FR3146345A1 - Thermal regulation device for components - Google Patents

Abstract

Title: Thermal regulation device for components The invention relates to a thermal regulation device (4) for components (6) whose operation is sensitive to temperature, said device (4) comprising: - a heat transfer fluid discharge channel (30); - at least two placement zones (204) each arranged to receive said component, each placement zone (204) being in thermal contact with the heat transfer fluid discharge channel (30) such that a component (6) placed in this placement zone (204) can exchange heat with heat transfer fluid circulating in the heat transfer fluid discharge channel (30). Figure for abstract: Fig. 8

Description

Thermal regulation device for components

The present invention relates to a thermal regulation device for components. The present invention relates to a module comprising such a thermal regulation device for components.

The present invention further relates to a method of assembling such a thermal regulation device.

It is now known to equip electric, thermal or hybrid vehicles with electrical energy storage components allowing an electrical supply to the various elements of the vehicle. These electrical energy storage components are generally composed of electrical energy storage cells positioned in a battery pack.

Today, car manufacturers are looking to provide more powerful electric or hybrid vehicles with increased electric range. To achieve this, more and more battery packs, and/or increasingly larger battery packs, are being installed on these electric or hybrid vehicles. It is known to install all or at least part of these battery packs on the floor of the vehicle, substantially across the entire width of the vehicle.

It is understood that, during vehicle operation, battery packs can release a significant amount of heat and therefore be subject to temperature increases that can cause them to be damaged or even destroyed in some cases. Consequently, their cooling is essential in order to keep them in good condition and thus ensure the reliability, autonomy and performance of the vehicle. Furthermore, the operation of battery packs can be less efficient in the event of low temperatures, as the electrical or electronic components equipping these battery packs then need time to warm up before operating at full capacity.

To do this, one or more thermal regulation devices intended to regulate the temperature of the battery packs are implemented to ensure the heating and/or cooling functions of the electrical or electronic components inside these battery packs and thus optimize the operation of the various components.

These thermal regulation devices are generally traversed by a heat transfer fluid which can, depending on requirements, either absorb the heat emitted by each battery pack in order to cool it or provide heat if the temperature of the battery pack is insufficient for its proper operation.

The temperature of the heat transfer fluid flowing through the thermal regulation device changes when the heat transfer fluid is in thermal contact with said components.

The heat transfer fluid, when it arrives with a low temperature in order to cool the components, tends to cool the first components it encounters more than the rest of the components downstream, because the heat transfer fluid has not had time to be heated by the components.

The temperature imbalance created between the first components and the rest of the downstream components is likely to result in non-optimal operation of components whose operation is sensitive to temperature.

The present invention aims to overcome this drawback, and in particular to avoid an imbalance in terms of temperature for the first components compared to the rest of the downstream components.

The invention thus relates to a thermal regulation device for components whose operation is sensitive to temperature, these components being in particular intended for energy storage and possibly being battery cells, in particular for vehicles, said device comprising:

- a heat transfer fluid distribution channel;

- a heat transfer fluid slowing cavity through which the distribution channel passes, the slowing cavity having a first fluid passage section which is both larger than a second passage section of the distribution channel at an upstream junction with the slowing cavity, and a third passage section of the distribution channel at a downstream junction with the slowing cavity,

- a heat transfer fluid circulation branch in which heat transfer fluid from the distribution channel is distributed, and

- at least one placement zone for receiving said component, this placement zone being opposite the heat transfer fluid slowdown cavity so that a component placed in this placement zone can exchange heat with heat transfer fluid.

Two areas are said to be "facing" each other when these areas overlap when observed along an axis perpendicular to these areas.

By means of the invention, the heat transfer fluid passing through the slowing-down cavity is slowed down. The reduction in the speed of the heat transfer fluid reduces the heat exchange, in particular compared to the case where the heat transfer fluid would not be slowed down in the absence of such a slowing-down cavity.

This has the effect of cooling the component located on the placement area opposite the slowdown cavity less than in the case where such a slowdown cavity is absent, when the heat transfer fluid arrives at a low temperature. In this way, overcooling of the component by the heat transfer fluid coming from the distribution channel is avoided.

Thus, the temperature imbalance between the first components encountered by the heat transfer fluid and the rest of the downstream components is reduced. Consequently, all the components can have an optimal operation due to a greater temperature homogeneity between the components.

This makes it possible to use the distribution channel to cool components placed on it. This allows a greater number of components to be placed overall on the thermal control device. This increases the energy storage capacity of the components for a given thermal control device size, and thus increases the range of a vehicle powered by this energy.

Advantageously, the invention makes it possible to reduce the temperature imbalance while promoting the reduction of the pressure loss compared to a channel without a slowing cavity.

Furthermore, in battery pack type applications, there is usually a strong constraint on the total available height (or available vertical space), which can give a limitation on the channel height. One aspect of the invention makes it possible to increase the passage section of the distribution channel, without increasing the height. This makes it possible to promote the speed of the fluid and the transfer of heat from the cells because the more the passage section of the distribution channel increases, the more the number of cells in contact can increase.

According to one aspect of the invention, the heat transfer fluid circulation branch is connected to the slowing cavity so that heat transfer fluid having passed through the slowing cavity is distributed in the heat transfer fluid circulation branch.

According to one aspect of the invention, the device comprises a heat transfer fluid evacuation channel.

According to one aspect of the invention, the circulation branch opens onto the heat transfer fluid evacuation channel.

According to one aspect of the invention, the heat transfer fluid circulation branch comprises at least one branch channel connecting to the heat transfer fluid discharge channel.

According to one aspect of the invention, the circulation branch comprises at least one rectilinear branch channel connecting to the heat transfer fluid evacuation channel.

According to one aspect of the invention, the circulation branch comprises at least one serpentine-shaped branch channel connecting to the heat transfer fluid discharge channel.

According to one aspect of the invention, the circulation branch comprises at least two rectilinear branch channels, each branch channel connecting to the heat transfer fluid evacuation channel.

According to one aspect of the invention, the branch channel connects to the heat transfer fluid discharge channel.

According to one aspect of the invention, the thermal regulation device comprises two plates, namely an upper plate and a lower plate.

According to one aspect of the invention, at least one of these plates comprises reliefs, in particular produced by stamping. These reliefs can form, for example, the distribution channel, the slowdown cavity and the heat transfer fluid circulation branch as well as the heat transfer fluid evacuation channel.

According to one aspect of the invention, one of the plates faces the components. This plate is defined as being the upper plate and comprises at least one placement zone. The other of the plates whose face opposes that of the upper plate is defined as being the lower plate.

According to one aspect of the invention, the device comprises two plates, namely an upper plate and a lower plate, the upper plate being the plate facing the components and comprising the placement area and the lower plate being one of the plates whose face opposes that of the upper plate.

According to one aspect of the invention, the placement area is located on one of these plates of the thermal regulation device.

According to one aspect of the invention, each branch comprises a tray, in particular flat, comprising a plurality of placement zones for receiving components.

According to one aspect of the invention, the distribution channel passes under this plate.

According to one aspect of the invention, the evacuation channel passes under this plate.

According to one aspect of the invention, the distribution channel is connected to a heat transfer fluid inlet.

According to one aspect of the invention, the discharge channel is connected to a heat transfer fluid outlet.

According to one aspect of the invention, the distribution channel has a general L shape.

According to one aspect of the invention, the discharge channel has a general L shape.

According to one aspect of the invention, the distribution and discharge channels are mirror symmetrical to each other such that the heat transfer fluid inlet and the heat transfer fluid outlet are symmetrical to each other.

According to one aspect of the invention, the distribution and evacuation channels each comprise a flat section bordered on each side by a flank.

According to one aspect of the invention, the flat part follows the path formed by the distribution and evacuation channels.

According to one aspect of the invention, the distribution channel is configured to distribute the heat transfer fluid in a plurality of heat transfer fluid circulation branches.

According to one aspect of the invention, these heat transfer fluid circulation branches are parallel to each other.

According to one aspect of the invention, these heat transfer fluid circulation branches connect to the distribution channel with a pitch between the heat transfer fluid circulation branches.

Thus, the slowing branches and cavities are spaced apart with a step.

According to one aspect of the invention, these heat transfer fluid circulation branches connect to the distribution channel with a regular pitch between the heat transfer fluid circulation branches.

According to one aspect of the invention, the regular pitch is substantially equal to the width of the circulation branch.

In an alternative embodiment, these heat transfer fluid circulation branches connect to the distribution channel with an irregular pitch between the heat transfer fluid circulation branches.

According to one aspect of the invention, the circulation branches have substantially the same width between them.

According to one aspect of the invention, at least some of the heat transfer fluid circulation branches furthest upstream in the direction of flow in the distribution channel are each connected to the distribution channel by a slowing cavity. The other heat transfer fluid circulation branches are not connected to the distribution channel by a slowing cavity.

In an alternative embodiment, all of the heat transfer fluid circulation branches each have a slowing cavity.

According to one aspect of the invention, the circulation branches are connected to each other by at least one crosspiece, in particular a crosspiece in the form of a straight strip.

According to one aspect of the invention, the circulation branches comprise at least one pair of branches connected to each other by at least one crosspiece, in particular in the form of a rectilinear strip.

According to one aspect of the invention, the two branches are connected to each other by the crosspiece only inside the pair of branches.

According to one aspect of the invention, the crosspiece is arranged perpendicular to each traffic branch.

According to one aspect of the invention, the crosspiece has a width substantially equal to the width of the traffic branch.

According to one aspect of the invention, an opening is formed between the two successive crosspieces.

According to one aspect of the invention, the opening has a substantially rectangular perimeter.

According to one aspect of the invention, the slowing cavity has a junction with the circulation branch different from the upstream and downstream junctions.

According to one aspect of the invention, the slowing cavities have dimensions which decrease from one circulation branch to the other in the direction of flow of heat transfer fluid in the distribution channel.

Thus, the volume of the cavities decreases from one branch to the other in the direction of flow of heat transfer fluid in the distribution channel. The dimensions of the slowing cavity can be adapted according to the heat flow that is to be reduced.

According to one aspect of the invention, the slowing cavity has a perimeter, in particular in a substantially rectangular shape, when the slowing cavity is observed along an axis perpendicular to the plane defined by the placement zone opposite said cavity.

According to one aspect of the invention, the rectangular perimeter of each slowing cavity is smaller from one cavity to another.

According to one aspect of the invention, the slowing cavity has a height that is maximum at its junction with the distribution channel. According to one aspect of the invention, the width of the slowing cavity can also be greater than those of the distribution and branch channels, which makes it possible, where appropriate, to collect the heat from several cells. Generally speaking, the invention makes it possible to play on the height, significantly, and also on the width to widen the thermal interfaces and reach more cells, which has the consequence of requiring a higher fluid slowing.

According to one aspect of the invention, the height in the slowing cavity at the junction with the branch channel is smaller than the height at its junction with the distribution channel.

According to one aspect of the invention, the height of the slowing cavity changes to a different height due to the presence of a side of the distribution channel.

According to one aspect of the invention, between the junction of the distribution channel with the slowing cavity and the junction of the branch channel and the slowing cavity, the height in the slowing cavity decreases, in particular by one or more steps.

• un premier palier ayant une hauteur, le premier palier étant défini entre la jonction du canal de distribution avec la cavité de ralentissement ; et
• un deuxième palier ayant une hauteur, le deuxième palier étant défini entre et la jonction du canal de branche et la cavité de ralentissement.

According to one aspect of the invention, the bearings comprise:

• a first step having a height, the first step being defined between the junction of the distribution channel with the retarding cavity; and
• a second step having a height, the second step being defined between and the junction of the branch channel and the slowing cavity.

According to one aspect of the invention, the height of the slowing cavity is defined along the axis perpendicular to the plane defined by the placement zone opposite said cavity.

According to one aspect of the invention, the slowing cavity is formed locally by a recess in one of the plates forming the device, in particular the lower plate, so that at the level of this recess, the height of the slowing cavity measured along the axis perpendicular to the plane defined by the placement zone facing the slowing cavity is reduced relative to the height of the first level defined between the junction of the distribution channel with the slowing cavity.

According to one aspect of the invention, the slowing cavity has dimensions arranged to be opposite at least two placement zones, preferably at least three placement zones.

According to one aspect of the invention, the slowing cavities have contours of different shapes relative to each other.

According to one aspect of the invention, the device comprises at least two placement zones forming a row of placement zones.

According to one aspect of the invention, the device comprises rows of placement areas which are parallel to each other. Each row comprises a plurality of placement areas.

According to one aspect of the invention, the rows of placement zones are arranged perpendicularly along an axis defined relative to the greatest length of the distribution channel.

According to one aspect of the invention, the device comprises a row of placement zones along the distribution channel.

According to one aspect of the invention, the device comprises a row of placement zones along the discharge channel.

Furthermore, two current trends are observed to optimize the heat exchange between the heat transfer fluid and the components. According to the first trend, we seek to optimize the heat transfer coefficient according to the evolution of the temperature difference between the heat transfer fluid circulation channels of the thermal control device. According to the second trend, we seek to reduce the pressure differences between the different heat transfer fluid circulation channels. However, it is noted that the design based on the reduction of the temperature difference between the channels is done to the detriment of the increase in the pressure differences between the channels, and vice versa. On the one hand, the application of the design based on the reduction of the pressure difference results in very low heat exchange towards the heat transfer fluid outlet. On the other hand, the application of the design based on the optimization of the heat transfer coefficient will result in a large pressure difference between the channels. The present invention aims to overcome these drawbacks, and in particular to optimize the heat transfer coefficient of heat exchange while minimizing the pressure difference between the heat transfer fluid channels.

The invention thus also relates to a thermal regulation device for components whose operation is sensitive to temperature, these components being in particular intended for energy storage and possibly being battery cells, in particular for vehicles, said device comprising:

- a heat transfer fluid evacuation channel;

- at least two heat transfer fluid circulation branches which each open into a collection zone of the discharge channel so that heat transfer fluid having circulated in the branches is discharged via the heat transfer fluid discharge channel, these collection zones being distributed along the discharge channel, and

- at least two placement zones each arranged to receive said component, each placement zone being in thermal contact with the heat transfer fluid evacuation channel so that a component placed in this placement zone can exchange heat with heat transfer fluid circulating in the heat transfer fluid evacuation channel,

the collection zones each have a cross-section which increases or remains constant when moving from one collection zone to the next in the direction of heat transfer fluid flow, and

for at least two consecutive collection areas, the downstream collection area has a larger cross-section than the upstream collection area.

In the invention, since the collection areas have a cross-section which increases, by increasing the height, As we approach the outlet, it is possible to maintain a constant exchange coefficient along the flow. To this end, the pressure loss is locally increased. In this case, the pressure gradient increases along the discharge channel.

It should be noted that the main factor contributing to the pressure difference is the average fluid velocity, which is proportional to the flow rate. In this case, the section must be increased in the same ratio to remain at iso-velocity.

The variation of the fluid passage section of the collection zones makes it possible to adapt the speed of the fluid passing through them. This makes it possible to adjust, collection zone by collection zone, the cooling capacity and thus to balance them. As a result, the temperatures of the cells facing each other are relatively homogeneous.

According to one aspect of the invention, each placement zone faces the heat transfer fluid evacuation channel so that a component placed in this placement zone can exchange heat with heat transfer fluid.

According to one aspect of the invention, the placement areas are substantially planar.

According to one aspect of the invention, the cross-section of these collection zones has a height which increases or remains constant when moving from one collection zone to the next in the direction of flow of the heat transfer fluid, and

for at least two consecutive collection areas, the downstream collection area has a height greater than that of the upstream collection area, the height being a dimension measured along an axis perpendicular to the plane of the location.

According to one aspect of the invention, at least two consecutive collection zones are spaced apart by a section of the discharge channel having a predetermined length.

According to one aspect of the invention, the section of the discharge channel is free of disturbing elements.

According to one aspect of the invention, the height between each collection area increases by a predetermined factor. In particular, after each connection of a circulation branch, the section of the collection area is increased by 40% to 60% of that of the channel coming from the circulation branch. For example, if the collection area is 100 mm2 in section, before a channel of the circulation branch of 20 mm2 connects to it, the section of the collection area, after the connection, is 100 + 50% x 20 = 110 mm2. This is only one possible example.

It is also possible to predict, for example, by following the direction of flow, that each time a channel adds its flow in the collection zone, then the following passage section increases by a predetermined value, for example by 1 mm in height.

According to one aspect of the invention, the heat transfer fluid is glycolated water.

According to one aspect of the invention, at least one of the collection zones comprises at least one disturbance element.

According to one aspect of the invention, at least one of the collection zones is free of any disturbing element.

According to one aspect of the invention, at least one of the collection zones comprises a group of disturbance elements comprising at least two disturbance elements.

According to one aspect of the invention, at least two of the collection zones each comprise a group of disturbance elements comprising at least two disturbance elements.

According to one aspect of the invention, the dimensions of the disturbance elements of the groups of disturbance elements are chosen so that the disturbances in the heat transfer fluid due to these disturbance elements are less and less strong from one group of disturbance elements to another depending on the direction of flow of the heat transfer fluid.

According to one aspect of the invention, the shape of the disturbance elements of the groups of disturbance elements is chosen so that the disturbances in the heat transfer fluid due to these disturbance elements are less and less strong from one group of disturbance elements to another depending on the direction of flow of the heat transfer fluid.

According to one aspect of the invention, the number of disturbance elements of the groups of disturbance elements is chosen so that the disturbances in the heat transfer fluid due to these disturbance elements are less and less strong from one group of disturbance elements to another depending on the direction of flow of the heat transfer fluid.

According to one aspect of the invention, the dimensions, shape, and/or number of disturbance elements of the groups of disturbance elements are chosen so that the disturbances in the heat transfer fluid due to these disturbance elements are less and less severe from one group of disturbance elements to another depending on the direction of flow of the heat transfer fluid.

According to one aspect of the invention, the disturbance elements of a group of disturbance elements have the same shape among themselves.

According to one aspect of the invention, the disturbance elements of a group of disturbance elements have different shapes from each other.

According to one aspect of the invention, the disturbance elements of a group of disturbance elements have the same dimensions between them.

According to one aspect of the invention, the disturbance elements of a group of disturbance elements have different dimensions from each other.

According to one aspect of the invention, the disturbance element is dome-shaped, in particular with an elongated base or a circular base. The disturbance element may have any other shape, for example a prism or pyramid or other

These disturbance elements can be arranged in different ways depending on the disturbances that we wish to generate.

For example, these disturbance elements are arranged in an aligned manner, or alternately on either side of a line.

According to one aspect of the invention, at least some of the disturbance elements may be arranged in the form of chevron patterns.

The aggressiveness of the disturbance elements or the patterns formed by these disturbance elements can be described as the ability to locally create the conditions for triggering turbulence in the flow. For example, a herringbone pattern causes a concentration of the flow before restriction of the section, while a round dome-shaped disturbance element only acts on the section. Finally, a smooth channel aims for the least disturbance and therefore the least aggressiveness. It can therefore be said that a herringbone pattern is more aggressive than an elongated dome-shaped disturbance element, which is itself more aggressive than a round dome-shaped disturbance element, which is itself more aggressive than a smooth channel. Preferably, the disturbance elements or the patterns formed by the disturbance elements are of a different nature, in particular they are less and less aggressive as one approaches the outlet. For example, the dome-shaped disturbance elements are placed closer to the outlet than the herringbones.

According to one aspect of the invention, the group of disturbance elements comprises at least one pair of disturbance elements formed by a first disturbance element and a second disturbance element, said first and second disturbance elements extending respectively between a first base and a first crest and between a second base and a second crest, said first crest having an elongated shape along a first straight line and said second crest having an elongated shape along a second straight line, said first straight line intersecting said second crest, and a third straight line parallel in the general direction of heat transfer fluid flow, said third straight line passing through the center of the first base intersects the second base.

According to one aspect of the invention, the first and second disturbance elements are dome-shaped, in particular each disturbance element having an elongated base. These disturbance elements advantageously form a chicane with two closely spaced changes of direction, and the spacing between these two disturbance elements in the pair is smaller than the spacing between two such pairs. The closer these disturbance elements in the same pair are, the more pronounced the chicane effect will be and therefore the more aggressive said pair will be. Generally speaking, the aggressiveness of such a pair of disturbance elements is less strong than for the chevron pattern but stronger than for the individual round or elongated dome pattern.

According to one aspect of the invention, the intersection between the first straight line and the third straight line forms an angle A, which is between 20° and 60°, in particular between 30° and 50°.

According to one aspect of the invention, the intersection between the second straight line and the third straight line forms an angle B, which is between 45° and 85°, in particular between 55° and 75°.

According to one aspect of the invention, the angles A and B are chosen so as to form a two-part chevron.

The more pointed the chevron, the more convergent the effect will be, and therefore more aggressive in terms of triggering turbulence. The more pointed the chevron, the less close two consecutive patterns can be placed, which gives an angle at the tip of the chevron advantageously between 55 and 75°.

According to one aspect of the invention, the height of the disturbance element is between 10 to 50% of the height of the evacuation channel, preferably between 20 to 40% of the height of the evacuation channel.

The invention also relates to a thermal regulation device for components whose operation is sensitive to temperature, these components being in particular intended for energy storage and possibly being battery cells, in particular for a vehicle, said device comprising:

- an evacuation channel;

- a heat transfer fluid circulation branch comprising a branch channel having an intermediate section located between an upstream section and a downstream section, these upstream and downstream sections passing opposite at least one internal component placement zone;

• le tronçon intermédiaire du canal dans la branche de circulation de fluide caloporteur ; et
• le canal d’évacuation ;

de sorte qu’un composant placé dans cette zone de placement d’extrémité de composant puisse échanger thermiquement avec du fluide caloporteur circulant :

• dans le tronçon intermédiaire de la branche de circulation de fluide caloporteur ; et
• dans le canal d’évacuation ; et

le tronçon intermédiaire du canal dans la branche de circulation de fluide comporte au moins un élément de perturbation d’écoulement de fluide caloporteur.- a component end placement area different from the component interior placement area, this component end placement area being at least partially in thermal contact with:

• the intermediate section of the channel in the heat transfer fluid circulation branch; and
• the drain channel;

so that a component placed in this component end placement zone can exchange heat with circulating heat transfer fluid:

• in the intermediate section of the heat transfer fluid circulation branch; and
• in the drain channel; and

the intermediate section of the channel in the fluid circulation branch comprises at least one heat transfer fluid flow disturbance element.

The term "inner placement zone" means an area which is remote from the discharge channel, namely that this inner area is cooled by the branch and not by the discharge channel. When the placement zones form a row, two "end placement zones" may be provided at the two opposite ends of the row, while the "inner placement zone" is located between these two end placement zones.

By virtue of the fact that said fluid flow disturbance element is strategically placed on the intermediate section of the fluid circulation branch, it is possible to significantly increase the heat exchanges between the component and the heat transfer fluid, without increasing the heat transfer fluid pressure losses, which would have the effect of limiting the circulation of heat transfer fluid, and therefore of limiting the heat exchange between the heat transfer fluid and the component.

Thus, this strategic placement of the heat transfer fluid flow disturbance element presents an optimal compromise between maximizing heat exchange and minimizing heat transfer fluid flow pressure losses.

According to one aspect of the invention, the intermediate section forms a bend in the canal, in particular a 180° bend in the canal.

According to one aspect of the invention, the downstream section continues to another 180° channel bend, then the channel ends with a terminal section which includes disturbance elements.

The bend of the channel, a place where the singular load losses are important due to its geometry, turns out to be one of the strategic places to maximize the heat exchange. In this way, the heat transfer fluid, although already hot, at the arrival of the discharge channel, can be cooled optimally due to the presence of the heat transfer fluid flow disturbance element.

According to one aspect of the invention, the bend formed by the intermediate section has a U shape.

According to one aspect of the invention, the upstream and downstream sections are straight.

According to one aspect of the invention, the channel in the circulation branch has an additional turn such that the fluid flow in the circulation branch completes at least two turns.

For example, the "extra bend" is located at one end of the branch opposite the bend formed by the intermediate section. The canal thus has, for example, a general serpentine shape.

Two areas are said to be "facing" each other when these areas overlap when observed along an axis perpendicular to these areas.

According to one aspect of the invention, the end placement zone is opposite the discharge channel.

According to one aspect of the invention, the end placement zone is at least partially opposite the intermediate section.

The area of the portion of the end placement zone, in particular in the form of a strip, which is opposite the intermediate section represents 1% to 20%, preferably 1% to 10%, of the total area of the end placement zone.

This strip is at least 2 times, or 4 times, or 5 times, or 10 times smaller than the total end placement zone area.

In other words, most of the end placement area is opposite the discharge channel.

According to one aspect of the invention, the channel of the heat transfer fluid circulation branch comprises a terminal section at the junction with a collection zone of the evacuation channel, and this terminal section comprises at least one fluid flow disturbance element. This terminal section optionally comprises a fluid flow constriction. This constriction makes it possible to adapt the flow rate of fluid circulating in the branch.

The constriction is preferably achieved by a reduction of the section by a narrowing or by a deformation of two walls facing each other. The constriction differs in particular from the disturbance element which can be achieved from a narrowing by the deformation of a single wall.

According to one aspect of the invention, the terminal section with fluid flow disturbance elements extends over at least one third, or at least one half of the length of the branch.

According to one aspect of the invention, the end placement zone is opposite both the intermediate section, the terminal section and the collection zone of the evacuation channel.

According to one aspect of the invention, the collection area is a portion of the discharge channel.

According to one aspect of the invention, the discharge channel is smooth, i.e. free of disturbing elements, outside the collection zone.

According to one aspect of the invention, the channel in the branch is smooth, i.e. free of disturbing elements, apart from the intermediate section and the terminal section.

According to one aspect of the invention, the intermediate section comprises a plurality of disturbance elements, in particular in the shape of a dome, in particular with an elongated base .

According to a particular embodiment, the intermediate section includes more disturbance elements than the upstream and downstream sections.

The invention also relates to a module comprising:

- the thermal regulation device according to the invention, and

• le canal de distribution de fluide caloporteur
• la cavité de ralentissement de fluide caloporteur ;
• le canal d’évacuation de fluide caloporteur.

- a plurality of components placed on the placement zones of the thermal regulation device, at least one of these placement zones being opposite at least one of:

• the heat transfer fluid distribution channel
• the heat transfer fluid slowdown cavity;
• the heat transfer fluid discharge channel.

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

Other features and advantages of the present invention will appear more clearly on reading the following description, provided for illustrative and non-limiting purposes, and the appended drawings in which:

There is a schematic bottom view, in perspective, of a module comprising a thermal regulation device according to the invention,

There is a schematic top view, in perspective, of the thermal regulation device according to the invention,

There is a schematic and partial top view of the thermal regulation device according to the invention,

There is a cross-sectional view of the module along axis AA of the ,

There is a cross-sectional view of the module along the BB axis of the ,

There is a cross-sectional view of the module along the CC axis of the ,

There is a cross-sectional view of the module along the DD axis of the ,

There is a schematic and partial top view of the device, at a collection area remote from the heat transfer fluid outlet of the device,

There is a cross-sectional view of the module at the collection area remote from the heat transfer fluid outlet of the device, and

There is a cross-sectional view of the module at the collection area near the heat transfer fluid outlet of the device.

Definitions

The z-axis is defined as an axis perpendicular to the plane defined by the placement area. The x and y axes are perpendicular to the z-axis so as to form an xyz trihedron.

The x-axis is, for example, the main extension axis of the distribution channel or the discharge channel. In particular, when the distribution channel or the discharge channel has a general L-shape, the x-axis is parallel to the longest straight portion of the distribution channel or the discharge channel.

An example of a dimension measured along this x-axis is the width of the slowdown cavity. The slowdown cavities can have the same width between them.

This definition of width applies analogously along the same x axis for the other elements forming the device, namely for the width of the crosspiece, the width of the circulation branch.

The y-axis is, for example, an axis parallel to the branches extending perpendicular to the main extension axis.

An example of a dimension measured along this y-axis is the length of the slowdown cavity. Slowdown cavities can have different lengths from each other.

The term “upstream” refers to the side of the device from which the heat transfer fluid is admitted into the device, or to the position of the heat transfer fluid before reaching the “downstream” position. For example, the term “upstream” will be used to refer to the relative position of the heat transfer fluid closer to a heat transfer fluid inlet or the heat transfer fluid distribution channel.

The term “downstream” refers to the position of the heat transfer fluid after reaching the “upstream” position.

The term "collection area height" means the maximum height measured in a single collection area. This height is measured, along an axis perpendicular to the plane of the placement area for receiving a component, between smooth walls of the collection area facing each other. This height is notably measured at locations in the collection area that are free of any disturbing element.

In the present invention, two areas are said to be "facing" when these areas overlap when observed along an axis perpendicular to these areas.

It was represented on the , a module 2 comprising a thermal regulation device 4 for components 6 whose operation is sensitive to temperature, these components 6 being in particular intended for energy storage and being able to be battery cells 6, in particular for vehicles.

As seen in Figures 1 to 3, said device 4 comprises:

- a heat transfer fluid distribution channel 8 connected to a heat transfer fluid inlet 9,

- four heat transfer fluid slowing cavities 10, 12, 14, 16 through which the distribution channel 8 passes,

- eight heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112, 114 having substantially the same width between them and parallel to each other in which heat transfer fluid is distributed from the distribution channel 8,

- eight rows 18 each comprising a plurality of placement zones 200 for receiving the components 6, said rows being arranged along an axis y and parallel to each other, these placement zones 200 being opposite the heat transfer fluid slowing cavities 10, 12, 14, 16 so that the components 6 placed in these placement zones 200 can exchange heat with the heat transfer fluid.

Each branch 100, 102, 104, 106, 108, 110, 112, 114 comprises a flat plate 21 comprising a plurality of placement areas 200 for receiving the components 6. The eight rows of placement areas 18 are formed on these flat plates 21.

The device 4 further comprises a heat transfer fluid discharge channel 30. The discharge channel 30 is connected to a heat transfer fluid outlet 32.

The distribution and evacuation channels 8, 32 pass under the trays 21.

The placement zones 200 include the interior placement zones and end placement zones 202, 204.

As is notably illustrated on the , the "inner placement zone" 202 is understood to mean an area which is distant from the discharge channel 30, namely that this inner zone 202 is cooled by the branches 102, 104, 106, 108, 110, 112 and not by the discharge channel 30. When the placement zones 202, 204 form a row, two "end placement zones" 204 may be provided at the two opposite ends of the row, while the "inner placement zone" 202 is located between these two end placement zones 204.

The distribution and evacuation channels 8, 30 each having a general L shape, are mirror symmetrical to each other so that the heat transfer fluid inlet 9 and the heat transfer fluid outlet 32 are symmetrical to each other.

The end placement zones 204 are respectively located on the longest straight portion of the distribution channel 8 and on the longest straight portion of the evacuation channel 30.

The heat transfer fluid circulation branches 100, 102, 104, 106 furthest upstream in the direction of flow in the distribution channel 8 are connected to the slowing-down cavities 10, 12, 14, 16 so that heat transfer fluid having passed through the slowing-down cavities 10, 12, 14, 16 is distributed in the heat transfer fluid circulation branches 100, 102, 104, 106 which open into the heat transfer fluid discharge channel 30. The other heat transfer fluid circulation branches 108, 110, 112, 114 are not connected to the distribution channel 8 by a circulation cavity.

As illustrated in particular in FIGS. 4 to 6, the slowing-down cavities 10, 12, 14, 16 have a first fluid passage section S1 which is both larger than a second passage section S2 of the distribution channel 8 at an upstream junction 22 with the slowing-down cavities 10, 12, 14, 16 and a third passage section S3 of the distribution channel 8 at a downstream junction 24 with the slowing-down cavities 10, 12, 14, 16.

By means of the invention, the heat transfer fluid passing through the slowing-down cavities 10, 12, 14, 16 is slowed down. The reduction in the speed of the heat transfer fluid reduces the heat exchange, in particular compared to the case where the heat transfer fluid would not be slowed down in the absence of such slowing-down cavities 10, 12, 14, 16.

This has the effect of cooling the components 6 located on the placement zones 200 opposite the slowdown cavities 10, 12, 14, 16 less than in the case where such slowdown cavities 10, 12, 14, 16 are absent, when the heat transfer fluid arrives with a low temperature. In this way, overcooling of the components 6 by the heat transfer fluid coming from the distribution channel 8 is avoided.

Thus, the temperature imbalance between the first components 6 encountered by the heat transfer fluid and the rest of the components 6 downstream is reduced. Consequently, all of the components 6 can have optimal operation due to greater temperature homogeneity between the components 6.

Thus, it is possible to use the distribution channel 8 to cool components 6 placed on it. It is thus possible to place a greater number of components 6 overall on the thermal regulation device 4. This increases the energy storage capacity of the components 6 for a given size of thermal regulation device 4, and thus increases the autonomy of a vehicle powered by this energy.

The heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112, 114 connect to the distribution channel 40 with a regular pitch between the heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112, 114, said regular pitch being substantially equal to the width of the circulation branch 100, 102, 104, 106, 108, 110, 112, 114 measured along the x axis.

Thus, the branches 100, 102, 104, 106 and slowing down cavities 10, 12, 14, 16 are spaced apart with the regular pitch.

As illustrated in particular in FIGS. 2 and 5, each heat transfer fluid circulation branch 100, 102, 104, 106, 108, 110, 112, 114 comprises a serpentine-shaped branch channel 40. The branch channel 40 has a passage section S4 connecting to the heat transfer fluid discharge channel 40.

The slowing cavities 10, 12, 14, 16 each have a junction 25 with the circulation branches 100, 102, 104, 106 different from the upstream and downstream junctions 22, 24. The junction 25 connects to the branch channel 40 having the passage section S4.

As shown in Figures 1 and 2, the thermal regulation device 4 comprises two plates 50, 52, namely an upper plate 50 and a lower plate 52.

These plates 50, 52 comprise reliefs, in particular produced by stamping. These reliefs can form, for example, the distribution channel 8, the slowdown cavities 10, 12, 14, 16 and the heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112, 114 as well as the heat transfer fluid evacuation channel 30.

The upper plate 50 faces the components 6 and has a plurality of placement areas 200. The lower plate 52 is defined as the state of the plate whose face opposes that of the upper plate 50.

The two plates 50, 52 can be welded or stamped so as to form the thermal regulation device 4.

The eight heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112, 114 comprise four pairs of branches connected to each other by four crosspieces 60 in the form of a rectilinear strip and having a width substantially equal to the width of each circulation branch 100, 102, 104, 106, 108, 110, 112, 114, and arranged perpendicular to each circulation branch 100, 102, 104, 106, 108, 110, 112, 114. These eight branches 100, 102, 104, 106, 108, 110, 112, 114 are connected to each other by the crosspieces 60 only inside each pair of branches. branches.

An opening 70 having a substantially rectangular perimeter is formed between the two successive crosspieces 60.

As shown in the , the slowing cavities 10, 12, 14, 16 have dimensions which decrease from one circulation branch 100, 102, 104, 106 to the other in the direction of flow of heat transfer fluid in the distribution channel 8.

Thus, the volume of the cavities 10, 12, 14, 16 decreases from one branch 100, 102, 104, 106 to the other in the direction of flow of heat transfer fluid in the distribution channel 8. The dimensions of the slowing down cavities 10, 12, 14, 16 can be adapted according to the heat flow that it is desired to reduce.

Still referring to Figures 3 and 6, it can be seen that the first slowing cavity 100 has dimensions arranged to be opposite three placement zones 200.

The second slowing cavity 102 has dimensions arranged to be opposite between two and three placement zones 200.

The third slowing cavity 104 has dimensions arranged to be opposite two placement zones 200.

The fourth slowing cavity 106 has dimensions arranged to be opposite one and a half placement zones 200.

As can be seen in particular on the , the distribution and evacuation channels 9, 30 each comprise a flat 80 bordered on each side by a flank 82.

The flats 80 follow the path formed by the distribution and evacuation channels 9, 30.

As seen in Figures 3 to 5, the slowing down cavities 10, 12, 14, 16 have a substantially rectangular shaped perimeter, when the slowing down cavities are observed along the z axis.

In the following, the first slowing cavity 10 is taken as an example. However, the characteristics of the first slowing cavity 10 are also valid for the other slowing cavities 12, 14, 16.

As illustrated in Figures 5 and 7, the slowing cavity 10 has a height hd which is maximum at its junction 22, 24 with the distribution channel 8. The height in the slowing cavities hb at the junction with the branch channel 40 is smaller than the height hd at its junction with the distribution channel 8.

The height of the slowing cavity hd changes to a height hint1 due to the presence of the side 82 of the distribution channel 8.

Between the junction of the distribution channel 8 with the slowing-down cavities 10, 12, 14, 16 and the junction of the branch channel 40 and the slowing-down cavities 10, 12, 14, 16, the height in the slowing-down cavities 10, 12, 14, 16 decreases, in particular by two steps 84, 86.

The first step 84 having a height hint1 is defined between the junction of the distribution channel 8 with the slowing down cavities 10, 12, 14, 16 and the second step 86 having a height hint2 is defined between and the junction of the branch channel 40 and the slowing down cavities 10, 12, 14, 16.

The slowing-down cavities 10, 12, 14, 16 are formed locally by recesses 90 of one of the plates forming the device 4, in particular of the lower plate 52, so that at the level of these recesses 90, the height hc of the slowing-down cavities 10, 12, 14, 16 measured along the z axis are reduced relative to the height hint of the first level 84 defined between the junction of the distribution channel 8 with the slowing-down cavities 10, 12, 14, 16.

The heights hd, hb, hc, hint1, hint2 are defined along the z axis.

As seen in Figures 1 and 8, the thermal regulation device 4 comprises:

- the seven heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112 each comprising the branch channel 40 having an intermediate section 120 located between an upstream section 130 and a downstream section 140 which are rectilinear, these upstream and downstream sections 130, 140 passing opposite at least one internal component placement zone 202;

• le tronçon intermédiaire 120 du canal 40 dans les branches de circulation de fluide caloporteur 102, 104, 106, 108, 110, 112 ; et
• le canal d’évacuation 30 ;

de sorte qu’un composant 6 placé dans cette zone de placement d’extrémité de composant 204 puisse échanger thermiquement avec du fluide caloporteur circulant :

• dans le tronçon intermédiaire 120 de les branches de circulation de fluide caloporteur 102, 104, 106, 108, 110, 112 ; et
• dans le canal d’évacuation 30 ; et

le tronçon intermédiaire du canal 120 dans les branches de circulation de fluide 102, 104, 106, 108, 110, 112 comporte des éléments de perturbation d’écoulement de fluide caloporteur 150 en forme de dôme de base allongée. - a component end placement zone 204 different from the component interior placement zone 202, this component end placement zone 204 being at least partially in thermal contact with:

• the intermediate section 120 of the channel 40 in the heat transfer fluid circulation branches 102, 104, 106, 108, 110, 112; and
• the evacuation channel 30;

so that a component 6 placed in this component end placement zone 204 can exchange heat with circulating heat transfer fluid:

• in the intermediate section 120 of the heat transfer fluid circulation branches 102, 104, 106, 108, 110, 112; and
• in the discharge channel 30; and

the intermediate section of the channel 120 in the fluid circulation branches 102, 104, 106, 108, 110, 112 comprises heat transfer fluid flow disturbance elements 150 in the form of an elongated base dome .

The end placement zone 204 faces the discharge channel 30 and is at least partially faces the intermediate section 120.

By virtue of the fact that said fluid flow disturbance elements 150 are strategically placed on the intermediate section 120 of the fluid circulation branches 102, 104, 106, 108, 110, 112, it is possible to significantly increase the heat exchanges between the component 6 and the heat transfer fluid, without increasing the heat transfer fluid pressure losses, which would have the effect of limiting the circulation of heat transfer fluid, and therefore of limiting the heat exchange between the heat transfer fluid and the component 6.

Thus, this strategic placement of the heat transfer fluid flow disturbance elements 150 presents an optimal compromise between maximizing heat exchange and minimizing heat transfer fluid flow pressure losses.

The intermediate section 120 forms a 180° bend in the canal with a U shape.

The downstream section 140 extends to another 180° channel bend, then the channel 40 ends with a terminal section 160 which includes disturbance elements 152.

The bend of channel 40, a place in which the singular pressure losses are important due to its geometry, turns out to be one of the strategic places to maximize the heat exchange. In this way, the heat transfer fluid, although it is already hot, at the arrival of the discharge channel 30, can be cooled optimally due to the presence of the heat transfer fluid flow disturbance elements 150.

The channel 40 has an additional bend 170 located at one end of the branches 102, 104, 106, 108, 110, 112, opposite the bend formed by the intermediate section 120 so that the flow of fluid in the circulation branches 102, 104, 106, 108, 110, 112 completes two bends.

The area of the portion of the end placement zone 204 in the form of a strip 206 which is opposite the intermediate section represents 1% to 20%, preferably 1% to 10%, of the total area of the end placement zone 204. This strip 206 is at least 10 times smaller than the total area of the end placement zone.

In other words, the majority of the end placement area 204 is opposite the discharge channel 30.

The terminal section 160 is in junction with a collection zone of the evacuation channel 180 which is a portion of the evacuation channel 30, and this terminal section 160 comprises fluid flow disturbance elements 154.

As illustrated in Figures 2 and 8, the terminal section 160 with fluid flow disturbance elements 154 extends over at least half the length of the branch 1.

The end placement zone 204 is opposite both the intermediate section 120, the terminal section 160 and the collection zone 180 of the evacuation channel 30.

The discharge channel 30 is smooth, i.e. free of disturbing elements 154, outside the collection zone 160.

The channel 40 in the branches 100, 102, 104, 106, 108, 110, 112 is smooth, namely free of disturbance elements 152, apart from the intermediate section 120 and the terminal section 160.

As illustrated in Figures 2 and 8, the device 4 comprises:

- six heat transfer fluid circulation branches 100, 102, 104, 106, 108, 110, 112 which each open into a collection zone 180 of the discharge channel 30 so that heat transfer fluid having circulated in the branches 100, 102, 104, 106, 108, 110, 112 is discharged via the heat transfer fluid discharge channel 30, these collection zones 180 being distributed along the discharge channel 30, and

- a plurality of placement zones 200 each arranged to receive the component 6, each placement zone 200 being in thermal contact with the heat transfer fluid evacuation channel 30 so that a component 6 placed in this placement zone 200 can exchange heat with heat transfer fluid circulating in the heat transfer fluid evacuation channel 30, this placement zone 200 being substantially planar,

the collection zones 180 each have a cross-section St which increases or remains constant when moving from one collection zone 180 to the next in the direction of flow of the heat transfer fluid, and

for at least two consecutive collection zones 180, the downstream collection zone has a larger cross-section St than that of the upstream collection zone.

In the invention, since the collection zones 180 have a cross-section which increases, by increasing the height, as one approaches the outlet, it is possible to maintain a constant exchange coefficient along the flow. For this purpose, the pressure loss is locally increased. In this case, the pressure gradient increases along the discharge channel 30.

It should be noted that the main factor contributing to the pressure difference is the average fluid velocity, which is proportional to the flow rate. In this case, the section St must be increased in the same ratio to remain at iso-velocity.

As illustrated in Figures 9 and 10, the cross sections Sc of the collection zones 180 corresponding respectively to the branches 112 and 102 respectively have a height hu and a height hd.

The height of the collection zone 180 increases when moving from a collection zone 180 upstream of the branch 112 to the collection zone 180 downstream of the branch 102 in the direction of flow of the heat transfer fluid.

In other words, the collection zone 180 downstream of the branch 102 has a height hd greater than the height hu of the collection zone 180 upstream, the heights hd and hu being dimensions measured along the z axis.

As shown in the , the width of the collection zone 180 measured along the x axis is substantially equal to the dimension of the branches measured along the same x axis. The two consecutive collection zones 180 are spaced apart by a section of the discharge channel 182 having a predetermined length. Each section of the discharge channel 182 is free of disturbance elements 154.

The height between each collection zone 180 increases by a predetermined factor. For example, following the direction of flow, each time a channel adds its flow into the collection zone, then the next passage section increases by a predetermined value, for example by 1 mm in height.

The collection zones 180 have between four and six disturbance elements 154.

These disturbance elements 154 are dome-shaped with an elongated base or with a circular base. These disturbance elements 154 may have any other shape, for example a prism or pyramid or other.

These disturbance elements 154 can be arranged in different ways depending on the disturbances that one wishes to generate.

For example, these disturbance elements 154 are arranged in an aligned manner, or alternately on either side of a line.

As seen in Figures 9 to 10, the height of the disturbance elements 154 measured along the z axis is between 10 to 50% of the height of the discharge channel.

In reference to the , the collection zone 180 receiving the heat transfer fluid coming from the first slowing cavity 10 is free of any disturbing element.

Claims (16)

Thermal regulation device (4) for components (6) whose operation is sensitive to temperature, these components (6) being in particular intended for energy storage and being able to be battery cells (6), in particular for vehicles, said device (4) comprising:
- a heat transfer fluid evacuation channel (30);
- at least two heat transfer fluid circulation branches (10, 12, 14, 16) which each open into a collection zone (180) of the discharge channel (30) so that heat transfer fluid having circulated in the branches (10, 12, 14, 16) is discharged via the heat transfer fluid discharge channel (30), these collection zones (180) being distributed along the discharge channel (30), and
- at least two placement zones (204) each arranged to receive said component, each placement zone (204) being in thermal contact with the heat transfer fluid evacuation channel (30) so that a component (6) placed in this placement zone (204) can exchange heat with heat transfer fluid circulating in the heat transfer fluid evacuation channel (30),
the collection zones (180) each have a cross-section (Sc) which increases or remains constant when moving from one collection zone to the next in the direction of flow of the heat transfer fluid, and
for at least two consecutive collection zones (180), the downstream collection zone (180) has a larger cross-section (Sc) than that of the upstream collection zone (180). The device of claim 1, wherein the placement areas (204) are substantially planar. Device according to claim 1 or 2, in which each placement zone (204) is opposite the heat transfer fluid evacuation channel so that a component (6) placed in this placement zone (204) can exchange heat with heat transfer fluid. Device according to any one of the preceding claims, in which the cross-section (Sc) of these collection zones (180) has a height (hd, hu) which increases or remains constant when passing from one collection zone (180) to the next in the direction of flow of heat transfer fluid, and for at least two consecutive collection zones (180), the downstream collection zone has a height (hd) greater than that of the upstream collection zone (hu), the height being a dimension measured along an axis perpendicular (z) to the plane of the location. Device according to any one of the preceding claims, in which, after each connection of a circulation branch, the section of the collection zone (180) is increased by 40% to 60% of that of the channel coming from the circulation branch (10, 12, 14, 16). Device according to any one of the preceding claims, at least one of the collection zones (180) comprises at least one disturbance element (154). Device according to the preceding claim, in which the disturbance elements or the patterns formed by the disturbance elements are of different nature, and in particular are less and less aggressive as one approaches the exit. Device according to the preceding claim, in which the disturbance elements are chosen from: chevron disturbance elements, elongated dome-shaped disturbance elements, round dome-shaped disturbance elements. Device according to any one of the preceding claims, the group of disturbance elements comprises at least one pair of disturbance elements formed by a first disturbance element (154) and a second disturbance element (154), said first and second disturbance elements (154) extending respectively between a first base and a first crest and between a second base and a second crest, said first crest having an elongated shape along a first straight line and said second crest having an elongated shape along a second straight line, said first straight line intersecting said second crest, and a third straight line parallel to the general direction of flow of heat transfer fluid, said third straight line passing through the center of the first base intersects the second base. Device according to the preceding claim, in which the first and second disturbance elements (154) are dome-shaped, in particular each disturbance element (154) having an elongated base. Device according to claim 9 or 10, in which the intersection between the first straight line and the third straight line forms an angle A, which is between 20° and 60°, in particular between 30° and 50°. Device according to one of claims 9 to 11, the intersection between the second straight line and the third straight line forms an angle B, which is between 45° and 85°, in particular between 55° and 75°. Device according to claim 11 and 12, in which the angles A and B are chosen so as to form a two-part chevron. Device according to any one of the preceding claims, in which the height of the disturbance element (154) is between 10 to 50% of the height of the evacuation channel (30), preferably between 20 to 40% of the height of the evacuation channel (30). Device according to any one of the preceding claims, in which at least two consecutive collection zones (180) are spaced apart by a section of the discharge channel (30) having a predetermined length. Module (2) comprising:
- the thermal regulation device (4) according to any one of the preceding claims, and
- a plurality of components (6) placed on the placement zones of the thermal regulation device (200; 202; 204), at least one of these placement zones (200; 202; 204) being opposite at least one of:

• the heat transfer fluid distribution channel (8)
• the heat transfer fluid slowing cavity (10, 12, 14, 16);
• the heat transfer fluid discharge channel (30).