Temperature control device

Abstract

The invention relates to a temperature control device (1) for cooling and / or heating at least one component, the operation of which is temperature-sensitive, this component (2) being in particular an electronic power module of an inverter or a battery cell or a microprocessor, and this temperature control 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 spacers (21, 22, 23) arranged in the chamber (14), one after the other on the fluid path, the spacers (21, 22, 23) being configured to act as a heat exchange surface between the heat transfer fluid that circulates in the chamber (14) and an outer face (10), and the spacers (21, 22, 23) comprising corrugated fins (25) with a corrugation direction that is substantially transverse to the fluid path, the corrugated fins of the spacers (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 spacers (21, 22, 23) having a fin pitch (FP) that is smaller in the second segment (T2) than in the first segment (T1) of the fluid path.

Description

DESCRIPTION Title: Thermal regulation device [1] The present invention relates to a thermal regulation device for cooling and / or heating at least one component whose operation is sensitive to temperature, this component being in particular an electronic power module of an inverter or a battery cell. [2] In the context of electrification in the automotive field, many electronic components are being developed or improved for higher power. Generally speaking, the electronics used are impacted by the quality of thermal management because electronic components have a temperature limit for use. Above all, there is a strong correlation between maximum temperature and component price. There are often alternatives that withstand higher temperatures but with a higher cost. Therefore, there is a significant need to optimize the cooling of these electronic components in order to improve durability or reduce the costs related to these components. Electronic components can be, for example, components of an electric machine of the vehicle, components of a DC-DC converter, an on-board charger, an inverter, etc. [3] For some of these components, the heat flux produced by these components is high due to the small surface areas (very small components). It is also required to have homogeneity of maximum temperatures between several heat sources that are the components. [4] In certain configurations, the liquid cooling circuits of electrical / electronic components are arranged in series to optimize compactness (or packaging) but this arrangement generates temperature constraints and minimum flow rate of a heat transfer fluid used to cool these components. [5] 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. Until now, a thermal device with a copper base plate with cooling elements in the form of machined pins immersed in a flow of coolant allows this thermal management. In this thermal device, the temperature is not homogeneous because the arrangement of the pins is the same throughout the plate, imposing a constant heat transfer coefficient. Due to natural heating of the fluid along the plate, the temperature difference decreases between the fluid and the switching cells, which generates a non-homogeneous temperature profile at the component level. [6] 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. [7] The invention thus relates to a thermal regulation device for cooling and / or heating at least one component whose operation is sensitive to temperature, this component being in particular an electronic power module of an inverter or a battery cell or a microprocessor, this thermal regulation device comprising: - a fluid circulation enclosure configured to receive a heat transfer fluid, this enclosure comprising a fluid path between a fluid inlet and a fluid outlet; - at least two spacers arranged in the enclosure, one after the other on the fluid path, the spacers being configured to serve as a heat exchange surface between the heat transfer fluid which circulates in the enclosure and the external face, and the spacers comprising corrugated fins with a direction of undulation which is substantially transverse to the fluid path, the corrugated fins of the spacers extending in 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 spacers having a fin pitch which is smaller in the second section than in the first section of the fluid path. [8] The invention makes it possible to have different surface densities associated with each section of the fluid path. Indeed, by reducing the pitch of the fins 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 another is increased. With more undulations, the heat exchange surface, and therefore the surface density, increases. Consequently, the heat exchanges are 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 a larger heat exchange surface where the temperature of the heat transfer fluid is higher. The invention makes it possible to have a wall temperature on the different placement zones where the components to be cooled are placed, which remains substantially homogeneous (without excessive variations).Thanks to the invention, it is not necessary to have the heat transfer fluid excessively cold at the inlet which would allow its temperature to be maintained at an acceptable level as it travels along the fluid path. On the contrary,. the invention rather recommends increasing heat exchanges when the heat transfer fluid has risen in temperature. [9] "Fin pitch" means 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 spacers having a fin pitch which 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 enclosure length 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 rectilinear 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 spacers in the enclosure. However, an overall flow direction can be defined between the fluid inlet and the fluid outlet. This overall flow direction is notably rectilinear. This is then referred to as an I-type 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 spacers 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 spacer have a constant pitch between all the corrugations.

[0024] Alternatively, for at least one of the interlayers, the pitch changes between at least some of the undulations within the interlayer, in particular in the same placement zone.

[0025] According to one aspect of the invention, the corrugated fins of the spacers 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 section of the fluid path and the second section of the fluid path, at least a third section of the fluid path, these first section, second section and third section being arranged one after the other in the direction of fluid flow, and at least three spacers are arranged in the enclosure, one after the other on the fluid path, the spacers being configured to serve as a heat exchange surface between the heat transfer fluid which circulates in the enclosure and the external face, and the spacers comprising corrugated fins with a direction of undulation which is substantially transverse to the fluid path, the corrugated fins of the spacers having a pitch which decreases from one of the sections to the other, in the direction of flow.

[0028] Of course, a number of successive sections of the fluid path greater than 3 is possible, with therefore a number of intercalaries 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 of the external face, on each of which one or more components can be placed.

[0030] For example, if there are three placement areas on each of which one or more components can be placed, the enclosure accommodates three spacers, each spacer facing one of the placement areas.

[0031] Alternatively, at least one of the spacers 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 areas of the external face, on each of which one or more components can be placed. For example, there may be two spacers and three placement areas. In this case, for example, one of the spacers extends opposite the first placement area and also a portion of the second placement area, and the other of the spacers extends opposite the remainder of the second placement area and the third placement area.

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

[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 spacers are arranged.

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

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

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

[0039] According to one aspect of the invention, the shutter is in the form of a slot 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 shutter is formed on a fin flank.

[0041] A "flank" is a part of the fin that extends longitudinally between a crest and a trough of the corrugation.

[0042] A wave thus has two sides which join along a crest.

[0043] According to one aspect of the invention, the ridge may have, in cross section, a rounded shape, for example 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 flanks is provided with a succession of shutters, in particular arranged from a longitudinal end of the flank to an opposite longitudinal end of the flank.

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

[0047] The shutter pitch is the distance between two consecutive shutters.

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

[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 varying louver pitch.

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

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

[0055] According to one aspect of the invention, the fin flank comprises a region of change in 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 shutters 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 spacer facing the first placement zone, on the fluid inlet side, all have a central flat region for making the change of direction.

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

[0059] For example, for the first placement zone, the flat 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 flat region of change of flow direction is located at the start 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 help reduce pressure losses and ensure good mechanical strength of the interlayer thanks to the change in direction. The fluid flow in the first placement area can thus be balanced.

[0062] The invention also relates, in combination or independently of the foregoing, to an interlayer configured to be placed in an enclosure of a thermal regulation device, on a fluid path in the enclosure, the interlayer comprising louvers and, between louvers, at least two planar regions of change of direction of flow 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 part and a second longitudinal part, and in the first longitudinal part, the interlayer comprises, between louvers, a flat region for changing the direction of flow, 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 interlayer comprises a flat region for changing the direction of flow which is located at the start of the second longitudinal part and which is followed by a series of louvers.

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

[0065] "Irregularly spaced" means that, if there are two planar regions of change in flow direction, these two planar regions do not divide the total length of the interlayer into three portions of equal length. If there are three flat regions of change of flow direction, the three flat regions do not divide the total length of the interlayer into four portions of the same length, etc.

[0066] Thus, thanks to the interlayer according to the invention, it is possible to generate heat exchange coefficients which are asymmetrical along the fluid path. In particular, it is possible to provide greater heat exchanges, for example, at locations where the heat transfer fluid has been heated upstream.

[0067] It is understood that the interlayer is made asymmetrical due to the asymmetrical location of the flat flow direction change region. The asymmetrical interlayer according to the invention is notably different from an interlayer which would be provided with a central flow direction change region, or different from an interlayer which would be provided with several flow direction change regions which 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 direction of corrugation 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 zone for placing the external face, and in the first longitudinal part, the fins comprise, between louvers, a flat region for changing the direction of flow, 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 flat region for changing the direction of flow which is located at the start 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 external face.

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

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

[0073] The louver pitch can be constant along each longitudinal portion of the spacer.

[0074] In this case, the pitch of the shutter may change when moving from one longitudinal part to the next.

[0075] According to one aspect of the invention, the corrugated fins of the spacers 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(P1)

[0077] In the case where corrugated fins delimit three or more longitudinal portions, the first longitudinal portion which is opposite the first placement zone comprises a flat region of change of direction of flow which is located in the middle of this first longitudinal portion, while the following longitudinal portions (in the direction of flow of the heat transfer fluid) each comprise a flat region of change of direction of flow which is located at the start of the longitudinal portion considered.

[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 an opposite side of the flank.

[0079] In other words, when considering a reference plane that contains the sidewall, one of the series of louvers is oriented with a positive angle relative to this reference plane, and the other series of louvers is oriented with a negative angle relative 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, successive series of shutters, by changing sign, also see a change in the absolute value of the angles.

[0082] In other words, the shutters in the downstream longitudinal part can be oriented with an angle (of absolute value) greater than the angle of the shutters 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 flat region between two series of successive shutters.

[0084] According to one aspect of the invention, the series of shutters 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 the other.

[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 flow direction change.

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

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

[0089] All the louvers from the fluid inlet to the fluid outlet have 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 in the enclosure is unique. The spacer is notably made of a single piece. Thus, the pitch of the shutters can vary along this single spacer.

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

[0093] According to one aspect of the invention, the shutter 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 split as one approaches the fluid outlet, so that the heat exchange coefficient increases. This allows the wall temperature to be balanced at the different placement areas of the external face.

[0095] The invention also relates to an interlayer, in particular configured to be placed in an enclosure of a thermal regulation device, on a fluid path in the enclosure, the interlayer comprising shutters and, between the shutters, a region flow direction change plane which is present on the interlayer at an asymmetrical 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: - make the shutters with a disc of chosen thickness to obtain a shutter pitch of a predetermined value.

[0097] Other characteristics, details and advantages of the invention will emerge more clearly on reading the description which follows on the one hand, and several examples of embodiment given for informational and non-limiting purposes with reference to the appended schematic drawings on the other hand, in which:

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

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

[0100] [Fig. 3] Figure 3 which shows, on the one hand, the spacers 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 figure 1;

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

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

[0103] The features, variants and different embodiments of the invention may be combined with each other in various combinations, 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 below in isolation from the other features described, 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 Figure 1.

[0105] The thermal regulation device 1 is part of an assembly 100 which comprises electronic components 2 placed on an external face 10 of the thermal regulation device 1 to be cooled by the flow of fluid (for example glycolated water) in the thermal regulation device 1. These components 2 are in particular electronic power modules of an inverter or battery cells, and are placed on the external face 10, at location zones 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 in direction X. 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 axis X, 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 enclosure 14 configured to receive a heat transfer fluid, this enclosure 14 comprising a fluid path 15 between the fluid inlet 5 and the fluid outlet 6. The enclosure 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 aluminum.

[0110] These plates 40 and 41 each comprise a peripheral edge 44 and a main recess 45 surrounded by the peripheral edge, and the plates 40 and 41 are assembled along the peripheral edge 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 on the fluid path. The spacers 21, 22, 23 can be brazed with the plates 40 and 41.

[0113] The spacers 21, 22, 23 are configured to serve as a heat exchange surface between the heat transfer fluid which circulates 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 (therefore to the X axis). The corrugated fins 25 of the spacers 21, 22, 23 extend successively in a first section T1 of the fluid path, a second section T2 of the fluid path which is downstream of the first section T1, and a third section T3 of the fluid path which is downstream of the second section T2.

[0115] As illustrated in Figure 3 (which shows, on the one hand, the spacers 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 spacers 21, 22, 23 have a pitch FP which decreases 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 section T1 of the fluid path passes under the first placement zone 110 of the external face 10, the second section T2 of the fluid path passes under the second placement zone 110 of the external face and the third section T3 of the fluid path passes under the third placement zone 110. Thus the corrugated fins 25 of the spacers 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 another is increased. With more undulations, the heat exchange surface, and therefore the surface density, increases. Consequently, the heat exchanges are increased in the second section T2 compared to the first section T2, etc. The invention thus makes it possible to compensate for the increase in the temperature of the heat transfer fluid along the fluid path by a larger heat exchange surface where the temperature of the heat transfer fluid is higher. The invention makes it possible to have a wall temperature on the different placement zones 11à where the components to be cooled are placed, 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 spacers 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 rectilinear 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 spacer 21, 22, 23 have a constant pitch FP between all the corrugations.

[0125] Alternatively, for at least one of the interlayers, the pitch changes between at least some of the undulations within the interlayer, in particular in the same placement zone.

[0126] The corrugated fins 25 of the spacers 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 example not illustrated, a number of successive sections of the fluid path greater than 3 is possible, with therefore a number of spacers greater than 3.

[0129] On the contrary, it would be possible for at least one of the spacers to extend 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 clearance between two successive spacers. In other words, the successive spacers 21, 22, 23 do not touch each other.

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

[0133] The fins 25 of the spacers 21, 22, 23 are provided with shutters 30, as can be seen in figure 4.

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

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

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

[0137] A corrugation thus has two sides 33 which join along a crest 34.

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

[0139] Each flank 33 extends substantially along a plane Pfla 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 shutters 30 seen along the Pfla plane (in the middle).

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

[0142] The 30 shutters have an LP shutter pitch along the X axis.

[0143] The LP shutter pitch is the distance between two consecutive 30 shutters.

[0144] In an exemplary embodiment of the invention, the shutters 30 follow one another with a constant shutter pitch LP.

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

[0146] In an exemplary embodiment of the invention illustrated in FIG. 5, there is arranged in the enclosure 14 an insert 50 which comprises a first longitudinal part P1, 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 P1, P2, P3 is opposite a placement zone 110 of the external face 10.

[0148] In the first longitudinal portion P1, the fins 25 comprise, between louvers 30, a flat region 51 for changing the direction of flow, which is located substantially in the middle of this first longitudinal portion P1, while, in the second and third longitudinal portions P2 and P3 of the insert 50, in the direction of flow of the heat transfer fluid, the fins 25 comprise a flat region 52, respectively 53, for changing the direction of flow which is located at the start of the second longitudinal portion P2, respectively of the third longitudinal portion P3, and which is followed by a series of louvers 30. The flat regions for changing the direction of flow 51, 52, 53 are thus present on the insert 50 at respective locations which are spaced irregularly along the fluid path.

[0149] The shutter pitch LP can be constant along each longitudinal part P1, P2, P3 of the spacer 50.

[0150] In this case, the pitch of the shutter LP changes when moving from one longitudinal part P1, P2, P3 to the next.

[0151] For example, the corrugated fins 25 of the spacers 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 P1.

[0152] The corrugated fins 25 of the spacers 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(P1) and LP(P3) <80%*LP(P2)

[0154] The fin flanks 33 have a series of louvers 30 oriented on one side of the flank 33, followed by another series of louvers 30 oriented on an opposite side of the flank 33.

[0155] In other words, when considering the reference plane Pfla which defines the flank 33, one of the series of louvers 30 are oriented with a positive angle A1 relative to this reference plane Pfla, and the other series of louvers 30 are oriented with a negative angle A2 relative to this reference plane Pfla. In other words, the louvers 30 on either side of the flat region 51, 52, 53 of change of direction of flow are mirror symmetrical relative to this region.

[0156] The positive angle and the negative angle are equal up to the sign. Alternatively, successive series of shutters, 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 flat region between two successive series of shutters 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 direction of flow, when the heat transfer fluid passes from one series of louvers to the other.

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

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

[0161] The absolute value of the angles A1 and A2 of the shutters 30 can be between 10° and 50°.

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

[0163] Alternatively, several spacers may be accommodated in the enclosure, and each spacer defines a longitudinal portion.

[0164] The LP shutter pitch decreases from one spacer to the next but the shutter 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, so that the heat exchange coefficient is increased. This makes it possible to balance the wall temperature at the different placement areas of the external face.

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

[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 slight deformation of the interlayers.

Claims

CLAIMS

1. Thermal regulation device (1) for cooling and / or heating at least one component (2) whose operation is sensitive to temperature, this component (2) being in particular an electronic power module of an inverter or a battery cell or a microprocessor, this thermal regulation 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 spacers (21, 22, 23) arranged in the enclosure (14), one after the other on the fluid path, the spacers (21, 22, 23) being configured to serve as a heat exchange surface between the heat transfer fluid which circulates in the enclosure (14) and an external face (10), and the spacers (21, 22, 23) comprising corrugated fins (25) with a direction of undulation which is substantially transverse to the fluid path, the corrugated fins of the spacers (21, 22, 23) extending in a first section (T1) of the fluid path and a second section (T2) of the fluid path which is downstream of the first section, the corrugated fins (25) of the spacers (21, 22, 23) having a fin pitch (FP) which is smaller in the second section (T2) than in the first section (T1) of the fluid path.

2. 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 placing a component and a second placement zone (110) for placing another component, these first placement zone and second placement zone being arranged one after the other so that the first section (T1) of the fluid path passes under the first placement zone of the external face and the second section (T2) of the fluid path passes under the second placement zone of the external face so that the corrugated fins (25) of the spacers (21, 22, 23) have a fin pitch which 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, in which the spacers (21, 22, 23) extend substantially over the entire length of the enclosure (14), and in particular the fluid path is generally rectilinear between the fluid inlet and the fluid outlet.

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

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

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

9. Thermal regulation device (1) according to one of the preceding claims, in which at least one of the spacers (21, 22, 23), in particular all the spacers (21, 22, 23), comprises at least one fin provided with shutters (30).

10. Thermal regulation device (1) according to one of the preceding claims, in which the fin flank (33) comprises a region of change in flow direction (51, 52, 53) of heat transfer fluid, formed in particular by a flat region between two successive series of louvers, and in particular the series of fins on either side of the flat region are respectively oriented with angles of opposite signs.

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