to the first plane (P1).

7. The cooling device (1) according to claim 5 or 6, wherein the heat transfer fluid (2) comprised between the first wall (120) and the second wall (122) comprises a first volume (v1) of heat transfer fluid disposed between the heat exchange surface (10) and a first guide surface (140) of the at least one heat transfer fluid mixing guide (14) and a second volume (v2) of heat transfer fluid disposed in contact with a second guide surface (142) of the at least one heat transfer fluid mixing guide (14), the first guide surface (140) having a concave shape and the second guide surface having a concave shape with respect to a first segment (S1) substantially coincident with the at least one fluid mixing guide (14) and parallel to the first direction (D1).

8. The cooling device (1) according to claim 7, wherein the at least one fluid mixing guide (14) comprises a reversal interface (15) of the heat transfer fluid configured to redirect the heat transfer fluid (2) comprised in the second heat transfer fluid volume (v2) in the direction of the first heat transfer fluid volume (v1).

9. The cooling device (1) according to claim 8, wherein the reversal interface (15) of the heat transfer fluid is configured to redirect the heat transfer fluid (2) comprised in the first heat transfer fluid volume (v1) in the direction of the second heat transfer fluid volume (v2).

10. The cooling device (1) according to one of claims 8 or 9, wherein the reversal interface (15) of the heat transfer fluid comprises a first flow reversal zone (150) linked to the first wall (120) and / or the second wall (122) and a second flow reversal zone (152) linked to the first wall (120) and / or the second wall (122), the first guide surface (140) in the first flow reversal zone (150) being concave relative to the heat exchange surface (10) and the second guide surface (142) in the second flow reversal zone (152) being convex relative to the heat exchange surface (10).

11. The cooling device (1) according to claim 10, wherein the first guide surface (140) in the first reversal zone (150) is concave between two endpoints of the first segment (S1), and the second guide surface (142) in the second reversal zone (152) is concave between the two endpoints of the first segment (S1).

12. The cooling device (1) according to one of claims 10 to 11, wherein the first reversal zone (150) is able to induce a first rotation of the heat transfer fluid (2) of the first volume (v1) of heat transfer fluid, and wherein the second reversal zone (152) is able to induce a second rotation of the heat transfer fluid of the second volume (v2) of heat transfer fluid (2) along an axis of rotation parallel to the first direction (D1).

13. The cooling device according to any one of claims 5 to 12, wherein the at least one mixing guide (14) comprises an additional guide extending perpendicularly to the first wall (120) and to the second wall (122), the additional guide comprising a first additional guide surface facing the first wall and a second additional guide surface facing the second wall, the first additional guide surface and the second additional guide surface having a convex shape along a second segment substantially coincident with the additional guide and parallel to the first direction (D1).

14. The cooling device according to claim 10, wherein the first guide surface (140) in the first reversal zone (150) and the second guide surface (142) in the second reversal zone (152) are defined by the following mathematical equation: D = f 1 X ⋅ sin f 2 X wherein D represents the displacement of the heat transfer fluid relative to the first direction (D1) between an inlet of the reversal interface and an outlet of the reversal interface along the first direction (D1), X represents a position of the heat transfer fluid along the first direction (D1) between the inlet of the inversion interface and the outlet of the inversion interface, with X arbitrarily set to 0 at the inlet to the inversion interface, and fx represent arbitrary mathematical functions.

15. The cooling device according to claim 10, wherein the first guide surface (140) in the first reversal zone (150) and the second guide surface (142) in the second reversal zone (152) are defined by the following mathematical equation: D = ∑ 0 n α n ⋅ X n wherein D represents the displacement of the heat transfer fluid relative to the first direction (D1) between an inlet of the reversal interface and an outlet of the reversal interface along the first direction (D1), X represents a position of the heat transfer fluid along the first direction (D1) between the inlet of the inversion interface and the outlet of the inversion interface, with X arbitrarily set to 0 at the inlet to the inversion interface, and αn represents a real coefficient type parameter.