Patent Publication Number: US-2022236017-A1

Title: Refrigerant/heat transfer liquid heat exchanger

Description:
The present invention relates to a refrigerant/heat transfer liquid heat exchanger. The present invention also relates to an installation comprising a refrigerant circuit, a heat transfer liquid circuit and such a refrigerant/heat transfer liquid heat exchanger. The present invention also relates to a method for cooling an electrical storage device of a motor vehicle using such an installation. 
     In the automotive sector, it is common to have to modify a temperature of a component such as an electric motor, a battery, a heat and/or cold storage device or similar. To this end, the motor vehicle is provided with an installation that comprises a refrigerant circuit inside which a refrigerant circulates, and a heat transfer liquid circuit inside which a heat transfer liquid circulates. The refrigerant circuit comprises a compressor for compressing the refrigerant, a thermal exchanger for cooling the refrigerant at constant pressure, an expansion member to allow the expansion of the refrigerant, and a refrigerant/heat transfer liquid heat exchanger that is arranged to allow a thermal transfer between the refrigerant and the heat transfer liquid. The heat transfer liquid circuit comprises a pump and a thermal exchanger capable of modifying a temperature of the component. 
     The refrigerant/heat transfer liquid heat exchanger is an exchanger comprising plates that are stacked and joined together in order to form tubes defining refrigerant circulation chambers or heat transfer liquid circulation chambers. The plate comprises four orifices in order to allow the intake and output of the refrigerant, and the intake and output of the heat transfer liquid into and from the circulation chambers situated on either side of a single plate. 
     The refrigerant/heat transfer liquid 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 in order to allow the intake and output of the refrigerant and the intake and output of the heat transfer liquid into and from the circulation chambers situated on either side of a single plate. The second cheek does not have any passages. 
     It is common to have to cool the component according to different modes, in particular when it comprises at least one electric battery. It is necessary to cool the electric battery when it is charging, during which the electric battery tends to heat up. The electric battery can be charged in rapid charging mode, in which a charging time is short and an electric charging current is high, or in normal charging mode, in which the charging time is long and the electric charging current is low. The heating of the electric battery is generally proportional to the electric charging current. 
     It is thus common to have to cool the electric battery in rapid charging mode, in which the electric battery dissipates a significant quantity of heat, requiring an equally significant cooling power supplied by the heat exchanger. It is also common to have to cool the electric battery in normal charging mode, in which the electric battery dissipates a small quantity of heat, which a considerably lower cooling power than that necessary in rapid charging mode is sufficient to dissipate. 
     In order to handle these two separate operating modes, the refrigerant/heat transfer liquid heat exchanger is usually configured to supply the high cooling power that is necessary when the electric battery is in rapid charging mode. 
     In other words, the refrigerant/heat transfer liquid heat exchanger is designed and configured to supply high cooling power, corresponding to the power necessary to dissipate the heat supplied by the battery in rapid charging mode. 
     Paradoxically, however, it appears that a refrigerant/heat transfer liquid heat exchanger configured in this way has degraded cooling performance when the cooling power requested is low. In other words, it appears that the refrigerant/heat transfer liquid heat exchanger configured in this way cools the electric battery less well in normal charging mode than it cools this same electric battery in rapid charging mode. 
     One aim of the present invention is to propose a refrigerant/heat transfer liquid heat exchanger configured to efficiently and rapidly supply the appropriate cooling power as a function of various operating modes of the electric battery. 
     The present invention improves the situation by proposing a refrigerant/heat transfer liquid heat exchanger having the following technical features. 
     An exchanger of the present invention is a refrigerant/heat transfer liquid heat exchanger comprising at least one stack of plates defining at least two heat exchange compartments that are sealed from each other, namely a first heat exchange compartment that includes a first refrigerant circulation path and a first heat transfer liquid circulation path, and a second heat exchange compartment that includes a second refrigerant circulation path and a second heat transfer liquid circulation path. 
     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 partially delimited by a single plate. 
     The refrigerant/heat transfer liquid heat exchanger advantageously comprises at least any one of the following technical features, alone or in combination: 
     the same plate defines the first refrigerant circulation path and the second refrigerant circulation path, 
     the same plate defines the first heat transfer liquid circulation path and the second heat transfer liquid circulation path, 
     the same plate jointly defines the first refrigerant circulation path, the first heat transfer liquid circulation path, the second refrigerant circulation path and the second heat transfer liquid circulation path, 
     the refrigerant/heat transfer liquid heat exchanger and its heat exchange compartments are integrally formed and cannot operate after any separation of the heat exchange compartments from each other, 
     the heat exchange compartments are sealed from each other in the sense that no fluid, which can equally be refrigerant and/or heat transfer liquid, can travel directly from one of the heat exchange compartments to the other, 
     the refrigerant circulation paths and the heat transfer liquid circulation paths are arranged so that they allow an exchange of heat energy between the refrigerant suitable for circulating inside the refrigerant circulation paths and the heat transfer liquid intended to circulate inside the heat transfer liquid circulation paths, the respective circulation paths being accommodated 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, a first passage, a second passage, a third passage and a fourth passage of which are assigned to the first heat exchange compartment, and a fifth passage, a sixth passage, a seventh passage and an eighth passage of which are assigned to the second heat exchange compartment, and the second cheek does not have any passages, 
     the first refrigerant circulation path includes a plurality of first refrigerant circulation chambers, the second refrigerant circulation path includes a plurality of second refrigerant circulation chambers, the first heat transfer liquid circulation path includes a plurality of first heat transfer liquid circulation chambers, the second heat transfer liquid circulation path includes a plurality of second heat transfer liquid circulation chambers, and a single plate jointly defines one of the first refrigerant circulation chambers, one of the second refrigerant circulation chambers, one of the first heat transfer liquid circulation chambers and one of the second heat transfer liquid circulation chambers, 
     a first refrigerant circulation chamber is interposed between two first heat transfer liquid circulation chambers and a first heat transfer liquid circulation chamber is interposed between two first refrigerant circulation chambers, 
     a second refrigerant circulation chamber is interposed between two second heat transfer liquid circulation chambers and a second heat transfer liquid circulation chamber is interposed between two second refrigerant 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, and 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, and 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, and said third volume is in particular of the order of one 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, and the fourth volume of a second heat transfer liquid circulation chamber is in particular of the order of two thirds, to within plus or minus 10%, of said second total volume, 
     the first volume and the third volume are equal, to within manufacturing tolerances, and the second volume and the fourth volume are equal, to within 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/heat transfer liquid heat exchanger comprises at least one manifold extending along a general axis of elongation that is parallel to a plane of separation jointly bordering the first heat exchange compartment and the second heat exchange compartment, 
     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 resting against each other, in contact with each other by means of the plane of separation, 
     the plane of separation that defines 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 to a second plane in which the second cheek is inscribed, 
     at least one of the heat exchange compartments comprises four manifolds, 
     the manifolds allow the intake or discharge of the refrigerant or of the heat transfer liquid inside the refrigerant/heat transfer liquid heat exchanger, 
     the first heat exchange compartment is provided with four manifolds and the second heat exchange compartment is provided with four manifolds, 
     two of the manifolds of a single heat exchange compartment are dedicated to the circulation of the refrigerant, and the other two manifolds of the same heat exchange compartment are dedicated to the circulation of the heat transfer liquid, 
     two of the manifolds of a single heat exchange compartment are in fluid communication with the first refrigerant circulation path and the other two manifolds of the same heat exchange compartment are in fluid communication with the first heat transfer liquid circulation path, 
     at least one of the manifolds extends from one end to the other of one of the heat exchange compartments along its general axis of elongation, which intersects a bottom plane in which a bottom of the plate extends, 
     the plate comprises at least one groove that sealably isolates the first heat exchange compartment and the second heat exchange compartment, 
     the first circulation chambers and the second circulation chambers are stacked along a stacking direction that is parallel to the general axis of elongation of the manifold, at least one circulation chamber, which can equally be the first circulation chamber or the second circulation chamber, being delimited by two immediately adjacent plates and at least the groove of one of these plates, 
     a refrigerant circulation chamber is interposed between two heat transfer liquid circulation chambers and a heat transfer liquid circulation chamber is interposed between two refrigerant circulation chambers, 
     a first refrigerant circulation chamber is interposed between two first heat transfer liquid circulation chambers and a first heat transfer liquid circulation chamber is interposed between two first refrigerant circulation chambers, 
     a second refrigerant circulation chamber is interposed between two second heat transfer liquid circulation chambers and a second heat transfer liquid circulation chamber is interposed between two second refrigerant circulation chambers, 
     each plate includes a raised edge made up of two longitudinal edges and two lateral edges and surrounding the bottom, which is provided with eight orifices, 
     the plates are assembled with each other by brazing of at least their raised edges, 
     the eight orifices comprise four orifices, a first orifice, a second orifice, a third orifice and a fourth orifice of which are arranged inside a first zone of the plate, and four other orifices, a fifth orifice, a sixth orifice, a seventh orifice and an eighth orifice of which are arranged inside a second zone of the plate, the first zone and the second zone being separated from each other by the groove, which originates from the bottom of the plate and extends between a first lateral edge and a second lateral 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 plate width taken perpendicularly between the first longitudinal edge and the second longitudinal edge, and the first zone width is in particular of the order of one 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, and the second zone width is in particular of the order of two thirds, to within plus or minus 10%, of the plate width, 
     according to a first embodiment, a first manifold and a third manifold constitute the first heat transfer liquid circulation path, the second manifold and the fourth manifold constitute the first refrigerant circulation path, the fifth manifold and the seventh manifold constitute the second refrigerant circulation path, and the seventh manifold and the eighth manifold constitute the second heat transfer liquid circulation path, 
     the first refrigerant circulation path and the first heat transfer liquid circulation path are I-shaped, 
     the second refrigerant circulation path and the second heat transfer liquid circulation path are I-shaped, 
     according to a second embodiment, the first manifold and the second manifold constitute the first heat transfer liquid circulation path, the third manifold and the fourth manifold constitute the first refrigerant circulation path, the fifth manifold and the sixth manifold constitute the second heat transfer liquid circulation path, and the seventh manifold and the eighth manifold constitute the second refrigerant circulation path, 
     the first refrigerant circulation path and the first heat transfer liquid circulation path 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 orifice has a sixth diameter, the seventh orifice has a seventh diameter and the eighth orifice has 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 and are larger than the second diameter and the fifth diameter, 
     in this case, the second orifice is an orifice for taking refrigerant into the first heat exchange compartment, the fourth orifice is an orifice for discharging refrigerant from the first heat exchange compartment, the fifth orifice is an orifice for taking refrigerant into the second heat exchange compartment and the seventh orifice is an orifice for discharging 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 smaller than the fourth diameter, and the fifth diameter is smaller than the seventh diameter, 
     in this case, the second orifice is an orifice for taking refrigerant into the first heat exchange compartment, the fourth orifice is an orifice for discharging refrigerant from the first heat exchange compartment, the fifth orifice is an orifice for taking refrigerant into the second heat exchange compartment and the seventh orifice is an orifice for discharging refrigerant from 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 larger than the fourth diameter, and the fifth diameter is larger than the seventh diameter, 
     in this case, the second orifice is an orifice for discharging refrigerant from the first heat exchange compartment, the fourth orifice is an orifice for taking refrigerant into the first heat exchange compartment, the fifth orifice is an orifice for discharging refrigerant from the second heat exchange compartment and the seventh orifice is an orifice for taking refrigerant into the second heat exchange compartment, 
     the bottom of the plate is provided with at least one rib that extends inside the first zone and/or the second zone, 
     these arrangements are such that a circulation of the refrigerant and of the heat transfer liquid are I-shaped and are either co-current or counter-current, 
     the rib is substantially perpendicular to the groove, and preferably the rib is perpendicular to the groove, 
     the rib is substantially parallel to the groove, and preferably the rib is parallel to the groove, 
     according to a first variant, a first recess extends parallel to the lateral edges from one of the longitudinal edges to a first recess free end, and a second recess extends parallel to the lateral edges from one of the longitudinal edges to a second recess free end, 
     the first recess extends from the first longitudinal edge to the first recess end, which is situated at a non-zero distance from the groove, and the second recess extends from the first longitudinal edge to the second recess end, which is situated at a non-zero distance from the groove, 
     these arrangements are such that a circulation of the refrigerant and of the heat transfer liquid are U-shaped and are co-current, 
     the first recess extends from the groove to the first recess end, which is situated at a non-zero distance from the first longitudinal edge, and the second recess extends from the groove to the second recess end, which is situated at a non-zero distance from the first longitudinal edge, 
     these arrangements are such that a circulation of the refrigerant and of the heat transfer liquid are U-shaped and are co-current, 
     according to a second variant, the first recess extends parallel to the longitudinal edges from one of the lateral edges to the first recess end, and the second recess extends parallel to the longitudinal edges from one of the lateral edges to the second recess end, 
     the first recess extends from the first lateral edge to the first recess end, which is situated at a non-zero distance from the second lateral edge, and the second recess extends from the first lateral edge to the second recess end, which is situated at a non-zero distance from the second lateral edge, 
     the first recess extends from the second lateral edge to the first recess end, which is situated at a non-zero distance from the first lateral edge, and the second recess extends from the second lateral edge to the second recess end, which is situated at a non-zero distance from the first lateral edge, 
     these arrangements are such that a circulation of the refrigerant and of the heat transfer liquid are U-shaped and are counter-current. 
     The present invention also relates to an installation for thermal treatment of a component provided on a motor vehicle, the installation comprising a refrigerant circuit, a heat transfer liquid circuit and such a refrigerant/heat transfer liquid heat exchanger, the refrigerant circuit comprising a first refrigerant circulation branch and a second refrigerant circulation branch that are arranged parallel to each other, the heat transfer liquid circuit comprising a first heat transfer liquid circulation branch and a second heat transfer liquid circulation branch that are arranged parallel to each other, the first refrigerant circulation path constituting the first refrigerant circulation branch, the first heat transfer liquid circulation path constituting the first heat transfer liquid circulation branch, the second refrigerant circulation path constituting the second refrigerant circulation branch and the second heat transfer liquid circulation path constituting the second heat transfer liquid circulation branch, 
     in other words, the first refrigerant circulation branch comprises the first refrigerant circulation path, the first heat transfer liquid circulation branch comprises the first heat transfer liquid circulation path, the second refrigerant circulation branch comprises the second refrigerant circulation path and the second heat transfer liquid circulation branch comprises the second heat transfer liquid circulation path. 
     The present invention also relates to a method for cooling an electrical storage device of a motor vehicle using such an installation, in which: 
     the refrigerant and the heat transfer liquid travel through the first heat exchange compartment and the second heat exchange compartment when the electrical storage device is in a rapid charging mode, 
     the refrigerant and the heat transfer liquid travel through the first heat exchange compartment only when the electrical storage device is in a normal charging mode, 
     the refrigerant and the heat transfer liquid travel through the second heat exchange compartment only when the electrical storage device is in an intermediate charging mode, 
     it will be understood that in rapid charging mode, a charging time of the electrical storage device is short and an electric charging current of the electrical storage device is high, in normal charging mode of the electrical storage device, the charging time is long and the electric charging current is low, and in intermediate charging mode of the electrical storage device, the charging time is between the short charging time and the long charging time and the electric charging current is between the low charging current and the high charging current. 
    
    
     
       The invention will be better understood on reading the following non-limiting description, given with reference to the appended drawings, in which: 
         FIG. 1  shows a first variant of an installation of the present invention, according to a first mode for cooling a component. 
         FIG. 2  shows the installation according to the first variant illustrated in  FIG. 1  and according to a second mode for cooling the component. 
         FIG. 3  shows a second variant of an installation of the present invention, according to the first mode for cooling a component. 
         FIG. 4  shows the installation according to the second variant illustrated in figure 3 and according to the second mode for cooling the component. 
         FIG. 5  shows the installation according to the second variant illustrated in  figures 3 and 4  and according to a third mode for cooling the component. 
         FIG. 6  is a perspective view of a first variant of a refrigerant/heat transfer liquid heat exchanger of the present invention, which constitutes the installation illustrated in  FIGS. 1 and 2 . 
         FIG. 7  is a perspective view of a second variant of a refrigerant/heat transfer liquid heat exchanger of the present invention, which constitutes the installation illustrated in  FIGS. 3 to 5 . 
         FIG. 8  schematically shows a front view of a first type of plate constituting the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 6 . 
         FIG. 9  schematically shows a front view of a second type of plate constituting a first embodiment of the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
         FIG. 10  schematically shows a front view of a third type of plate constituting a second embodiment of the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
         FIG. 11  schematically shows a front view of a fourth type of plate constituting the second embodiment of the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
         FIG. 12  schematically shows a front view of a fifth type of plate constituting a third embodiment of the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
         FIG. 13  schematically shows a front view of a sixth type of plate constituting the third embodiment of the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
         FIG. 14  schematically shows a lateral cross-section of four plates illustrated in  FIG. 8  assembled with each other. 
         FIG. 15  schematically shows a lateral cross-section of four plates illustrated in  FIG. 9  assembled with each other. 
         FIG. 16  schematically shows a lateral cross-section of four plates, two of which are plates of the third type illustrated in  FIG. 10  and two of which are plates of the fourth type illustrated in  FIG. 11 , assembled with each other to form the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
         FIG. 17  schematically shows a lateral cross-section of four plates, two of which are plates of the fifth type illustrated in  FIG. 12  and two of which are plates of the sixth type illustrated in  FIG. 13 , assembled with each other to form the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 7 . 
     
    
    
     In  FIGS. 1 to 5 , a motor vehicle is provided with a component  1  which must be cooled or heated, for example in order to optimize the operation thereof. Such a component i is for example an electric motor or internal combustion engine suitable for at least partially propelling the motor vehicle, an electrical storage device comprising at least one electric battery intended to store electrical energy, a device for storing heat and/or cold energy, or similar. The component i is more particularly an electrical storage device comprising at least one electric battery that can be charged in particular in rapid charging mode, in which a charging time is short and an electric charging current is high, or in normal charging mode, in which the charging time is long and the electric charging current is low. The present invention aims to efficiently cool the electric battery, regardless of its charging mode: rapid charging mode in which the battery heats up rapidly and significantly, as shown in  FIGS. 1 and 3 , normal charging mode in which the electric battery heats up slowly and slightly, as shown in  FIGS. 2 and 4 , or intermediate charging mode in which the battery heats up moderately, in particular more than in normal charging mode and less than in rapid charging mode, as shown in  FIG. 5 . 
     To this end, the motor vehicle is provided with an installation  2  that comprises a refrigerant circuit  3  inside which a refrigerant  4  circulates, for example carbon dioxide or similar, and a heat transfer liquid circuit  5  inside which a heat transfer liquid  6  circulates, in particular glycol water or similar. The installation  2  is configured to modify a temperature of the component  1 , and in particular to cool the component  1 . 
     The installation  2  comprises at least one refrigerant/heat transfer liquid heat exchanger  10  according to the present invention. The installation  2  is described below in order to better understand the present invention, but the features of the installation  2  described do not limit the refrigerant/heat transfer liquid heat exchanger  10  of the present invention. In other words, the installation  2  is able to have distinct structural features and/or operating modes different from those described, without the refrigerant/heat transfer liquid heat exchanger  10  departing from the rules of the present invention. 
     The refrigerant circuit  3  successively comprises a compressor  7  for compressing the refrigerant  4 , a refrigerant/external air exchanger  8  for cooling the refrigerant  4  at constant pressure, for example placed on the front face of the motor vehicle, an expansion member  9  to allow the expansion of the refrigerant  4 , a first member  11  for controlling a supply of refrigerant  4  to the refrigerant/heat transfer liquid heat exchanger  10  and the refrigerant/heat transfer liquid heat exchanger  10 , which is arranged to allow a thermal transfer between the refrigerant  4  and the heat transfer liquid  6 . 
     The first control member  11  is capable of directing the refrigerant  4  coming from the expansion member  9  towards at least any one of a first refrigerant circulation branch  11   a  and a second refrigerant circulation branch  11   b  comprised in the refrigerant circuit  3 , the first refrigerant circulation branch  11   a  and the second refrigerant circulation branch  11   b  being arranged parallel to each other. The first refrigerant circulation branch  11   a  and the second refrigerant circulation branch  11   b  are formed parallel between a first point of the refrigerant circuit  51  and a second point of the refrigerant circuit  52 . The first point of the refrigerant circuit  51  is situated between the expansion member  9  and the refrigerant/heat transfer liquid heat exchanger  10 , while the second point of the refrigerant circuit  52  is placed between the refrigerant/heat transfer liquid heat exchanger  10  and the compressor  7 . 
     The first point of the refrigerant circuit  51  is provided with the first member  11  for controlling the supply of refrigerant  4  to the refrigerant/heat transfer liquid heat exchanger  10 . According to another variant, the second point of the refrigerant circuit  52  is provided with the first member  11  for controlling the supply of refrigerant  4  to the refrigerant/heat transfer liquid heat exchanger  10 . The refrigerant/heat transfer liquid heat exchanger  10  constitutes the first refrigerant circulation branch  11   a  and the second refrigerant circulation branch  11   b.    
     The first control member  11  comprises, for example, a three-way valve or any other control means permitting or prohibiting the supply of refrigerant  4  to the first refrigerant circulation branch  11   a  and/or to the second refrigerant circulation branch  11   b.    
     The heat transfer liquid circuit  5  successively comprises a pump  14  to cause the heat transfer liquid  6  to circulate inside the heat transfer liquid circuit  5 , a second member  12  for controlling the supply of heat transfer liquid  6  to the refrigerant/heat transfer liquid heat exchanger  10 , which also constitutes the refrigerant circuit  3 , and a thermal exchanger  16 , the thermal exchanger  16  being capable of modifying a temperature of the component  1 , in particular by direct contact formed between the component  1  and the thermal exchanger  16 . 
     The second control member  12  is capable of directing the heat transfer liquid  6  coming from the pump  14  towards at least any one of a first heat transfer liquid circulation branch  12   a  and a second heat transfer liquid circulation branch  12   b  comprised in the heat transfer liquid circuit  5 , the first heat transfer liquid circulation branch  12   a  and the second heat transfer liquid circulation branch  12   b  being arranged parallel to each other. The first heat transfer liquid circulation branch  12   a  and the second heat transfer liquid circulation branch  12   b  are formed 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 heat transfer liquid circuit  61  is situated between pump  14  and the refrigerant/heat transfer liquid heat exchanger  10 , while the second point of the heat transfer liquid circuit  62  is placed between the refrigerant/heat transfer liquid heat exchanger  10  and the thermal exchanger  16 . 
     The first point of the heat transfer liquid circuit  61  is provided with the second member  12  for controlling a supply of heat transfer liquid  6  to the refrigerant/heat transfer liquid heat exchanger  10 . According to another variant, the second point of the heat transfer liquid circuit  62  is provided with second member  12  for controlling a supply of heat transfer liquid  6  to the refrigerant/heat transfer liquid heat exchanger  10 . The refrigerant/heat transfer liquid heat exchanger  10  constitutes the first heat transfer liquid circulation branch  12   a  and the second heat transfer liquid circulation branch  12   b.    
     The second control member  12  comprises, for example, a three-way valve or any other control means permitting or prohibiting the supply of heat transfer liquid  6  to the first heat transfer liquid circulation branch  12   a  and/or to the second heat transfer liquid circulation branch  12   b.    
     In order to constitute the first refrigerant circulation branch  11   a  and the second refrigerant circulation branch  11   b  as well as the first heat transfer liquid circulation branch  12   a  and the second heat transfer liquid circulation branch  12   b,  the refrigerant/heat transfer liquid heat exchanger  10  has a particular structure and layout. 
     The refrigerant/heat transfer liquid heat exchanger  10  comprises at least two refrigerant circulation paths  21   a,    21   b  and at least two heat transfer liquid circulation paths  22   a,    22   b.    
     More particularly, the refrigerant/heat transfer liquid heat exchanger  10  comprises at least a first refrigerant circulation path  21   a  and a second refrigerant circulation path  21   b.  The first refrigerant circulation path  21   a  and the second refrigerant circulation path  21   b  are arranged parallel to each other inside the refrigerant/heat transfer liquid heat exchanger  10 . The first refrigerant circulation path  21   a  thus forms an integral part of the first refrigerant circulation branch  11   a  and the second refrigerant circulation path  21   b  forms an integral part of the second refrigerant circulation branch  11   b.    
     Likewise, the refrigerant/heat transfer liquid heat exchanger  10  comprises at least a first heat transfer liquid circulation path  22   a  and a second heat transfer liquid circulation path  22   b.  The first heat transfer liquid circulation path  22   a  and the second heat transfer liquid circulation path  22   b  are arranged parallel to each other inside the refrigerant/heat transfer liquid heat exchanger  10 . The first heat transfer liquid circulation path  22   a  thus forms an integral part of the first heat transfer liquid circulation branch  12   a  and the second heat transfer liquid circulation path  22   b  forms an integral part of the second heat transfer liquid circulation branch  12   b.    
     The first refrigerant circulation path  21   a  and the first heat transfer liquid circulation path  22   a  are arranged so that the refrigerant  4  present inside the first refrigerant circulation path  21   a  exchanges heat energy with the heat transfer liquid  6  present inside the first heat transfer liquid circulation path  22   a.    
     Likewise, the second refrigerant circulation path  21   b  and the second heat transfer liquid circulation path  22   b  are arranged so that the refrigerant  4  present inside the second refrigerant circulation path  21   b  exchanges heat energy with the heat transfer liquid  6  present inside the second heat transfer liquid circulation path  22   b.    
     The first refrigerant circulation path  21   a  includes a plurality of first refrigerant circulation chambers  211   a  and the first heat transfer liquid circulation path  22   a  includes a plurality of first heat transfer liquid circulation chambers  221   a,  a first refrigerant circulation chamber  211   a  being interposed between two first heat transfer liquid circulation chambers  221   a  and a first heat transfer liquid circulation chamber  221   a  being interposed between two first refrigerant circulation chambers  211   a.    
     The second refrigerant circulation path  21   b  includes a plurality of second refrigerant circulation chambers  211   b  and the second heat transfer liquid circulation path  22   b  includes a plurality of second heat transfer liquid circulation chambers  221   b,  a second refrigerant circulation chamber  211   b  being interposed between two second heat transfer liquid circulation chambers  221   b  and a second heat transfer liquid circulation chamber  221   b  being interposed between two second refrigerant circulation chambers  211   b.    
     The refrigerant/heat transfer liquid heat exchanger  10  is an exchanger that 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  that 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/heat transfer liquid heat exchanger  10  is made up of two heat exchange compartments  41 ,  42  that are sealed from each other and that are positioned side by side and both bordered by the first cheek  23  and the second cheek  24 . 
     The first cheek  23  and the second cheek  24  consist of end plates of the refrigerant/heat transfer liquid heat exchanger  10 , the first cheek  23  and the second cheek  24  being parallel to each other. 
     The first heat exchange compartment  41  houses the first refrigerant circulation path  21   a  and the first heat transfer liquid circulation path  22   a,  while the second heat exchange compartment  42  houses the second refrigerant circulation path  21   b  and the second heat transfer liquid circulation path  22   b.    
     The refrigerant/heat transfer liquid heat exchanger  10  is a one-piece heat exchanger in the sense that the heat exchange compartments  41 ,  42  constituting the refrigerant/heat transfer liquid heat exchanger  10  can only be separated from each other by dislocating and/or destroying at least one of the heat exchange compartments  41 ,  42 . 
     According to a first variant illustrated in  FIGS. 1 and 2 , the first heat exchange compartment  41  has a volume that is half, to within 10%, of the total volume of the refrigerant/heat transfer liquid heat exchanger  10 , and the second heat exchange compartment  42  has a volume that is the other half, to within 10%, of the total volume of the refrigerant/heat transfer liquid heat exchanger  10 . 
     In  FIG. 1 , the component  1  is in rapid charging mode and requires significant cooling power. The first control member ii thus permits the circulation of the refrigerant  4  towards the first refrigerant circulation branch  11   a  and towards the second refrigerant circulation branch  11   b,  so that the refrigerant  4  travels through the entire volume of the refrigerant/heat transfer liquid heat exchanger  10 . Likewise, the second control member  12  permits the circulation of the heat transfer liquid  6  towards the first heat transfer liquid circulation branch  12   a  and towards the second heat transfer liquid circulation branch  12   b,  so that the heat transfer liquid  6  travels through the entire volume of the refrigerant/heat transfer liquid heat exchanger  10 . These arrangements are such that an exchange surface between the refrigerant circulation paths  21   a,    21   b  and the heat transfer liquid circulation paths  22   a,    22   b  is as large as possible, in order to optimize the cooling of the heat transfer liquid  6 , and consequently of the component  1 . 
     In  FIG. 2 , the component  1  is in normal charging mode and requires low cooling power, less than the significant cooling power. The first control member  11  thus permits the circulation of the refrigerant  4  towards one of the refrigerant circulation branches  11   a,    11   b,  for example the first refrigerant circulation branch  11   a,  and prohibits the circulation of the refrigerant  4  towards the other of the refrigerant circulation branches  11   a,    11   b,  for example the second refrigerant circulation branch  11   b,  so that the refrigerant  4  travels through the first heat exchange compartment  41  of the refrigerant/heat transfer liquid heat exchanger  10  only. Likewise, the second control member  12  permits the circulation of the heat transfer liquid  6  towards one of the heat transfer liquid circulation branches  12   a,    12   b,  for example the first heat transfer liquid circulation branch  12   a,  and prohibits the circulation of the heat transfer liquid  6  towards the other of the heat transfer liquid circulation branches  12   a,    12   b,  for example the second heat transfer liquid circulation branch  12   b,  so that the heat transfer liquid  6  travels through the first heat exchange compartment  41  of the refrigerant/heat transfer liquid heat exchanger  10  only. These arrangements are such that an exchange surface between the refrigerant circulation paths  21   a,    21   b  and the heat transfer liquid circulation paths  22   a,    22   b  is minimal, in order to cool the heat transfer liquid  6  according to the cooling requirement of the component  1 , which is less than when it is in rapid charging mode. 
     These arrangements are such that the refrigerant/heat transfer liquid heat exchanger  10  configured in this way and associated with the first control member  11  and the second control member  12  is capable of efficiently and rapidly supplying the appropriate cooling power as a function of the two aforementioned operating modes of the component  1 . 
     According to a variant illustrated in  figures 3 to 5 , the first heat exchange compartment  41  has a volume that is one third, to within 10%, of a total volume of the refrigerant/heat transfer liquid heat exchanger  10 , while the second heat exchange compartment  42  has a volume that is two thirds, to within 10%, of the total volume of the refrigerant/heat transfer liquid heat exchanger  10 . 
     In  FIG. 3 , the component  1  is in rapid charging mode and requires significant cooling power. The first control member  11  thus permits the circulation of the refrigerant  4  towards the first refrigerant circulation branch  11   a  and towards the second refrigerant circulation branch  11   b,  so that the refrigerant  4  travels through the entire volume of the refrigerant/heat transfer liquid heat exchanger  10 . Likewise, the second control member  12  permits the circulation of the heat transfer liquid  6  towards the first heat transfer liquid circulation branch  12   a  and towards the second heat transfer liquid circulation branch  12   b,  so that the heat transfer liquid  6  travels through the entire volume of the refrigerant/heat transfer liquid heat exchanger  10 . These arrangements are such that an exchange surface between the refrigerant circulation paths  21   a,    21   b  and the heat transfer liquid circulation paths  22   a,    22   b  is as large as possible, in order to optimize the cooling of the heat transfer liquid  6 , and consequently of the component  1 . 
     In  FIG. 4 , the component  1  is in normal charging mode and requires low cooling power, less than the significant cooling power. The first control member  11  thus prohibits the circulation of the refrigerant  4  towards the second refrigerant circulation branch  11   b  and permits the circulation of the refrigerant  4  towards the first refrigerant circulation branch  11   a,  so that the refrigerant  4  travels through the first heat exchange compartment  41  of the refrigerant/heat transfer liquid heat exchanger  10  only. Likewise, the second control member  12  prohibits the circulation of the heat transfer liquid  6  towards the second heat transfer liquid circulation branch  12   b  and permits the circulation of the heat transfer liquid  6  towards the first heat transfer liquid circulation branch  12   a,  so that the heat transfer liquid  6  travels through the first heat exchange compartment  41  of the refrigerant/heat transfer liquid heat exchanger  10  only. These arrangements are such that an exchange surface between the refrigerant circulation paths  21   a,    21   b  and the heat transfer liquid circulation paths  22   a,    22   b  is minimal, in order to cool the heat transfer liquid  6  according to the cooling requirement of the component  1 , which is less than when it is in rapid charging mode. 
     In  FIG. 5 , the component  1  is in intermediate charging mode and requires moderate cooling power, greater than the low cooling power and less than the significant cooling power. The first control member ii thus permits the circulation of the refrigerant  4  towards the second refrigerant circulation branch  11   b  and prohibits the circulation of the refrigerant  4  towards the first refrigerant circulation branch  11   a,  so that the refrigerant  4  travels through the second heat exchange compartment  42  of the refrigerant/heat transfer liquid heat exchanger  10  only. Likewise, the second control member  12  permits the circulation of the heat transfer liquid  6  towards the second heat transfer liquid circulation branch  12   b  and prohibits the circulation of the heat transfer liquid  6  towards the first heat transfer liquid circulation branch  12   a,  so that the heat transfer liquid  6  travels through the second heat exchange compartment  42  of the refrigerant/heat transfer liquid heat exchanger  10  only. These arrangements are such that an exchange surface between the refrigerant circulation paths  21   a,    21   b  and the heat transfer liquid circulation paths  22   a,    22   b  is moderate, in order to cool the heat transfer liquid  6  according to the cooling requirement of the component  1 , which is less than when it is in rapid charging mode and is greater than that necessary when the component  1  is in normal charging mode. 
     These arrangements are such that the refrigerant/heat transfer liquid heat exchanger  10  configured in this way and associated with the first control member  11  and the second control member  12  is capable of efficiently and rapidly supplying the appropriate cooling power as a function of the three aforementioned operating modes of the component  1 . 
     In  FIGS. 6 and 7 , the refrigerant/heat transfer liquid heat exchanger  10  is shown schematically in an orthonormal frame of reference Oxyz related to the refrigerant/heat transfer liquid 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/heat transfer 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  extends mainly inside a first plane P 1  that is parallel to the plane Oyz. The second cheek  24  extends mainly inside a second plane P 2  that is also parallel to the plane Oyz. 
     In other words, the refrigerant/heat transfer liquid heat exchanger  10  is transversely delimited 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 the second heat exchange compartment  42  are jointly transversely delimited by the first cheek  23  on one side and the second cheek  24  on the other side. It will be understood from this that the first heat exchange compartment  41  and the second heat exchange compartment  42  are laterally positioned side by side. In yet other words, a plane of separation P 3  that defines the first heat exchange compartment  41  and the second heat exchange compartment  42  is orthogonal to the first plane P 1  and to the second plane P 2  and is parallel to a plane Oxz. 
     The first cheek  23  is provided with eight passages  31 ,  32 ,  33 ,  34 ,  35 ,  36 ,  37 ,  38 , which are preferably circular. It will be 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 made up of an orifice allowing the circulation of the refrigerant  4  or the heat transfer liquid  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 direction Oy and are situated near a first side  25  of the refrigerant/heat transfer liquid heat exchanger  10 , parallel to the plane Oxy. The first passage  31  is situated near a first flank  26  of the refrigerant/heat transfer liquid heat exchanger  10 , the first flank  26  extending in a plane parallel to the plane Oxz. The second passage  32  is situated near the plane of separation P 3  interposed between the first heat exchange compartment  41  and the second heat exchange compartment  42 . The first flank  26  and the plane of separation P 3  laterally border the first heat exchange compartment  41 . 
     The third passage  33  and the fourth passage  34  are aligned in a direction parallel to the direction Oy and are situated near a second side  27  of the refrigerant/heat transfer liquid heat exchanger  10 , parallel to the plane Oxy. The second side  27  and the first side  25  vertically border the refrigerant/heat transfer liquid heat exchanger  10 . The third passage  33  is situated near the first flank  26  of the refrigerant/heat transfer liquid heat exchanger  10 . The fourth passage  34  is situated near the plane of separation P 3  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 sixth passage  36  are aligned in a direction parallel to the direction Oy and are situated near the first side  25  of the refrigerant/heat transfer liquid heat exchanger  10 , parallel to the plane Oxy. The fifth passage  35  is situated near the plane of separation P 3 . The sixth passage  36  is situated near a second flank  28  of the refrigerant/heat transfer liquid heat exchanger  10 . The second flank  28  is parallel to the first flank  26  and to the plane Oxz. 
     The seventh passage  37  and eighth passage  38  are aligned in a direction parallel to the direction Oy and are situated near a second side  27  of the refrigerant/heat transfer liquid heat exchanger  10 . The seventh passage  37  is situated near the plane of separation P 3 . The eighth passage  38  is situated near the second flank  28  of the refrigerant/heat transfer liquid heat exchanger  10 . 
     The first passage  31 , the third passage  33 , the sixth passage  36  and the eighth passage  38  are arranged at respective corners 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 manifold  71 , the second passage  32  gives access to a second manifold  72 , the third passage  33  gives access to a third manifold  73 , the fourth passage  34  gives access to a fourth manifold  74 , the fifth passage  35  gives access to a fifth manifold  75 , the sixth passage  36  gives access to a sixth manifold  76 , the seventh passage  37  gives access to a seventh manifold  77  and the eighth passage  38  gives access to an eighth manifold  78 . The manifolds  71 ,  72 ,  73 ,  74 ,  75 ,  76 ,  77 ,  78  extend along a respective general axis of elongation A 2  which is parallel to the axis Ox and perpendicular to the first plane P 1  and to the second plane P 2 . The manifolds  71 ,  72 ,  73 ,  74 ,  75 ,  76 ,  77 ,  78  are suitable for supplying refrigerant  4  or heat transfer liquid  6  to the chambers  211   a,    211   b,    221   a,    221   b.  The first manifold  71 , the second manifold  72 , the third manifold  73  and the fourth manifold  74  are assigned to the first heat exchange compartment  41 . The fifth manifold  75 , the sixth manifold  76 , the seventh manifold  77  and the eighth manifold  78  are assigned to the second heat exchange compartment  42 . 
     The first heat exchange compartment  41  is generally parallelepipedal and extends over a first compartment height X 1  taken between the first side  25  and the second side  27  parallel to the axis Oz. The first heat exchange compartment  41  extends over a first compartment length X 2  taken between the first cheek  23  and the second cheek  24  parallel to the axis Ox. The first heat exchange compartment  41  extends over a first compartment width X 3  taken between the first flank  26  and the plane of separation P 3  parallel to the axis Oy. 
     The second heat exchange compartment  42  is generally parallelepipedal and extends over a second compartment height X 4  taken between the first side  25  and the second side  27  parallel to the axis Oz. The second heat exchange compartment  42  extends over a second compartment length X 5  taken between the first cheek  23  and the second cheek  24  parallel to the axis Ox. The second heat exchange compartment  42  extends over a second compartment width X 6  taken between the plane of separation P 3  and the second flank  28  parallel to the axis Oy. 
     The first compartment height X 1  and the second compartment height X 4  are equal, to within manufacturing tolerances, and the first compartment length X 2  and the second compartment length X 5  are equal, to within manufacturing tolerances. 
     In  FIG. 6 , which shows the refrigerant/heat transfer liquid heat exchanger  10  of the installation  2  illustrated in  FIGS. 1 and 2 , the first compartment width X 3  is equal to the second compartment width X 6 , to within manufacturing tolerances. 
     The refrigerant/heat transfer liquid heat exchanger  10  is a plate exchanger that comprises the first cheek  23 , the second cheek  24  and a plurality of plates of a first type  105   a,  which are interposed between the first cheek  23  and the second cheek  24 . The first cheek  23 , the second cheek  24  and the plates of the first type  105   a  are for example brazed together to form the heat exchange compartments  41 ,  42  of the refrigerant/heat transfer liquid heat exchanger  10 . 
     In  FIG. 7 , which shows the refrigerant/heat transfer liquid heat exchanger  10  of the installation  2  illustrated in  figures 3 to 5 , the first compartment width X 3  is equal to half of the second compartment width X 6 , to within manufacturing tolerances. 
     The refrigerant/heat transfer liquid heat exchanger  10  is a plate exchanger that comprises the first cheek  23 , the second cheek  24  and either a plurality of plates of a second type  105   b,  or a plurality of plates of a third type  105   c  and a fourth type  105   d,  or a plurality of plates of a fifth type  105   e  and a sixth type  105   f,  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  105   b,    105   c,    105   d,    105   e,    105   f  are for example brazed together to form the heat exchange compartments  41 ,  42  of the refrigerant/heat transfer liquid heat exchanger  10 . 
     Advantageously, and equally for a refrigerant/heat transfer liquid heat exchanger  10  shown in either  FIG. 6  or  FIG. 7 , a single plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  defines at least one of the first circulation paths  21   a,    22   a  of the first heat exchange compartment  41  and one of the second circulation paths  22   a,    22   b  of the second heat exchange compartment  42 . 
     Preferably, a single plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  defines the two first circulation paths  21   a,    22   a  of the first heat exchange compartment  41  and the two second circulation paths  22   a,    22   b  of the second heat exchange compartment  42 . 
     Preferably, a single plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  jointly defines one of the first refrigerant circulation chambers  211   a,  one of the second refrigerant circulation chambers  211   b,  one of the first heat transfer liquid circulation chambers  221   a  and one of the second heat transfer liquid circulation chambers  221   b.    
     In  FIGS. 8 to 17 , each plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  extends mainly along an axis of elongation A 1 . Each plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  comprises a bottom  106 , and at least one raised edge  107  which surrounds the bottom  106 . In other words, the raised edge  107  is formed on the periphery of the bottom  106 , which extends inside a bottom plane P 4 , and the raised edge  107  surrounds the bottom  106 . It will be understood that each exchange plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  is arranged in the form of a generally rectangular tub, the bottom of the tub consisting of the bottom  106 , and the edges of the tub consisting of the raised edge  107 . More particularly, the raised edge  107  comprises two longitudinal raised edges  108   a,    108   b  which are formed opposite each other, and two lateral raised edges  109   a,    109   b  which are formed opposite each other. The longitudinal raised edges  108   a,    108   b  are parallel to the axis of elongation A 1 , while the lateral raised edges  109   a,    109   b  are orthogonal to the axis of elongation A 1 . 
     In  FIGS. 8 to 13 , each plate  105   a,    1015   b,    105   c,    105   d,    105   e,    105   f  comprises eight orifices  51 ,  52 ,  53 ,  54 ,  55 ,  56 ,  57 ,  58 , in particular circular, a first orifice  51  having a first diameter Di, a second orifice  52  having a second diameter D 2 , a third orifice  53  having a third diameter D 3  and a fourth orifice  54  having a fourth diameter D 4  of which are arranged inside a first zone Z 1  of the plate  15   a,    105   b,    105   c,    105   d,    105   e,    105   f  and a fifth orifice  55  having a fifth diameter D 5 , a sixth orifice  56  having a sixth diameter D 6 , a seventh orifice  57  having a seventh diameter D 7  and an eighth orifice  58  having an eighth diameter D 8  of which are positioned inside a second zone Z 2  of the plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f,  the first zone Z 1  and the second zone Z 2  being separated from each other by a groove  200 . The groove  200  is formed in the bottom  106  of the plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  and extends between the first lateral edge  109   a  and the second lateral edge  109   b.  The groove  200  is parallel to the axis of elongation A 1  and to the longitudinal raised edges  108   a,    108   b.    
     The first zone Z 1  is arranged in a quadrilateral, in particular rectangular, and is bordered by a first longitudinal raised edge  108   a,  the groove  200 , a first portion ma of the first lateral edge and a first portion  112   a  of the second lateral edge. 
     The second zone Z 2  is also arranged in a quadrilateral, in particular rectangular, and is bordered by a second longitudinal raised edge  108   b,  the groove  200 , a second portion nib of the first lateral edge and a second portion  112   b  of the second lateral edge. 
     The first portion ma of the first lateral edge and the second portion nib of the first lateral edge are separated from each other by the groove  200 . The first portion  112   a  of the second lateral edge and the second portion  112   b  of the second lateral edge are also separated from each other by the groove  200 . 
     The first portion  111   a  of the first lateral edge and the second portion  111   b  of the first lateral edge together form the first lateral edge  109   a.  The first portion  112   a  of the second lateral edge and the second portion  112   b  of the second lateral edge together form the second lateral edge  109   b.    
     The first zone Z 1  constitutes the first heat exchange compartment  41  and the second zone Z 2  constitutes the second heat exchange compartment  42 . The groove  200  thus sealably 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 corners of the first zone Z 1 . Two of these orifices  51 ,  52 ,  53 ,  54  are configured to communicate with one of the first circulation chambers  211   a,    221   a  formed on one side of the bottom io 6 , and another two of these orifices  51 ,  52 ,  53 ,  54  are configured to communicate with the other of the first circulation chambers  211   a,    221   a  formed on another side of the bottom  106 . To this end, 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 not provided with a collar. As a result, two of these orifices  51 ,  52 ,  53 ,  54  encircled by these collars  120  extend in a plane offset relative to the bottom plane P 4 , parallel to the plane Oyz, in which the bottom  106  is inscribed. The other two of these orifices  51 ,  52 ,  53 ,  54  extend in the bottom plane P 4 . 
     The fifth orifice  55 , the sixth orifice  56 , the seventh orifice  57  and the eighth orifice  58  are respectively distributed at each of the corners of the second zone Z 2 . Two of these orifices  55 ,  56 ,  57 ,  58  are configured to communicate with one of the second circulation chambers  211   b,    221   b  formed on one side of the bottom io 6 , and another two of these orifices  55 ,  56 ,  57 ,  58  are configured to communicate with the other of the first circulation chambers  211   b,    221   b  formed on another side of the bottom io 6 . To this end, 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 not provided with a collar. As a result, two of these orifices  55 ,  56 ,  57 ,  58  encircled by these collars  120  extend in a plane offset relative to the bottom plane P 4 , parallel to the plane Oyz, in which the bottom io 6  is inscribed. The other two of these orifices  55 ,  56 ,  57 ,  58  extend in the bottom plane P 4 . 
     The first orifices  51  of the plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are assembled with each other, so that peripheral rims of these first orifices  51  together define the first manifold  71 . The second orifices  52  of the plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are assembled with each other, so that peripheral rims of these second orifices  52  together define the second manifold  72 . The third orifices  53  of the plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are assembled with each other, so that peripheral rims of these third orifices  53  together define the third manifold  73 . The fourth orifices  54  of the plates  105   a,    105   b,    105   c,    105   d,  lose,  105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,  lose,  105   f  are assembled with each other, so that peripheral rims of these fourth orifices  54  together define the first manifold  71 . The fifth orifices  55  of the plates  105   a,    105   b,    105   c,    105   d,  lose,  105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,  lose,  105   f  are assembled with each other, so that peripheral rims of these fifth orifices  55  together define the fifth manifold  75 . The sixth orifices  56  of the plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are assembled with each other, so that peripheral rims of these sixth orifices  56  together define the sixth manifold  76 . The seventh orifices  57  of the plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are assembled with each other, so that peripheral rims of these seventh orifices  57  together define the seventh manifold  77 . The eighth orifices  58  of the plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are formed opposite each other when these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are assembled with each other, so that peripheral rims of these eighth orifices  58  together define the eighth manifold  78 . 
     In  FIG. 8 , which illustrates a plate of the first type  105   a,  the groove  200  is formed equidistant from the two longitudinal raised edges  108   a,    108   b.  The first zone Z 1  and the second zone Z 2  have equal surface areas, to within manufacturing tolerances. The plate of the first type  105   a  constitutes the refrigerant/heat transfer liquid heat exchanger  10  shown in  FIG. 6 . 
     The four orifices provided with a collar  120 , namely the first orifice  51  and the third orifice  53  for those in the first zone Z 1 , and the sixth orifice  56  and the eighth orifice  58  for those in the second zone Z 2 , are formed near a respective lateral edge  109   a,    109   b  that are longitudinally opposite each other. These arrangements are such that the circulation chambers  211   a,    211   b,    221   a,    221   b  are each I-shaped. The plate of the first type  105   a  in the stack of plates that immediately succeeds the plate of the first type  105   a  illustrated is identical to the one described with reference to  FIG. 8 , with the exception that the first orifice  51 , the third orifice  53 , the sixth orifice  56  and the eighth orifice  58  are not provided with a collar, while the second orifice  52 , the fourth orifice  54 , the fifth orifice  55  and the seventh orifice  57  are provided with a collar  120 , in order to seal the circulation chambers  211   a,    211   b,    221   a,    221   b  from each other, a collar  120  of a plate of the first type  105 a being in contact with the bottom  106  of the immediately successive plate of the first type  105   a.    
     The first diameter Di, the third diameter D 3 , the sixth diameter D 6  and the eighth diameter D 8  are equal to each other. The first manifold  71 , the third manifold  73 , the sixth manifold  76  and the eighth manifold  78 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the heat transfer liquid  6  circulates. According to the example illustrated, the third manifold  73  is a manifold for taking the heat transfer liquid  6  into the first heat exchange compartment  41 , while the first manifold  71  is a manifold for discharging the heat transfer liquid  6  from the first heat exchange compartment  41 . Likewise, the eighth manifold  78  is a manifold for taking the heat transfer liquid  6  into the second heat exchange compartment  42 , while the sixth manifold  76  is a manifold for discharging the heat transfer liquid  6  from the second heat exchange compartment  42 . 
     The second diameter D 2  is smaller than the fourth diameter D 4  and the fifth diameter D 5  is smaller than the seventh diameter D 7 . The second manifold  72 , the fourth manifold  74 , the fifth manifold  75  and the seventh manifold  77 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the refrigerant  4  circulates. According to the example illustrated, the second manifold  72  is a manifold for taking the refrigerant  4  into the first heat exchange compartment  41 , while the fourth manifold  74  is a manifold for discharging the refrigerant  4  from the first heat exchange compartment  41 . Likewise, the fifth manifold  75  is a manifold for taking the refrigerant  4  into the second heat exchange compartment  42 , while the seventh manifold  77  is a manifold for discharging the refrigerant  4  from the second heat exchange compartment  42 . 
     These arrangements are such that the heat transfer liquid  6  and the refrigerant  4  circulate counter-currently to each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
     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 heat transfer liquid  6  and the refrigerant  4  circulate co-currently with each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
     In  FIGS. 9 to 13 , which respectively illustrate a plate of the second type  105   b,  a plate of the third type  105   c,  a plate of the fourth type  105   d,  a plate of the fifth type  105   e  and a plate of the sixth type  105   f,  the groove  200  is formed at a first distance W 1  from the first longitudinal raised edge  108   a  that is equal to half of a second distance W 2  taken between the groove  200  and the second longitudinal edge  108   b,  these distances W 1 , W 2  being taken orthogonally to the longitudinal raised edges  108   a,    108   b  and to the groove  200 . The first zone Z 1  has a surface area that is equal to half of a surface area of the second zone Z 2 , to within manufacturing tolerances. 
       FIG. 9  illustrates a plate of the second type  105   b,  which constitutes the refrigerant/heat transfer 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 in the first zone Z 1 , and the sixth orifice  56  and the eighth orifice  58  for those in the second zone Z 2 , are formed near a respective lateral edge  109   a,    109   b  that are longitudinally opposite each other. These arrangements are such that the circulation chambers  211   a,    211   b,    221   a,    221   b  are each I-shaped. The plate of the second type  105   b  in the stack of plates that immediately succeeds the plate of the second type  105   b  illustrated is identical to the one described with reference to  FIG. 9 , with the exception that the first orifice  51 , the third orifice  53 , the sixth orifice  56  and the eighth orifice  58  are not provided with a collar, while the second orifice  52 , the fourth orifice  54 , the fifth orifice  55  and the seventh orifice  57  are provided with a collar  120 , in order to seal the circulation chambers  211   a,    211   b,    221   a,    221   b  from each other, a collar  120  of a plate of the second type  105   b  being in contact with the bottom  106  of the immediately successive plate of the second type  105   b.    
     The first diameter Di, the third diameter D 3 , the sixth diameter D 6  and the eighth diameter D 8  are equal to each other. The first manifold  71 , the third manifold  73 , the sixth manifold  76  and the eighth manifold  78 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the heat transfer liquid  6  circulates. According to the example illustrated, the third manifold  73  is a manifold for taking the heat transfer liquid  6  into the first heat exchange compartment  41 , while the first manifold  71  is a manifold for discharging the heat transfer liquid  6  from the first heat exchange compartment  41 . Likewise, the eighth manifold  78  is a manifold for taking the heat transfer liquid  6  into the second heat exchange compartment  42 , while the sixth manifold  76  is a manifold for discharging the heat transfer liquid  6  from the second heat exchange compartment  42 . 
     The second diameter D 2  is smaller than the fourth diameter D 4  and the fifth diameter D 5  is smaller than the seventh diameter D 7 . The second manifold  72 , the fourth manifold  74 , the fifth manifold  75  and the seventh manifold  77 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the refrigerant  4  circulates. According to the example illustrated, the second manifold  72  is a manifold for taking the refrigerant  4  into the first heat exchange compartment  41 , while the fourth manifold  74  is a manifold for discharging the refrigerant  4  from the first heat exchange compartment  41 . Likewise, the fifth manifold  75  is a manifold for taking the refrigerant  4  into the second heat exchange compartment  42 , while the seventh manifold  77  is a manifold for discharging the refrigerant  4  from the second heat exchange compartment  42 . 
     These arrangements are such that the heat transfer liquid  6  and the refrigerant  4  circulate counter-currently to each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 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 heat transfer liquid  6  and the refrigerant  4  circulate co-currently with each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
       FIG. 10  illustrates a plate of the third type  105   c,  which constitutes the refrigerant/heat transfer liquid heat exchanger  10  shown in  FIG. 7 , alternately superposed with a plate of the fourth type  105   d  illustrated in  FIG. 11 . 
     The bottom  106  of a plate of the third type  105   c  and the bottom  106  of a plate of the fourth type  105   d  comprise ribs  111   a,    113   b  that are arranged so that the circulation chambers  211   a,    211   b,    221   a,    221   b  have a U-shaped profile. The ribs  113   a,    113   b  are formed in a first direction D that is preferably parallel to the lateral raised edges  109   a,    109   b.  In other words, the first direction D is preferably orthogonal to the axis of elongation A 1  of the exchange plate of the third type  105   c  and the plate of the fourth type  105   d.  A first rib  113   a  is formed inside the first zone Z 1  and a second rib  113   b  is formed inside the second zone Z 2 . 
     In  FIG. 10 , the first rib  113   a  of the plate of the third type  105   c  extends between a first rib first end  114  and a first rib second end  115 , the first rib first end  114  being in contact with the raised edge  107 , and preferably in contact with the first longitudinal raised edge  108   a.  The first rib second end  115  is situated with a first non-zero gap E 1  between it and the groove  200 , the first gap E 1  being taken along the first direction D between the first rib second end  115  and the groove  200 . 
     The second rib  113   b  of the plate of the third type  105   c  extends between a second rib first end  116  and a second rib second end  117 , the second rib first end  116  being in contact with the raised edge  107 , and preferably in contact with the second longitudinal raised edge  108   b.  The second rib second end  117  is situated with a second non-zero gap E 2  between it and the groove  200 , the second gap E 2  being taken along the first direction D between the second rib second end  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 in the first zone Z 1 , and the sixth orifice  56  and the eighth orifice  58  for those in the second zone Z 2 , are formed near a respective lateral edge  109   a,    109   b  that are longitudinally opposite each other. 
     In  FIG. 11 , the first rib  113   a  of the plate of the fourth type  105   d  extends between a first rib first end  114  and a first rib second end  115 , the first rib first end  114  being in contact with the groove  200 . The first rib second end  115  is situated with a third non-zero gap E 3  between it and the first longitudinal raised edge  108   a,  the third gap E 3  being taken along the first direction D between the first rib second end  115  and the first longitudinal raised edge  108   a.    
     The second rib  113   b  of the plate of the fourth type  105   d  extends between a second rib first end  116  and a second rib second end  117 , the second rib first end  116  being in contact with the groove  200 . The second rib second end  117  is situated with a fourth non-zero gap E 4  between it and the second longitudinal raised edge  108   b,  the second gap E 2  being taken along the first direction D between the second rib second end  117  and the second longitudinal raised edge  108   b.    
     The four orifices provided with a collar  120 , namely the second orifice  52  and the fourth orifice  54  for those in the first zone Z 1 , and the fifth orifice  55  and the seventh orifice  57  for those in the second zone Z 2 , are formed near a respective lateral edge  109   a,    109   b  that are longitudinally opposite each other. 
     The collars  120  of a plate of the third type  105   c  are in contact with the bottom  106  of the immediately successive plate of the fourth type  105   d  and the collars  120  of a plate of the fourth type  105   d  are in contact with the bottom  106  of the immediately successive plate of the third type  105   c.    
     In  FIGS. 10 and 11 , the first diameter D 1 , the third diameter D 3 , the sixth diameter D 6  and the eighth diameter D 8  are equal to each other. The first manifold  71 , the third manifold  73 , the sixth manifold  76  and the eighth manifold  78 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the heat transfer liquid  6  circulates. According to the example illustrated, the third manifold  73  is a manifold for taking the heat transfer liquid  6  into the first heat exchange compartment  41 , while the first manifold  71  is a manifold for discharging the heat transfer liquid  6  from the first heat exchange compartment  41 . Likewise, the eighth manifold  78  is a manifold for taking the heat transfer liquid  6  into the second heat exchange compartment  42 , while the sixth manifold  76  is a manifold for discharging the heat transfer liquid  6  from the second heat exchange compartment  42 . 
     The second diameter D 2  is larger than the fourth diameter D 4  and the fifth diameter D 5  is larger than the seventh diameter D 7 . The second manifold  72 , the fourth manifold  74 , the fifth manifold  75  and the seventh manifold  77 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the refrigerant  4  circulates. According to the example illustrated, the fourth manifold  74  is a manifold for taking the refrigerant  4  into 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 a manifold for taking the refrigerant  4  into the second heat exchange compartment  42 , while the fifth manifold  75  is a manifold for discharging the refrigerant  4  from the second heat exchange compartment  42 . 
     These arrangements are such that the heat transfer liquid  6  and the refrigerant  4  circulate co-currently with each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
     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 heat transfer liquid  6  and the refrigerant  4  circulate counter-currently to each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
       FIG. 12  illustrates a plate of the fifth type  105   e,  which constitutes the refrigerant/heat transfer liquid heat exchanger  10  shown in  FIG. 7 , alternately superposed with a plate of the sixth type  105   e  illustrated in  FIG. 13 . 
     The bottom  106  of a plate of the fifth type  105   e  and the bottom  106  of a plate of the sixth type  105   f  comprise ribs  113   a,    113   b  that are arranged so that the circulation chambers  211   a,    211   b,    221   a,    221   b  have a U-shaped profile. The ribs  113   a,  n 3   b  are formed in a second direction D′ that is preferably parallel to the longitudinal raised edges  108   a,    108   b.  In other words, the second direction D′ is for example parallel to the axis of elongation A 1  of the exchange plate of the fifth type  105   e  and the plate of the sixth type  105   f.  A first rib  113   a  is formed inside the first zone Z 1  and a second rib  113   b  is formed inside the second zone Z 2 . 
     In  FIG. 12 , the first rib  113   a  of the plate of the fifth type  105   e  extends between a first rib first end  114  and a first rib second end  115 , the first rib first end  114  being in contact with the raised edge  107 , and preferably in contact with the first lateral raised edge  109   a.  The first rib second end  115  is situated with a fifth non-zero gap E 5  between it and the second lateral raised edge  109   b,  the fifth gap E 5  being taken along the second direction D′ between the first rib second end  115  and the second lateral raised edge  109   b.    
     The second rib  113   b  of the plate of the fifth type  105   e  extends between a second rib first end  116  and a second rib second end  117 , the second rib first end  116  being in contact with the raised edge  107 , and preferably in contact with the first lateral raised edge  109   a.  The second rib second end  117  is situated with a sixth non-zero gap E 6  between it and the second lateral raised edge  109   b,  the sixth gap E 6  being taken along the second direction D′ between the second rib second end  117  and the second lateral raised edge  109   b.    
     The four orifices provided with a collar  120 , namely the first orifice  51  and the second orifice  52  for those in the first zone Z 1 , and the fifth orifice  55  and the sixth orifice  56  for those in the second zone Z 2 , are formed near the first lateral raised edge  109   a.    
     In  FIG. 13 , the first rib  113   a  of the plate of the sixth type  105   f  extends between a first rib first end  114  and a first rib second end  115 , the first rib first end  114  being in contact with the second lateral raised edge  109   b.  The first rib second end  115  is situated with a seventh non-zero gap E 7  between it and the first lateral raised edge  109   a,  the seventh gap E 7  being taken along the second direction D′ between the first rib second end  115  and the first lateral raised edge  109   a.    
     The second rib  113   b  of the plate of the sixth type  105   f  extends between a second rib first end  116  and a second rib second end  117 , the second rib first end  116  being in contact with the second lateral raised edge  109   b.  The second rib second end  117  is situated with an eighth non-zero gap E 8  between it and the first lateral raised edge  109   a,  the eighth gap E 8  being taken along the second direction D′ between the second rib second end  117  and the first lateral raised edge  109   a.    
     The four orifices provided with a collar  120 , namely the third orifice  53  and the fourth orifice  54  for those in the first zone Z 1 , and the seventh orifice  57  and the eighth orifice  58  for those in the second zone Z 2 , are formed near the second lateral raised edge  109   b.    
     The collars  120  of a plate of the fifth type  105   e  are in contact with the bottom  106  of the immediately successive plate of the sixth type  105   f  and the collars  120  of a plate of the sixth type  105   f  are in contact with the bottom  106  of the immediately successive plate of the fifth type  105   e.    
     In  FIGS. 12 and 13 , the first diameter Di, the third diameter D 3 , the sixth diameter D 6  and the eighth diameter D 8  are equal to each other. The first manifold  71 , the third manifold  73 , the sixth manifold  76  and the eighth manifold  78 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the heat transfer liquid  6  circulates. According to the example illustrated, the second manifold  72  is a manifold for taking the heat transfer liquid  6  into the first heat exchange compartment  41 , while the first manifold  71  is a manifold for discharging the heat transfer liquid  6  from the first heat exchange compartment  41 . Likewise, the sixth manifold  76  is a manifold for taking the heat transfer liquid  6  into the second heat exchange compartment  42 , while the fifth manifold  75  is a manifold for discharging the heat transfer liquid  6  from the second heat exchange compartment  42 . 
     The second diameter D 2  is larger than the fourth diameter D 4  and the fifth diameter D 5  is larger than the seventh diameter D 7 . The second manifold  72 , the fourth manifold  74 , the fifth manifold  75  and the seventh manifold  77 , which originate from the orifices the diameters of which have the aforementioned features, are in particular manifolds inside which the refrigerant  4  circulates. According to the example illustrated, the fourth manifold  74  is a manifold for taking the refrigerant  4  into 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 a manifold for taking the refrigerant  4  into the second heat exchange compartment  42 , while the fifth manifold  75  is a manifold for discharging the refrigerant  4  from the second heat exchange compartment  42 . 
     These arrangements are such that the heat transfer liquid  6  and the refrigerant  4  circulate counter-currently to each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 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 heat transfer liquid  6  and the refrigerant  4  circulate co-currently with each other inside the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
     In  FIGS. 14 to 17 , a plurality of plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are nested inside each other in contact with each other at least by means of their raised edge  107  and their groove  200 , in order to jointly form the first heat exchange compartment  41  and the second heat exchange compartment  42 . In other words, four exchange plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are stacked on top of each other in a stacking direction D″ that is parallel to the axis Ox and perpendicular to the bottom plane P 4 . The exchange plates  105 a,  105   b,    105   c,    105   d,    105   e,    105   f  form between them a space that forms the circulation chambers  211   a,    211   b,    221   a,    221   b  for the refrigerant  4  or the heat transfer liquid  6 . 
     In other words, the first circulation chambers  211   a,    221   a  and the second circulation chambers  211   b,    221   b  are stacked along the stacking direction D″. Each circulation chamber  211   a,    211   b,    221   a,    221   b  is delimited at least by the bottoms  106  of two immediately adjacent plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  and by the groove  200  of one of these plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f.    
     The grooves  200  of two successive plates  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  are fitted into each other in order to provide 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  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  can be laterally offset from each other, a crown of a plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  then being in contact with the bottom  106  of the immediately successive plate  105   a,    105   b,    105   c,    105   d,    105   e,    105   f  in order to provide a seal between the first heat exchange compartment  41  and the second heat exchange compartment  42 . 
     In  FIG. 16  more particularly, it will be noted that the recesses  113   a,    113   b  of a plate of the third type  105   c  include a summit  118  that emerges from the bottom  106  of the plate of the third type  105   c  and that is in contact with the bottom of a plate of the fourth type  105   d.  Likewise, the recesses  113   a,    113   b  of a plate of the fourth type  105   d  include a summit  118  that emerges from the bottom  106  of the plate of the fourth type  105   d  and that is in contact with the bottom of a plate of the third type  105   c.  It will be noted that these arrangements can transposed identically for the plates of the fifth type  105   e  and the plates of the sixth type  105   f.    
     All of these arrangements are such that a method according to the present invention for cooling the component  1  using the installation  2  described above, and comprising a refrigerant/heat transfer liquid heat exchanger  10  shown in  FIG. 6 , makes it possible to cool the component  1 , in two appropriate modes, depending on the charging state of the electrical storage device  1 , and in particular on the basis of a choice of activation of the first control member  11  and/or the second control member  12  in which: 
     the refrigerant  4  and the heat transfer liquid  6  travel through the first heat exchange compartment  41  and the second heat exchange compartment  42  when the electrical storage device  1  is in a rapid charging mode; 
     the refrigerant  4  and the heat transfer liquid  6  travel through either one of the first heat exchange compartment  41  and the second heat exchange compartment  42  when the electrical storage device  1  is in a normal charging mode. 
     All of these arrangements are such that a method according to the present invention for cooling the component  1  using the installation  2  described above, and comprising a refrigerant/heat transfer liquid heat exchanger  10  shown in  FIG. 7 , makes it possible to cool the component  1 , in three appropriate modes, depending on the charging state of the electrical storage device  1 , and in particular on the basis of a choice of activation of the first control member  11  and/or the second control member  12  in which: 
     the refrigerant  4  and the heat transfer liquid  6  travel through the first heat exchange compartment  41  and the second heat exchange compartment  42  when the electrical storage device  1  is in a rapid charging mode; 
     the refrigerant  4  and the heat transfer liquid  6  travel through the first heat exchange compartment  41  only when the electrical storage device  1  is in a normal charging mode; 
     the refrigerant  4  and the heat transfer liquid  6  travel through the second heat exchange compartment  42  only when the electrical storage device  1  is in an intermediate charging mode.