Electrical energy storage device with dual thermal control and associated vehicle.

Abstract

The invention relates to a thermally controlled energy storage device for an electric vehicle, having high heat dissipation capacities. The device comprises: - a plurality of electric cells (101) - a first heat exchange device comprising a bent gravity heat pipe (111), in heat exchange capacity with one side of the cells (101) and a cold source of a second heat exchange device (120), the cold source comprising at least two cold plates (121-122). The second heat exchange device (120) comprises at least one pulsed heat pipe (123) having: - a first wing (123a) extending under a condensation portion of the gravity heat pipe and in heat exchange capacity with a portion of the edge of the cells (101) - a second wing (123b) extending in heat exchange capacity with at least one of the cold plates (121-122); - a core (123c) connecting the wings (123a, 123b). Figure for the abbreviation: Fig. 6

Description

Title of the invention: Dual thermal control electrical energy storage device and associated vehicle.

[0001] The invention relates to the technical field of thermal control or mastery of devices for storing electrical energy in chemical form for electric vehicles, in other words electrical accumulators or so-called "power" batteries (as opposed to accessory batteries fitted to thermal vehicles and only used to start the thermal engine and to power the vehicle's equipment).

[0002] As is known, an electric battery is a set of electrical accumulators connected together so as to create an electrical generator of desired voltage and capacity. These accumulators are often called battery elements or cells. Such a battery, and therefore these accumulators or cells, allow(s) to store electrical energy in chemical form and to restore it to the electric motor in the form of direct current, in a controlled manner.

[0003] Among the disadvantages of batteries, we can note: - their high costs, - their autonomy, - their charging time, - the difficulty in controlling the temperature they reach, particularly in situations of "(ultra)fast charge" ("(ultra)fast charge" in English), which can lead to the destruction of the battery, or even the vehicle.

[0004] Being able to cool, or more generally thermally control one or more cells is therefore a major objective.

[0005] Conventionally, the battery comprises a plurality of electrical cells arranged parallel to each other, along a line, each cell having two faces connected by a peripheral edge comprising at least a first side, a second side and a third side, the second side and the third side being parallel to each other and transverse to the first side.

[0006] Three types of cells exist: so-called "prismatic" cells, so-called "pouch" cells, and so-called "cylindrical" cells.

[0007] The invention only concerns “prismatic” cells, and “pocket” or “pouch” cells.

[0008] A prismatic cell carries the electrical terminals on the first side only. In other words, the first side carries the anode terminal and the cathode terminal, spaced apart from each other by a determined distance, the second and third sides being free of any boundary.

[0009] A pouch cell carries the electrical terminals laterally, in the use position, that is to say that the anode and cathode terminals are located on only the second side and third side of the cell, one terminal per side. In other words, if the second side carries the anode terminal, then the third side carries the cathode terminal and vice versa, the first side being free of any terminal.

[0010] The present invention relates to both types of cells, prismatic and pocket.

[0011] Thermally controlled devices comprising a battery are already known. electric and at least one cold plate capable of heat exchange with the battery cells.

[0012] The cold plate comprises two parallel faces, between which a channel for circulating a heat transfer fluid winds thanks to a pump. The channel comprises a fluid inlet and outlet connected to an external fluid circuit which connects, in a closed loop, the channel of the cold plate to a heat exchanger with the surrounding air, typically a radiator.

[0013] The cold plate is thus placed against the battery by one of its faces (preferably by means of a layer of thermal interface material, or TIM) to allow the capture of calories coming from the battery and to conduct them towards the radiator for evacuation from the vehicle.

[0014] This device is very simple, and only allows heat to escape through one side of the cold plate. Its thermal regulation capabilities are therefore limited.

[0015] The invention proposes a much more efficient system allowing, in particular, to take advantage of both sides of the cold plate.

[0016] Indeed, the thermal capacities of this device do not allow all the heat necessary to be evacuated when charging the batteries, and there is a significant need to propose a thermally controlled device for storing electrical energy having high thermal evacuation capacities.

[0017] It is also necessary that this heat evacuation is carried out in such a way as to obtain a temperature distribution within the cell which is both as homogeneous as possible, and in which the difference between the highest temperature and the lowest temperature does not exceed ten degrees Celsius, preferably five degrees Celsius, advantageously three degrees Celsius.

[0018] This need must also be met while limiting the size and / or weight of the entire device comprising the electricity storage cells and the thermal management part.

[0019] Also proposed is a thermally controlled device for storing electrical energy in chemical form for a vehicle, the device comprising: - a plurality of electrical cells; - a first heat exchange device comprising an angled gravity heat pipe having an evaporation part capable of heat exchange with one side of the cells and a condensation part capable of heat exchange with a cold source of a second heat exchange device, the cold source comprising at least two cold plates; the second heat exchange device comprising at least one pulsed heat pipe having: - a first wing extending under the condensation part of the gravity heat pipe and capable of heat exchange with part of the cell section; - a second wing extending in heat exchange capacity with at least one of the cold plates; - a soul connecting the wings.

[0020] More specifically, the thermally controlled device may comprise: - an electric battery having a plurality of electric cells each having two faces connected by an edge, where the cell is thinnest and where at least a first side, a second side and a third side are located, the second side and third side being parallel to each other and transverse to the first side, each cell comprising a cathode terminal and an anode terminal located on one side or on two different sides of the edge, the terminals of adjacent cells being connected to each other to form the battery, the cells being arranged parallel to each other, in a longitudinal direction, face to face, the thermally controlled device being characterized in that it further comprises: - a first heat exchange device comprising a gravity heat pipe capable of heat exchange with at least the second side or the third side of the cells and a cold source of at least one second heat exchange device, first heat exchange device in which: * the gravity heat pipe comprises a body internally integrating a series of juxtaposed channels containing a heat-transfer substance and two transverse volumes into which the ends of the channels open so that they communicate fluidically with each other via these transverse volumes; * the body of the gravity heat pipe is bent, in an L or C shape, so that the channels each have at least one curved part located between two wings, a first wing carrying at least one vaporization part and a second wing carrying a condensation part, the condensation part being located at a higher elevation level than that of the vaporization part relative to gravity in the position of use; * the gravity heat pipe is arranged so that the first wing carrying the part vaporization extending laterally opposite the second side or the third side of the cell slice at a first distance, preferably zero, while the second wing of the gravity heat pipe carrying the condensation part extending laterally above the first side of the cell slice, at a second distance strictly greater than the first distance; the second heat exchange device comprising: - the cold source which comprises at least a first cold plate and a second cold plate in which a heat transfer fluid circulates between an inlet and an outlet, the first and second cold plates extending parallel to each other, longitudinally, flat and facing the first side of the cells; - at least one pulsed heat pipe comprising a body internally integrating at least one channel closed on itself to form a loop and incorporating a heat-transfer substance, the channel having convolutions and extending between an evaporation part in thermal contact with at least a part of the first side of the slice of the cells, and a second condensation part in thermal contact with a face of each of the first and second cold plates, the body of the pulsed heat pipe being bent in C to present: - a first wing extending longitudinally between the first side of the cell slice and the condensation part of the gravity heat pipe(s), and comprising the evaporation part with heat exchange capacity with at least part of the first side of the cell slice, - a second wing parallel to the first wing and comprising the condensation portion extending in heat exchange capacity with at least one of the first and second cold plates; - a soul connecting the first and second wing.

[0021] According to other embodiments: - - the second wing of said at least one pulsed heat pipe can extend between two of said at least two cold plates and be capable of heat exchange with two of said at least two cold plates; -1 device may comprise at least one first pulsed heat pipe and at least one second pulsed heat pipe and in which: * the first wing of the first pulsed heat pipe extends longitudinally between the first side of the cell slice and the condensation portion of the gravity heat pipe(s), and in heat exchange capacity with a first half-length of the first side of the cell slice, and the second wing of the first pulsed heat pipe extends between, and in heat exchange capacity with, the first and second cold plates; and * the first wing of the second pulsed heat pipe extends longitudinally between the first side of the cell slice and the condensation part of the gravity heat pipe(s), and in heat exchange capacity with a second half-length of the first side of the cell slice, and the second wing of the second pulsed heat pipe extends in heat exchange capacity with a free face of the second cold plate; - the device may comprise at least one first pulsed heat pipe and at least one second pulsed heat pipe and in which: * the first wing of the first pulsed heat pipe extends longitudinally between the first side of the cell slice and the condensation portion of the gravity heat pipe(s), and it is capable of heat exchange with a length of the first side of the cell slice, and the second wing of the first pulsed heat pipe extends between, and is capable of heat exchange with, the first and second cold plates; and * the first wing of the second pulsed heat pipe extends longitudinally under the fourth side of the cell slice, and it is capable of heat exchange with a length of the fourth side of the cell slice, and the second wing of the second pulsed heat pipe extends in heat exchange capacity at least with a free face of the second cold plate; - the cold source of the second heat exchange device may comprise at least a third cold plate; - the third cold plate can be arranged parallel to and opposite the second cold plate, with heat exchange capacity with the second wing of the second pulsed heat pipe; - the third cold plate can be arranged against the first cold plate, capable of heat exchange with said at least one gravity heat pipe, the first and second cold plates being connected to a first heat transfer fluid circuit and the third cold plate being connected to a second heat transfer fluid circuit independent of the first heat transfer fluid circuit; - the cold source of the second heat exchange device may comprise a fourth cold plate arranged parallel to and opposite the second cold plate, capable of heat exchange with a free face of the second wing of the second pulsed heat pipe; - the pulsed heat pipe(s) may be in thermal contact against the first side and / or the fourth side of the cell or of the terminals carried by said first side, a layer of electrically insulating material being interposed between the pulsed heat pipe(s) and the first side of the cell or of the terminals carried by said first side; - the cold plates and the pulsed heat pipe(s) can be in a single block within from which the cold plates and the pulsed heat pipe(s) are functionally separated from each other by a single wall; - the device may further comprise a housing in which the plurality of cells are arranged, the housing comprising: * a base on which the cells and a plurality of gravitational heat pipes rest, and * a clamping means configured to clamp each gravity heat pipe against the second side and / or the third side of the cell(s) located opposite, so that the or each vaporization part of the gravity heat pipe(s) is pressed against the cell(s) located opposite; - the clamping means may comprise upright walls, resting against the bottom and surrounding the cells and the plurality of said gravity heat pipes, as a whole; and / or the cold plate that covers the second wing of the second pulsed heat pipe, can be fixed to the housing so that all the cells and all the gravity heat pipes and pulsed heat pipes, as a whole, are clamped between the housing and the cold plate that covers the second wing of the second pulsed heat pipe.

[0022] The present solution also relates to an electric or hybrid vehicle comprising: - at least one electric motor to move it, and - at least one preceding thermally controlled device connected to the electric motor to supply it with electricity; - at least one electrical outlet connected to said at least one thermally controlled device to charge it with electricity.

[0023] Other characteristics of the invention will be set out in the detailed description below, given with reference to the appended drawings, which illustrate, respectively:

[0024] [Fig-1] a schematic view of the principle of an electric vehicle equipped with a thermally controlled device according to the invention;

[0025] [Fig.2] a schematic perspective view of a gravity heat pipe used in the thermally controlled device according to the invention;

[0026] [Fig.3] a schematic perspective view, seen from below, of a pulsed heat pipe used in the thermally controlled device according to the invention;

[0027] [Fig.4] a schematic view of the operating principle of the pulsed heat pipe of the [Fig.3] used in the thermally controlled device according to the invention;

[0028] [Fig.5], a schematic perspective view of the principle of the first device heat exchange of a thermally controlled device according to the invention, comprising gravity heat pipes;

[0029] [Fig.6], a schematic sectional view of the first and second heat exchange device of a first embodiment of a device thermally controlled according to the invention, comprising a pulsed heat pipe and two cold plates;

[0030] [Fig.7] a schematic view of the principle in longitudinal section of a second embodiment of a thermally controlled device according to the invention, comprising two pulsed heat pipes and two cold plates;

[0031] [Fig.8] a schematic view of the principle in longitudinal section of a third embodiment of a thermally controlled device according to the invention, comprising two pulsed heat pipes and three cold plates, the condensation part of each of the pulsed heat pipes being in contact with two of the three cold plates;

[0032] [Fig.9] a schematic view of the principle in longitudinal section of a fourth embodiment of a thermally controlled device according to the invention, comprising a pulsed heat pipe and two cold plates applied against each other, forming a double cold plate between the condensation part of the gravity heat pipe and the condensation part of the pulsed heat pipe;

[0033] [Fig. 10] a schematic view of the principle in longitudinal section of a fifth embodiment of a thermally controlled device according to the invention, comprising a pulsed heat pipe, two cold plates applied against each other, forming a double cold plate between the condensation part of the gravity heat pipe and the condensation part of the pulsed heat pipe, and a terminal cold plate covering the other face of the condensation part of the pulsed heat pipe and thus covering the assembly;

[0034] [Fig. 11] a schematic view of the principle in longitudinal section of a sixth embodiment of a thermally controlled device according to the invention, comprising two pulsed heat pipes, two cold plates applied against each other, forming a double cold plate between the condensation part of the gravity heat pipe and the condensation part of a first pulsed heat pipe, and an intermediate single cold plate, that is to say in thermal contact with on the one hand the condensation part of the first pulsed heat pipe and on the other hand the condensation part of the second pulsed heat pipe;

[0035] [Fig. 12] a schematic view of the principle in longitudinal section of a seventh preferred embodiment of a thermally controlled device according to the invention, similar to the sixth embodiment, but comprising a fourth terminal cold plate covering the other face of the condensation part of the second pulsed heat pipe and thus capping the assembly;

[0036] [Fig. 13] a schematic view of the principle in longitudinal section of an eighth embodiment of a thermally controlled device according to the invention, comprising two pulsed heat pipes and three cold plates, the condensation part of each of the pulsed heat pipes being in contact with two of the three cold plates, the first branch of a first pulsed heat pipe being capable of heat exchange with the first side of the cell slice, and the first branch of a second pulsed heat pipe being capable of heat exchange with the fourth side of the cell slice;

[0037] [Fig. 14] a schematic view of the principle in longitudinal section of a ninth preferred embodiment of a thermally controlled device according to the invention, similar to the sixth embodiment, but comprising a fourth terminal cold plate covering the other face of the condensation part of the second pulsed heat pipe and thus covering the assembly, the first branch of a first pulsed heat pipe being capable of heat exchange with the first side of the slice of the cells, and the first branch of a second pulsed heat pipe being capable of heat exchange with the fourth side of the slice of the cells;

[0038] [Fig. 15] a realistic schematic perspective view, partially exploded, in operational position of a tenth embodiment of a thermally controlled device according to the invention, and comprising pocket cells, gravity heat pipes capable of heat exchange with the second and third sides carrying the electrical terminals, a first pulsed heat pipe whose first branch is arranged in capacity for heat exchange with the first side of the slice of the cells, and a second pulsed heat pipe whose first branch is arranged in capacity for heat exchange with the fourth side of the slice of the cells;

[0039] [Fig. 16] a realistic schematic perspective view, partially exploded, in operational position with clamping means, of a first variant of the seventh preferred embodiment of [Fig. 12] of a thermally controlled device according to the invention, comprising frontally two pulsed heat pipes whose condensation part is inserted between the double cold plate and the intermediate cold plate, and dorsally, not visible, two pulsed heat pipes whose condensation part is inserted between the intermediate cold plate and the terminal cold plate;

[0040] [Fig. 17] a partial realistic schematic cross-sectional view of the thermally controlled device of [Fig. 16];

[0041] [Fig. 18] a partial realistic schematic view in longitudinal section of the thermally controlled device of [Fig. 16];

[0042] [Fig. 19] a partial realistic schematic view in longitudinal section of the thermally controlled device of [Fig. 16], in which the stack of cold plates and pulsed heat pipes is made in a block in which the separation between a cold plate channel and a pulsed heat pipe channel is constituted by a single wall;

[0043] [Fig.20] a realistic exploded schematic perspective view of the assembly of cold plates and pulsed heat pipes of the seventh embodiment;

[0044] [Fig.21] a realistic exploded schematic perspective view of the cold plate double of the seventh embodiment;

[0045] [Fig.22] a realistic schematic sectional view of an outlet of the ca- fluid circuit carrier outside the cold plates in contact with the pulsed heat pipes;

[0046] [Fig.23] a realistic schematic sectional view of an outlet of the ca- fluid circuit the carrier outside the cold plate in contact with the gravity heat pipes;

[0047] [Fig.24] a realistic schematic front view, in operational position of a second variant of the seventh preferred embodiment of a thermally controlled device according to the invention, comprising frontally a pulsed heat pipe whose condensation part is inserted between the double cold plate and the intermediate cold plate, and a pulsed heat pipe whose condensation part is inserted between the intermediate cold plate and the terminal cold plate, and comprising dorsally, partially visible, two heat pipes similar to the first arranged in opposition;

[0048] [Fig.25] a schematic view of the principle of a thermally controlled device according to the invention, the cold plates of which are connected to an operational heat transfer fluid circuit;

[0049] [Fig.26] a schematic view of the temperature gradient obtained within a cell in a thermally controlled device comprising only L-shaped gravity heat pipes; and

[0050] [Fig.27] a schematic view of the temperature gradient obtained within a cell in a thermally controlled device comprising a combination of L-shaped gravity heat pipes and C-shaped pulsed heat pipes.

[0051] In this text, the expressions “vertical” and “along the Earth’s gravitational field” are equivalent, and “horizontal” and “perpendicular to the Earth’s gravitational field” are equivalent.

[0052] What is described below refers to observations made in the (functional) use position of the device, in which the cell walls extend vertically, and the gravity heat pipes (see definition below) are located laterally and above the cells (possibly also below when the gravity heat pipes are C-shaped). In this position, the first side of the cell edge is horizontal and constitutes the top of the cells. The fourth side constitutes the bottom, and the second and third sides constitute the lateral edges of the cells.

[0053] In this position also, the second heat exchange device comprising the cold plates and the pulsed heat pipes (see definition below) is located either above the cells (see Figures 6 to 12), or above and below the cells (see Figures 13 to 15). The cold plates are arranged horizontally, parallel to all of the first sides of the cell slices. The two wings of the C-shaped pulsed heat pipes also extend horizontally and parallel to the cold plates and to all of the first sides and / or the fourth sides of the cell slices. Consequently, the core connecting the two wings of the pulsed heat pipes extends substantially vertically, even if it may have a curvature: the portion of the core connected to the first wing comprising the evaporation part is located below the portion of the core connected to the second wing comprising the condensation part, relative to the direction of gravity.

[0054] Indeed, generally speaking and as provided here, in a heat pipe, the vaporization of a liquid in contact with a hot source makes it possible to absorb a large quantity of energy efficiently and to restore it to a cold source distant from the hot source, thus making it possible to regulate the temperature of the hot source by maintaining, lowering, or limiting the increase in temperature depending on the case).

[0055] Heat pipes are, or contain, thermally conductive tubes or channels, often made of metal, used to transport heat using the principle of phase transition transfer (also called phase change). The channels are included in the "body", which forms a closed (watertight, hermetic) single-piece enclosure around them. Depending on the heat pipes used, they include several juxtaposed channels arranged in parallel, or a single channel closed on itself and forming convolutions. These two types of channels will be described in more detail later.

[0056] The heat pipes comprise a vaporization part where the heat transfer substance can be heated, until it is vaporized, by calories from at least one of the hot sources (in the present application, these are the cells), and a condensation part where the heat transfer substance can be cooled, until it is condensed, by heat exchange with a cold source (in the application a cold plate).

[0057] The heat pipe(s) concerned here, unlike cold plates, do not require a pumping element (porous body, pump, etc.) to operate. They are therefore closed, sealed devices containing a heat-transfer substance, i.e. for the entirety of the present disclosure, a phase-change fluid, in liquid phase at the condensation temperature useful for the domain concerned, in equilibrium with its vapor phase at the vaporization temperature useful for the domain concerned, the movement of the heat-transfer substance being generated by a difference in state and not by a pumping element.

[0058] According to the invention, two types of heat pipes are used in combination.

[0059] The first type of heat pipe is called “gravitational” and is illustrated in [Fig.2].

[0060] A gravity heat pipe 20 according to the invention has a bent body 21 having two ends 22-23 and internally integrating a series of parallel juxtaposed micro-channels 24 containing a heat-transfer substance.

[0061] At each of the ends 22-23 of the heat pipe there is a transverse volume, respectively 25 and 26, into which the channels open so that they communicate fluidically with each other via these transverse volumes 25 and 26. The latter therefore allow balancing of fluid (communicating vessel principle) and / or pressure (in especially in the vapor phase) at the ends of the heat pipe.

[0062] The first end 22 of the gravity heat pipe is intended to be arranged, in the position of use, in a heat exchange capacity with a hot part of the cells (the second and / or the third side), and the second end 23 of the gravity heat pipe is intended to be arranged, in the position of use, in a heat exchange capacity with a cold source of a second heat exchange device which will be detailed later.

[0063] Thus, the first end 22 of the bent gravity heat pipe has a vaporization part PV where the heat transfer substance can be heated, until it is vaporized, by calories from at least one of the cells, and the second end 23 of the bent gravity heat pipe has a condensation part PC where the heat transfer substance can be cooled, until it is condensed, by heat exchange with the cold source of the second heat exchange device.

[0064] In other words, in a gravity heat pipe, the condensation part PC is located at a higher elevation level than that of the vaporization part PV relative to gravity.

[0065] The first type of heat pipe is therefore called “gravitational”, in the sense that the internal geometry of the channels 24 and the transverse volumes 25 and 26 ensures that the return of the heat-transfer substance from the condensation part PC to the vaporization part PV is done by gravity, as opposed to capillary heat pipes where the fluid movements are done by capillarity thanks to a porous material, or wick, present in the channels of the heat pipe. Capillary heat pipes are therefore not concerned by the present invention.

[0066] The gravity heat pipes advantageously used in the invention as a first heat exchange device can be of several types of operating modes: flooded, thermosiphon or pulsed. The preferred arrangement according to the invention has particularly efficient thermal performance with gravity heat pipes having a hybrid operating mode between thermosiphon and pulsed. This hybrid operation means that a succession of vapor pockets separated by liquid will circulate by gravity difference from the evaporation zone to the condensation zone. In pure thermosiphon, the bubbles gather in the center of the channel until only vapor rises to the condensation zone.

[0067] This succession of steam pockets allows for optimal heat exchange efficiency.

[0068] In the vaporization part, or evaporator, the liquid is heated by the cells in thermal contact with the evaporator. The liquid evaporates to the condensation part, or condenser, in which the vapor is condensed. The condenser is in thermal contact with the cold source of the second heat exchange device (described below), allowing the heat transported by the heat pipe to be evacuated from the second and / or third side of the cells. The condensate then joins the evaporator, by gravity. The liquid then undergoes new evaporation / condensation cycles allowing heat to be evacuated from the cells to the cold source.

[0069] For the heat pipe to operate by gravity, the channels, enclosed in the sealed body, stand up, with the condensation part located at a higher elevation level than that of the vaporization part relative to gravity.

[0070] Under these conditions, the curved portion 27 located between the vaporization portion and the condensation portion must be understood as located between the end 22 of the vaporization portions PV and the opposite end 23 of the condensation portion PC, following the main elongation direction of the heat pipe channels. The curved portion is an adiabatic intermediate zone, where the heat transfer substance undergoes no or very little heat exchange.

[0071] The second type of heat pipe is called “pulsed” and is illustrated in Figures 3 and 4.

[0072] As illustrated in [Fig.3], a pulsed heat pipe 30 used in the invention comprises a body 31 internally integrating at least one channel 32 (or tube) closed on itself to form a loop and incorporating a heat-transfer substance.

[0073] The channel 32 having convolutions 33 (that is to say curved parts following straight or inverted curved parts) to form a coil of length much greater than the length of the body 31 of the pulsed heat pipe 30.

[0074] The body of the pulsed heat pipe 30 according to the invention is bent in C to present: - a first wing 31a comprising the evaporation part intended to be arranged in heat exchange capacity with at least a part of the first side or the fourth side of the slice of the cells, - a second wing 31b parallel to the first wing 31a and comprising the condensation part intended to be arranged in heat exchange capacity with at least one cold plate; and - a core 31c connecting the first wing 31a and the second wing 31b.

[0075] Thus, the channel 32 extends between the evaporation part located in the first wing 31a and intended to be in thermal contact with a hot surface of the cells (the first or fourth side of the slice of the cells), and a condensation part located in the second wing 32b and intended to be in thermal contact with a face of a cold plate.

[0076] [Fig.4] is a schematic representation of the operating principle of two pulsed heat pipes 30 arranged flat between a hot surface SC and a cold surface SF. It will be noted on this occasion that the cold surface advantageously has a greater large heat exchange area with the pulsed heat pipe 30 than the hot surface. This principle is also applied in the preferred embodiments of the invention.

[0077] In use, the heat transfer substance 34 evaporates locally in the evaporation part in heat exchange capacity with the hot surface SC, and by increasing the pressure moves towards the condensation part arranged in heat exchange capacity with the cold surface SF. Concomitantly, the heat transfer substance condenses locally in the condensation part and, by decreasing the pressure, moves towards the evaporation part.

[0078] This results in the formation of a succession of vapor bubbles 34a and liquid portions 34b in the channel, and a natural closed-loop circulation between the evaporation and condensation parts, allowing the transfer of heat from the evaporation part to the condensation part.

[0079] The invention uses these two types of heat pipes in combination, allowing not only better heat evacuation, but also better heat homogeneity within the cells. In other words, this combination makes it possible to obtain a temperature gradient between the hottest point and the coldest point of the cell being charged which is both narrower and whose highest temperature is lower than that obtained with only one of the types of heat pipes. This is illustrated and described in relation to Figures 26 and 27.

[0080] It is thus possible to obtain a temperature difference between the hottest parts and the coldest parts of the cells (also called "temperature gradient") of between 5 and 7 degrees Celsius, whereas only one of the types of heat pipes (in particular the gravity heat pipe) is not capable of ensuring a temperature gradient of less than 25 degrees Celsius, which is already much lower than what can be obtained with the cold plates of the prior art.

[0081] In Figures 5 to 25 is thus illustrated, in whole or in part depending on the figures, a thermally controlled device 100 for storing electrical energy in chemical form for a vehicle 10 illustrated in [Fig.l].

[0082] The device according to the invention is intended to equip an electric or hybrid vehicle 10. As illustrated in [Fig.l], this vehicle comprises an electric motor 1, powered by a storage battery 2 connected to the engine 1 and, if it is hybrid, to an electric generator (not illustrated). In addition to the electric motor 1 and the battery 2, the vehicle 10 comprises a computer 3, an AC / DC charger / converter 4, a transmission 5 and a differential 6.

[0083] The computer 3 controls the energy flows via numerous sensors. It also manages the recharging of the battery 2 when the vehicle 10 is connected to a charging station. In particular, when a temperature sensor indicates that a battery module or a part of a battery module or a cell of a module If the battery temperature exceeds the safe temperature during charging (usually 45°C), the calculator 3 reduces the charging intensity, which lengthens the battery charging time, but preserves its integrity.

[0084] The cells of the battery 2 provide electrical energy which is stored therein. They are rechargeable, via an electrical outlet 7 connected to it through the computer 3 and the AC / DC charger / converter 4 (or a functional equivalent directly integrated into the battery modules; see below).

[0085] Indeed, the battery 2 delivering a direct current (DC) and the electric motor using an alternating current (AC), the vehicle 10 also comprises an AC / DC charger / converter 4.

[0086] The latter therefore has the primary function of converting the DC current from the battery into AC current usable by the motor.

[0087] The AC / DC charger / converter 4 also allows the battery to be charged by an AC charging station by converting the AC current into DC current for the battery 2, and / or by a DC charging station, the latter type of charging being the fastest, because the DC direct current is directly "injected" without conversion into the battery 2.

[0088] In a new generation of battery modules 2, the function of the AC / DC charger / converter 4 is provided by components directly integrated into each battery module, thus making them controllable independently of each other, and saving space in the vehicle. In addition to transforming the current from the battery to the motor, this makes it possible either to convert the AC current into DC current for the cells of the battery 2 when the vehicle is connected to an AC terminal, or to inject the DC direct current directly, without conversion, into the cells of the battery 2 when the vehicle is connected to a DC terminal.

[0089] In other words, by integrating the function of the AC / DC 4 charger / converter directly into each battery module, it is possible to do without an external AC / DC 4 charger / converter while allowing charging and discharging of the battery directly in AC. It is thus possible to do without the charger (AC / DC) during charging and the converter during discharging (DC / AC).

[0090] Thermal management of the battery and, in particular, homogeneous thermal management within a cell, but also within the modules and within the battery is therefore a major issue to ensure rapid charging of the battery while preserving its integrity. Thermal management in the case of direct AC alternating current will be all the more critical to maintain the ideal temperature during charging and discharging operations.

[0091] The current constraints are as follows: i) The maximum temperature within any cell of the battery (pouch or prismatic; see definitions below) must be less than 45°C; ii) The difference between the maximum temperature and the minimum temperature within any cell of the battery must be less than 6°C, preferably 4°C, advantageously 3°C; iii) The difference between the maximum temperature of two cells or two modules (sets of cells) must not exceed more than 5°C.

[0092] According to the invention, the battery 2 is composed of a set of thermal management devices 100, allowing the battery 2 (cells and modules) to be temperature controlled (amplitude, but also homogeneity of temperature gradient within the cells and within the modules), or even to be also mechanically protected, so that it does not overheat, at least when it is operating, and in particular when it is recharged with electrical energy.

[0093] A thermally controlled device 100 according to the invention is partially illustrated in [Fig.5], only its first heat exchange device being illustrated in combination with the cells, this for the sake of clarity of the figure and of the description concerning this part of the invention.

[0094] The thermally controlled device 100 comprises a plurality of electrical cells 101, also called accumulators, arranged parallel to each other, in a longitudinal direction LL.

[0095] The cells 101 each have two faces 102 connected by a slice 103 where the cell is thinnest and which goes around the cell. On this slice 103, there are located a first side 103a, a second side 103b, a third side 103c, and a fourth side 103d on which the cell 101 rests in the position of use.

[0096] The second and third sides 103b-103c are parallel to each other and transverse to the first side 103a and to the fourth side 103d.

[0097] Each cell 101 comprises a cathode terminal 104 and an anode terminal 105 located on a single side (the first side 103a) or on two different sides (the second 103b and the third side 103c) of the wafer 103, depending on the type of cell: - the prismatic cells (illustrated in [Fig.5]) carry the cathode terminal 104 and the anode terminal 105 on the first side 103a; - the pocket cells, or “pouch” in English, carry the cathode terminal 104 on the second side 103b and the anode terminal 105 on the third side 103c, or vice versa.

[0098] Each terminal 104-105 projects relative to the side which carries it. The terminals 104, respectively 105 of the adjacent cells are connected to each other to form the battery, by means of cables or connection combs (not shown in the figures), the cells being arranged parallel to each other, in the longitudinal direction LL, face 101a against face 101a.

[0099] In both cases, each cell 101 is substantially parallelepipedal, with along its edge 103, successively four sides, two by two adjacent and transverse. On the thinnest periphery, or edge, the first 103a and fourth 103d sides are the longest; these are the horizontal sides, respectively upper and lower with reference to the position of use. The second 103b and third 103c sides are the shortest; these are typically the vertical, lateral sides, respectively left and right, cell seen from the front, on one of its two largest opposite faces 102.

[0100] As known: - a prismatic cell is a cell having an externally rigid envelope or a rigid body in the shape of a rectangular parallelepiped where the first side, the second side, the third side and the fourth side are located, and - a pocket cell has an external envelope or flexible body where the first side, the second side, the third side and the fourth side are also located. A pocket cell is so called because of its sachet or pocket format.

[0101] As shown schematically in [Fig.5], the device 100 further comprises a first heat exchange device 110 comprising three “gravity” heat pipes 111 capable of heat exchange with a second 103b and / or third 103c on the side of the cells 101, and with a cold source of a second heat exchange device 120, not illustrated in this figure.

[0102] As explained previously, the gravity heat pipe 111 used in the invention as the first heat exchange device has an internal geometry of the channels which ensures that the return of the heat transfer substance from the condensation part to the vaporization part is done by gravity.

[0103] In the arrangement according to the invention, the gravity heat pipes 111 face the second 103b and / or third 103c side of the cells, and they have a first upright wing 111a, substantially vertical in the position of use, then are bent (above-mentioned bend), then have a second flat wing 111b, therefore substantially horizontal, which extends at least above at least a part of the first side 103a of the (each) cell concerned 101. In other words, the second flat wing 111b may be located above all or part of the first side 103a and / or below all or part of the fourth side 103d opposite the first side 103a.

[0104] This covers L-shaped, U-shaped (inverted) and C-shaped shapes. With an L-shaped or C-shaped shape, this is considered from bottom to top. With a U-shaped (inverted) shape, after the second horizontal (flat) wing 111b, the heat pipe continues with a second bend and then descends again, presenting a third, substantially vertical, upright wing, similar to the first upright wing 111a.

[0105] The (each) upright wing 111a includes the vaporizing portion. The wing 111b extending flat includes the condensation part. In other words, we can consider that the heat pipe, therefore the channels, is (are) bent in the adiabatic zone, between the vaporization and condensation parts which follow one another.

[0106] The channels, which therefore extend (each and together) between their ends, can communicate fluidically with each other, at one and / or the other of these ends, therefore at the lower end of the vaporization part and at the upper end of the condensation part.

[0107] The liquid phase of the heat transfer substance can then circulate from one channel to another, at the base of the heat pipe; the same applies to the vapor phase at the end of the condensation part.

[0108] Thus, the channels of the gravity heat pipe(s) extend parallel to the edge of the cells, vertically then horizontally.

[0109] The radius of curvature of the elbow will thus be a compromise between: - fluid continuity in the channels at this location, - a first minimum distance dl (preferably zero to obtain support) from the vaporization part of the heat pipe opposite (or against in the event of contact) the first, second or third side of the cell (or of each cell) located opposite the vaporization part (side without cathode and anode terminals), - a second distance d2, strictly greater than the first distance (projection of the cathode and anode terminals on the first side which carries them), sufficient to allow condensation in the condensation part of the horizontal wing 111b.

[0110] For mechanical / thermal synergy, it is provided that the first distance is zero by blocking the vertical wing 111a of the heat pipes 111 against the second 103b and / or third 103c sides of the cells (or the terminals carried by these sides for pocket cells). The gravity heat pipes 111 being rigid, this horizontal blocking ensures a blocking that is also vertical, in the sense that the horizontal wing 111b remains at the second distance from the first side 101a of the cells.

[0111] As illustrated in [Fig.5], the first heat exchange device 110 further comprises a clamping means 112 configured to clamp the vertical wing 11a of each heat pipe 111 against the second side 103b and / or the third side 103c of the cell(s) located opposite, so that the or each vaporization part is pressed against the cell(s) located opposite.

[0112] For example, the clamping means 112 consists of two C-shaped pieces surrounding the heat pipes at their vaporization portion, so as to constrain them against the cells when the assembly is inserted into the receiving housing (not shown) of the assembly. In other words, the clamping means 112 serves as a clamping spacer between the upright walls of the housing and the vaporization portions of the heat pipes.

[0113] Alternatively, the clamping means may comprise a spring bearing against the vaporization portion of the heat pipes and against either a spacer or the walls of the housing, so as to constrain the vaporization portions of the heat pipes against the second side and / or the third side of the cell(s) located opposite.

[0114] If the thermally controlled electrical energy storage device comprising only one or more gravity heat pipes is entirely satisfactory, the second distance between the horizontal part of the heat pipe and the first side of the cells must be large to allow condensation in the upper part of the heat pipe despite the heat released by the first side of the cell. The size of the device is therefore relatively large compared to the quantity of heat evacuated.

[0115] The idea behind the invention is to take advantage of the constraints of the previous gravity heat pipe to transform them into an advantage and allow greater heat evacuation.

[0116] Thus, according to the invention, the device uses the space located between the condensation part of the gravity heat pipe(s) and the first side of the cells to recover the heat emitted by this first side and evacuate it away from the cell and the gravity heat pipe, facilitating condensation within this gravity heat pipe and thus improving its efficiency and the temperature distribution within the cell by synergy effect.

[0117] According to the invention, the thermally controlled electrical energy storage device comprises a second heat exchange device 120 illustrated in FIGS. 6 to 15.

[0118] In the first embodiment of [Fig.6], the second heat exchange device 120 comprises a cold source 121-122 and a pulsed heat pipe 123.

[0119] The cold source 121-122 is used for condensation in the gravity heat pipe(s) 111 of the first heat exchange device and for condensation in the pulsed heat pipe(s) 123.

[0120] The cold source comprises at least a first cold plate 121 and a second cold plate 122 in which a heat transfer fluid circulates between an inlet 124a and an outlet 124b (see [Fig. 12]). The first 121 and second 122 cold plates extend parallel to each other, longitudinally, flat and facing the first side 103a of the cells 101.

[0121] The pulsed heat pipe 123 comprises a body bent in C to present: - a first wing 123a extending longitudinally between the first side 103a of the slice 103 of the cells 101 and the condensation part 111b of the gravity heat pipe(s) 111, and comprising the evaporation part, - a second wing 123b, parallel to the first wing 123a, and comprising the part of condensation; - a core 123c connecting the first wing 123a and the second wing 123b.

[0122] According to the invention, the first wing 123a is capable of heat exchange with at least a part of the first side 103a of the slice 103 of the cells 101, so that it is interposed between this first side 103a of the cells and the condensation part 111b of the gravity heat pipe 111 of the first heat exchange device 110.

[0123] The first wing 123a comprising the vaporization part of the pulsed heat pipe 123, it captures heat from the first side 103a of the cells, heat which thus does not diffuse towards the condensation part 111b of the gravity heat pipe 111, despite the distance separating it from the first side 103a of the cells.

[0124] Thus, at a distance identical to that provided in the prior devices, the condensation of the condensation part 111b of the gravity heat pipe 111 can therefore be done more easily.

[0125] As a corollary, with condensation identical to that obtained in the prior devices, it is possible to reduce the distance between the condensation part 111b of the gravity heat pipe 111 and the first side 103a of the cells (subject to leaving sufficient space to slide the first wing 123a of the pulsed heat pipe 123 therein), which makes it possible to improve the compactness of the device.

[0126] In other words, the second heat exchange device 120 not only acts by itself in regulating the temperature of the cells, but it has a synergistic effect on the entire thermally controlled electrical energy storage device, by improving the efficiency of the first heat exchange device 110, and by reducing the amplitude of the temperature gradient between the hottest point and the coldest point of each cell.

[0127] Figures 7 and 8 and 10 to 15 illustrate embodiments of a second heat exchange device that are more thermally efficient than the first of [Fig.6], and particularly suitable for large cell (or module) assemblies. For these large modules, two pulsed heat pipes can be arranged face to face.

[0128] In a first option illustrated in Figures 7, 8, and 10 to 12, each of the evaporation zones is arranged so as to cover a part (generally half the length) of the first side of the edge of the cells of the module. The evaporation zones are then opposite and on the same plane.

[0129] In a second option illustrated in Figures 13 to 15, the evaporation zone of a first pulsed heat pipe is arranged along the entire length of the first side of the module cell slice, and the evaporation zone of a second pulsed heat pipe is arranged along the entire length of the fourth side of the module cell slice. The condensation zones will in all cases be one above the other and separated by a cooling channel of a cold plate.

[0130] In the second embodiment illustrated in [Fig.7], the second heat exchange device 220 comprises a first pulsed heat pipe 223 and a second pulsed heat pipe 224 of two different types called A and B in the remainder of this description.

[0131] In both types A and B of pulsed heat pipe 223-224, the first wing 223a-224a of each of the pulsed heat pipes 223-224 extends longitudinally between the first side 103a of the slice 103 of the cells 101 and the condensation portion 111b of the gravity heat pipe(s) 111. Each of the first wings 223a-224a is capable of heat exchange with only a first half-length D / 2 of the first side 103a of the slice 103 of the cells 101, so that together, the first wings 223a-224a of the pulsed heat pipes 223-224 are in thermal contact longitudinally with the entire first side 103a of the slice 103 of the cells 101.

[0132] The first pulsed heat pipe 223 is of type A according to which the second wing 223b extends between the first and second cold plates and is capable of heat exchange with them.

[0133] The second pulsed heat pipe 224 is of type B according to which the second wing 224b of the second pulsed heat pipe 224 extends in heat exchange capacity with a free face of the second cold plate 122. The term “free face of the second cold plate 122” is understood to mean the face which is not in contact with the second wing 223b of the first pulsed heat pipe 223.

[0134] The use of these two types A and B of pulsed heat pipes is advantageous, because they each have a surface area capable of heat exchange with the hot source (half the length of the edge of the cells 101) less than the surface area capable of heat exchange with the cold source (equal to at least one cold plate face).

[0135] Thus, at equal width, the heat pipes have, by their first wing 223a-224a, a length in heat exchange capacity of only half a length D / 2 of the first side 103a of the slice 103 of the cells 101, whereas their respective second wings 223b-224b have a length in heat exchange capacity equal to the length D of the cold plates.

[0136] This arrangement promotes the efficiency of heat dissipation.

[0137] [Fig.8] illustrates a third embodiment 320 which is even more efficient, in which the cold source of the second heat exchange device comprises a third cold plate 125.

[0138] In this embodiment, the third cold plate 125 is arranged parallel to and opposite the second cold plate 122, capable of heat exchange with the second wing 224b of the second pulsed heat pipe 224.

[0139] In other words, the third cold plate 125 is a so-called cold plate “terminal” which covers the upper face of the condensation part 224b of the second pulsed heat pipe 224 and which thus covers the assembly.

[0140] The addition of this third terminal cold plate makes it possible to obtain two heat exchange faces for the condensation part 224b of the second pulsed heat pipe 224, thus improving the evacuation of heat from the cells 101.

[0141] [Fig.9] illustrates the possibility of specializing the cold sources and the heat evacuation circuits between the gravity heat pipes of the first heat exchange device and the pulsed heat pipes of the second heat exchange device, the synergy effect still being present since the vaporization part of the pulsed heat pipe is interposed between the first side of the cell slice and the gravity heat pipe.

[0142] Thus, the fourth embodiment of the second heat exchange device 420 of [Fig.9] still comprises two cold plates 421 and 422, but these two cold plates are arranged against each other.

[0143] Furthermore, the first cold plate 421 is connected to a first heat transfer fluid circuit 421a and the second cold plate 422 is connected to a second heat transfer fluid circuit 422a independent of the first heat transfer fluid circuit 421a.

[0144] In this arrangement, the first cold plate is capable of heat exchange with the condensation part 111b of the gravity heat pipe, and the second cold plate is capable of heat exchange with the condensation part 423b of the pulsed heat pipe 423.

[0145] Thus the calories absorbed by the first cold plate 421 are evacuated in a first circuit 421a, and the calories absorbed by the second cold plate 422 are evacuated in a second circuit 422a, which improves the condensation in the condensation part 111b of the gravity heat pipe and in the condensation part 423b of the pulsed heat pipe 423.

[0146] This double cold plate arrangement is particularly interesting, because it increases the heat exchange capacity and ensures optimal evaporation in gravity heat pipes and pulsed heat pipes.

[0147] Furthermore, by dissociating the heat evacuation circuits, i.e. the cold sources, it is possible to best adapt the circulation in the cold plates according to the different operations of the gravity heat pipes and the pulsed heat pipes.

[0148] Figures 10 to 12 illustrate embodiments similar to Figures 6 to 8, but incorporating a double cold plate instead of a single cold plate between the gravity heat pipes and the pulsed heat pipes. The heat transfer fluid circuits are not illustrated in these figures for the sake of clarity.

[0149] Thus, in the fifth embodiment of [Fig.10], the cold source of the second heat exchange device 520 comprises a first cold plate 521, a second cold plate 522 and a third cold plate 525. The third cold plate 525 is arranged against the first cold plate 521, with heat exchange capacity with the gravity heat pipe(s) 111. The first cold plate is arranged with heat exchange capacity with the second condensation wing 523b of the pulsed heat pipe 523. The second cold plate 522 is arranged parallel and opposite the first cold plate 521, with heat exchange capacity with the second wing 523b of the pulsed heat pipe 523.

[0150] In other words, the second cold plate 522 is a terminal cold plate which covers the upper face of the condensation part 523b of the pulsed heat pipe 523 and which thus covers the assembly.

[0151] Furthermore, the first and second cold plates are connected to a first heat transfer fluid circuit (not shown) and the third cold plate is connected to a second heat transfer fluid circuit (not shown), independent of the first heat transfer fluid circuit.

[0152] In this embodiment, the calories absorbed from the pulsed heat pipe 523 by the first and second cold plates 521-522 are discharged in a first circuit, and the calories absorbed from the gravity heat pipe 111 by the third cold plate 525 are discharged in a second circuit, which improves condensation in the condensation portion 111b of the gravity heat pipe and in the condensation portion 523b of the pulsed heat pipe 523.

[0153] [Fig. 11] illustrates the possibility of using two pulsed heat pipes of two different types A and B with a cold source comprising a double cold plate.

[0154] This sixth embodiment is therefore similar to that illustrated in [Fig.7], with the difference that instead of using a single cold plate between the gravity heat pipe and the pulsed heat pipe, a double cold plate is used.

[0155] More specifically, the second heat exchange device 620 comprises a first pulsed heat pipe 623 of type A and a second pulsed heat pipe 624 of type B, similar to what has been described in relation to [Fig.7].

[0156] Unlike the embodiment of [Fig.7], the first pulsed heat pipe 623 has a second wing 623b which extends between the first cold plate 621 and the second cold plate 622 and it is capable of heat exchange with them.

[0157] The gravity heat pipe 111 is capable of heat exchange with a third cold plate 625 forming with the first cold plate 621 a double cold plate, that is to say that the first cold plate 621 and the third cold plate have one face in contact with each other.

[0158] The second pulsed heat pipe 624 is of type B according to which the second wing 624b of the second pulsed heat pipe 624 extends in heat exchange capacity with a face of the second cold plate 622 which is not in contact with the second wing 623b of the first pulsed heat pipe 623.

[0159] This arrangement has the same advantages as that of [Fig.7], with a higher heat evacuation capacity thanks to the double cold plate and the separation of the fluid circuit of the cold plates 621 and 622 in heat exchange capacity with the pulsed heat pipes 623 and 624, and of the fluid circuit of the cold plate 625 in heat exchange capacity with the gravity heat pipe(s) 111.

[0160] The seventh embodiment of the second heat exchange device 720 of [Fig. 12] is similar to that of [Fig. 11], but it further comprises a fourth terminal cold plate 726, covering the assembly, and capable of heat exchange with the face of the second wing 624b of the pulsed heat pipe 624 which is not in contact with the second cold plate 622.

[0161] This is one of the preferred embodiments, because it combines all the previous advantages: separate heat transfer fluid circulation circuits between the cold plate in contact with the gravity heat pipe(s) and the cold plates in contact with the pulsed heat pipes, use of pulsed heat pipes of two different types each absorbing heat from a part of the first side of the cells, and evacuating it through a second condensation wing with heat exchange capacity with two cold plates each.

[0162] As previously indicated, Figures 13, 14 and 15 illustrate a second option for arranging the pulsed heat pipes to further reduce the amplitude of the temperature gradient within each cell.

[0163] Thus, figures 13, 14 and 15 illustrate a third type of pulsed heat pipe, called type C in the remainder of this description, and making it possible to capture calories from the fourth side of the cells.

[0164] In the eighth embodiment illustrated in [Fig. 13], the second heat exchange device 350 comprises a first pulsed heat pipe 351 of type A, and a second pulsed heat pipe 352 of type C.

[0165] The first pulsed heat pipe 351 of type A comprises a first wing 351a extending longitudinally between the first side 103a of the slice 103 of the cells 101 and the condensation part 111b of the gravity heat pipe(s) 111. The first wing 351a is capable of heat exchange with a complete length D of the first side 103a of the slice 103 of the cells 101, that is to say with the entire first side 103a of the slice 103 of the cells 101.

[0166] As explained previously, the first pulsed heat pipe 351 of type A has a second wing 351b extending between the first 121 and the second 122 cold plates and is capable of heat exchange with them.

[0167] Unlike the heat pipe of type A, the second pulsed heat pipe 352 of type C comprises a first wing 352a extending longitudinally in heat exchange capacity with the fourth side 103d of the slice 103 of the cells 101, and it extends over a full length D of the fourth side 103d of the slice 103 of the cells 101, that is to say with the entire fourth side 103d of the slice 103 of the cells 101.

[0168] The second pulsed heat pipe 352 of type C has a second wing 352b extending between the second 122 and the third 125 cold plates and is capable of heat exchange with them.

[0169] The use of these two types A and C of pulsed heat pipes is advantageous, because they each have a surface area capable of heat exchange with the hot source (the length of the slice of the cells 101) which is less than the surface area capable of heat exchange with the cold source (corresponding to two lengths of cold plates).

[0170] Thus, the heat pipes 351 and 352 have, by their first wing 351a-352a, a length in heat exchange capacity equal to a length D of the first side 103a and of the fourth side 103d of the slice 103 of the cells 101, while their respective second wing 352b-352b have a length in heat exchange capacity equal to two lengths D of the cold plates, since the second wing is in heat exchange capacity with two cold plates.

[0171] This arrangement promotes the efficiency of heat removal and significantly reduces the amplitude of the temperature gradient within each cell, since the heat is removed from four sides of the cells: the second and third sides by the gravity heat pipes and the first and fourth sides by the pulsed heat pipes.

[0172] This efficiency is even more marked with the use of a double cold plate between the first pulsed heat pipe and the gravity heat pipe.

[0173] This is illustrated in the ninth embodiment of [Fig.14].

[0174] As in [Fig. 13], the second heat exchange device 750 comprises a first pulsed heat pipe 751 of type A, and a second pulsed heat pipe 752 of type C.

[0175] In this embodiment, the first pulsed heat pipe 751 of type A has a second wing 751b extending between the first 621 and the second 622 cold plates and is capable of heat exchange with them.

[0176] The gravity heat pipe is capable of heat exchange with the third cold plate 625 forming with the first cold plate 621 a double cold plate, that is to say that the first cold plate 621 and the third cold plate 625 have one face in contact with each other.

[0177] The second pulsed heat pipe 352 of type C has a second wing 352b extending between the second cold plate 622 and a fourth cold plate 625, and it is capable of heat exchange with them.

[0178] The tenth embodiment 760 illustrated in [Fig. 15] shows, in a partially exploded manner, the implementation of pulsed heat pipes 761-762, respectively of type A and type C, with pocket cells 101' carrying their terminals on the second and third sides, opposite the vaporization part of the gravity heat pipes 111.

[0179] The use of 762 type C pulsed heat pipes is particularly interesting with pocket cells, because this makes it possible to obtain very homogeneous thermal regulation in each cell, from all four sides, and in a symmetrical manner.

[0180] It is also understood that the embodiments of the invention illustrated with prismatic cells are adaptable to pocket cells and vice versa.

[0181] [Fig. 16] illustrates a realistic perspective view of a first variant of the embodiment of [Fig. 12].

[0182] In this first illustrated variant, with reference to the position of use, the second heat exchange device 720 comprises frontally (i.e. in the foreground in the figure), two pulsed heat pipes 623 of type A, i.e. the second wing of which is located between the first cold plate 621 and the second cold plate 622.

[0183] At the rear, not visible due to the perspective, the second heat exchange device comprises two pulsed heat pipes 624 of type B, that is to say the second wing of which is located between the second cold plate 622 and the fourth cold plate 726.

[0184] [Fig.17] is a partial cross-section along line XILXII of [Fig.16], which shows the stacking of heat pipes 111-623-624 alternating with cold plates 621-622-625-726, as well as an example of the internal structure of the various components.

[0185] It is thus noted that in the structure of the double cold plate 621-625, the two cold plates are applied against each other by one of their faces, and the first cold plate 621 is capable of heat exchange with the wing 623b of the pulsed heat pipes 623, while the cold plate 625 is capable of heat exchange with the wing 111b of the gravity heat pipes 111.

[0186] The channel structure of the pulsed heat pipes is also distinguished: the pulsed heat pipe 623 has a channel 623d, and the pulsed heat pipe 624 has a channel 624d.

[0187] [Fig. 18] is a partial longitudinal section along line XIII-XIII of [Fig. 16], which shows the C-shaped structure of the pulsed heat pipe 624, type B, and a partial view of the second wing 623b of the pulsed heat pipe 623.

[0188] This embodiment has the advantage of manufacturing a second heat exchange device according to the invention with stacked standard cold plates, the only modification being the fluidic connection of the cold plates in contact with the pulsed heat pipes (see [Fig.22]). The disadvantage is the doubling of the walls in contact with the cold plates and the pulsed heat pipes. In other words, each exchange surface is made up of two walls which form a significant thermal resistance and increase the thickness of the entire second heat exchange device.

[0189] Another example of the realization of the internal structure of the different components is illustrated in [Fig. 19].

[0190] In the previous embodiments, each element (cold plate / pulsed heat pipe) comprised its own structure, and the assembly resulted from the stacking in thermal contact of each of these elements. However, each cold plate and each pulsed heat pipe comprises two external walls separated by a corrugated internal wall delimiting the channel(s). Their stacking therefore results in two external walls of two juxtaposed elements being against each other. The resulting thickness separating two channels is therefore double.

[0191] For example, in the case of the structure of Figures 17 and 18, enlargement E illustrates the stacking of the outer wall of a cold plate above the outer wall of a pulsed heat pipe, and enlargement F illustrates the stacking of the outer wall of a pulsed heat pipe above the outer wall of a cold plate.

[0192] In the context of the invention and as illustrated in [Fig. 19], it is advantageous to produce all the cold plates and pulsed heat pipes in a single block in which the separation between the channel of a pulsed heat pipe and the channel of a cold plate consists of only a single wall. The functionally identical elements bear the same references as in [Fig. 17] to allow the analogy to be understood.

[0193] In other words, the cold plates and the pulsed heat pipe(s) are in a single block within which the cold plates and the pulsed heat pipe(s) are functionally separated from each other by a single wall. This means that this block ensures the functionality of the pulsed heat pipes and the cold plates with a single separating wall between a channel ensuring the cold plate function and a channel ensuring the pulsed heat pipe function.

[0194] Thus, in the illustrated embodiment, the block comprises two flat walls 630 and 631, between which are placed four corrugated walls 632. The whole thus forms the channel 623d of the pulsed heat pipe 623, the channel 624d of the pulsed heat pipe 624, as well as the channels of the cold plates 621, 622 and 726.

[0195] Under the lower flat wall 630, a corrugated wall 633 is fixed, forming the channel of the cold plate 625 in contact with the gravity heat pipes 111.

[0196] This embodiment requires manufacturing more specific to the use described, but has the advantage of reducing the height of the assembly while promoting thermal exchanges between pulsed heat pipes and cold plates.

[0197] This embodiment also allows for easier replacement in the event of a failure because the assembly can be removed and replaced in one operation.

[0198] [Fig.20] is an exploded perspective view of the cold plate assembly and pulsed heat pipes according to the preferred embodiment of the invention with two cold plates 622-726 and one double cold plate 621-625.

[0199] This view shows the head-to-tail arrangement of a pulsed heat pipe 623 of type A and a pulsed heat pipe 624 of type B, as well as the possibility of juxtaposing in parallel several (here two) pulsed heat pipes 623-624 to thermally regulate a set of cells 101.

[0200] This [Fig.20] also illustrates the two circuits 625c-625d and 124a-124b of heat transfer fluid for the evacuation of heat, on the one hand from the cold plate 625 intended to be capable of heat exchange with the condensation part of the gravity heat pipes 111 and, on the other hand, from the set of three cold plates 621-622-726 intended to be capable of heat exchange with the condensation part of the pulsed heat pipes 623-624 located, respectively, in the second wings 623b and 624b.

[0201] [Fig.21] is an exploded view of the double cold plate 621-625 and illustrates the possibility of interposing between said cold plates, a layer 626 of thermal interface material (or TIM for “thermal interface material” in English).

[0202] Such a material is well known to improve the thermal coupling between two components, by limiting the thermal resistance which hinders the dissipation of heat at the interface of the two components.

[0203] Although this is not shown so as not to make the figures cumbersome, it is of course preferable to provide a layer of such a thermal interface material between the gravity and pulsed heat pipes and the cold plate(s) with which they are in contact to improve the heat transfer from the condensation part of the heat pipes and the cold plate in thermal contact with it.

[0204] [Fig.21] also partially illustrates the two separate heat transfer fluid circuits for heat removal from the double cold plate 621-625.

[0205] Thus, the cold plate 625, intended to be in contact with the condensation part of the second wing 111b of the gravity heat pipe(s) 111, has an inlet 625a for cold heat transfer fluid and an outlet 625b for hot heat transfer fluid, both extended by a fluid circulation tube, respectively 625c and 625d.

[0206] In the same way, the cold plate 621, intended to be in contact with the condensation part of the second wing 623b of the pulsed heat pipe(s) 623, has an inlet 621a for cold heat transfer fluid and an outlet 621b for hot heat transfer fluid, both extended by a fluid circulation tube, respectively 124a and 124b.

[0207] The two tubes 625c and 625d pass through two sealed holes 621c located in the upper cold plate 621, without fluid communication with said upper cold plate 621. These holes 621 are simply there to allow the passage of the tubes 625c and 625d and limit the size of the assembly. In other words, the circuit of heat transfer fluid entering and leaving the cold plate 625 does not mix with the heat transfer fluid circuit entering and leaving the upper cold plate 621, which are therefore independent.

[0208] For the heat transfer fluid circuit in the cold plates 621-622-726, on the contrary, the tubes 124a and 124b pass through holes communicating with the interior of the cold plates 622 and 726.

[0209] Figures 22 and 23 are sectional views of an outlet of the heat transfer fluid circuit, respectively outside the cold plates 621-622-726 in contact with the pulsed heat pipes 623-624 and outside the cold plate 621 in contact with the gravity heat pipe(s) 111.

[0210] [Fig.22] shows the fluid communication between the cold plates 621, 622 and 726 at the tube 625d. Thus, the heat transfer fluid present in these cold plates can exit (arrows F1) out of the channels of the cold plates in the tube 625d towards the rest of the circuit comprising a heat exchanger to evacuate the heat from the heat transfer fluid into the environmental air (see [Fig.25]).

[0211] On the contrary, as shown in [Fig.23], the tube 625d communicating with the outlet 625b of the cold plate 625, does not communicate with the interior of the cold plates 621, 622 and 726. The heat transfer fluid circulating in the cold plate 625 can therefore exit in the direction of the arrows F2, while the heat transfer fluid circulating in the cold plates 621, 622 and 726 collides with the tube 625d and remains in these cold plates (arrows F3).

[0212] It is therefore possible to obtain a thermally controlled device of small size, while comprising two independent heat transfer fluid circuits, one for the cold plate in contact with the gravity heat pipe(s) 111, the other for the set of cold plates in contact with the pulsed heat pipes, which optimizes the thermal control of the cells 101.

[0213] [Fig.24] illustrates a second variant of the preferred embodiment of the invention, comprising frontally, on the right in the figure, a pulsed heat pipe 623 of type A, the condensation part of which is inserted between the double cold plate and the intermediate cold plate, and, on the left in the figure, a pulsed heat pipe 624 of type B the condensation part of which is inserted between the intermediate cold plate and the terminal cold plate.

[0214] Dorsally, the device comprises two heat pipes similar to the first, but arranged in opposition: facing the pulsed heat pipe 623 of type A, we see the second wing 624b of a heat pipe 624 of type B, and facing the pulsed heat pipe 623 of type B on the left, there is a pulsed heat pipe 623 of type A hidden by the core 624c of pulsed heat pipe 624.

[0215] Finally, [Fig.25] illustrates a thermally controlled device according to the invention, the cold plates 621, 622 and 726 of which are connected to a circuit 800 of ca- fluid operational carrier, including a radiator to evacuate heat from the heat transfer fluid to the ambient air.

[0216] In an operation aimed at reducing the temperature of the cells, the heat transfer fluid enters the cold plates 621, 622 and 726 through the tube 124a at a temperature T1 sufficient to generate condensation in the second wings 623b and 624b of the pulsed heat pipes 623 and 624 and recover heat from these pulsed heat pipes. The heat transfer fluid then leaves the cold plates 621, 622 and 726 through the tube 124b at a temperature T2 higher than the temperature T1.

[0217] This circulation of fluid is created by a pump 801, which pumps the heat transfer fluid towards a three-way valve 802.

[0218] This three-way valve 802 is connected to the outlet 124b of the device according to the invention, to a radiator 803 for cooling the heat transfer fluid, and to a heater 804. The three-way valve 802 can be controlled by the electronic system on board the vehicle to selectively direct the heat transfer fluid to the radiator 803 to cool it or to the heater 804 to heat it, as required.

[0219] In fact, the optimal temperature range for operating and recharging batteries is between 5 and 25 degrees Celsius.

[0220] During charging, batteries tend to heat up considerably and it is necessary to cool the battery cells to avoid any runaway and fire phenomena. This can also be the case during use: the pump 801 and the three-way valve 802 are then controlled in response to a signal transmitted by a temperature sensor present in the battery.

[0221] The cooled fluid having circulated in the radiator 803 can then return directly to the inlet 124a of the thermally controlled device according to the invention, or pass through a heat exchanger 805 of an additional thermal circuit in order to manage the calories in the vehicle more generally and using the thermal behavior of the thermally controlled device according to the invention.

[0222] Alternatively, in certain weather conditions or, more frequently when the vehicle is being recharged "cold", i.e. when the batteries are at a temperature below 5°C, it is preferable to preheat the battery cells which charge or operate more efficiently when at a temperature above 5°C. The three-way valve is then controlled to direct the fluid to the heater 804. The heated fluid then returns to the inlet 124a to heat the cells. Once the optimum operating temperature is reached, the three-way valve is controlled to direct the heat transfer fluid to the radiator 803 in order to limit the temperature rise of the battery for the remainder of the operation (use or charging).

[0223] The heat transfer fluid therefore enters the device according to the invention with a temperature temperature T2 different (higher or lower depending on the situation) than the temperature T1 of the fluid leaving the device.

[0224] The fluid circuit of course comprises an expansion tank 806 in order to absorb the variations in volume of the heat transfer fluid generated by the changes in temperature.

[0225] As explained previously, when the device according to the invention comprises a double cold plate (see figures 9 to 12, and 14 to 24) between the gravity heat pipe(s) and the pulsed heat pipe(s), the system according to the invention has two separate cooling circuits: a first 800 for the pulsed heat pipe(s) and a second 900 for the gravity heat pipe(s).

[0226] This arrangement is particularly effective in terms of evacuating calories from the battery, and especially from the vehicle.

[0227] Indeed, although this is not illustrated in [Fig.25], the inlet 625c and the outlet 625d of the cold plate 625 capable of heat exchange with the gravity heat pipe(s) can also be connected to the pump 801, the radiator 803 and the heater 804 to improve the thermal control of the battery cells during use of the vehicle.

[0228] As illustrated in [Fig.25], the inlet 625c and the outlet 625d of the cold plate 625 can also be connected to a second circuit 900 of heat transfer fluid connected to the charging socket 7 of the vehicle specially adapted for this use. This charging socket 7 thus comprises: - an electrical circuit 7a connected to the battery to recharge it from an electrical source 1000 external to the vehicle (the circuit 7a is illustrated schematically; it of course includes the other electrical or electronic elements of the vehicle, in particular the computer 3 and the AC / DC charger / converter 4, whether the latter is independent or integrated directly into the battery modules); - an inlet 901 and an outlet 902 fluidly connected respectively to the inlet 625c and to the outlet 625d of the cold plate 625.

[0229] The heat transfer fluid circuit 900 also comprises a socket 903 complementary to the socket 7 of the vehicle, the complementary socket 903 being electrically connected to a source 1000 of electrical energy (AC or DC) and fluidically to a source 904 of cold fluid, external to the vehicle.

[0230] To this end, the additional socket 903 comprises: - an electrical circuit 7b connected to the source 1000 of electrical energy; - an inlet 905 and an outlet 906 fluidly connected to the source 904 of cold fluid external to the vehicle.

[0231] The cold liquid source 904 can, when the sockets 7 and 903 are connected, inject a very cold liquid into the cold plate, i.e. at a temperature much cooler than that which can be obtained with the 803 radiator of the first circuit.

[0232] Indeed, such a radiator can generally extract a maximum of 12 kilowatts (kW), while the objective is to extract 20 to 25 kW during charging.

[0233] By connecting the second circuit to a source of cold fluid 904, for example at 5 degrees Celsius, it is perfectly possible to extract these 25kW from the battery and from the vehicle.

[0234] It is therefore possible to obtain heat transfer fluid circuits at different cold temperatures, without mixing, when the vehicle is charging.

[0235] It is of course possible to reverse the connections of the circuits, by providing that the inlet 124a and the outlet 124b of the cold plates 621, 622 and 726 capable of heat exchange with the pulsed heat pipes are connected to the cold fluid circuit 900 external to the vehicle, and that the inlet 625c and the outlet 625d of the cold plate 625 capable of heat exchange with the gravity heat pipes are connected to the heat transfer fluid circuit 800 internal to the vehicle.

[0236] [Fig.26] illustrates the temperature gradient within a cell 101 when the latter is only capable of heat exchange with gravity heat pipes 20. The gradient illustrated is the temperature difference between the coldest points and the hottest points of the cell.

[0237] It can be seen, on the one hand, that the gradient is regular transversely: the center of the cell 101 is hot over the entire height of the cell and the areas located along the second 103b and third 103c sides of the cell are cold over the entire height. In addition, the amplitude of the temperature gradient between the edges and the center is also significant: around 22 to 23 degrees Celsius. In view of the thermal constraint ii) mentioned above, limiting the amplitude of the temperature gradient within the cell is an essential issue.

[0238] [Fig.27] illustrates the temperature gradient within a cell 101 when the latter is capable of heat exchange with gravity heat pipes 20 and pulsed heat pipes 30 (symbolized in gray in the figure) above the first side 103a and below the fourth side 103d of the cell.

[0239] It can be seen that the temperature gradient is not regular transversely. Only the core of the cell has the hottest temperature. The second, third and fourth sides are the coldest. The center of the first side is also a cold zone, thanks to the pulsed heat pipe arranged between the terminals, above the first side of the cell.

[0240] The temperature gradient between the coldest and warmest areas does not exceed 5 to 6 degrees Celsius.

[0241] The parts located under the terminals of the cell are also hot, but a little less than the core: if the pulsed heat pipes do not cover the terminals, the areas located under the latter nevertheless benefit from a small absorption of calories from the pulsed heat pipes.

[0242] It can thus be seen that the amplitude of the gradient is reduced (approximately 5 to 6 degrees Celsius) compared to the amplitude of the gradient obtained with the device of [Fig.26] (approximately 22 to 23 degrees Celsius).

[0243] Pulsed heat pipes do not just cool the first side and the fourth side in a similar way to gravity heat pipes, because otherwise only the core of the cell would be hot, but the gradient would be similar to that in [Fig.26].

[0244] Their arrangement ensures a synergistic effect by cooling not only the cell from the first side and possibly the fourth side, but also by promoting condensation within the gravity heat pipes, which improves their efficiency. The result is therefore better cooling of the cells, but also a lower thermal amplitude within the cells, which makes it possible to meet thermal constraints i) and ii).

[0245] Furthermore, the fact that the gravity heat pipes and the pulsed heat pipes all extend along the modules, this makes it possible to ensure thermal control of the complete module and to respond to thermal constraint iii) by preventing the central cells within the module from reaching the maximum operating temperature (45 degrees Celsius).

Claims

Claims

1. A thermally controlled device (100) for storing electrical energy in chemical form for a vehicle, the controlled device comprising: - a plurality of electrical cells (101); - a first heat exchange device (110) comprising a bent gravity heat pipe (111), having an evaporation part capable of heat exchange with one side of the cells (101) and a condensation part capable of heat exchange with a cold source of a second heat exchange device (120, 220, 320, 420, 520, 620, 720, 750, 760), the cold source comprising at least two cold plates (121, 421, 521, 621-122, 422, 522, 622); the second heat exchange device (120, 220, 320, 420, 520, 620, 720, 750, 760) comprising at least one pulsed heat pipe (30, 123, 223, 224, 423, 523, 623, 624, 751, 752, 761, 762) having: - a first wing (31a, 123a, 223a, 224a, 623a, 624a, 751a, 752a) extending under the condensation part of the gravity heat pipe and capable of heat exchange with a part of the slice of the cells (101); - a second wing (31b, 123b, 223b, 224b, 623b, 624b, 751b, 752b) extending in heat exchange capacity with at least one of the cold plates (121, 421, 521, 621-122, 422, 522, 622); and - a core (31c, 123c, 223c, 224c, 623c, 624c, 751c, 752c) connecting the wings (31a, 123a, 223a, 224a, 623a, 624a, 751a, 752a-123b31b, 123b, 223b, 224b, 623b, 624b, 751b, 752b).

2. Thermally controlled device according to claim 1, comprising an electric battery (100) having a plurality of electric cells (101) each having two faces (102) connected by a wafer (103), where the cell is thinnest and where at least a first side (103a), a second side (103b) and a third side (103c) are located, the second side (103b) and third side (103c) being parallel to each other and transverse to the first side (103a), each cell (101) comprising a cathode terminal (104) and an anode terminal (105) located on a single side or on two different sides of the wafer, the terminals of adjacent cells being connected to each other to form the battery, the cells being arranged parallel to each other, in a longitudinal direction (LL), face to face, device in which: - the gravity heat pipe (20, 111) of the first heat exchange device (110) is capable of heat exchange with at least the second side (103b) or the third side (103c) of the cells (101) and the cold source of at least one second heat exchange device (120, 220, 320, 420, 520, 620, 720, 750, 760), - the gravity heat pipe (20, 111) comprises a body (21) internally integrating a series of juxtaposed channels (24) containing a heat-transfer substance and two transverse volumes (25, 26) into which the ends of the channels open so that they communicate fluidically with each other via these transverse volumes; - the body (21) of the gravity heat pipe is bent, in an L or in a C, so that the channels each have at least one curved part (27) located between two wings, a first wing carrying at least one vaporization part (PV) and a second wing carrying a condensation part (PC), the condensation part being located at a higher elevation level than that of the vaporization part relative to gravity in the position of use; - the gravity heat pipe (20, 111) is arranged such that the first wing carrying the vaporization part (PV) extends laterally opposite the second side (103b) or the third side (103c) of the slice (103) of the cells (101) at a first distance (dl), preferably zero, while the second wing of the gravity heat pipe carrying the condensation part (PC) extends laterally above the first side (103a) of the slice (103) of the cells (101), at a second distance (d2) strictly greater than the first distance (dl); - the second heat exchange device (120, 220, 320, 420, 520, 620, 720, 750, 760) comprises: * the cold source which comprises at least a first cold plate (121, 421, 521, 621) and a second cold plate (122, 422, 522, 622) in which a heat transfer fluid circulates between an inlet (124a) and an outlet (124b), the first and second cold plates (121, 421, 521, 621-122, 422, 522, 622) extending parallel to each other, longitudinally, flat and facing the first side (103a) of the cells (101); * at least one pulsed heat pipe (30, 123, 223, 224, 423, 523, 623, 624, 751, 752, 761, 762) comprising a body (31) internally integrating at least one channel (32) closed on itself to form a loop and incorporating a heat-transfer substance, the channel (32) having convolutions (33) and extending between an evaporation part in thermal contact with at least a part of the first side (103a) of the slice (103) of the cells (101), and a second condensation part in thermal contact with a face of each of the first and second cold plates (121, 421, 521, 621-122, 422, 522, 622), the body (32) of the pulsed heat pipe being bent in C to have: - the first wing (31a, 123a, 223a, 224a, 623a, 624a, 751a, 752a) extending longitudinally between the first side (103a) of the slice of the cells (101) and the condensation part of the one or more gravity heat pipe(s), and comprising the evaporation part with heat exchange capacity with at least part of the first side (103a) of the slice of the cells (101), - the second wing (31b, 123b, 223b, 224b, 623b, 624b, 751b,752b) parallel to the first wing (31a) and comprising the condensation portion extending in heat exchange capacity with at least one of the first and second cold plates (121, 421, 521, 621-122, 422, 522, 622); - the core (31c, 123c, 223c, 224c, 623c, 624c, 751c, 752c) connecting the first (31a, 123a, 223a, 224a, 623a, 624a, 751a, 752a) and the second wing (31b, 123b, 223b, 224b, 623b, 624b, 751b, 752b).,

3. Thermally controlled device according to claim 1 or 2, wherein the second wing (31b, 123b, 223b, 224b, 623b, 624b, 751b, 752b) of said at least one pulsed heat pipe (30, 123, 223, 224, 423, 523, 623, 624, 751, 752, 761, 762) extends between two of said at least two cold plates (121, 421, 521, 621-122, 422, 522, 622) and is capable of heat exchange with two of said at least two cold plates (121, 421, 521, 621-122, 422, 522, 622).

4. Thermally controlled device according to any one of claims 1 to 3, comprising at least one first pulsed heat pipe (223, 623) and at least one second pulsed heat pipe (224, 624) and wherein: - the first wing (223a, 623a) of the first pulsed heat pipe (223, 623) extends longitudinally between the first side (103a) of the slice of the cells (101) and the condensation part of the gravity heat pipe(s) (111), and in heat exchange capacity with a first half-length (D / 2) of the first side (103a) of the slice of the cells (101), and the second wing (223b, 623b) of the first pulsed heat pipe (223, 623) extends between, and in heat exchange capacity with, there first and second cold plates (121, 521, 621-122, 522, 622); and - the first wing (224a, 624a) of the second pulsed heat pipe (224, 624) extends longitudinally between the first side (103a) of the slice of the cells (101) and the condensation part of the gravity heat pipe(s) (111), and in heat exchange capacity with a second half-length (D / 2) of the first side (103a) of the slice of the cells (101), and the second wing (224b, 624b) of the second pulsed heat pipe (224, 624) extends in heat exchange capacity with a free face of the second cold plate (122, 622).

5. Thermally controlled device according to any one of claims 1 to 3, comprising at least one first pulsed heat pipe (351, 751) and at least one second pulsed heat pipe (352, 752) and wherein: - the first wing (351a, 751a) of the first pulsed heat pipe (351, 751) extends longitudinally between the first side (103a) of the slice of the cells (101) and the condensation part of the gravity heat pipe(s) (111), and it is capable of heat exchange with a length (D) of the first side (103a) of the slice of the cells (101), and the second wing (351b, 751b) of the first pulsed heat pipe (351, 751) extends between, and is capable of heat exchange with, the first and the second cold plate (121, 621-122, 622);and - the first wing (352a, 752a) of the second pulsed heat pipe (352, 752) extends longitudinally under the fourth side (103d) of the slice of the cells (101), and it is capable of heat exchange with a length (D) of the fourth side (103d) of the slice of the cells (111), and the second wing (352b, 752b) of the second pulsed heat pipe (352, 752) extends in heat exchange capacity at least with a free face of the second cold plate (122, 622).;

6. Thermally controlled device according to claim 4 or 5, wherein the cold source of the second heat exchange device comprises at least one third cold plate (125, 525, 625).

7. Thermally controlled device according to claim 6, in which the third cold plate (125) is arranged parallel and opposite the second cold plate (125), in heat exchange capacity with the second wing (224b, 352b) of the second pulsed heat pipe (224, 352).

8. A thermally controlled device according to claim 6, wherein the third cold plate (525, 625) is arranged against the first cold plate (521, 621), capable of heat exchange with said at least one gravity heat pipe (111), the first (521, 621) and the second cold plate (522, 622) being connected to a first heat transfer fluid circuit and the third cold plate (525, 625) being connected to a second heat transfer fluid circuit independent of the first heat transfer fluid circuit.

9. Thermally controlled device according to claim 8, in which the cold source of the second heat exchange device comprises a fourth cold plate (726) arranged parallel to and opposite the second cold plate (622), capable of heat exchange with a free face of the second wing (624b, 752b) of the second pulsed heat pipe (624, 752).

10. A thermally controlled device according to claim 2, wherein the pulsed heat pipe(s) is / are in thermal contact against the first side (103a) and / or the fourth side (103d) of the cell or terminals carried by said first side, a layer of electrically insulating material being interposed between the pulsed heat pipe(s) and the first side of the cell or terminals carried by said first side.

11. A thermally controlled device according to one of the preceding claims, wherein the cold plates and the pulsed heat pipe(s) are in a single block within which the cold plates and the pulsed heat pipe(s) are functionally separated from each other by a single wall (632).

12. Thermally controlled device according to one of claims 2 to 11, further comprising a housing in which the plurality of cells are arranged, the housing comprising: — a bottom on which the cells and a plurality of gravity heat pipes rest, and — a clamping means (112) configured to clamp each gravity heat pipe against the second side (103b) and / or the third side (103c) of the cell(s) (101) located opposite, so that the or each vaporization part of the gravity heat pipe(s) is pressed against the cell(s) located opposite.

13. Thermally controlled device according to the preceding claim, in which the clamping means (112) comprises upright walls, bearing against the bottom and surrounding the cells (101) and the plurality of said gravity heat pipes (111), as a whole.

14. A thermally controlled device according to claim 11 in combination with any one of claims 8 to 10, wherein the cold plate (125, 726) which covers the second wing (224b, 352b, 624b, 752b) of the second pulsed heat pipe (224, 352, 624, 752), is fixed to the housing so that all the cells (101) and all the gravity heat pipes (111) and pulsed heat pipes (223, 224, 351, 352, 623, 624, 751, 752), as a whole, are clamped between the housing and the cold plate (125, 726) which covers the second wing (224b, 352b, 624b, 752b) of the second pulsed heat pipe (224, 352, 624, 752).

15. Electric or hybrid vehicle (10) comprising: - at least one electric motor (1) for moving it, and - at least one thermally controlled device (100) according to one of claims 1 to 14, connected to the electric motor to supply it with electricity; - at least one electrical outlet (7) connected to said at least one thermally controlled device to charge it with electricity.

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