EP3973239A1

EP3973239A1 - Refrigerant/heat transfer liquid heat exchanger

Info

Publication number: EP3973239A1
Application number: EP20731398.2A
Authority: EP
Inventors: Jugurtha Benouali
Original assignee: Valeo Systemes Thermiques SAS
Current assignee: Valeo Systemes Thermiques SAS
Priority date: 2019-05-21
Filing date: 2020-05-18
Publication date: 2022-03-30
Also published as: FR3096449B1; US20220236017A1; CN114144634A; FR3096449A1; WO2020234213A1

Abstract

The present invention relates to a refrigerant/heat transfer liquid heat exchanger (10) comprising at least one stack of plates (105b, 105c, 105d, 105e, 105f) delimiting at least two heat exchange compartments (41, 42) which are sealed with respect to one another, including a first heat exchange compartment (41), which has a first circulation path for a refrigerant (21a) and a first circulation path for a heat transfer liquid (22a), and a second heat exchange compartment (42) which has a second circulation path for a refrigerant (21b) and a second circulation path for a heat transfer liquid (22b). At least one of the circulation paths (21a, 22a) of the first heat exchange compartment (41) and one of the circulation paths (22a, 22b) of the second heat exchange compartment (42) are at least partially delimited by a same plate (105b, 105c, 105d, 105e,105f).

Description

Title:

Refrigerant / heat transfer liquid heat exchanger

The present invention relates to a refrigerant / coolant liquid heat exchanger. The present invention also relates to an installation comprising a refrigerant circuit, a heat transfer liquid circuit and such a coolant / heat transfer liquid heat exchanger. The present invention also relates to a method for cooling a

electrical storage device of a motor vehicle by means of such an installation.

In the automotive industry, it is common to have to modify a

temperature of a component, such as an electric motor, a battery, a calorie and / or cold storage device or the like. To this end, the motor vehicle is equipped with an installation which comprises a refrigerant circuit inside which circulates a refrigerant fluid and a heat transfer liquid circuit inside which circulates a heat transfer liquid. The refrigerant circuit comprises a compressor for compressing the refrigerant, a heat exchanger for cooling the refrigerant at constant pressure, an expansion member to allow an expansion of the refrigerant and a refrigerant / coolant heat exchanger which is arranged to allow heat transfer between the coolant and the coolant. The heat transfer liquid circuit comprises a pump and a heat exchanger capable of modifying a

component temperature.

The refrigerant / coolant heat exchanger is a

exchanger comprising plates stacked and joined together to form tubes delimiting circulation chambers for the refrigerant or heat transfer liquid. The plate comprises four orifices to allow an inlet and an outlet of the refrigerant fluid, and an inlet and an outlet of the coolant liquid inside the circulation chambers located on either side of the same plate. The coolant / coolant heat exchanger is bordered by a first cheek and a second cheek between which the plates are arranged. The first cheek is provided with four passages to allow an inlet and an outlet of the coolant, and an inlet and an outlet of the heat-transfer liquid inside the circulation chambers situated on either side of the same plate. The second cheek is free of passage.

It is common to have to cool the component in different ways, especially when it includes at least one electric battery. Indeed, it is necessary to cool the electric heater during its

charging during which the electric battery tends to heat up. The electric battery can be recharged in the fast charging mode in which a charging time is short and a charging electric current is high, or in a normal charging mode in which the charging time is long and the charging electric current is low. However, the heating of the electric battery is generally proportional to the electric current of charge.

Thus, it is common to have to cool the electric battery in fast charge mode in which the electric battery dissipates a large amount of heat requiring that a cooling power supplied by the heat exchanger is also large. It is also common to have to cool the electric battery in normal charge mode in which the electric battery dissipates a small amount of heat, which is sufficient to dissipate cooling power considerably less than that required in fast charging mode.

To deal with these two distinct modalities of operation,

the refrigerant / coolant heat exchanger is

usually configured to provide the high cooling power that is required when the electric battery is in fast charge mode. In other words, the coolant / coolant heat exchanger is sized and configured to provide high cooling power, corresponding to that required to dissipate the heat supplied by the battery in fast charge mode.

However, and paradoxically, it appears that a fluid heat exchanger The refrigerant / coolant thus configured has a degraded cooling efficiency when the required cooling power is low. In other words, it appears that the refrigerant / coolant liquid heat exchanger thus configured cools the electric coil less well in normal charging mode than this same electric coil in fast charging mode.

An object of the present invention is to provide a refrigerant / coolant liquid heat exchanger configured to efficiently and rapidly supply cooling power adapted as a function of various operating modes of the electric battery.

The present invention improves the situation by providing a refrigerant / coolant liquid heat exchanger having the following technical characteristics.

An exchanger of the present invention is a refrigerant / coolant liquid heat exchanger comprising at least one stack of plates delimiting at least two heat exchange compartments sealed relative to each other, including a first compartment of heat exchange which comprises a first circulation path of a refrigerant fluid and a first circulation path of a coolant liquid, as well as a second heat exchange compartment which comprises a second circulation path of the refrigerant fluid and a second circulation path of the heat transfer liquid.

According to the present invention, at least one of the circulation paths of the first heat exchange compartment and one of the circulation paths of the second heat exchange compartment are at least partly delimited by the same plate.

The coolant / coolant heat exchanger advantageously comprises any at least of the following technical characteristics, taken alone or in combination:

- the same plate delimits the first circulation path for the refrigerant fluid and the second circulation path for the refrigerant fluid, - the same plate delimits the first circulation path of the coolant liquid and the second circulation path of the coolant liquid,

- The same plate jointly delimits the first path for circulating the coolant, the first path for circulating the coolant liquid, the second path for circulating the coolant and the second path for circulating the coolant,

- the refrigerant / coolant heat exchanger and its heat exchange compartments are integral and cannot operate after dissociation of the heat exchange compartments between them,

- the heat exchange compartments are sealed with respect to each other in the sense that no fluid, either refrigerant fluid and / or heat transfer liquid, can pass directly from one of the compartments to the other. heat exchange,

the circulation paths of the refrigerant fluid and the circulation paths of the coolant liquid are arranged so as to allow an exchange of calories between the coolant fluid intended to circulate inside the circulation paths of the coolant fluid and the coolant liquid intended for circulate inside the circulation paths of the heat transfer liquid, the circulation paths whatever they may be housed inside the first heat exchange compartment or the second heat exchange compartment,

- the first heat exchange compartment and the second

heat exchange compartment are bordered by a first cheek and a second cheek,

- the first cheek is provided with eight passages, including a first passage, a second passage, a third passage and a fourth passage assigned to the first heat exchange compartment, and including a fifth passage, a sixth passage, a seventh passage and an eighth passage assigned to the second heat exchange compartment, the second cheek is free of passage, - The first refrigerant circulation path comprises a plurality of first refrigerant circulation chambers, the second refrigerant circulation path comprises a plurality of second refrigerant circulation chambers, the first heat transfer liquid circulation path comprises a plurality of first heat transfer liquid circulation chambers, the second heat transfer liquid circulation path comprises a plurality of second heat transfer liquid circulation chambers, and the same plate jointly defines one of the first refrigerant circulation chambers, the 'one of the second coolant circulation chambers, one of the first coolant liquid circulation chambers and one of the second coolant liquid circulation chambers,

a first coolant circulation chamber is interposed between two first coolant liquid circulation chambers and a first coolant liquid circulation chamber is interposed between two first coolant circulation chambers,

- A second coolant circulation chamber is interposed between two second coolant circulation chambers and a second coolant liquid circulation chamber is interposed between two second coolant circulation chambers,

- A first volume of a first refrigerant circulation chamber is between 30% and 50% of a first total volume of a first refrigerant circulation chamber and of a second refrigerant circulation chamber, said first volume is in particular of the order of one third, to within plus or minus 10%, of said first total volume,

a second volume of a second refrigerant circulation chamber is between 50% and 70% of said first total volume, said second volume is in particular of the order of two thirds, to within plus or minus 10%, of said first total volume, - a third volume of a first heat transfer liquid circulation chamber is between 30% and 50% of a second total volume of a first heat transfer liquid circulation chamber and of a second heat transfer liquid circulation chamber, said third volume is in particular of the order of a third, to within plus or minus 10%, of said second total volume,

- a fourth volume of a second heat transfer liquid circulation chamber is between 50% and 70% of said second total volume, the fourth volume of a second heat transfer liquid circulation chamber is in particular of the order of two thirds, within plus or minus 10%, of said second total volume,

- the first volume and the third volume are equal, up to the manufacturing tolerances, the second volume and the fourth volume are equal to the nearest manufacturing tolerances,

- the first volume and the third volume are different, and the second volume and the fourth volume are different,

- the sum of the first volume and the second volume is equal to the sum of the third volume and the fourth volume,

- The refrigerant / coolant heat exchanger comprises at least one manifold extending along a general axis of extension which is parallel to a separation plane jointly bordering the first heat exchange compartment and the second heat exchange compartment. heat exchange,

- the first heat exchange compartment and the second

heat exchange compartment are arranged side by side,

- the first heat exchange compartment and the second

heat exchange compartment are next to each other while being in contact with each other through the separation plane,

- the separation plane which delimits the first heat exchange compartment and the second heat exchange compartment is orthogonal to a first plane in which the first cheek is inscribed and a second plane in which the second cheek is inscribed,

- at least one of the heat exchange compartments has four collectors,

- the collectors allow admission or discharge of refrigerant or heat transfer liquid inside the refrigerant / heat transfer liquid heat exchanger,

- the first heat exchange compartment has four collectors and the second heat exchange compartment has four collectors,

- two of the collectors of the same heat exchange compartment are dedicated to the circulation of the refrigerant fluid, and the other two collectors of the same heat exchange compartment are dedicated to the circulation of the coolant,

- two of the collectors of the same heat exchange compartment are in fluid communication with the first circulation path of the refrigerant fluid and the other two collectors of the same heat exchange compartment are in fluid communication with the first circulation path heat transfer liquid,

- at least one of the collectors extends from one end to the other of one of the

heat exchange compartments along its axis of general extension which intersects with a bottom plane in which extends a bottom of the plate,

- the plate includes at least one groove which seals off the first heat exchange compartment and the second heat exchange compartment,

- The first circulation chambers on the one hand and the second circulation chambers on the other hand are stacked along a stacking direction which is parallel to the general axis of extension of the collector, at least one chamber of circulation, indifferently first circulation chamber or second circulation chamber, being delimited by two immediately adjacent plates and at least the groove of one of these plates, a coolant circulation chamber is interposed between two coolant liquid circulation chambers and a coolant liquid circulation chamber is interposed between two coolant circulation chambers,

- each plate has a raised edge formed by two longitudinal edges and two lateral edges and surrounding the bottom which is provided with eight holes,

- the plates are assembled together by brazing at least their raised edges,

- the eight orifices include four orifices including a first orifice, a second orifice, a third orifice and a fourth orifice arranged inside a first zone of the plate, and four other orifices including a fifth orifice, a sixth orifice, a seventh orifice and an eighth orifice arranged inside a second zone of the plate, the first zone and the second zone being separated from each other by the groove which comes from the bottom of the plate and which extends between a first side edge and a second side edge of the plate.

- the first zone constitutes the first heat exchange compartment and the second zone constitutes the second heat exchange compartment,

- the groove is parallel to the first longitudinal edge and to the second longitudinal edge,

- a first zone width taken perpendicularly between a first longitudinal edge and the groove is between 30% and 50% of a width of plate taken perpendicularly between the first longitudinal edge and the second longitudinal edge, the first zone width is in particular of the order of a third, to within plus or minus 10%, of the plate width,

a second zone width taken perpendicularly between the groove and the second longitudinal edge is between 50% and 70% of the plate width, the second zone width is in particular of the order of two thirds, plus or minus 10 % near, of the plate width,

- According to a first embodiment, a first manifold and a third manifold are constitutive of the first circulation path of the heat transfer liquid, the second manifold and the fourth manifold are constitutive of the first circulation path of the refrigerant fluid, the fifth manifold and the seventh manifold are constitutive of the second circulation path of the coolant, and the seventh manifold and the eighth manifold are constitutive of the second circulation path of the coolant liquid,

- the first circulation path for the refrigerant fluid and the first circulation path for the coolant liquid are shaped in an "I" shape,

- the second coolant circulation path and the second coolant liquid circulation path are shaped in an "I" shape, - according to a second embodiment, the first manifold and the second manifold are constitutive of the first coolant liquid circulation path , the third manifold and the fourth manifold constitute the first path for circulating the refrigerant fluid, the fifth manifold and the sixth manifold are constitutive of the second path for circulating the coolant liquid, and the seventh manifold and the eighth manifold are constitutive of the second path circulation of the refrigerant,

- the first path for circulating the refrigerant fluid and the first path for circulating the coolant liquid are "U" shaped,

- the second refrigerant circulation path and the second heat transfer liquid circulation path are "U" shaped, - the first orifice has a first diameter, the second orifice has a second diameter, the third orifice has a third diameter and the fourth orifice has a fourth diameter, the fifth orifice has a fifth diameter , the sixth hole is of a sixth diameter, the seventh hole is of a seventh diameter and the eighth hole is of an eighth diameter,

- According to a first embodiment, the first diameter, the third diameter, the sixth diameter and the eighth diameter are equal, the second diameter and the fifth diameter are equal, and the fourth diameter and the seventh diameter are equal by being greater than second diameter and fifth diameter,

- in this case, the second orifice is an orifice for admitting the refrigerant fluid inside the first heat exchange compartment, the fourth orifice is an orifice for discharging the refrigerant fluid out of the first compartment of heat exchange, the fifth port is an inlet port for refrigerant fluid inside the second

heat exchange compartment and the seventh port is a port for discharging the refrigerant from the second heat exchange compartment,

- According to a second embodiment, the first diameter and the third diameter are equal, the sixth diameter and the eighth diameter are equal, the second diameter is less than the fourth diameter, and the fifth diameter is less than the seventh diameter,

heat exchange compartment and the seventh orifice is an orifice for discharging the refrigerant fluid out of the second heat exchange compartment, - According to a third embodiment, the first diameter, the third diameter, the sixth diameter and the eighth diameter are equal, the second diameter is greater than the fourth diameter, and the fifth diameter is greater than the seventh diameter,

- In this case, the second orifice is an orifice for discharging the refrigerant fluid out of the first heat exchange compartment, the fourth orifice is an orifice for admitting the refrigerant fluid inside the first compartment of heat exchange, the fifth port is an outlet for refrigerant fluid out of the second heat exchange compartment and the seventh port is an inlet for refrigerant fluid inside the second heat exchange compartment ,

- the bottom of the plate is provided with at least one rib which extends inside the first zone and / or the second zone,

- these arrangements are such that a circulation of the refrigerant fluid and the heat transfer liquid are arranged in "I" and are either co-current or counter-current,

- the rib is substantially perpendicular to the groove, preferably the rib is perpendicular to the groove,

- the rib is substantially parallel to the groove, preferably the rib is parallel to the groove,

- According to a first variant, a first groove extends parallel to the side edges from one of the longitudinal edges to a free end of the first groove, and a second groove extends parallel to the side edges from one of the edges longitudinal to a free end of a second groove,

- the first groove extends from the first longitudinal edge to the end of the first groove which is located at a non-zero distance from the groove, and the second groove extends from the first longitudinal edge to the end 'end of a second groove which is located at a non-zero distance from the groove, - These arrangements are such that a circulation of the refrigerant fluid and of the heat transfer liquid are arranged in a "U" and are co-current,

- the first groove extends from the groove to the end of the first groove which is located at a non-zero distance from the first longitudinal edge, and the second groove extends from the groove to the end of second groove which is located at a non-zero distance from the first longitudinal edge,

- these arrangements are such that a circulation of the refrigerant fluid and of the heat transfer liquid are arranged in a "U" and are co-current,

- According to a second variant, the first groove extends parallel to the longitudinal edges from one of the lateral edges to the end of the first groove, and the second groove extends parallel to the longitudinal edges from one of the edges lateral to the end of the second groove,

- the first groove extends from the first side edge to the end of the first groove which is located at a non-zero distance from the second side edge, and the second groove extends from the first side edge to the end of the second groove which is located at a non-zero distance from the second side edge,

- the first groove extends from the second side edge to the end of the first groove which is located at a non-zero distance from the first side edge, and the second groove extends from the second side edge to the end of the second groove which is located at a non-zero distance from the first side edge,

- these arrangements are such that a circulation of the refrigerant fluid and of the heat transfer liquid are arranged in a "U" and are counter-current,

The present invention also relates to an installation for the heat treatment of a component fitted to a motor vehicle, the installation comprising a refrigerant circuit, a coolant circuit and such a coolant / coolant liquid heat exchanger, the circuit of refrigerant fluid comprising a first circulation branch coolant and a second branch for circulating the coolant which are arranged in parallel with one another, the coolant circuit comprising a first branch for circulating the coolant and a second branch for circulating the coolant which are arranged in parallel with each other, the first circulation path of the refrigerant fluid being constitutive of the first circulation branch of the refrigerant fluid, the first circulation path of the coolant liquid being constitutive of the first circulation branch of the coolant liquid , the second path for circulating the coolant being constituting the second branch for circulating the coolant and the second path for circulating the coolant liquid being constituting the second branch for circulating the coolant,

- In other words, the first circulation branch of the coolant fluid comprises the first circulation path of the coolant fluid, the first circulation branch of the coolant liquid comprises the first circulation path of the coolant liquid, the second circulation branch of the coolant fluid comprises the second path for circulating the coolant and the second branch for circulating the coolant liquid comprises the second path for circulating the coolant,

The present invention also relates to a method for cooling an electrical storage device of a motor vehicle by means of such an installation, in which:

- the first heat exchange compartment and the second

the heat exchange compartment are traversed by the refrigerant fluid and the heat transfer liquid when the electrical storage device is in a fast charge mode,

- only the first heat exchange compartment is traversed by the refrigerant fluid and the heat transfer liquid when the electrical storage device is in normal charging mode,

- only the second heat exchange compartment is traversed by the refrigerant fluid and by the heat transfer liquid when the electrical storage device is in an intermediate charging mode, - It is understood that in fast charge mode, a charging time of the electrical storage device is short and that an electrical charging current of the electrical storage device is high, that in normal charge mode of the electrical storage device, the charging time is long and the charging electric current is small, and in intermediate charging mode of the electric storage device, the charging time is between short time and long charging time and charging electric current is included between low charge current and high charge current.

The invention will be better understood on reading the following non-limiting description, drawn up with reference to the appended drawings, in which:

[Fig. î] - Figure i shows a first embodiment of an installation of the present invention, according to a first mode of

cooling of a component.

[Fig. 2] - Figure 2 shows the installation according to the first variant embodiment illustrated in Figure i and according to a second mode of

component cooling.

[Fig. 3] - Figure 3 shows a second alternative embodiment of the installation of the present invention, according to the first mode of

cooling of a component.

[Fig. 4] - Figure 4 shows the installation according to the second variant embodiment illustrated in Figure 3 and according to the second mode of

component cooling.

[Fig. 5] - Figure 5 shows the installation according to the second variant embodiment illustrated in Figures 3 and 4 and according to a third method of cooling the component.

[Fig. 6] - Figure 6 shows in perspective a first variant embodiment of a refrigerant / coolant liquid heat exchanger of the present invention which constitutes the installation illustrated in Figures 1 and 2.

[Fig. 7] - Figure 7 shows in perspective a second variant embodiment of a refrigerant / coolant liquid heat exchanger of the present invention which constitutes the installation illustrated in Figures 3 to 5.

[Fig. 8] - Figure 8 shows schematically a front view of a first type plate constituting the refrigerant / coolant liquid heat exchanger shown in Figure 6.

[Fig. 9] - Figure 9 shows schematically a front view of a plate of the second type constituting a first embodiment of the refrigerant / coolant heat exchanger shown in Figure 7.

[Fig. 10] - Figure 10 schematically shows a front view of a third type plate constituting a second embodiment of the coolant / coolant heat exchanger shown in Figure 7.

[Fig. 11] - Figure 11 shows schematically a front view of a fourth type plate constituting the second mode of the refrigerant / coolant heat exchanger shown in Figure 7.

[Fig. 12] - Figure 12 shows schematically a front view of a fifth type plate constituting a third embodiment of the coolant / coolant heat exchanger shown in Figure 7.

[Fig. 13] - Figure 13 shows schematically a front view of a sixth type plate constituting the third embodiment of the refrigerant / coolant heat exchanger shown in Figure 7.

[Fig. 14] - Figure 14 shows schematically a side section of four plates illustrated in Figure 8 assembled together.

[Fig. 15] - figure 15 shows schematically a side section of four plates illustrated in figure 9 assembled together.

[Fig. 16] - figure 16 shows schematically a side section of four plates, including two plates of the third type illustrated in figure 10 and two plates of the fourth type illustrated in figure 11, assembled between they to form the refrigerant / liquid heat exchanger

coolant shown in Figure 7.

[Fig. 17] - figure 17 shows schematically a side section of four plates, including two plates of the fifth type illustrated in figure 12 and two plates of the sixth type illustrated in figure 13, assembled together to form the refrigerant heat exchanger. / liquid

coolant shown in Figure 7.

In Figures 1 to 5, a motor vehicle is equipped with a component 1 that should be cooled or heated, for example to optimize its operation. Such a component 1 is for example an electric or thermal motor intended to at least partially propel the motor vehicle, an electric storage device comprising at least one electric battery provided for storing electric energy, a device for storing calories and / or frigories or the like. Component 1 is more particularly an electrical storage device comprising at least one electric battery, which can be recharged in particular in fast charging mode in which a charging time is short and an electric charging current is high, or else in normal charging mode. wherein the charging time is long and the charging electric current is small. The present invention aims to effectively cool the electric battery, whatever its charging mode: fast charging mode in which the electric battery heats up quickly and strongly, as shown in Figures 1 and 3, or charging mode normal in which the electric battery heats up slowly and weakly, as shown in Figures 2 and 4, or alternatively in an intermediate mode in which the battery heats up

moderately, especially more than in normal charge mode and less than in fast charge mode, as shown in Figure 5.

To this end, the motor vehicle is equipped with an installation 2 which comprises a refrigerant fluid circuit 3 inside which circulates a refrigerant fluid 4, carbon dioxide for example or the like, and a coolant circuit 5 to l 'Inside which circulates a coolant 6, in particular glycol water or the like. Installation 2 is configured to modify a temperature of component 1, and in particular to cool component 1.

The installation 2 comprises at least one refrigerant / coolant liquid heat exchanger 10 according to the present invention. Installation 2 is described below for a better understanding of the present invention, but the characteristics of installation 2 described are in no way restrictive for the refrigerant / coolant heat exchanger 10 of the present invention. In other words, the installation 2 is likely to have distinct structural characteristics and / or different operating methods than those described without the refrigerant / coolant heat exchanger 10 departing from the rules of the present invention.

The refrigerant fluid circuit 3 successively comprises a compressor 7 for compressing the refrigerating fluid 4, a refrigerating fluid / external air exchanger 8 for cooling the refrigerating fluid 4 at constant pressure, for example placed on the front face of the motor vehicle, an expansion member 9 to allow an expansion of the coolant 4, a first control member 11 of a supply of coolant 4 to the coolant / coolant heat exchanger 10 and the coolant / coolant heat exchanger 10 which is arranged to allow heat transfer between the coolant 4 and the coolant 6.

The first control member 11 is able to direct the refrigerant fluid 4 coming from the expansion member 9 to at least any one of a first branch of circulation of the refrigerant fluid 11a and of a second branch of circulation of the refrigerant. refrigerant fluid 11b that comprises the refrigerant fluid circuit 3, the first refrigerant fluid circulation branch 11a and the second refrigerant fluid circulation branch 11b being arranged in parallel with each other. The first refrigerant fluid circulation branch 11a and the second refrigerant fluid circulation branch 11b are formed in parallel between a first point of the refrigerant fluid circuit 51 and a second point of the refrigerant fluid circuit 52. The first point of the fluid circuit refrigerant 51 is located between the expansion member 9 and the coolant / coolant liquid heat exchanger 10, while the second point of the coolant circuit 52 is placed between the coolant / coolant liquid heat exchanger 10 and the compressor 7.

The first point of the coolant circuit 51 is equipped with the first control member 11 of the supply of coolant 4 to the coolant / coolant liquid heat exchanger 10. According to another variant, the second point of the fluid circuit refrigerant 52 is equipped with the first control member 11 of the refrigerant fluid supply 4 to the refrigerant / coolant liquid heat exchanger 10.

The refrigerant / coolant liquid heat exchanger 10 constitutes the first refrigerant fluid circulation branch 11a and the second refrigerant fluid circulation branch 11b.

The first control member 11 comprises for example a three-way valve or any other control means allowing or preventing a supply of coolant 4 to the first refrigerant circulation branch 11a and / or to the second fluid circulation branch. refrigerant 11b.

The heat transfer liquid circuit 5 successively comprises a pump 14 for circulating the heat transfer liquid 6 inside the heat transfer liquid circuit 5, a second control member 12 for a supply of heat transfer liquid 6 to the fluid heat exchanger. refrigerant / heat transfer liquid 10, which also constitutes the refrigerant fluid circuit 3, and a heat exchanger 16, the heat exchanger 16 being able to modify a temperature of the component 1, in particular by direct contact made between the component 1 and the heat exchanger 16.

The second control member 12 is able to direct the heat transfer liquid 6 coming from the pump 14 towards any one at least of a first heat transfer liquid circulation branch 12a and of a second heat transfer liquid circulation branch 12b. that comprises the heat transfer liquid circuit 5, the first heat transfer liquid circulation branch 12a and the second heat transfer liquid circulation branch 12b being arranged in parallel with one another. The first heat transfer liquid circulation branch 12a and the second coolant liquid circulation branch 12b are arranged in parallel between a first point of the heat transfer liquid circuit 61 and a second point of the heat transfer liquid circuit 62. The first point of the liquid circuit coolant 61 is located between the pump 14 and the coolant / coolant heat exchanger 10 while the second point of the coolant circuit 62 is placed between the coolant / coolant heat exchanger 10 and the heat exchanger 16.

The first point of the coolant circuit 61 is equipped with the second control member 12 of a supply of coolant 6 to the coolant / coolant heat exchanger 10. According to another variant, the second point of the liquid circuit coolant 62 is equipped with the second control member 12 with a supply of coolant 6 to the coolant / liquid heat exchanger

coolant 10. The refrigerant / liquid heat exchanger

coolant 10 is a component of the first heat transfer liquid circulation branch 12a and of the second heat transfer liquid circulation branch 12b.

The second control member 12 comprises for example a three-way valve or any other control means allowing or prohibiting a supply of coolant 6 to the first heat transfer liquid circulation branch 12a and / or to the second liquid circulation branch. coolant 12b.

To constitute the first branch of circulation of the coolant 11a and of the second branch of circulation of the coolant 11b as well as of the first branch of circulation of the coolant liquid 12a and of the second branch of circulation of the coolant 12b, the refrigerant / coolant heat exchanger 10 has a particular structure and arrangement.

Indeed, the coolant / coolant liquid heat exchanger 10 comprises at least two circulation paths of the coolant 21a, 21b and at least two circulation paths for the coolant liquid 22a, 22b.

More particularly, the refrigerant / coolant liquid heat exchanger 10 comprises at least a first refrigerant circulation path 21a and a second refrigerant circulation path 21b. The first coolant circulation path 21a and the second coolant circulation path 21b are arranged parallel to each other inside the coolant / coolant liquid heat exchanger 10. Thus, the first refrigerant fluid circulation path 21a forms an integral part of the first refrigerant fluid circulation branch 11a and the second refrigerant fluid circulation path 21b forms an integral part of the second refrigerant fluid circulation branch 11b.

Likewise, the coolant / coolant liquid heat exchanger 10 comprises at least a first coolant liquid circulation path 22a and a second coolant liquid circulation path 22b. The first heat transfer liquid circulation path 22a and the second heat transfer liquid circulation path 22b are arranged parallel to each other inside the refrigerant / coolant liquid heat exchanger 10. Thus, the first heat transfer liquid circulation path 22a is an integral part of the first heat transfer liquid circulation branch 12a and the second heat transfer liquid circulation path 22b is an integral part of the second heat transfer liquid circulation branch 12b.

The first circulation path of the refrigerant fluid 21a and the first circulation path of the coolant liquid 22a are arranged so that the refrigerant fluid 4 present inside the first circulation path of the refrigerant fluid 21a exchanges calories with the liquid coolant 6 present inside the first circulation path of the coolant liquid 22a.

Likewise, the second path for circulating the refrigerant fluid 21b and the second path for circulating the coolant liquid 22b are arranged so that the refrigerant 4 present inside the second coolant circulation path 21b exchanges calories with the coolant liquid 6 present inside the second coolant liquid circulation path 22b.

The first coolant circulation path 21a comprises several first coolant circulation chambers 211a and the first coolant liquid circulation path 22a comprises several first coolant liquid circulation chambers 221a, a first coolant circulation chamber 211a being interposed between two first coolant liquid circulation chambers 221a and a first heat transfer liquid circulation chamber 221a being interposed between two first coolant circulation chambers 211a.

The second coolant circulation path 21b comprises several second coolant circulation chambers 211b and the second coolant liquid circulation path 22b comprises several second coolant liquid circulation chambers 221b, a second coolant circulation chamber 211b being interposed between two second coolant liquid circulation chambers 221b and a second coolant liquid circulation chamber 221b being interposed between two second coolant circulation chambers 211b.

The refrigerant / coolant heat exchanger 10 is an exchanger which comprises a first heat exchange compartment 41 extending between a first cheek 23 and a second cheek 24 and a second heat exchange compartment 42 which s 'also extends between the first cheek 23 and the second cheek 24. In other words, the first heat exchange compartment 41 and the second heat exchange compartment 42 are both delimited by the first cheek 23 and the second cheek 24. The refrigerant / coolant heat exchanger 10 is formed by two heat exchange compartments 41, 42 which are sealed with each other and which are arranged side by side while both being bordered by the first plays 23 and the second plays 24. The first cheek 23 and the second cheek 24 consist of end plates of the coolant / coolant heat exchanger 10, the first cheek 23 and the second cheek 24 being parallel to one another.

The first heat exchange compartment 41 houses the first path for circulating the refrigerant fluid 21a and the first path for circulating the coolant liquid 22a while the second heat exchange compartment 42 houses the second path for circulating the refrigerant 21b. and the second heat transfer liquid circulation path 22b.

The refrigerant / coolant heat exchanger 10 is a one-piece heat exchanger in the sense that the heat exchange compartments 41, 42 constituting the coolant / coolant heat exchanger 10 cannot be separated. one from the other only from a dislocation and / or destruction of at least one of the heat exchange compartments 41, 42.

According to a first variant embodiment illustrated in FIGS. 1 and 2, the first heat exchange compartment 41 represents by volume one half, to within 10%, of the total volume of the refrigerant / coolant liquid heat exchanger 10 and the second heat exchange compartment 42 represents by volume the other half, to within 10%, of the total volume of the refrigerant / coolant liquid heat exchanger 10.

In Figure 1, component 1 is in fast charging mode and requires significant cooling power. Also, the first control member 11 allows circulation of the coolant 4 towards the first branch of circulation of the coolant 11a and towards the second branch of circulation of the coolant 11b, so that the entire volume of the exchanger refrigerant / coolant liquid heat 10 is traversed by the coolant 4. Likewise, the second control member 12 allows circulation of the coolant liquid 6 towards the first circulation branch of the coolant liquid 12a and towards the second circulation branch of the coolant. coolant 12b, so that the entire volume of the coolant / coolant heat exchanger 10 is traversed by the coolant 6. These arrangements are such that a exchange surface between the circulation paths of the coolant 21a, 21b and the circulation paths of the coolant 22a, 22b is as large as possible, in order to optimize cooling of the coolant 6, and subsequently of the component 1.

In figure 2, component 1 is in normal charging mode and requires low cooling power, lower than the powers of

significant cooling. Also, the first control member 11 allows circulation of the coolant 4 towards one of the branches of circulation of the coolant 11a, 11b, for example the first branch of circulation of the coolant 11a, and prohibits circulation of the coolant 4 towards the other of the refrigerant fluid circulation branches 11a, 11b, for example the second refrigerant circulation branch 11b, such that only the first heat exchange compartment 41 of

the refrigerant / coolant liquid heat exchanger 10 is traversed by the coolant 4. Likewise, the second control member 12 allows circulation of the coolant liquid 6 to one of the coolant liquid circulation branches 12a, 12b, for example the first circulation branch of the coolant liquid 12a, and prohibits circulation of the coolant liquid 6 towards the other of the circulation branches of the coolant liquid 12a, 12b, for example the second circulation branch of the coolant liquid 12b, in such a way that only the first heat exchange compartment 41 of the coolant / coolant liquid heat exchanger 10 is traversed by the coolant 6. These arrangements are such that an exchange surface between the circulation paths of the coolant fluid 21a, 21b and the circulation paths of the heat transfer liquid 22a, 22b is minimum, in order to cool the heat transfer liquid 6 according to the need for cooling ssement of component 1, which is less than when the latter is in fast charge mode.

These arrangements are such that the refrigerant / heat transfer liquid heat exchanger 10 thus configured and associated with the first control member 11 and the second control member 12 is able to provide

efficiently and quickly cooling power adapted according to the two aforementioned operating modes of component 1. According to an alternative embodiment illustrated in FIGS. 3 to 5, the first heat exchange compartment 41 represents by volume one third, to within 10%, of a total volume of the refrigerant / coolant liquid heat exchanger 10 while the second heat exchange compartment 42 represents by volume two thirds, to within 10%, of the total volume of the refrigerant / coolant liquid heat exchanger 10.

In Figure 3, component 1 is in fast charging mode and requires significant cooling power. Also, the first control member 11 allows circulation of the coolant 4 towards the first branch of circulation of the coolant 11a and towards the second branch of circulation of the coolant 11b, so that the entire volume of the exchanger refrigerant / coolant liquid heat 10 is traversed by the coolant 4. Likewise, the second control member 12 allows circulation of the coolant liquid 6 towards the first circulation branch of the coolant liquid 12a and towards the second circulation branch of the coolant. heat transfer liquid 12b, so that the entire volume of the refrigerant / heat transfer liquid heat exchanger 10 is traversed by the heat transfer liquid 6. These arrangements are such that an exchange surface between the circulation paths of the refrigerant 21a, 21b and the circulation paths of the coolant 22a, 22b is as large as possible, in order to optimize cooling ement of heat transfer liquid 6, and consecutively of component 1.

In figure 4, component 1 is in normal charging mode and requires low cooling power, less than the power of

significant cooling. Also, the first control member 11 prohibits a circulation of the refrigerant 4 towards the second branch of

circulation of the coolant 11b and allows circulation of the coolant 4 towards the first branch of circulation of the coolant 11a, such that only the first heat exchange compartment 41 of the coolant / coolant heat exchanger 10 is traversed by the coolant 4. Similarly, the second control member 12 prohibits circulation of the coolant 6 to the second circulation branch of the coolant 12b and allows circulation of the liquid. coolant 6 to the first heat transfer liquid circulation branch 12a, so that only the first heat exchange compartment 41 of the coolant / coolant liquid heat exchanger 10 is traversed by the heat transfer liquid 6. These arrangements are such that an exchange surface between the circulation paths of the coolant 21a, 21b and the circulation paths of the coolant 22a, 22b is minimal, in order to cool the coolant 6 according to the cooling requirement of the component 1, which is less than when the latter is in fast charge mode.

In Figure 5, component 1 is in intermediate load mode and requires medium cooling power, greater than low cooling power, and less than power of

significant cooling. Also, the first control member 11 allows circulation of the refrigerant 4 towards the second branch of

circulation of the refrigerant fluid 11b and prevents circulation of the refrigerant fluid 4 towards the first branch of circulation of the refrigerant fluid 11a, so that only the second heat exchange compartment 42 of the refrigerant / coolant liquid heat exchanger 10 is traversed by the coolant 4. Likewise, the second control member 12 allows circulation of the coolant 6 towards the second circulation branch of the coolant liquid 12b and prevents circulation of the coolant 6 towards the first liquid circulation branch. coolant 12a, so that only the second heat exchange compartment 42 of the coolant / coolant heat exchanger 10 is traversed by the coolant 6. These arrangements are such that an exchange surface between the refrigerant circulation paths 21a, 21b and the coolant liquid circulation paths 22a, 22b is average , in order to cool the heat transfer liquid 6 according to the cooling requirement of component 1, which is less than when the latter is in rapid charge mode and which is greater than that necessary when component 1 is under normal charge.

These arrangements are such that the refrigerant / coolant liquid heat exchanger 10 thus configured and associated with the first control member. control he and the second control organ 12 is able to provide

efficiently and quickly a cooling power adapted according to the three aforementioned operating modes of component 1.

In FIGS. 6 and 7, the refrigerant / coolant liquid heat exchanger 10 is shown schematically in an orthonormal reference Oxyz linked to the coolant / coolant heat exchanger 10, in which a direction Ox is a transverse direction, a direction Oy is a lateral direction and a direction Oz is a longitudinal direction. The refrigerant / coolant liquid heat exchanger 10 is generally parallelepipedal and extends transversely between the first cheek 23 and the second cheek 24 which transversely border the refrigerant / heat transfer liquid heat exchanger 10. The first cheek 23 s' mainly extends inside a first plane Pi which is parallel to the Oyz plane. The second cheek 24 mainly extends inside a second plane P2 which is also parallel to the Oyz plane.

In other words, the coolant / coolant heat exchanger 10 is transversely bounded by the first cheek 23 on one side and the second cheek 24 on the other side. More particularly, the first

heat exchange compartment 41 and second heat exchange compartment 42 are jointly transversely bounded by the first cheek 23 on one side and the second cheek 24 on the other side. It is understood in this, that the first heat exchange compartment 41 and the second heat exchange compartment 42 are laterally arranged side by side of each other. In other words, a separation plane P3 which delimits the first heat exchange compartment 41 and the second heat exchange compartment 42 is orthogonal to the first plane Pi and to the second plane P2 and is parallel to an Oxz plane.

The first cheek 23 is provided with eight passages 31, 32, 33, 34, 35, 36, 37,

38, which are preferably circular. It is understood that the first passage 31, the second passage 32, the third passage 33, the fourth passage 34, the fifth passage 35, the sixth passage 36, the seventh passage 37 and the eighth passage 38 are for example each formed of a orifice allowing circulation of the coolant 4 or the coolant 6 through the first cheek 23.

A first passage 31, a second passage 32, a third passage 33 and a fourth passage 34 are assigned to the first heat exchange compartment 41.

The first passage 31 and the second passage 32 are aligned in a direction parallel to the Oy direction and are located near a first side 25 of the coolant / coolant heat exchanger 10, parallel to the Oxy plane. The first passage 31 is located near a first blank 26 of the refrigerant / coolant liquid heat exchanger 10, the first blank 26 extending in a plane parallel to the Oxz plane. The second passage 32 is located near the separation plane P3 interposed between the first heat exchange compartment 41 and the second heat exchange compartment 42. The first blank 26 and the separation plane P3 laterally border the first compartment. heat exchange 41.

The third passage 33 and the fourth passage 34 are aligned in a direction parallel to the Oy direction and are located near a second side 27 of the coolant / coolant heat exchanger 10, parallel to the Oxy plane. The second side 27 and the first side 25 vertically border the refrigerant / coolant liquid heat exchanger 10. The third passage 33 is located near the first blank 26 of the coolant / coolant heat exchanger 10. The fourth passage 34 is located near the separation plane P3 interposed between the first heat exchange compartment 41 and the second heat exchange compartment 42.

A fifth passage 35, a sixth passage 36, a seventh passage 37 and an eighth passage 38 are assigned to the second heat exchange compartment 42.

The fifth passage 35 and the sixth passage 36 are aligned in a direction parallel to the direction Oy and are located near the first side 25 of the coolant / coolant heat exchanger 10, parallel to the Oxy plane. The fifth passage 35 is located near the separation plane P3. The sixth passage 36 is located near a second blank 28 of the refrigerant / coolant liquid heat exchanger 10. The second blank 28 is parallel to the first blank 26 and to the Oxz plane.

The seventh passage 37 and the eighth passage 38 are aligned in a direction parallel to the direction Oy and are located near the second side 27 of the coolant / coolant heat exchanger 10. The seventh passage 37 is located near the separation plane P3. The eighth passage 38 is located near the second blank 28 of the coolant / coolant heat exchanger 10.

The first passage 31, the third passage 33, the sixth passage 36 and the eighth passage 38 are disposed at respective angles of the first cheek 23, which is generally rectangular.

The first passage 31 and the third passage 33 are aligned in a direction parallel to the direction Oz, the second passage 32 and the fourth passage 34 are also aligned in a direction parallel to the direction Oz, the fifth passage 35 and the seventh passage 37 are also aligned in a direction parallel to the direction Oz, and the sixth passage 36 and the eighth passage 38 are aligned in a direction parallel to the direction Oz.

The first passage 31 gives access to a first collector 71, the second passage 32 gives access to a second collector 72, the third passage 33 gives access to a third collector 73, the fourth passage 34 gives access to a fourth collector 74, the fifth passage 35 gives access to a fifth collector 75, the sixth passage 36 gives access to a sixth collector 76, the seventh passage 37 gives access to a seventh collector 77 and the eighth passage 38 gives access to an eighth collector 78. The collectors 71, 72, 73, 74, 75, 76, 77, 78 extend along a respective general axis of extension A2 which is parallel to the axis Ox and perpendicular to the first plane Pi and to the second plane P2. The collectors 71, 72, 73, 74, 75, 76, 77, 78 are intended to supply refrigerant 4 or coolant 6 to the chambers 211a, 211b, 221a, 221b. The first collector 71, the second collector 72, the third collector 73 and the fourth collector 74 are assigned to the first heat exchange compartment 41. The fifth collector 75, the sixth collector 76, the seventh collector 77 and the eighth collector 78 are assigned to the second heat exchange compartment 42.

The first heat exchange compartment 41 is generally

parallelepipedal and extends along a first compartment height Xi taken between the first side 25 and the second side 27 parallel to the Oz axis. The first heat exchange compartment 41 extends along a first length of compartment X2 taken between the first cheek 23 and the second cheek 24 parallel to the Ox axis. The first heat exchange compartment 41 extends along a first compartment width X3 taken between the first blank 26 and the separation plane P3 parallel to the Oy axis.

The second heat exchange compartment 42 is generally parallelepipedal and extends along a second compartment height X4 taken between the first side 25 and the second side 27 parallel to the Oz axis. The second heat exchange compartment 42 extends along a second length of compartment X5 taken between the first cheek 23 and the second cheek 24 parallel to the Ox axis. The second heat exchange compartment 42 extends along a second compartment width X6 taken between the separation plane P3 and the second blank 28 parallel to the Oy axis.

The first compartment height Xi and the second compartment height X4 are equal, up to manufacturing tolerances, the first compartment length X2 and the second compartment length X5 are equal, up to the manufacturing tolerances.

In Figure 6, which shows the refrigerant / coolant heat exchanger 10 of the installation 2 illustrated in Figures 1 and 2, the first width of compartment X3 is equal to the second width of compartment X6, to the tolerances of manufacturing close.

The coolant / coolant heat exchanger 10 is a plate exchanger which comprises the first cheek 23, the second cheek 24 and a plurality of first type plates 105a which are interposed between the first cheek 23 and the second cheek 24. The first cheek 23, the second cheek 24 and the first type plates 105a are for example brazed together to form the compartments d. heat exchange 41, 42 of the refrigerant / coolant heat exchanger 10.

In FIG. 7, which represents the refrigerant / coolant liquid heat exchanger 10 of the installation 2 illustrated in FIGS. 3 to 5, the first width of compartment X3 is equal to half of the second width of compartment X6, within manufacturing tolerances.

The refrigerant / coolant heat exchanger 10 is a plate exchanger which comprises the first cheek 23, the second cheek 24 and either a plurality of plates of second type 105b, or a plurality of plates of third type 105c and of fourth type 105d, or a plurality of plates of fifth type 105e and sixth type 105f which are interposed between the first cheek 23 and the second cheek 24. The first cheek 23, the second cheek 24 and the aforementioned plates 105b, 105c, 105d, 105e, 105f are for example brazed together to form the heat exchange compartments 41, 42 of the refrigerant / coolant liquid heat exchanger 10.

Advantageously, and for a refrigerant / coolant liquid heat exchanger 10 indifferently shown in FIG. 6 or in FIG. 7, the same plate 105a, 105b, 105c, 105d, 105e, 105f defines at least one of the first circulation paths 21a, 22a of the first heat exchange compartment 41 and one of the second circulation paths 22a, 22b of the second heat exchange compartment 42. Preferably, the same plate 105a, 105b, 105c, 105d, 105e, 105f defines the first two Circulation paths 21a, 22a of the first heat exchange compartment 41 and the two second circulation paths 22a, 22b of the second heat exchange compartment 42.

Preferably, the same plate 105a, 105b, 105c, 105d, 105e, 105f jointly defines one of the first refrigerant circulation chambers 211a, one of the second fluid circulation chambers refrigerant 211b, one of the first coolant liquid circulation chambers 221a and one of the second coolant liquid circulation chambers 221b.

In Figures 8 to 17, each plate 105a, 105b, 105c, 105d, 105e, 105f extends mainly along an axis of elongation Ai. Each plate 105a, 105b, 105c, 105d, 105e, 105f comprises a base 106 and at least one raised edge 107 which surrounds the base 106. In other words, the raised edge 107 is formed at the periphery of the base 106, which extends inside a bottom plane P4, and the raised edge 107 surrounds the bottom 106. It is understood that each exchange plate 105a, 105b, 105c, 105d, 105e, 105f is arranged in a generally rectangular tub, the bottom of the bathtub consisting of the bottom 106 and the edges of the bathtub consisting of the raised edge 107. More particularly, the raised edge 107 comprises two longitudinal raised edges 108a, 108b arranged opposite one of the another and two raised side edges 109a, 109b formed vis-à-vis one another. The longitudinal raised edges 108a, 108b are parallel to the axis of elongation Ai while the raised lateral edges 109a, 109b are orthogonal to the axis of elongation A1.

In FIGS. 8 to 13, each plate 105a, 105b, 105c, 105d, 105e, 105f comprises eight orifices 51, 52, 53, 54, 55, 56, 57, 58, in particular circular, including a first orifice 51 of a first diameter Di, a second orifice 52 with a second diameter D2, a third orifice 53 with a third diameter D3 and a fourth orifice 54 with a fourth diameter D4 arranged inside a first zone Z1 of the plate 105a, 105b, 105c, 105d, 105e, 105f, and including a fifth hole 55 with a fifth diameter D5, a sixth hole 56 with a sixth diameter D6, a seventh hole 57 with a seventh diameter D7 and an eighth hole 58 of an eighth diameter D8 arranged inside a second zone Z2 of the plate 105a, 105b, 105c, 105d, 105e, 105f, the first zone Z1 and the second zone Z2 being separated from one of the another by a groove 200. The groove 200 is formed in the bottom 106 of the plate 105a, 105b, 105c, 105d, 105e, 105f and extends between the first lateral edge 109a and the second me side edge 109b. The groove 200 is parallel to the axis of elongation Ai and to the longitudinal raised edges 108a, 108b. The first zone Z1 is arranged in a quadrilateral, in particular

rectangular, and is bordered by a first longitudinal raised edge 108a, the groove 200, a first portion of the first lateral edge ma and a first portion of the second lateral edge 112a.

The second zone Z2 is also arranged in a quadrilateral, in particular rectangular, and is bordered by a second longitudinal raised edge 108b, the groove 200, a second portion of the first lateral edge 111b and a second portion of the second lateral edge 112b.

The first portion of the first side edge 111a and the second portion of the first side edge 111b are separated from each other by the groove 200. The first portion of the second side edge 112a and the second portion of the second side edge 112b are also separated from each other by the groove 200.

The first portion of the first side edge 111a and the second portion of the first side edge 111b together form the first side edge 109a. The first portion of the second side edge 112a and the second portion of the second side edge 112b together form the second side edge 109b.

The first zone Z1 constitutes the first heat exchange compartment 41 and the second zone Z2 constitutes the second heat exchange compartment 42. Thus, the groove 200 sealingly isolates the first heat exchange compartment 41. and the second heat exchange compartment 42.

The first orifice 51, the second orifice 52, the third orifice 53 and the fourth orifice 54 are respectively distributed at each of the angles of the first zone Z1. Two of these orifices 51, 52, 53, 54 are configured to communicate with one of the first circulation chambers 211a, 221a formed on one side of the bottom 106 and two other of these orifices 51, 52, 53, 54 are configured to communicate with the other of the first circulation chambers 211a, 221a formed on another side of the bottom 106. For this purpose, two of these orifices 51, 52, 53, 54 are provided with a collar 120 and the other two of these orifices 51, 52, 53, 54 are free from it. It follows that two of these orifices 51, 52, 53, 54 surrounded by these collars 120 extend in a plane offset from the bottom plane P4, parallel to the Oyz plane, in which the bottom 106 is inscribed. The other two of these orifices 51, 52, 53, 54 extend in the bottom plane P4.

The fifth orifice 55, the sixth orifice 56, the seventh orifice 57 and the eighth orifice 58 are respectively distributed at each of the angles of the second zone Z2. Two of these orifices 55, 56, 57, 58 are configured to communicate with one of the second circulation chambers 211b, 221b formed on one side of the bottom 106 and two other of these orifices 55, 56, 57, 58 are configured to communicate with the other of the first circulation chambers 211b, 221b formed on another side of the bottom 106. For this purpose, two of these orifices 55, 56, 57, 58 are provided with a collar 120 and the other two of these orifices 55, 56, 57, 58 are free. As a result, two of these orifices 55, 56, 57, 58 surrounded by these collars 120 extend in a plane offset with respect to the bottom plane P4, parallel to the Oyz plane, in which the bottom 106 is inscribed. two other of these orifices 55, 56, 57, 58 extend in the bottom plane P4.

The first orifices 51 of the plates 105a, 105b, 105c, 105d, 105e, 105f are formed vis-à-vis each other when these plates 105a, 105b, 105c, 105d, 105e, 105f are assembled together, in such so that the peripheral edges of these first orifices 51 together delimit the first manifold 71. The second orifices 52 of the plates 105a, 105b, 105c, 105d, 105e, 105f are arranged vis-à-vis each other when these plates 105a , 105b, 105c, 105d, 105e, 105f are assembled together, such that the peripheral edges of these second orifices 52 together delimit the second manifold 72. The third orifices 53 of the plates 105a, 105b, 105c, 105d, 105e, 105f are arranged vis-à-vis each other when these plates 105a, 105b, 105c, 105d, 105e, 105f are assembled together, so that peripheral edges of these third orifices 53 together delimit the third manifold 73 The fourth orifices 54 of the plates 105a, 105b, 105c, 105d, 105e, 105f are arranged vis-à-vis each other when these plates 105a, 105b, 105c, 105d, 105e, 105f are assembled together, such that peripheral edges of these fourth orifices 54 together define the first collector 71. The fifth orifices 55 of the plates 105a, 105b, 105c, 105d, 105e, 105f are formed vis-à-vis each other when these plates 105a, 105b, 105c, 105d, 105e, 105f are assembled together, in such so that the peripheral edges of these fifth orifices 55 together delimit the fifth manifold 75. The sixth orifices 56 of the plates 105a, 105b, 105c, 105d, 105e, 105f are arranged opposite each other when these plates 105a , 105b, 105c, 105d, 105e, 105f are assembled together, such that the peripheral edges of these sixth orifices 56 together define the sixth manifold 76. The seventh orifices 57 of the plates 105a, 105b, 105c, 105d, 105e, 105f are arranged vis-à-vis each other when these plates 105a, 105b, 105c, 105d, 105e, 105f are assembled together, such that peripheral edges of these seventh orifices 57 together delimit the seventh manifold 77 The eighth holes 58 of p lacquers 105a, 105b, 105c, 105d, 105e, 105f are arranged vis-à-vis each other when these plates 105a, 105b, 105c, 105d, 105e, 105f are assembled together, such that peripheral edges of these eighth orifices 58 together delimit the eighth manifold 78.

In FIG. 8 which illustrates a plate of the first type 105a, the groove 200 is formed at an equal distance from the two longitudinal raised edges 108a, 108b.

The first zone Z1 and the second zone Z2 have equal surfaces, up to manufacturing tolerances. The first type 105a plate is

component of the coolant / coolant heat exchanger 10 shown in Figure 6.

The four orifices provided with a collar 120, namely the first orifice 51 and the third orifice 53 for those of the first zone Z1, and the sixth orifice 56 and the eighth orifice 58 for those of the second zone Z2, are provided at proximity to a respective side edge 109a, 109b which are longitudinally opposed to each other. These arrangements are such that the circulation chambers 211a, 211b, 221a, 221b are each shaped in an "I". The first type plate 105a immediately successive in the stack of plates to the first type plate 105a illustrated is identical to that depicted in Fig. 8 except that the first port 51, the third port 53, the sixth port 56 and the eighth port 58 are free of a collar while the second port 52, the fourth port 54, the fifth port 55 and the seventh port 57 are provided with a collar 120, to seal the flow chambers 211a, 211b, 221a, 221b to each other, a collar 120 of a first type plate 105a being in contact with the bottom 106 of the immediately successive first type plate 105a.

The first diameter D1, the third diameter D3, the sixth diameter D6 and the eighth diameter D8 are equal to each other. The first collector 71, the third collector 73, the sixth collector 76 and the eighth collector 78, coming from the orifices whose diameters have the aforementioned characteristics, are in particular collectors inside which circulates the heat transfer liquid 6. According to the example illustrated, the third manifold 73 is a coolant liquid inlet manifold 6 inside the first heat exchange compartment 41 while the first manifold 71 is a coolant liquid discharge manifold 6 out of the first compartment d heat exchange 41. Likewise, the eighth manifold 78 is an intake manifold for the coolant liquid 6 inside the second heat exchange compartment 42 while the sixth manifold 76 is a liquid discharge manifold. coolant 6 outside the second heat exchange compartment 42.

The second diameter D2 is smaller than the fourth diameter D4 and the fifth diameter D5 is smaller than the seventh diameter D7. The second manifold 72, the fourth manifold 74, the fifth manifold 75 and the seventh manifold 77, resulting from the orifices whose diameters have the same

the aforementioned characteristics are in particular collectors inside which the refrigerant 4 circulates. According to the example illustrated, the second collector 72 is an inlet manifold for the refrigerant 4 inside the first heat exchange compartment. 41 while the fourth manifold 74 is a manifold for discharging the refrigerant fluid 4 out of the first heat exchange compartment 41. Likewise, the fifth manifold 75 is an inlet manifold for the refrigerant fluid 4 inside the second heat exchange compartment 42 while the seventh collector 77 is a collector for discharging the refrigerant 4 from the second heat exchange compartment 42. These arrangements are such that the circulation of the heat transfer liquid 6 and of the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are countercurrent to one of the other. By reversing the direction of circulation of the heat transfer liquid 6 inside the first manifold 71 and the third manifold 73, and / or the sixth manifold 76 and the eighth manifold 78, a refrigerant / heat transfer liquid heat exchanger 10 is obtained. inside which the circulation of the heat transfer liquid 6 and of the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are co-current with one another.

In Figures 9 to 13, which respectively illustrate a second type plate 105b, a third type plate 105c, a fourth type plate 105d, a fifth type plate 105e and a sixth type plate 105f, the groove 200 is provided at a first distance Wi from the first longitudinal raised edge 108a which is equal to one half of a second distance W2 taken between the groove 200 and the second longitudinal edge 108b, these distances Wi, W2 being taken orthogonally to the raised longitudinal edges 108a, 108b and in the groove 200. The first zone Z1 has an area which is equal to half of an area of the second zone Z2, up to manufacturing tolerances.

FIG. 9 illustrates a second type plate 105b which constitutes the refrigerant / coolant liquid heat exchanger 10 shown in FIG. 7.

The four orifices provided with a collar 120, namely the first orifice 51 and the third orifice 53 for those of the first zone Z1, and the sixth orifice 56 and the eighth orifice 58 for those of the second zone Z2, are provided at proximity to a respective side edge 109a, 109b which are longitudinally opposed to each other. These arrangements are such that the circulation chambers 211a, 211b, 221a, 221b are each shaped in an "I". The second type plate 105b immediately successive in the stack of plates to the second type plate 105b illustrated is identical to that depicted in FIG. 9 except that the first port 51, the third port 53, sixth port 56 and eighth port 58 are free of collar while second port 52, fourth port 54, fifth port 55 and seventh port 57 are provided with collar 120, to seal the chambers circulation 211a, 211b, 221a, 221b to each other, a collar 120 of a second type plate 105b being in contact with the bottom 106 of the immediately successive second type plate 105b.

the aforementioned characteristics are in particular collectors inside which the refrigerant 4 circulates. According to the example illustrated, the second collector 72 is an inlet manifold for the refrigerant 4 inside the first heat exchange compartment. 41 while the fourth manifold 74 is a manifold for discharging the refrigerant fluid 4 out of the first heat exchange compartment 41. Likewise, the fifth manifold 75 is an inlet manifold for the refrigerant fluid 4 inside the second heat exchange compartment 42 while the seventh collector 77 is a collector for evacuating the refrigerant fluid 4 from the second heat exchange compartment 42.

These arrangements are such that the circulation of the heat transfer liquid 6 and of the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are countercurrent to one of the other. By reversing the direction of circulation of the heat transfer liquid 6 inside the first manifold 71 and the third manifold 73, and / or the sixth manifold 76 and the eighth manifold 78, a refrigerant / heat transfer liquid heat exchanger 10 is obtained. inside which the circulation of the heat transfer liquid 6 and of the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are co-current with one another.

Figure 10 illustrates a third type plate 105c which constitutes the refrigerant / coolant liquid heat exchanger 10 shown in Figure 7, in alternate superposition with a fourth type plate 105d shown in Figure 11.

The bottom 106 of a third type plate 105c and the bottom 106 of a fourth type plate 105d comprise ribs 113a, 113b which are arranged so that the circulation chambers 211a, 211b, 221a, 221b have a " U ”. The ribs 113a, 113b are formed in a first direction D which is preferably parallel to the raised lateral edges 109a, 109b. In other words, the first direction D is preferably orthogonal to the axis of elongation A1 of the third type exchange plate 105c and the fourth type plate 105d. A first rib 113a is formed inside the first zone Z1 and a second rib 113b is formed inside the second zone Z2.

In FIG. 10, the first rib 113a of the third type plate 105c extends between a first end of first rib 114 and a second end of first rib 115, the first end of first rib 114 being in contact with the raised edge. 107, and

preferably in contact with the first longitudinal raised edge 108a. The second end of the first rib 115 is located at a first gap El non-zero of the groove 200, the first distance El being taken along the first direction D between the second end of the first rib 115 and the groove 200.

The second rib 113b of the third type plate 105c extends between a first end of the second rib 116 and a second end of the second rib 117, the first end of the second rib 116 being in contact with the raised edge 107, and preferably in contact with the second longitudinal raised edge 108b. The second end of the second rib 117 is located at a second non-zero distance E2 from the groove 200, the second distance E2 being taken along the first direction D between the second end of the second rib 117 and the groove 200.

The four orifices provided with a collar 120, namely the first orifice 51 and the third orifice 53 for those of the first zone Z1, and the sixth orifice 56 and the eighth orifice 58 for those of the second zone Z2, are provided at proximity to a respective side edge 109a, 109b which are longitudinally opposed to each other.

In Figure 11, the first rib 113a of the fourth type plate 105d extends between a first end of first rib 114 and a second end of first rib 115, the first end of first rib 114 being in contact with groove 200 The second end of the first rib 115 is located at a third non-zero distance E3 from the first longitudinal raised edge 108a, the third distance E3 being taken along the first direction D between the second end of the first rib 115 and the first edge longitudinal survey 108a.

The second rib 113b of the fourth type plate 105d extends between a first end of a second rib 116 and a second end of a second rib 117, the first end of the second rib 116 being in contact with the groove 200. The second end of the second rib 116 second rib 117 is located at a fourth non-zero distance E4 from the second longitudinal raised edge 108b, the second distance E2 being taken along the first direction D between the second end of second rib 117 and the second longitudinal raised edge 108b. The four orifices provided with a collar 120, namely the second orifice 52 and the fourth orifice 54 for those of the first zone Z1, and the fifth orifice 55 and the seventh orifice 57 for those of the second zone Z2, are provided at proximity to a respective side edge 109a, 109b which are longitudinally opposed to each other.

The collars 120 of a third type plate 105c are in contact with the bottom 106 of the immediately successive fourth type plate 105d and the collars 120 of a fourth type plate 105d are in contact with the bottom 106 of the third type plate. 105c immediately successive.

In Figures 10 and 11, the first diameter Di, the third diameter D3, the sixth diameter D6 and the eighth diameter D8 are equal to each other. The first collector 71, the third collector 73, the sixth collector 76 and the eighth collector 78, coming from the orifices whose diameters have the aforementioned characteristics, are in particular collectors inside which circulates the heat transfer liquid 6. According to the example illustrated, the third manifold 73 is a coolant liquid inlet manifold 6 inside the first heat exchange compartment 41 while the first manifold 71 is a coolant liquid discharge manifold 6 out of the first compartment d heat exchange 41. Likewise, the eighth manifold 78 is an intake manifold for the coolant liquid 6 inside the second heat exchange compartment 42 while the sixth manifold 76 is a liquid discharge manifold. coolant 6 outside the second heat exchange compartment 42.

The second diameter D2 is greater than the fourth diameter D4 and the fifth diameter D5 is greater than the seventh diameter D7. The second manifold 72, the fourth manifold 74, the fifth manifold 75 and the seventh manifold 77, resulting from the orifices whose diameters have the same

the aforementioned characteristics are in particular collectors inside which the refrigerant 4 circulates. According to the example illustrated, the fourth collector 74 is an intake manifold for the refrigerant 4 inside the first heat exchange compartment. 41 while the second collector 72 is a collector for discharging the refrigerant fluid 4 out of the first heat exchange compartment 41. Likewise, the seventh manifold 77 is an inlet manifold for the refrigerant fluid 4 inside the second heat exchange compartment 42 while the fifth manifold 75 is a manifold of refrigerant. evacuation of the refrigerant fluid 4 out of the second heat exchange compartment 42.

These arrangements are such that the circulation of the coolant 6 and the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are common with each other. By reversing the direction of circulation of the heat transfer liquid 6 inside the first manifold 71 and the third manifold 73, and / or the sixth manifold 76 and the eighth manifold 78, a refrigerant / heat transfer liquid heat exchanger 10 is obtained. the interior of which the circulation of the heat transfer liquid 6 and of the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are countercurrent with each other.

FIG. 12 illustrates a fifth-type plate 105th which constitutes the refrigerant / coolant liquid heat exchanger 10 shown in FIG. 7, in alternate superposition with a sixth-type 105th plate illustrated in FIG. 13.

The bottom 106 of a fifth type plate 105e and the bottom 106 of a sixth type plate 105f include ribs 113a, 113b which are arranged so that the circulation chambers 211a, 211b, 221a, 221b have a " U ”. The ribs 113a, 113b are formed in a second direction D ’which is preferably parallel to the raised edges

longitudinal 108a, 108b. In other words, the second direction D ’is for example parallel to the axis of elongation Ai of the fifth type exchange plate 105e and the sixth type plate 105f. A first rib 113a is formed inside the first zone Z1 and a second rib 113b is formed inside the second zone Z2.

In Figure 12, the first rib 113a of the fifth type plate 105e extends between a first end of the first rib 114 and a second end of first rib 115, the first end of first rib 114 being in contact with the raised edge 107, and

preferably in contact with the first side raised edge 109a. The second end of the first rib 115 is located at a fifth non-zero deviation E5 from the second lateral raised edge 109b, the fifth deviation E5 being taken along the second direction D 'between the second end of the first rib 115 and the second edge side reading 109b.

The second rib 113b of the fifth type plate 105e extends between a first end of a second rib 116 and a second end of a second rib 117, the first end of the second rib 116 being in contact with the raised edge 107, and preferably in contact with the first side raised edge 109a. The second end of the second rib 117 is located at a non-zero sixth deviation E6 from the second lateral raised edge 109b, the sixth deviation E6 being taken along the second direction D 'between the second end of the second rib 117 and the second edge side reading 109b.

The four orifices provided with a collar 120, namely the first orifice 51 and the second orifice 52 for those of the first zone Z1, and the fifth orifice 55 and the sixth orifice 56 for those of the second zone Z2, are provided at proximity to the first side raised edge 109a.

In Fig. 13, the first rib 113a of the sixth type plate 105f extends between a first end of first rib 114 and a second end of first rib 115, the first end of first rib 114 being in contact with the second edge. side reading 109b. The second end of the first rib 115 is situated at a seventh non-zero deviation E7 from the first lateral raised edge 109a, the seventh deviation E7 being taken along the second direction D 'between the second end of the first rib 115 and the first edge side reading 109a.

The second rib 113b of the sixth type plate 105f extends between a first end of a second rib 116 and a second end of a second rib 117, the first end of the second rib 116 being in contact with the second side raised edge 109b. The second end of second rib 117 is located at an eighth non-zero deviation E8 from the first lateral raised edge 109a, the eighth deviation E8 being taken along the second direction D 'between the second end of the second rib 117 and the first lateral raised edge 109a .

The four orifices provided with a collar 120, namely the third orifice 53 and the fourth orifice 54 for those of the first zone Z1, and the seventh orifice 57 and the eighth orifice 58 for those of the second zone Z2, are provided at proximity to the second side edge 109b.

The collars 120 of a fifth type plate 105e are in contact with the bottom 106 of the immediately successive sixth type plate 105f and the collars 120 of a sixth type plate 105f are in contact with the bottom 106 of the fifth type plate. 105th immediately successive.

In Figures 12 and 13, the first diameter Di, the third diameter D3, the sixth diameter D6 and the eighth diameter D8 are equal to each other. The first collector 71, the third collector 73, the sixth collector 76 and the eighth collector 78, coming from the orifices whose diameters have the aforementioned characteristics, are in particular collectors inside which circulates the heat transfer liquid 6. According to the example illustrated, the second manifold 72 is a coolant liquid inlet manifold 6 inside the first heat exchange compartment 41 while the first manifold 71 is a coolant liquid discharge manifold 6 out of the first compartment d heat exchange 41. Likewise, the sixth manifold 76 is a coolant liquid inlet manifold 6 inside the second heat exchange compartment 42 while the fifth manifold 75 is a liquid discharge manifold. coolant 6 outside the second heat exchange compartment 42.

the aforementioned characteristics are in particular collectors inside which the refrigerant 4 circulates. According to the example illustrated, the fourth manifold 74 is a manifold for entering the refrigerant fluid 4 inside the first heat exchange compartment 41 while the second manifold 72 is a manifold for discharging the refrigerant 4 from the first heat exchange compartment 41. Likewise, the seventh manifold 77 is an inlet manifold for the refrigerant fluid 4 inside the second heat exchange compartment 42 while the fifth manifold 75 is a manifold for discharging the refrigerant fluid 4 out of the chamber. second heat exchange compartment 42.

These arrangements are such that the circulation of the heat transfer liquid 6 and of the refrigerant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are countercurrent with each other. other. By reversing the direction of circulation of the heat transfer liquid 6 inside the first manifold 71 and the second manifold 72, and / or the fifth manifold 75 and the sixth manifold 76, a refrigerant / heat transfer liquid heat exchanger 10 is obtained. inside which the circulation of the heat transfer liquid 6 and of the coolant 4 inside the first heat exchange compartment 41 and the second heat exchange compartment 42 are co-current with one another.

In Figures 14 to 17, a plurality of plates 105a, 105b, 105c, 105d, 105e, 105f are nested one inside the other and in contact with one another at least through their edge. raised 107 and their groove 200, to jointly form the first heat exchange compartment 41 and the second heat exchange compartment 42. In other words, four exchange plates 105a, 105b, 105c, 105d, 105e, 105f are stacked one above the other in a stacking direction D ”which is parallel to the Ox axis and perpendicular to the bottom plane P4. The exchange plates 105a, 105b, 105c, 105d, 105e, 105f leave between them a space which forms the circulation chambers 211a, 211b, 221a, 221b of the refrigerant 4 or of the heat transfer liquid 6.

In other words, the first circulation chambers 211a, 221a on the one hand and the second circulation chambers on the other hand 211b, 221b are stacked along stacking direction D ”. Each circulation chamber 211a, 211b, 221a, 221b is delimited at least by the bases 106 of two immediately adjacent plates 105a, 105b, 105c, 105d, 105e, 105f and by the groove 200 of one of these plates 105a, 105b, 105c, 105d, 105e, 105b

The grooves 200 of two successive plates 105a, 105b, 105c, 105d, 105e, 105f are nested one inside the other to ensure a seal between the first heat exchange compartment 41 and the second heat exchange compartment 42. According to another embodiment, the grooves 200 of two successive plates 105a, 105b, 105c, 105d, 105e, 105f can be laterally offset from each other, a top of a plate 105a, 105b, 105c , 105d, 105e, 105f then being in contact with the bottom 106 of the plate 105a, 105b, 105c, 105d, 105e, 105f immediately successive to ensure a seal between the first heat exchange compartment 41 and the second compartment of heat exchange 42.

In FIG. 16 more particularly, it is noted that the grooves 113a, 113b of a third type plate 105c comprise a top 118 which emerges from the bottom 106 of the third type plate 105c and which is in contact with the bottom of a fourth type plate 105d. Likewise, the grooves 113a, 113b of a fourth type plate 105d have a top 118 which emerges from the bottom 106 of the fourth type plate 105d and which contacts the bottom of a third type plate 105c. Note that these provisions can be transposed identically for the fifth type 105e plates and the sixth type 105b plates

All of these arrangements are such as a cooling method according to the present invention of component 1 by means of installation 2

previously described, and comprising a refrigerant / coolant liquid heat exchanger 10 shown in FIG. 6, allows component 1 to be cooled, according to two appropriate methods, depending on the state of charge of the electrical storage device 1, and in particular from a choice of activating the first control organ 11 and / or the second control organ 12 in which: - the first heat exchange compartment 41 and the second

heat exchange compartment 42 are traversed by the coolant 4 and by the coolant 6 when the electrical storage device 1 is in a fast charging mode;

- Any one of the first heat exchange compartment 41 and of the second heat exchange compartment 42 is traversed by the refrigerant fluid 4 and by the heat transfer liquid 6 when the electrical storage device 1 is in a charging mode normal.

described above, and comprising a refrigerant / coolant liquid heat exchanger 10 shown in FIG. 7, allows component 1 to be cooled, in three appropriate ways, depending on the state of charge of the electrical storage device 1, and in particular from a choice of activating the first control organ 11 and / or the second control organ 12 in which:

- the first heat exchange compartment 41 and the second

- Only the first heat exchange compartment 41 is traversed by the refrigerant 4 and by the coolant 6 when the electrical storage device 1 is in a normal charging mode;

- Only the second heat exchange compartment 42 is traversed by the refrigerant 4 and by the coolant 6 when the electrical storage device 1 is in an intermediate charging mode.

Claims

1. Refrigerant / heat transfer liquid heat exchanger (Io) comprising at least one stack of plates (105a, 105b, 105c, 105d, 105e, 105f) delimiting at least two heat exchange compartments (41, 42) sealed l 'one relative to the other, including a first heat exchange compartment (41) which has a first path for the circulation of a refrigerant fluid (21a) and a first path for the circulation of a heat transfer liquid (22a) , as well as a second heat exchange compartment (42) which comprises a second circulation path for the refrigerant fluid (21b) and a second circulation path for the coolant liquid (22b), characterized in that at least one of the Circulation paths (21a, 22a) of the first heat exchange compartment (41) and one of the circulation paths (22a, 22b) of the second heat exchange compartment (42) are at least partly delimited by the same plate (105a, 105b, 105c, 105d, 105e, 105f).

2. Refrigerant / coolant liquid heat exchanger (10) according to claim 1, characterized in that the first refrigerant circulation path (21a) comprises a plurality of first refrigerant circulation chambers (211a), the second coolant circulation path (21b) comprises a plurality of second coolant circulation chambers (211b), the first coolant liquid circulation path (22a) comprises a plurality of first coolant liquid circulation chambers (221a), the second heat transfer liquid circulation path (22b) comprises a plurality of second heat transfer liquid circulation chambers (221b), and a same plate (105a, 105b, 105c, 105d, 105e, 105f) jointly defines one of the first refrigerant circulation chambers (211a), one of the second refrigerant circulation chambers (211b), one of the first circulation chambers d u heat transfer liquid (221a) and one of the second heat transfer liquid circulation chambers (221b).

3. Refrigerant / coolant heat exchanger (10) according to any one of the preceding claims, characterized in that the refrigerant / coolant heat exchanger (10) comprises at least one manifold (71, 72, 73, 74, 75, 76, 77, 78) extending along a general axis of extension (A2) which is parallel to a separation plane (P3) jointly bordering the first heat exchange compartment (41) and the second heat exchange compartment (42).

4. Refrigerant / coolant heat exchanger (10) according to claim 3, characterized in that at least one of

heat exchange compartments (41, 42) includes four collectors (71, 72, 73, 74, 75, 76, 77, 78).

5. Refrigerant / heat transfer liquid heat exchanger (10) according to any one of claims 3 and 4, characterized in that at least one of the collectors (71, 72, 73, 74, 75, 76, 77, 78 ) extends from one end to the other of one of the heat exchange compartments (41, 42) along its axis of general extension (A2) which intersects with a bottom plane (P4) in which extends a bottom (106) of the plate (105a, 105b, 105c, 105d, 105e, 105f).

6. Refrigerant / heat transfer liquid heat exchanger (10) according to any one of the preceding claims, characterized in that the plate (105a, 105b, 105c, 105d, 105e, 105f) comprises at least one groove (200) which sealingly isolates the first heat exchange compartment (41) and the second heat exchange compartment (42).

7. Refrigerant / coolant liquid heat exchanger (10) according to claim 6, characterized in that the first circulation chambers (211a, 221a) on the one hand and the second circulation chambers on the other hand (211b, 221b ) are stacked along a stacking direction (D ”) which is parallel to the general extension axis (A2) of the manifold (71, 72, 73, 74, 75, 76, 77, 78), at least one circulation chamber (211a, 211b, 221a, 221b) being delimited by two immediately adjacent plates (105a, 105b, 105c, 105d, 105e, 105f) and at least the groove (200) of one of these plates ( 105a, 105b, 105c, 105d, 105e, 105f).

8. Refrigerant / heat transfer liquid heat exchanger (10) according to claim 6, characterized in that a refrigerant circulation chamber (211a, 211b) is interposed between two chambers of circulation of the heat transfer liquid (221a, 221b) and in that a circulation chamber of the heat transfer liquid (221a, 221b) is interposed between two circulation chambers of the refrigerant fluid (211a, 211b).

9. Refrigerant / coolant liquid heat exchanger (10) according to any one of claims 6 to 8, characterized in that each plate (105a, 105b, 105c, 105d, 105e, 105f) has a raised edge (107) formed by two longitudinal edges (108a, 108b) and two lateral edges (109a, 109b) and surrounding the bottom (106) which is provided with eight orifices (51, 52, 53, 54, 55, 56, 57, 58) .

10. Refrigerant / heat transfer liquid heat exchanger (10) according to claims 6 and 9, characterized in that the eight orifices (51, 52, 53, 54, 55, 56, 57, 58) comprise four orifices (51, 52, 53, 54) including a first orifice (51), a second orifice (52), a third orifice (53) and a fourth orifice (54) arranged inside a first zone (Z1) of the plate (105a, 105b, 105c, 105d, 105e, 105f), and four other orifices (55, 56, 57, 58) including a fifth orifice (55), a sixth orifice (56), a seventh orifice (57) and a eighth orifice (58) arranged inside a second zone (Z2) of the plate (105a, 105b, 105c, 105d, 105e, 105f), the first zone (Z1) and the second zone (Z2) being separated one from the other by the groove (200) which comes from the bottom (106) of the plate (105a, 105b, 105c, 105d, 105e, 105f) and which extends between a first lateral edge (109a) and a second side edge (109b) of the plate (105a, 105b, 105c, 105d, 105e, 105f).

11. Refrigerant / heat transfer liquid heat exchanger (10) according to claim 10, characterized in that the bottom (106) of the plate (105a, 105b, 105c, 105d, 105e, 105f) is provided with at least one rib (113a, 113b) which extends inside the first zone (Z1) and / or the second zone (Z2).

12. Refrigerant / heat transfer liquid heat exchanger (10) according to claim 11, characterized in that the rib (113a, 113b) is perpendicular to the groove (200).

13. Refrigerant / heat transfer liquid heat exchanger (10) according to claim 11, characterized in that the rib (113a, 113b) is parallel to the groove (200).

14. Installation (2) for heat treatment of a component fitted to a motor vehicle, the installation (2) comprising a refrigerant circuit (3), a coolant circuit (5) and a refrigerant / fluid heat exchanger. heat transfer liquid (10) according to any one of the preceding claims, the refrigerant fluid circuit (3)

comprising a first branch for circulating the coolant (10a) and a second branch for circulating the coolant (10b) which are arranged in parallel with each other, the coolant circuit (5) comprising a first branch of circulation of the coolant liquid (15a) and a second circulation branch of the coolant liquid (15b) which are arranged in parallel to each other, characterized in that the first circulation path of the coolant (21a) is constitutive of the first refrigerant fluid circulation branch (10a), the first coolant liquid circulation path (22a) constitutes the first coolant liquid circulation branch (15a), the second refrigerant fluid circulation path (21b) is constituting the second circulation branch of the coolant (10b) and the second circulation path of the coolant liquid (22b) is constituting the second circulation branch d u heat transfer liquid (15b).

15. A method of cooling an electrical storage device (1) of a motor vehicle by means of an installation (2) according to

claim 14, wherein the first heat exchange compartment (41) and the second heat exchange compartment (42) are traversed by the refrigerant fluid (4) and by the heat transfer liquid (6) when the storage device electric (1) is in a fast charging mode;

only the first heat exchange compartment (41) is traversed by the refrigerant (4) and by the coolant (6) when the electrical storage device (1) is in a normal charging mode;

only the second heat exchange compartment (42) is traversed by the coolant (4) and by the heat transfer liquid (6) when the electrical storage device (1) is in an intermediate charging mode.