Thermal regulation device

Abstract

Title: Thermal regulation device The invention relates to a thermal regulation device (1) for the cooling and / or heating of at least one component whose operation is sensitive to temperature, this component (2) being in particular a power electronic module of an inverter or a battery cell or a microprocessor, this thermal regulation device (1) comprising: a fluid circulation chamber (14) configured to receive a heat transfer fluid, this chamber (14) comprising a fluid path (15) between a fluid inlet and a fluid outlet;at least two interlayers (21, 22, 23) are arranged in the enclosure (14), one after the other along the fluid path. The interlayers (21, 22, 23) are configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure (14) and an external face (10). The interlayers (21, 22, 23) have corrugated fins (25) with a corrugation direction that is substantially transverse to the fluid path. The corrugated fins of the interlayers (21, 22, 23) extend into a first segment (T1) of the fluid path and a second segment (T2) of the fluid path downstream of the first segment. The corrugated fins (25) of the interlayers (21, 22, 23) have a fin pitch (FP) that is smaller in the second segment. (T2) than in the first segment (T1) of the fluid path. Figure for the abbreviation: Fig. 3;

Description

Title of the invention: Thermal regulation device

[0001] The present invention relates to a thermal regulation device for the cooling and / or heating of at least one component whose operation is sensitive to temperature, this component being in particular a power electronic module of an inverter or a battery cell.

[0002] In the context of automotive electrification, many electronic components are being developed or improved for higher power output. Generally speaking, the electronics used are impacted by the quality of thermal management, as electronic components have a maximum operating temperature. In particular, there is a strong correlation between maximum temperature and component price. Alternatives that withstand higher temperatures often exist, but at a higher cost. Consequently, there is a significant need to optimize the cooling of these electronic components in order to improve durability or reduce their associated costs. Examples of electronic components include components of a vehicle's electric motor, components of a DC-DC converter, an on-board charger, an inverter, etc.

[0003] For some of these components, the heat flux produced by these components is high due to their small surface areas (very small components). Furthermore, homogeneity of maximum temperatures is required between the various heat sources, namely the components.

[0004] In certain configurations, the liquid cooling circuits of electrical / electronic components are arranged in series to optimize compactness (or packaging) but this arrangement generates constraints on temperature and minimum flow rate of a heat transfer fluid used to cool these components.

[0005] The components to be cooled are, for example, switching cell modules of an inverter. This type of component is temperature-sensitive and requires precise thermal management. To date, a thermal device with a copper base plate and machined pin-shaped cooling elements immersed in a flow of coolant has provided this thermal management. In this thermal device, the temperature is not homogeneous because the pin arrangement is the same along the entire length of the plate, imposing a constant heat transfer coefficient. Due to the natural heating of the fluid along the plate, the temperature difference between the fluid and the switching cells decreases, resulting in a non-homogeneous temperature profile across the components.

[0006] The present invention aims in particular to further improve the thermal regulation of components, in particular for cooling them, by proposing thermally efficient solutions with a simpler design and / or less expensive to manufacture.

[0007] The invention thus relates to a thermal regulation device for the cooling and / or heating of at least one temperature-sensitive component, this component being in particular a power electronic module of an inverter, a battery cell, or a microprocessor, this thermal regulation device comprising: - a fluid circulation chamber configured to receive a heat transfer fluid, this chamber comprising a fluid path between a fluid inlet and a fluid outlet; - at least two interlayers arranged in the enclosure, one after the other on the fluid path, the interlayers being configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure and the external face, and the interlayers having corrugated fins with a corrugation direction that is substantially transverse to the fluid path, the corrugated fins of the interlayers extending into a first section of the fluid path and a second section of the fluid path which is downstream of the first section, the corrugated fins of the interlayers having a fin pitch that is smaller in the second section than in the first section of the fluid path.

[0008] The invention allows for different surface densities to be associated with each section of the fluid path. Indeed, by reducing the fin pitch when moving from one section of the fluid path to another (in the direction of the heat transfer fluid flow), the number of undulations from one section of the fluid path to the next is increased. With more undulations, the heat exchange surface area, and therefore the surface density, increases. Consequently, heat exchange is increased in the second section compared to the first section. The invention thus makes it possible to compensate for the increase in the temperature of the heat transfer fluid along the fluid path by providing a larger heat exchange surface area where the heat transfer fluid temperature is higher. The invention also makes it possible to maintain a substantially homogeneous wall temperature (without excessive variations) in the different placement areas where the components to be cooled are located.Thanks to the invention, it is not necessary for the heat transfer fluid to be excessively cold at the inlet to maintain its temperature at an acceptable level as it travels through the fluid path. On the contrary, the invention promotes increased heat exchange once the heat transfer fluid has heated up.

[0009] The term "fin pitch" refers to the distance between two consecutive crests of the corrugated fins.

[0010] According to one aspect of the invention, the external face of the thermal regulation device comprises at least a first placement zone for placing a component and a second placement zone for placing another component, these first placement zone and second placement zone being arranged one after the other so that the first section of the fluid path passes under the first placement zone of the external face and the second section of the fluid path passes under the second placement zone of the external face.

[0011] Thus the corrugated fins of the interlayers have a fin pitch that is smaller under the second placement zone than under the first placement zone

[0012] According to one aspect of the invention, the spacers extend substantially over the entire length of the enclosure.

[0013] According to one aspect of the invention, the length of the spacer(s) is between 130 mm and 185 mm.

[0014] According to one aspect of the invention, the length of the enclosure is the dimension of the enclosure measured along the fluid path.

[0015] For example, the length of the enclosure is the distance measured between the fluid inlet and the fluid outlet.

[0016] According to one aspect of the invention, the fluid path is generally straight between the fluid inlet and the fluid outlet.

[0017] Of course, the heat transfer fluid is subject to flow disturbances due to the presence of the interlayers in the enclosure. However, an overall flow direction can be defined between the fluid inlet and the fluid outlet. This overall flow direction is, in particular, rectilinear. This is referred to as I-flow.

[0018] According to one aspect of the invention, the spacers extend substantially over the entire width of the enclosure.

[0019] According to one aspect of the invention, the width of the spacer(s) is between 40 mm and 50 mm.

[0020] According to one aspect of the invention, the height of the spacer(s) is between 8 mm and 11 mm.

[0021] According to one aspect of the invention, the width of the enclosure is the dimension of the enclosure measured transversely to the fluid path and parallel to the plane in which it extends.

[0022] Thus all the heat transfer fluid passes successively through the different interlayers when the heat transfer fluid circulates between the fluid inlet and the fluid outlet.

[0023] According to one aspect of the invention, the corrugated fins of each interlayer have a constant pitch between all the undulations.

[0024] Alternatively, for at least one of the spacers, the pitch changes between at least some of the undulations within the spacer, in particular in the same placement area.

[0025] According to one aspect of the invention, the corrugated fins of the interlayers have, in the second section, a fin pitch (FP) which is at most 80%, or 70%, or 60%, or 50%, of the fin pitch in the first section of the fluid path.

[0026] For example: FP(section 2) <80% *FP(section 1)

[0027] According to one aspect of the invention, the fluid path comprises, in addition to the first fluid path section and the second fluid path section, at least a third fluid path section, these first, second and third sections being arranged one after the other in the direction of the fluid flow, and at least three interlayers are arranged in the enclosure, one after the other on the fluid path, the interlayers being configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure and the external face, and the interlayers having corrugated fins with a corrugation direction that is substantially transverse to the fluid path, the corrugated fins of the interlayers having a pitch that is decreasing from one of the sections to the other, in the direction of flow.

[0028] Of course, a number of successive fluid path segments greater than 3 is conceivable, with therefore a number of interlayers greater than 3.

[0029] According to one aspect of the invention, the enclosure houses a number of spacers which is equal to the number of placement zones on the outer face, on each of which one or more components can be placed.

[0030] For example, if there are three placement zones on each of which one or more components can be placed, the enclosure houses three spacers, each spacer being opposite one of the placement zones.

[0031] Alternatively, at least one of the dividers extends opposite two successive placement zones.

[0032] According to one aspect of the invention, the enclosure houses a number of spacers that is smaller than the number of placement zones on the outer face, on each of which one or more components can be placed. For example, there may be two spacers and three placement zones. In this case, for example, one of the spacers extends opposite the first placement zone and also a portion of the second placement zone, and the other of the spacers extends opposite the remainder of the second placement zone and the third placement zone.

[0033] According to one aspect of the invention, the spacers are separate parts. In other words, the spacers do not form a single, monolithic part.

[0034] According to one aspect of the invention, the spacers are arranged in the enclosure with a gap between two successive spacers. In other words, the successive spacers do not touch each other.

[0035] For example, the enclosure comprises a single chamber in which the at least two interlayers are arranged.

[0036] Alternatively, the successive interlayers are arranged in the enclosure by being placed end to end in contact with each other.

[0037] According to one aspect of the invention, at least one of the interlayers, in particular all the interlayers, comprises at least one fin provided with louvers.

[0038] According to one aspect of the invention, all the fins of the interlayer are provided with louvers.

[0039] According to one aspect of the invention, the louver is in the form of a slit bordered by a strip of material, formed by cutting and folding a portion of material from the fin.

[0040] According to one aspect of the invention, the louver is formed on a fin side.

[0041] A part of the fin which extends longitudinally between a crest and a trough of the undulation is called a "flank".

[0042] A wave thus presents two flanks which join along a ridge.

[0043] According to one aspect of the invention, the ridge may have, in cross-section, a rounded shape, for example in the shape of an arc of a circle.

[0044] According to one aspect of the invention, each flank extends substantially along a plane.

[0045] According to one aspect of the invention, at least one of the fin sides is provided with a succession of louvers, in particular arranged from one longitudinal end of the side to an opposite longitudinal end of the side.

[0046] According to one aspect of the invention, the shutters have a shutter pitch.

[0047] The louver pitch is the distance that separates two consecutive louvers.

[0048] According to one aspect of the invention, at least one of the fin flanks is provided with shutters that follow one another with a constant shutter spacing.

[0049] According to one aspect of the invention, the corrugated fins in the enclosure are all provided with louvers.

[0050] According to one aspect of the invention, the louvers of all the fins all have the same louver pitch.

[0051] In other words, the louver pitch does not vary when moving from the fluid inlet to the fluid outlet.

[0052] Alternatively, the corrugated fins have a louver pitch that varies.

[0053] According to one aspect of the invention, the louver pitch can be constant along each spacer.

[0054] In this case, the louver pitch changes when moving from one spacer to the next.

[0055] According to one aspect of the invention, the fin side comprises a region of change of direction of flow of heat transfer fluid, formed in particular by a flat region between two series of successive louvers.

[0056] According to one aspect of the invention, the series of louvers on either side of the flat region are respectively oriented with angles of opposite signs.

[0057] According to one aspect of the invention, the fins of the interlayer opposite the first placement zone, on the fluid inlet side, all have a central flat region to make the change of direction.

[0058] According to one aspect of the invention, the region of change of direction of flow can also be located at the beginning of a placement zone on which one or more components can be placed.

[0059] For example, for the first placement zone, the planar region of change of flow direction is located in the middle of this first placement zone, while for the following zones (in the direction of flow of the heat transfer fluid), the planar region of change of flow direction is located at the beginning of the placement zone considered.

[0060] Thus the heat transfer fluid changes direction in the middle of the first placement zone and, for the following zones, the fluid changes direction when passing from one placement zone to another.

[0061] The flat regions reduce pressure losses and ensure good mechanical stability of the interlayer thanks to the change in direction. Fluid flow in the first placement zone can thus be balanced.

[0062] The invention further relates, in combination or independently of the above, to an interlayer configured to be placed in a housing of a thermal regulation device, on a fluid path in the housing, the interlayer comprising louvers and, between louvers, at least two planar regions of change of flow direction which are present on the interlayer at two respective locations which are irregularly spaced along the fluid path.

[0063] Advantageously, the interlayer comprises a first longitudinal portion and a second longitudinal portion, and in the first longitudinal portion, the interlayer includes, between louvers, a flat region of change of flow direction, in particular which is located substantially in the middle of this first longitudinal portion, while, in the second longitudinal portion of the interlayer, in the direction of flow of the heat transfer fluid, the interlayer includes a flat region of change of flow direction which is located at the beginning of the second longitudinal part and which is followed by a series of louvers.

[0064] The invention further relates, in combination with or independently of the foregoing, to a thermal regulation device for the cooling and / or heating of at least one temperature-sensitive component, this component being in particular a power electronic module of an inverter or a battery cell or a microprocessor, this thermal regulation device comprising: - a fluid circulation chamber configured to receive a heat transfer fluid, this chamber comprising a fluid path between a fluid inlet and a fluid outlet; - an external face; - at least one interlayer disposed in the enclosure, and configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure and the external face, the interlayer comprising louvers and, between louvers, at least two flat regions of change of flow direction which are present on the interlayer at two respective locations which are irregularly spaced along the fluid path.

[0065] The term "irregularly spaced" means that, if there are two planar regions of change of flow direction, these two planar regions do not divide the total length of the spacer into three portions of equal length. If there are three planar regions of change of flow direction, the three planar regions do not divide the total length of the spacer into four portions of equal length, etc.

[0066] Thus, thanks to the interlayer according to the invention, it is possible to generate heat transfer coefficients that are asymmetrical along the fluid path. In particular, it is possible to provide greater heat exchange, for example, in places where the heat transfer fluid has been preheated.

[0067] It is understood that the interlayer is rendered asymmetrical due to the asymmetrical location of the planar region of change of flow direction. The asymmetric interlayer according to the invention is notably different from an interlayer that would be provided with a central region of change of flow direction, or different from an interlayer that would be provided with several regions of change of flow direction that would be arranged symmetrically along the fluid path.

[0068] According to one aspect of the invention, the interlayer comprises fins, which are in particular corrugated with a corrugation direction which is substantially transverse to the fluid path.

[0069] According to one aspect of the invention, the interlayer comprises a first longitudinal part and a second longitudinal part, and in particular each longitudinal part being opposite a placement zone of the external face, and in the first longitudinal part, the fins comprise, between louvers, a planar region of change of flow direction, in particular which is located substantially in the middle of this first longitudinal part, while, in the second longitudinal part of the interlayer, in the direction of flow of the heat transfer fluid, the fins comprise a planar region of change of flow direction which is located at the beginning of the second longitudinal part and which is followed by a series of louvers.

[0070] According to one aspect of the invention, the flat region of change of direction of flow which is located substantially in the middle of the first longitudinal part of the interlayer is substantially opposite the center of a placement zone of the outer face.

[0071] According to one aspect of the invention, the fins have a louver pitch which is smaller in the second longitudinal part of the interlayer than in the first longitudinal part.

[0072] Thus, the louver density (the number of louvers per unit length) increases in the direction of the heat transfer fluid flow, so that there can be more louvers on the fluid outlet side than on the fluid inlet side. This increases the heat transfer coefficient at the fluid outlet, where the fluid is warmer due to its upstream path along the fluid path. The invention thus makes it possible to homogenize the temperatures on the external surface of the thermal control device.

[0073] The louver pitch can be constant along each longitudinal part of the interlayer.

[0074] In this case, the louver pitch can change when moving from one longitudinal part to the next.

[0075] According to one aspect of the invention, the corrugated fins of the interlayers have, in the second longitudinal part, a louver pitch (LP) which is at most 80%, or 70%, or 60%, or 50%, of the louver pitch in the first longitudinal part.

[0076] For example LP(P2) <80%*LP(Pl)

[0077] In the case where corrugated fins delimit three or more longitudinal parts, the first longitudinal part which is opposite the first zone placement includes a planar region of change of flow direction which is located in the middle of this first longitudinal part, while the following longitudinal parts (in the direction of flow of the heat transfer fluid) each include a planar region of change of flow direction which is located at the beginning of the longitudinal part under consideration.

[0078] According to one aspect of the invention, at least one of the fin flanks has a series of louvers oriented on one side of the flank, followed by another series of louvers oriented on the opposite side of the flank.

[0079] In other words, when considering a reference plane which contains the flank, one of the sets of louvers is oriented with a positive angle with respect to this reference plane, and the other set of louvers is oriented with a negative angle with respect to this reference plane.

[0080] According to one aspect of the invention, the positive angle and the negative angle are equal up to the sign.

[0081] Alternatively, the series of successive louvers, by changing sign, also see a change in the absolute value of the angles.

[0082] In other words, the louvers in the downstream longitudinal part can be oriented with an angle (of absolute value) greater than the angle of the louvers in the upstream longitudinal part.

[0083] According to one aspect of the invention, the region of change of direction of flow of heat transfer fluid, is formed by a planar region between two series of successive louvers.

[0084] According to one aspect of the invention, the series of louvers on either side of the flat region are respectively oriented with angles of opposite signs.

[0085] Thus the heat transfer fluid makes a turn at the level of the flat region, when the heat transfer fluid passes from one series of louvers to another.

[0086] According to one aspect of the invention, the number of placement zones is odd. For example, in this case, only the first placement zone sees a central planar region of change of flow direction.

[0087] For example, for three successive placement zones, the louvers can have the following sequence of orientations: positive, negative, positive, negative.

[0088] According to one aspect of the invention, the absolute value of the angles of the louvers can be between 10° and 50°.

[0089] All the louvers from the fluid inlet to the fluid outlet are in the same orientation (either positive or negative). In this case, there is no change in the orientation of the louvers.

[0090] According to one aspect of the invention, the fin pitch is constant throughout the different longitudinal parts of the interlayer.

[0091] According to one aspect of the invention, the spacer within the enclosure is unique. In particular, the spacer is made in one piece. Thus, the louver pitch can vary along this single spacer.

[0092] Alternatively, several interlayers are housed in the enclosure, and each interlayer defines a longitudinal part.

[0093] According to one aspect of the invention, the louver pitch decreases from one spacer to the next.

[0094] Thus, the number of louvers can increase in the direction of flow, and the heat transfer fluid is further divided as one approaches the fluid outlet, thereby increasing the heat transfer coefficient. This allows the wall temperature to be balanced at the different placement zones of the external face.

[0095] The invention further relates to an interlayer particularly configured to be placed in a housing of a thermal regulation device, on a fluid path in the housing, the interlayer comprising louvers and, between louvers, a planar region of change of direction of flow which is present on the interlayer at an asymmetric location between two longitudinal ends of the interlayer.

[0096] The invention also relates to a method for manufacturing an interlayer comprising corrugated fins with louvers, comprising the following step: - making the louvers with a disk of chosen thickness to obtain a louver pitch of a predetermined value.

[0097] Other features, details and advantages of the invention will become clearer upon reading the following description on the one hand, and several illustrative and non-limiting examples of embodiments given with reference to the accompanying schematic drawings on the other hand, in which:

[0098] [Fig. 1] The [Fig. 1] is a perspective representation of a thermal regulation device according to an example of an embodiment of the invention;

[0099] [Fig.2] The [Fig.2] is a cross-sectional representation of the thermal regulation device of the [Fig.1];

[0100] [Fig.3] The [Fig.3] which shows, on the one hand, the interlayers at the top in cross-section, and on the other hand, at the bottom, the fluid path in the enclosure, for the thermal regulation device of the [Fig.1];

[0101] [Fig.4] The [Fig.4] is a detailed representation of the louvers of the thermal regulation device of the [Fig.1];

[0102] [Fig.5] Fig.5 shows, in addition to the fluid path (at the bottom), the side of the fins (at the top) and the arrangement of the louvers seen along the Pfla plane (in the middle) according to another embodiment of the invention.

[0103] The features, variants and different embodiments of the invention can be combined with each other in various ways, in provided that they are not incompatible or mutually exclusive. In particular, variants of the invention may be conceived comprising only a selection of features, described hereafter in isolation from the other described features, if this selection of features is sufficient to confer a technical advantage and / or to differentiate the invention from the prior art.

[0104] Figures 1 and 2 show a thermal regulation device 1 for cooling and / or heating components 2 whose operation is sensitive to temperature. Only one of these components 2 is shown in [Fig. 1].

[0105] The thermal control device 1 is part of an assembly 100 which includes electronic components 2 placed on an external face 10 of the thermal control device 1 to be cooled by the flow of fluid (for example glycol water) in the thermal control device 1. These components 2 are in particular power electronic modules of an inverter or battery cells, and are placed on the external face 10, in location areas 110.

[0106] This thermal regulation device 1 comprises a collector base 4 forming a base of the thermal regulation device 1, this collector base 4 having a longitudinal shape along the X direction. This collector base 4 comprises a fluid inlet 5 and a fluid outlet 6 configured to be connected respectively to an external fluid inlet pipe and a fluid outlet pipe. This fluid inlet 5 and this fluid outlet 6 are arranged at two opposite ends along the X axis of the collector base 4.

[0107] A cover plate 40 forms with the collector base plate 4, here brazed together, a heat transfer fluid circulation chamber 14 configured to receive a heat transfer fluid, this chamber 14 having a fluid path 15 between the fluid inlet 5 and the fluid outlet 6. The chamber 14 defines a single fluid flow chamber.

[0108] The cover plate 40 defines the external face 10.

[0109] The cover plate 40 and the collector base 14 are for example made of metal, for example of aluminium.

[0110] These plates 40 and 41 each have a peripheral rim 44 and a main recess 45 surrounded by the peripheral rim, and the plates 40 and 41 are assembled along the peripheral rim 44.

[0111] The two main recesses 45 define a volume forming the enclosure 14.

[0112] Three spacers 21, 22, 23 are arranged in the enclosure 14, one after the other along the fluid path. The spacers 21, 22, 23 can be brazed to the plates 40 and 4L.

[0113] The interlayers 21, 22, 23 are configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure 14 and the external face 10.

[0114] The spacers 21, 22, 23 comprise corrugated fins 25 with a corrugation direction Y which is substantially transverse to the fluid path (i.e. to the X axis). The corrugated fins 25 of the spacers 21, 22, 23 extend successively in a first segment T1 of the fluid path, a second segment T2 of the fluid path which is downstream of the first segment T1, and a third segment T3 of the fluid path which is downstream of the second segment T2.

[0115] As illustrated in [Fig. 3] (which shows, on the one hand, the dividers at the top in cross section, and on the other hand, at the bottom, the fluid path in the enclosure), the corrugated fins 25 of the interlayers 21, 22, 23 have a pitch FP which is decreasing from one of the sections to the other, in the direction of the flow path 15.

[0116] The placement zones 110 are arranged one after the other so that the first segment T1 of the fluid path passes under the first placement zone 110 of the outer face 10, the second segment T2 of the fluid path passes under the second placement zone 110 of the outer face and the third segment T3 of the fluid path passes under the third placement zone 110. Thus the corrugated fins 25 of the interlayers 21, 22, 23 have a fin pitch FP which is smaller under the second placement zone than under the first placement zone, and smaller under the third placement zone than under the second placement zone.

[0117] By reducing the pitch of the fins FP when moving from one section of the fluid path to another (in the direction of the heat transfer fluid flow), the number of undulations from one section of the fluid path to the next is increased. With more undulations, the heat exchange surface area, and therefore the surface density, increases. Consequently, heat exchange is increased in the second section T2 compared to the first section T2, and so on. The invention thus makes it possible to compensate for the increase in the temperature of the heat transfer fluid along the fluid path by providing a larger heat exchange surface area where the heat transfer fluid temperature is higher. The invention makes it possible to have a wall temperature in the different placement areas 1 where the components to be cooled are located, which remains substantially homogeneous (without excessive variations).

[0118] The "fin pitch" is defined as the distance between two consecutive crests of the corrugated fins 25, along the Y direction.

[0119] The interlayers 21, 22, 23 extend together substantially over the entire length of the enclosure 14.

[0120] The length of each spacer 21, 22, 23 is between 130 mm and 185 mm.

[0121] The fluid path 15 is generally straight between the fluid inlet 5 and the fluid outlet 6.

[0122] The spacers 21, 22, 23 extend substantially over the entire width of the enclosure 14 (width measured along the Y axis).

[0123] The width of the spacers 21, 22, 23 is between 40 mm and 50 mm, and their height is between 8 mm and 11 mm.

[0124] The corrugated fins 25 of each interlayer 21, 22, 23 have a constant pitch FP between all the corrugations.

[0125] Alternatively, for at least one of the spacers, the pitch changes between at least some of the undulations within the spacer, in particular in the same placement area.

[0126] The corrugated fins 25 of the interlayers 21, 22, 23 have, in the second section, a fin pitch FP(T2) which is at most 80%, or 70%, or 60%, or 50%, of the fin pitch in the first section FP(T1) of the fluid path.

[0127] For example, it is possible to have FP(T2) <80%*FP(T1), and FP(T3) <80%*FP(T2).

[0128] In an unillustrated example, a number of successive fluid path segments greater than 3 is conceivable, with therefore a number of spacers greater than 3.

[0129] On the contrary, it would be possible that at least one of the dividers extends opposite two successive placement zones 110.

[0130] In the example described, the spacers 21, 22, 23 are separate parts. In other words, the spacers 21, 22, 23 do not form a single part (a monolithic part).

[0131] The spacers 21, 22, 23 are arranged in the enclosure 14 with a gap between two successive spacers. In other words, the successive spacers 21, 22, 23 do not touch each other.

[0132] Alternatively, the successive interlayers 21, 22, 23 are arranged in the enclosure 14 by being placed end to end in contact with each other.

[0133] The wings 25 of the intercalary pieces 21, 22, 23 are provided with louvers 30, as can be seen in [Fig.4].

[0134] Each louver 30 is in the form of a slit 31 bordered by a strip of material 32, formed by cutting and folding a portion of material from the fin 25.

[0135] The louvers 30 are formed on a flank 33 of fin.

[0136] A part of the fin which extends longitudinally along the X axis, between a crest and a trough of the undulation, is called a "flank".

[0137] A wave thus presents two flanks 33 which join along a ridge 34.

[0138] The ridge 34 may have, in cross-section, a rounded shape, for example in the form of an arc of a circle.

[0139] Each flank 33 extends substantially along a Plia plane as illustrated in figures 3 and 5.

[0140] Figure 5 shows, in addition to the fluid path (at the bottom), the side 33 of the fins (at the top) and the arrangement of the louvers 30 views along the Plia plane (in the middle).

[0141] The louvers 30 are arranged from one longitudinal end of the flank 33 to an opposite longitudinal end of the flank 33.

[0142] The louvers 30 have a louver pitch LP along the X axis.

[0143] The LP louver pitch is the distance that separates two consecutive 30 louvers.

[0144] In one embodiment of the invention, the louvers 30 follow one another with a constant louver pitch LP.

[0145] In another embodiment of the invention illustrated in [Fig.5], the corrugated fins 25 have a louver pitch LP which varies.

[0146] In an example of an embodiment of the invention illustrated in [Fig.5], an interlayer 50 is arranged in the enclosure 14, which comprises a first longitudinal part PI, a second longitudinal part P2, and a third longitudinal part P2, which follow one another in the direction of the fluid path 15.

[0147] Each longitudinal part PI, P2, P3 is opposite a placement zone 110 of the external face 10.

[0148] In the first longitudinal section PI, the fins 25 include, between louvers 30, a planar region 51 of change of flow direction, which is located substantially in the middle of this first longitudinal section PI, while, in the second and third longitudinal sections P2 and P3 of the interlayer 50, in the direction of flow of the heat transfer fluid, the fins 25 include a planar region 52, respectively 53, of change of flow direction which is located at the beginning of the second longitudinal section P2, respectively of the third longitudinal section P3, and which is followed by a series of louvers 30. The planar regions of change of flow direction 51, 52, 53 are thus present on the interlayer 50 at respective locations which are irregularly spaced along the fluid path.

[0149] The louver pitch LP can be constant along each longitudinal part PI, P2, P3 of the spacer 50.

[0150] In this case, the louver pitch LP changes when moving from one longitudinal part PI, P2, P3 to the next.

[0151] For example, the corrugated fins 25 of the interlayers have, in the second longitudinal part P2, a louver pitch LP(P2) which is at most 80%, or 70%, or 60%, or 50%, of the louver pitch LP(P1) in the first longitudinal part PL

[0152] The corrugated fins 25 of the intercalaries have, in the third longitudinal part P3, a louver pitch LP(P3) which is at most 80%, or 70%, or 60%, or 50%, of the louver pitch LP(P2) in the second longitudinal part P2.

[0153] For example LP(P2) <80%*LP(Pl) and LP(P3) <80%*LP(P2)

[0154] The wing sides 33 have a series of louvers 30 oriented to one side of the side 33, followed by another series of louvers 30 oriented to the opposite side of the side 33.

[0155] In other words, when considering the reference plane Pfla that defines the flank 33, one of the sets of louvers 30 is oriented at a positive angle A1 with respect to this reference plane Pfla, and the other set of louvers 30 is oriented at a negative angle A2 with respect to this reference plane Pfla. In other words, the louvers 30 on either side of the planar region 51, 52, 53 of change of flow direction are mirror images with respect to this region.

[0156] The positive angle and the negative angle are equal up to a difference of sign. Alternatively, successive series of louvers, by changing sign, also see a change in the absolute value of the angles.

[0157] The region 51, 52, 53 of change of direction of flow of heat transfer fluid, is formed by a planar region between two series of successive louvers 30.

[0158] The series of louvers 30 on either side of the flat region are respectively oriented with angles of opposite signs. Thus the heat transfer fluid makes a turn at the level of the flat region 51, 52, 53 of change of flow direction, when the heat transfer fluid passes from one series of louvers to the other.

[0159] In the example described, the number of placement zones 110 is odd. Thus, only the first placement zone 110 sees a central planar region.

[0160] For example, for three successive placement zones 110, the louvers 30 can have the following sequence of orientations: positive, negative, positive, negative.

[0161] The absolute value of angles Al and A2 of the shutters 30 can be between 10° and 50°.

[0162] In the example described in [Fig.5], the fin pitch FP is constant throughout the different longitudinal parts of the spacer 50.

[0163] Alternatively, several interlayers can be housed in the enclosure, and each interlayer defines a longitudinal part.

[0164] The LP louver pitch decreases from one spacer to the next, but the louver pitch can be constant along each spacer.

[0165] Thus, the number of louvers 30 can increase in the direction of flow, and the heat transfer fluid is further split as one approaches the fluid outlet, thereby increasing the heat transfer coefficient. This allows for balancing the wall temperature, at the level of the different placement zones of the external face.

[0166] The corrugated fins 25 are straight from one longitudinal end of the intercalary to an opposite longitudinal end of the intercalary.

[0167] Alternatively, the corrugated fins can be of the Roll offset type. Thus the fins are periodically offset transversely relative to each other.

[0168] The interlayer(s) are compressed between these plates. This may be accompanied by a slight deformation of the interlayer(s).

Claims

1.

2. Demands Thermal control device (1) for cooling and / or heating at least one temperature-sensitive component (2), this component (2) being in particular a power electronic module of an inverter or a battery cell or a microprocessor, this thermal control device (1) comprising: - a fluid circulation enclosure (14) configured to receive a heat transfer fluid, this enclosure (14) comprising a fluid path (15) between a fluid inlet (5) and a fluid outlet (6); - at least two interlayers (21, 22, 23) arranged in the enclosure (14), one after the other along the fluid path, the interlayers (21, 22, 23) being configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure (14) and an external face (10), and the interlayers (21, 22, 23) having corrugated fins (25) with a corrugation direction that is substantially transverse to the fluid path, the corrugated fins of the interlayers (21, 22, 23) extending in a first segment (T1) of the fluid path and a second segment (T2) of the fluid path that is downstream of the first segment, the corrugated fins (25) of the interlayers (21, 22, 23) having a fin pitch (FP) that is smaller in the second segment (T2) that in the first segment (Tl) of the fluid path, and in which at least one of the interlayers (21, 22, 23), in particular all the interlayers (21, 22, 23),includes at least one fin equipped with louvers (30). Thermal regulation device (1) according to the preceding claim, wherein the external face (10) of the thermal regulation device comprises at least a first placement zone (110) for positioning one component and a second placement zone (110) for positioning another component, these first and second placement zones being arranged one after the other such that the first segment (T1) of the fluid path passes under the first placement zone of the external face and the second segment (T2) of the fluid path passes under the second placement zone of the outer face so that the corrugated fins (25) of the interlayers (21, 22, 23) have a fin pitch that is smaller under the second placement zone than under the first placement zone

3. Thermal regulation device (1) according to one of the preceding claims, wherein the spacers (21, 22, 23) extend substantially over the entire length of the enclosure (14), and in particular the fluid path is generally straight between the fluid inlet and the fluid outlet.

4. Thermal regulation device (1) according to any one of the preceding claims, wherein the spacers (21, 22, 23) extend substantially over the entire width of the enclosure (14).

5. Thermal regulation device (1) according to any one of the preceding claims, wherein the corrugated fins (25) of each spacer have a constant pitch (FP) between all the corrugations of the spacer.

6. Thermal regulation device (1) according to any one of the preceding claims, wherein the corrugated fins of the spacers (21, 22, 23) have, in the second section, a fin pitch (FP) which is at most 80%, or 70%, or 60%, or 50%, of the fin pitch in the first section of the fluid path.

7. A thermal regulation device (1) according to any one of the preceding claims, wherein the fluid path comprises, in addition to the first fluid path section and the second fluid path section, at least a third fluid path section (T3), these first, second, and third sections being arranged one after the other in the direction of fluid flow, and at least three interlayers (21, 22, 23) are arranged in the enclosure (14), one after the other on the fluid path, the interlayers (21, 22, 23) being configured to serve as a heat exchange surface between the heat transfer fluid circulating in the enclosure (14) and the external face, and the interlayers (21, 22, 23) having corrugated fins with a corrugation direction that is substantially transverse to the fluid path, the corrugated fins of the interlayers (21, 22,23) exhibiting a pitch that decreases from one section to the other, in the direction of flow.

8. Thermal regulation device (1) according to any one of the preceding claims, wherein the enclosure (14) comprises a single chamber in which are arranged at least two interlayers (21, 22, 23).

9. Thermal control device (1) according to any one of the preceding claims, wherein the fin side (33) comprises a flow direction change region (51, 52, 53) of heat transfer fluid, formed in particular by a planar region between two successive sets of louvers, and in particular the fin sets on either side of the planar region are respectively oriented with angles of opposite signs.