Patent Publication Number: US-2022219505-A1

Title: Monoblock heat exchanger comprising at least two heat exchange blocks, each comprising a circulation path for a refrigerant and a circulation path for a heat transfer liquid

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 channels or heat transfer liquid circulation channels. 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 channels situated on either side of the same plate. 
     The refrigerant/heat transfer liquid heat exchanger is longitudinally bordered by a first cheek and a second cheek between which the plates are arranged. The first cheek is provided with four passages to allow the intake and output of the refrigerant, and the intake and output of the heat transfer liquid into and from the circulation channels situated on either side of the same 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. Specifically, 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 recharged 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. Now, 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. 
     According to the present invention, the refrigerant/heat transfer liquid heat exchanger is a monoblock refrigerant/heat transfer liquid heat exchanger comprising at least two heat exchange blocks sealed with respect to each other, including a first heat exchange block comprising a first circulation path for a refrigerant and a first circulation path for a heat transfer liquid, and a second heat exchange block comprising a second circulation path for the refrigerant and a second circulation path for the heat transfer liquid, the heat exchange blocks being joined by means of a partition plate. 
     The refrigerant/heat transfer liquid heat exchanger advantageously comprises at least any one of the following technical features, alone or in combination:
         the refrigerant/heat transfer liquid heat exchanger is monoblock in the sense that the heat exchange blocks that make up the heat exchanger cannot be separated from one another without destroying one at least of the heat exchange blocks,   the refrigerant/heat transfer liquid heat exchanger and its heat exchange blocks are integrally formed and cannot operate after any separation of the heat exchange blocks from each other,   the partition plate fluidically isolates the first heat exchange block from the second heat exchange block,   the heat exchange blocks 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 blocks to the other,   the circulation paths for the refrigerant and the circulation paths for the heat transfer liquid are arranged so as to allow an exchange of heat between the refrigerant intended to circulate inside the circulation paths for the refrigerant and the heat transfer liquid provided to circulate inside the circulation paths for the heat transfer liquid, the circulation paths being equally housed inside the first heat exchange block or the second heat exchange block,   a first volume of the first heat exchange block is between 50% and 70% of a total volume of the monoblock refrigerant/heat transfer liquid heat exchanger,   a second volume of the second heat exchange block is between 30% and 50% of the total volume of the monoblock refrigerant/heat transfer liquid heat exchanger,   the first heat exchange block and the second heat exchange block are butted longitudinally via the partition plate,   the partition plate is equipped with centering means for centering the first heat exchange block and the second heat exchange block on the partition plate,   the centering means comprise at least a plurality of bosses,   the bosses equip both faces of the partition plate,   each boss has an apex which is intended to be brazed onto any one of the heat exchange blocks,   the partition plate is equipped with means for fixing the refrigerant/heat transfer liquid heat exchanger,   the fixing means allow fixing of the refrigerant/heat transfer liquid heat exchanger on a part in its environment,   the fixing means comprise at least one opening equipping a region of the partition plate overhanging any one of the flanks and/or sides of the refrigerant/heat transfer liquid heat exchanger,   the refrigerant/heat transfer liquid heat exchanger extends longitudinally between a first cheek and a second cheek, the first cheek being provided with four passages, including a first passage, a second passage, a third passage and a fourth passage, and the second cheek being provided with four passages, including a fifth passage, a sixth passage, a seventh passage and an eighth passage,   the first heat exchange block is bordered longitudinally on one side by the first cheek and on the other side by the partition plate,   the second heat exchange block is bordered longitudinally on one side by the partition plate and on the other side by the second cheek,   the first passage and the second passage constitute the first circulation path for the refrigerant, the third passage and the fourth passage constitute the first circulation path for the heat transfer liquid, the fifth passage and the sixth passage constitute the second circulation path for the refrigerant, and the seventh passage and the eighth passage constitute the second circulation path for the heat transfer liquid,   the first circulation path for the refrigerant and the first circulation path for the heat transfer liquid are U-shaped,   the second circulation path for the refrigerant and the second circulation path for the heat transfer liquid are U-shaped,   the first passage and the fourth passage constitute the first circulation path for the refrigerant, the second passage and the third passage constitute the first circulation path for the heat transfer liquid, the fifth passage and the eighth passage constitute the second circulation path for the refrigerant, and the sixth passage and the seventh passage constitute the second circulation path for the heat transfer liquid,   the first circulation path for the refrigerant and the first circulation path for the heat transfer liquid are I-shaped,   the second circulation path for the refrigerant and the second circulation path for the heat transfer liquid are I-shaped,   the refrigerant/heat transfer liquid heat exchanger is a plate exchanger comprising the partition plate and exchange plates which are assembled together by brazing,   the first heat exchange block, the second heat exchange block and the partition plate are secured by way of a mechanical assembly means,   the mechanical assembly means comprises assembly means by screwing by means of screws, nuts or the like, by clipping, by interlocking or the like,   the exchange plates constituting the first heat exchange block are identical to the exchange plates constituting the second heat exchange block,   the exchange plates are first-type exchange plates intended to shape the refrigerant/heat transfer liquid heat exchanger into a U-shaped heat exchanger,   the exchange plates are second-type exchange plates intended to shape the refrigerant/heat transfer liquid heat exchanger into an I-shaped heat exchanger.       

     The present invention also relates to an installation for thermal treatment of a component equipping 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, wherein the first refrigerant circulation path constitutes the first refrigerant circulation branch, the first heat transfer liquid circulation path constitutes the first heat transfer liquid circulation branch, the second refrigerant circulation path constitutes the second refrigerant circulation branch and the second heat transfer liquid circulation path constitutes the second heat transfer liquid circulation branch,
         the first heat exchange block is installed on the first refrigerant circulation branch and on the first heat transfer liquid circulation branch,   the second heat exchange block is installed on the second refrigerant circulation branch and on the second heat transfer liquid circulation branch,   the first refrigerant circulation branch and the second refrigerant circulation branch are formed in parallel between a first point of the refrigerant circuit and a second point of the refrigerant circuit, any one at least of the first point of the refrigerant circuit and of the second point of the refrigerant circuit being equipped with a first control member for controlling a supply of refrigerant to the heat exchange blocks of the refrigerant/heat transfer liquid heat exchanger,   the first control member is for example a three-way valve or any other control means allowing or preventing a supply of refrigerant to the first refrigerant circulation branch and/or to the second refrigerant circulation branch,   the first heat transfer liquid circulation branch and the second heat transfer liquid circulation branch are formed in parallel between a first point of the heat transfer liquid circuit and a second point of the heat transfer liquid circuit, any one at least of the first point of the heat transfer liquid circuit and of the second point of the heat transfer liquid circuit being equipped with a second control member for controlling a supply of a heat transfer liquid to the heat exchange blocks of the refrigerant/heat transfer liquid heat exchanger,   the second control member is for example a three-way valve or any other control means allowing or preventing a supply of heat transfer liquid to the first circulation branch of the heat transfer liquid and/or to the second circulation branch of the heat transfer liquid.       

     The present invention also relates to a method for cooling an electrical storage device of a motor vehicle by means of such an installation, wherein:
         the refrigerant and the heat transfer liquid travel through the first heat exchange block and the second heat exchange block when the electrical storage device is in a rapid charging mode, and   the refrigerant and the heat transfer liquid travel through only the first heat exchange block when the electrical storage device is in an intermediate charging mode,   the refrigerant and the heat transfer liquid travel through only the second heat exchange block when the electrical storage device is in a normal charging mode.       

    
    
     
       The invention will be better understood on reading the following nonlimiting description, given with reference to the appended drawings, in which: 
         FIG. 1  shows an installation of the present invention, according to a first mode of cooling a component. 
         FIG. 2  shows the installation illustrated in  FIG. 1 , according to a second mode of cooling the component. 
         FIG. 3  shows the installation illustrated in  FIGS. 1 and 2 , according to a third mode of cooling the component. 
         FIG. 4  shows in perspective a refrigerant/heat transfer liquid heat exchanger of the present invention which constitutes the installation illustrated in  FIGS. 1 to 3 . 
         FIG. 5  schematically illustrates the refrigerant/heat transfer liquid heat exchanger shown in  FIG. 4 . 
         FIG. 6  shows a front view of a partition plate constituting the refrigerant/heat transfer liquid heat exchanger shown in  FIGS. 4 and 5 . 
         FIG. 7  shows a profile view of the partition plate shown in  FIG. 6 . 
         FIG. 8  schematically illustrates a first-type exchange plate constituting a first variant embodiment of the refrigerant/heat transfer liquid heat exchanger illustrated in  FIGS. 4 and 5 . 
         FIG. 9  schematically illustrates a second-type exchange plate constituting a second variant embodiment of the refrigerant/heat transfer liquid heat exchanger illustrated in  FIGS. 4 and 5 . 
         FIG. 10  schematically illustrates a refrigerant/heat transfer liquid heat exchanger made from plates illustrated in  FIG. 8 . 
         FIG. 11  schematically illustrates a refrigerant/heat transfer liquid heat exchanger made from plates illustrated in  FIG. 9 . 
         FIG. 12  schematically illustrates an end plate constituting one embodiment of the refrigerant/heat transfer liquid heat exchanger illustrated in  FIG. 10 or 11 . 
     
    
    
     In  FIGS. 1 to 3 , a motor vehicle is equipped with a component  1  which should be cooled or heated, for example in order to optimize the operation thereof. Such a component  1  is for example an electric motor or combustion engine intended for at least partially propelling the motor vehicle, an electrical storage device comprising at least one electric battery intended to store electrical energy, a heat and/or cold storage device or similar. The component  1  is more particularly an electrical storage device comprising at least one electric battery that can be recharged 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 electric battery heats up rapidly and significantly, as shown in  FIG. 1 , normal charging mode in which the electric battery heats up slowly and slightly, as shown in  FIG. 2 , 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. 3 . 
     To this end, the motor vehicle is equipped 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 component  1 , and in particular to cool the component  1 . 
     The installation  2  comprises at least one refrigerant/heat transfer liquid heat exchanger  11  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 in any way limit the refrigerant/heat transfer liquid heat exchanger  11  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  11  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  10  for controlling a supply of refrigerant  4  to the refrigerant/heat transfer liquid heat exchanger  11  and the refrigerant/heat transfer liquid heat exchanger  11 , which is designed to allow a thermal transfer between the refrigerant  4  and the heat transfer liquid  6 . 
     The first control member  10  is capable of directing the refrigerant  4  coming from the expansion member  9  toward at least any one of a first refrigerant circulation branch  10   a  and a second refrigerant circulation branch  10   b  which the refrigerant circuit  3  comprises, the first refrigerant circulation branch  10   a  and the second refrigerant circulation branch  10   b  being arranged parallel to each other. The first refrigerant circulation branch  10   a  and the second refrigerant circulation branch  10   b  are formed in 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  11 , while the second point of the refrigerant circuit  52  is placed between the refrigerant/heat transfer liquid heat exchanger  11  and the compressor  7 . 
     The first point of the refrigerant circuit  51  is equipped with the first member  10  for controlling the supply of refrigerant  4  to the refrigerant/heat transfer liquid heat exchanger  11 . According to another variant, the second point of the refrigerant circuit  52  is equipped with the first member  10  for controlling the supply of refrigerant  4  to the refrigerant/heat transfer liquid heat exchanger  11 . The refrigerant/heat transfer liquid heat exchanger  11  constitutes the first refrigerant circulation branch  10   a  and the second refrigerant circulation branch  10   b.    
     The first control member  10  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  10   a  and/or to the second refrigerant circulation branch  10   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  15  for controlling the supply of heat transfer liquid  6  to the refrigerant/heat transfer liquid heat exchanger  11 , the refrigerant/heat transfer liquid heat exchanger  11  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  15  is capable of directing the heat transfer liquid  6  coming from the pump  14  toward at least any one of a first heat transfer liquid circulation branch  15   a  and a second heat transfer liquid circulation branch  15   b  which the heat transfer liquid circuit  5  comprises, the first heat transfer liquid circulation branch  15   a  and the second heat transfer liquid circulation branch  15   b  being arranged parallel to each other. The first heat transfer liquid circulation branch  15   a  and the second heat transfer liquid circulation branch  15   b  are formed in parallel between a first point of the heat transfer liquid circuit  61  and a second point of the heat transfer liquid circuit  62 . The first point of the heat transfer liquid circuit  61  is situated between pump  14  and the refrigerant/heat transfer liquid heat exchanger  11 , while the second point of the heat transfer liquid circuit  62  is placed between the refrigerant/heat transfer liquid heat exchanger  11  and the thermal exchanger  16 . 
     The first point of the heat transfer liquid circuit  61  is equipped with the second member  15  for controlling a supply of heat transfer liquid  6  to the refrigerant/heat transfer liquid heat exchanger  11 . According to another variant, the second point of the heat transfer liquid circuit  62  is equipped with the second member  15  for controlling a supply of heat transfer liquid  6  to the refrigerant/heat transfer liquid heat exchanger  11 . The refrigerant/heat transfer liquid heat exchanger  11  constitutes the first heat transfer liquid circulation branch  15   a  and the second heat transfer liquid circulation branch  15   b.    
     The second control member  15  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  15   a  and/or to the second heat transfer liquid circulation branch  15   b.    
     In order to constitute the first refrigerant circulation branch  10   a  and the second refrigerant circulation branch  10   b  as well as the first heat transfer liquid circulation branch  15   a  and the second heat transfer liquid circulation branch  15   b , the refrigerant/heat transfer liquid heat exchanger  11  has a particular structure and layout. 
     Specifically, the refrigerant/heat transfer liquid heat exchanger  11  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  11  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  11 . The first refrigerant circulation path  21   a  thus forms an integral part of the first refrigerant circulation branch  10   a  and the second refrigerant circulation path  21   b  forms an integral part of the second refrigerant circulation branch  10   b.    
     Likewise, the refrigerant/heat transfer liquid heat exchanger  11  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  11 . The first heat transfer liquid circulation path  22   a  thus forms an integral part of the first heat transfer liquid circulation branch  15   a  and the second heat transfer liquid circulation path  22   b  forms an integral part of the second heat transfer liquid circulation branch  15   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.    
     Preferably, the first refrigerant circulation path  21   a  comprises a plurality of first refrigerant circulation channels  211   a  and the first heat transfer liquid circulation path  22   a  comprises a plurality of first heat transfer liquid circulation channels  221   a , a first refrigerant circulation channel  211   a  being interposed between two first heat transfer liquid circulation channels  221   a  and a first heat transfer liquid circulation channel  221   a  being interposed between two first refrigerant circulation channels  211   a.    
     Preferably, the second refrigerant circulation path  21   b  comprises a plurality of second refrigerant circulation channels  211   b  and the second heat transfer liquid circulation path  22   b  comprises a plurality of second heat transfer liquid circulation channels  221   b , a second refrigerant circulation channel  211   b  being interposed between two second heat transfer liquid circulation channels  221   b  and a second heat transfer liquid circulation channel  221   b  being interposed between two second refrigerant circulation channels  211   b.    
     The refrigerant/heat transfer liquid heat exchanger  11  is an exchanger which comprises a first heat exchange block  41  extending between a first cheek  23  and a partition plate  40  and a second heat exchange block  42  which extends between the partition plate  40  and a second cheek  24 . In other words, the refrigerant/heat transfer liquid heat exchanger  11  is formed of two heat exchange blocks  41 ,  42  which are sealed with each other and which are separated and fluidically isolated from one another by the partition plate  40 . 
     The first heat exchange block  41  houses the first refrigerant circulation path  21   a  and the first heat transfer liquid circulation path  22   a , while the second heat exchange block  42  houses the second refrigerant circulation path  21   b  and the second heat transfer liquid circulation path  22   b . It is understood in this that the first refrigerant circulation path  21   a  and the first heat transfer liquid circulation path  22   a  are situated on one side of the partition plate  40  and that the second refrigerant circulation path  21   b  and the second heat transfer liquid circulation path  22   b  are situated on the other side of the partition plate  40 . 
     The refrigerant/heat transfer liquid heat exchanger  11  is a monoblock heat exchanger in the sense that the heat exchange blocks  41 ,  42  constituting the refrigerant/heat transfer liquid heat exchanger  11  can be separated from one another only by a dislocation and/or destruction of at least one of the heat exchange blocks  41 ,  42 . 
     According to a variant embodiment, the first heat exchange block  41  represents by volume two thirds, to within 10%, of a total volume of the refrigerant/heat transfer liquid heat exchanger  11 , while the second heat exchange block  42  represents by volume one third, to within 10%, of the total volume of the refrigerant/heat transfer liquid  11  heat exchanger. 
     In  FIG. 1 , the component  1  is in rapid charging mode and requires significant cooling power. The first control member  10  thus permits the circulation of the refrigerant  4  toward the first refrigerant circulation branch  10   a  and toward the second refrigerant circulation branch  10   b , so that the refrigerant  4  travels through the entire volume of the refrigerant/heat transfer liquid heat exchanger  11 . Likewise, the second control member  15  permits the circulation of the heat transfer liquid  6  toward the first heat transfer liquid circulation branch  15   a  and toward the second heat transfer liquid circulation branch  15   b , so that the heat transfer liquid  6  travels through the entire volume of the refrigerant/heat transfer liquid heat exchanger  11 . 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 intermediate charging mode and requires average cooling power, less than the significant cooling power. The first control member  10  thus permits the circulation of the refrigerant  4  toward the first refrigerant circulation branch  10   a  and prohibits the circulation of the refrigerant  4  toward the second refrigerant circulation branch  10   b , so that the refrigerant  4  travels through the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11  only. Likewise, the second control member  15  permits the circulation of the heat transfer liquid  6  toward the first heat transfer liquid circulation branch  15   a  and prohibits the circulation of the heat transfer liquid  6  toward the second heat transfer liquid circulation branch  15   b , so that the heat transfer liquid  6  travels through the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11  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 average, 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. 3 , the component  1  is in normal charging mode and requires low cooling power, less than the significant and average cooling powers. The first control member  10  thus prohibits the circulation of the refrigerant  4  toward the first refrigerant circulation branch  10   a  and permits the circulation of the refrigerant  4  toward the second refrigerant circulation branch  10   b , so that the refrigerant  4  travels through the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11  only. Likewise, the second control member  15  prohibits the circulation of the heat transfer liquid  6  toward the first heat transfer liquid circulation branch  15   a  and permits the circulation of the heat transfer liquid  6  toward the second heat transfer liquid circulation branch  15   b , so that the heat transfer liquid  6  travels through the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11  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 or intermediate charging mode. 
     These arrangements are such that the refrigerant/heat transfer liquid heat exchanger  11  configured in this way and associated with the first control member  10  and the second control member  15  is capable of efficiently and rapidly supplying the appropriate cooling power as a function of the operating modes of the component  1 . 
     In  FIGS. 4 and 5 , the refrigerant/heat transfer liquid heat exchanger  11  is shown schematically in an orthonormal frame of reference Oxyz related to the refrigerant/heat transfer liquid heat exchanger  11 , in which a direction Ox is a longitudinal direction, a direction Oy is a lateral direction and a direction Oz is a vertical direction. The refrigerant/heat transfer liquid heat exchanger  11  is generally parallelepipedal and extends longitudinally between the first cheek  23  and the second cheek  24  which longitudinally border the refrigerant/heat transfer liquid heat exchanger  11  and which each extend mainly inside a plane parallel to the plane Oyz. 
     The first cheek  23  is provided with four passages, including a first passage  31 , a second passage  32 , a third passage  33  and a fourth passage  34 , which are preferably circular. It is understood that the first passage  31 , the second passage  32 , the third passage  33  and the fourth passage  34  are for example each formed of an orifice to allow circulation of the refrigerant  4  and/or of the heat transfer liquid  6  through the first cheek  23 . 
     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  11 , parallel to the plane Oxy. The first passage  31  is situated near a first flank  26  of the refrigerant/heat transfer liquid heat exchanger  11 , the first flank  26  extending in a plane parallel to the plane Oxz. The second passage  32  is situated near a second flank  27  of the refrigerant/heat transfer liquid heat exchanger  11 , the second flank  27  extending in a plane parallel to the plane Oxz. The first flank  26  and the second flank  27  laterally border the refrigerant/heat transfer liquid heat exchanger in. 
     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  28  of the refrigerant/heat transfer liquid heat exchanger  11 , parallel to the plane Oxy. The second side  28  and the first side  25  vertically border the refrigerant/heat transfer liquid heat exchanger  11 . The third passage  33  is situated near the first flank  26  of the refrigerant/heat transfer liquid heat exchanger  11 . The fourth passage  34  is situated near the second flank  27  of the refrigerant/heat transfer liquid heat exchanger  11 . 
     The first passage  31 , the second passage  32 , the third passage  33  and the fourth passage  34  are arranged at respective angles of the first cheek  23 , which is generally rectangular. 
     In  FIG. 5  more particularly, the second cheek  24  is provided with four passages, including a fifth passage  35 , a sixth passage  36 , a seventh passage  37  and an eighth passage  38 , which are preferably circular. It is understood that the fifth passage  35 , the sixth passage  36 , the seventh passage  37  and the eighth passage  38  are for example each formed of an orifice to allow circulation of the refrigerant  4  and/or of the heat transfer liquid  6  through the second cheek  24 . 
     The fifth passage  35  and the sixth passage  36  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  11 , parallel to the Oxy plane. The fifth passage  35  is situated near the first flank  26  of the refrigerant/heat transfer liquid  11  heat exchanger. The sixth passage  36  is situated near the second flank  27  of the refrigerant/heat transfer liquid heat exchanger  11 . 
     The seventh passage  37  and the eighth passage  38  are aligned in a direction parallel to the direction Oy and are situated near the second side  28  of the refrigerant/heat transfer liquid heat exchanger  11 . The seventh passage  37  is situated near the first flank  26  of the refrigerant/heat transfer liquid heat exchanger  11 . The eighth passage  38  is situated near the second flank  27  of the refrigerant/heat transfer liquid heat exchanger  11 . 
     The fifth passage  35 , the sixth passage  36 , the seventh passage  37  and the eighth passage  38  are arranged at respective angles of the second cheek  24 , which is generally rectangular and of substantially identical shape to that of the first cheek  23 . 
     Preferably, the first passage  31  and the fifth passage  35  are aligned in a direction parallel to the direction Ox, the second passage  32  and the sixth passage  36  are aligned in a direction parallel to the direction Ox, the third passage  33  and the seventh passage  37  are aligned in a direction parallel to the direction Ox, and the fourth passage  34  and the eighth passage  38  are aligned in a direction parallel to the direction Ox. 
     The first exchange block  41  is generally parallelepiped and extends along a first block height X 1  taken between the first side  25  and the second side  28  parallel to the axis Oz. The first exchange block  41  extends along a first block length X 2  taken between the first cheek  23  and the partition plate  40  parallel to the axis Ox. The first exchange block  41  extends along a first block width X 3  taken between the first flank  26  and the second flank  27  parallel to the axis Oy. 
     The second exchange block  42  is generally parallelepiped and extends along a second block height X 4  taken between the first side  25  and the second side  28  parallel to the axis Oz. The first exchange block  41  extends along a second block length X 5  taken between the partition plate  40  and the second cheek  24  parallel to the axis Ox. The first exchange block  41  extends along a second block width X 6  taken between the first flank  26  and the second flank  27  parallel to the axis Oy. 
     Preferably, the first block height X 1  and the second block height X 4  are equal, to within the manufacturing tolerances, the first block length X 2  is twice the second block length X 5 , to within the manufacturing tolerances, and the first block width X 3  and the second block width X 6  are equal, to within the manufacturing tolerances. 
     In  FIG. 6 , the partition plate  40  is generally rectangular. The partition plate  40  extends between a first lateral rim  40   a  and a second lateral rim  40   b  which are parallel to the axis Oz, and extends between a first transverse rim  40   c  and a second transverse rim  40   d  which are parallel to the axis Oy. The partition plate  40  extends along a plate height X 7  taken between the first transverse rim  40   c  and the second transverse rim  40   d  parallel to the axis Oz. The partition plate  40  extends along a plate width X 8  taken between the first lateral rim  40   a  and the second lateral rim  40   b  parallel to the axis Oy. 
     The plate height X 7  is strictly greater than the first block height X 1  and the second block height X 4 , so that the partition plate  40  emerges beyond the first side  25  and the second side  28 . In other words, the partition plate  40  comprises a first region  40   e  which overhangs the first side  25  and a second region  40   f  which overhangs the second side  28 . 
     The plate width X 8  is strictly greater than the first block width X 3  and the second block width X 6 , such that the partition plate  40  emerges beyond the first flank  26  and the second flank  27 . In other words, the partition plate  40  comprises a third region  40   g  which overhangs the first flank  26  and a fourth region  40   h  which overhangs the second flank  27 . 
     The partition plate  40  is provided with fixing means  43  which equip any one at least of the regions  40   e ,  40   f ,  40   g ,  40   h  that the partition plate  40  comprises. The fixing means  43  are intended to allow installation of the refrigerant/heat transfer liquid heat exchanger  11  on a support that the motor vehicle comprises, such as an element of a chassis of the motor vehicle or the like. Preferably, the fixing means  43  comprise at least one opening  44 , and preferably four openings  44  distributed at the corners of the partition plate  40 , these openings  44  being suitable for receiving fixing bolts or the like. 
     In  FIGS. 6 and 7 , the partition plate  40  is provided with centering means  45  for centering the first heat exchange block  41  and the second heat exchange block  42 . The centering means  45  are intended to position the first heat exchange block  41  and the second heat exchange block  42  on either side of the partition plate, forming the regions  40   e ,  40   f ,  40   g ,  40   h , which jointly border and surround the first heat exchange block  41  and the second heat exchange block  42 . The centering means  45  comprise a plurality of bosses  46  which are distributed over each of the faces  47  of the partition plate  40 . The bosses  46  are preferably distributed at the edge of the regions  40   e ,  40   f ,  40   g ,  40   h  of the partition plate which the bosses  46  at least partially delimit. Each boss  46  is for example arranged substantially in a half-ovoid, in particular obtained by stamping the partition plate  40 . Each boss  46  comprises an apex  48  which is intended to come into contact against the first heat exchange block  41  or the second heat exchange block  42 , in order to be brazed therewith. 
     The refrigerant/heat transfer liquid heat exchanger  11  is a plate exchanger which comprises the first cheek  23 , the second cheek  24 , the partition plate  40  and a plurality of first-type exchange plates  105   a , such as the first-type exchange plate  105   a  illustrated in  FIG. 8 , or else a plurality of second-type exchange plates  105   b , such as the second-type exchange plate  105   b  illustrated in  FIG. 9 . 
     In  FIGS. 8 and 9 , each exchange plate  105   a ,  105   b , equally first-type exchange plate  105   a  illustrated in  FIG. 8  or else second-type exchange plate  105   b  illustrated in  FIG. 9 , extends mainly along an axis of elongation A 1 . Each exchange plate  105   a ,  105   b  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 1 , and the raised edge  107  surrounds the bottom  106 . It will be understood that each exchange plate  105   a ,  105   b  is arranged as a generally rectangular bathtub, the bottom of the bathtub consisting of the bottom  106  and the edges of the bathtub consisting of the raised edge  107 . More particularly, the raised edge  107  comprises two lateral raised edges  108   a ,  108   b  which are formed opposite each other, and two transverse raised edges  109   a ,  109   b  which are formed opposite each other. 
     Each exchange plate  105   a ,  105   b  comprises four orifices  110 , in particular circular orifices, which are distributed in pairs at each transverse end of the first-type exchange plate  105   a , and more particularly at each of the corners of the bottom  106  of the exchange plate  105   a ,  105   b . Two of these orifices  110  are configured to communicate with one of the circulation paths  21   a ,  21   b ,  22   a ,  22   b  formed on one side of the bottom  106  and the other two orifices  110  are configured to communicate with one of the circulation paths  21   a ,  21   b ,  22   a ,  22   b  formed on another side of the bottom  106 . 
     The bottom  106  is provided with a plurality of protuberances  112  to disturb a circulation of the refrigerant  4  or of the heat transfer liquid  6  and to improve heat exchange between the refrigerant  4  and the heat transfer liquid  6 . 
     To form the first heat exchange block  41  or the second heat exchange block  42 , a plurality of exchange plates  105   a ,  105   b  are nested one inside the other and in contact with one another at least via their raised edges  107 . In other words, two exchange plates  105   a ,  105   b  are stacked one above the other and form between them a space which forms the circulation channel  211   a ,  211   b ,  221   a ,  221   b  for the refrigerant  4  or for the heat transfer liquid  6 . 
     In  FIG. 8 , which illustrates the first-type exchange plate  105   a , two of the orifices no formed at the same transverse end of the first-type exchange plate  105   a  are each surrounded by a collar  120 , so that these orifices  110  surrounded by this collar  120  extend in a plane offset from the bottom plane P 1 , parallel to the plane Oyz, in which the bottom  106  is inscribed. The other two orifices no situated at the other transverse end of the first-type plate  105   a  extend in the bottom plane P 1 . 
     The bottom  106  comprises a rib  113  which is arranged so that the circulation channel  211   a ,  211   b ,  221   a ,  221   b  has a U-shaped profile. The rib  113  is parallel to a direction D of elongation of the raised lateral edges  108   a ,  108   b , the direction D of elongation of the raised lateral edges  108   a ,  108   b  being preferably parallel to the axis of elongation A 1  of the first-type exchange plate  105   a . The rib  113  extends between a first end  114  and a second end  115 , the first end  114  being in contact with the raised edge  107 , and preferably in contact with a first transverse raised edge  109   a  which the raised edge  107  comprises. The second end  115  is situated at a first non-zero distance D 1  from the raised edge  107 , the first distance D 1  being taken along the axis of elongation A 1  between the second end  115  and a second transverse raised edge  109   b , opposite the first transverse raised edge  109   a.    
     These arrangements are such that the circulation channel  211   a ,  211   b ,  221   a ,  221   b  is shaped in a “U” whose branches of the “U” are parallel to the raised lateral edges  108   a ,  108   b  of the first-type exchange plate  105   a  and are separated by the rib  113 , and the base of the “U” of which adjoins the second transverse edge  109   b . The rib  113  is formed at an equal second distance D 2  from the two lateral edges  108   a ,  108   b  of the first-type exchange plate  105   a , the second distance D 2  being measured between the rib  113 , taken at its center, and one of the raised lateral edges  108   a ,  108   b , perpendicular to the axis of elongation A 1  of the first-type exchange plate  105   a.    
     It follows from these arrangements that the refrigerant/heat transfer liquid heat exchanger  11  obtained from such first-type exchange plates  105   a  is illustrated in  FIG. 10 . In this case, the first passage  31  and the second passage  32  form an integral part of the first refrigerant circulation path  21   a , which is shown in bold and continuous lines. The first passage  31  is for example an intake of the refrigerant  4  inside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 , while the second passage  32  is a discharge of the refrigerant  4  outside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 . The third passage  34  and the fourth passage  34  form an integral part of the first heat transfer liquid circulation path  22   a , which is shown in bold and dotted lines. The third passage  34  is for example an intake of the heat transfer liquid  6  inside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 , while the fourth passage  34  is a discharge of the heat transfer liquid  6  outside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 . It is understood in this that inside the first heat exchange block  41 , the first circulation path for the refrigerant  21   a  is arranged in a “U” and that the first circulation path for the heat transfer liquid  22   a  is also arranged in a “U”. 
     The fifth passage  35  and the sixth passage  36  form an integral part of the second circulation path for the refrigerant  21   b , which is shown in bold and solid lines. The fifth passage  35  is for example an intake of the refrigerant  4  inside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 , while the sixth passage  36  is a discharge of the refrigerant  4  outside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 . The seventh passage  37  and the eighth passage  38  form an integral part of the second circulation path for the heat transfer liquid  22   b , which is shown in bold and dotted lines. The seventh passage  37  is for example an intake of the heat transfer liquid  6  inside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 , while the eighth passage  38  is a discharge of the heat transfer liquid  6  outside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 . It is understood in this that inside the second heat exchange block  42 , the second circulation path for the refrigerant  21   b  is arranged in a “U” and that the second circulation path for the heat transfer liquid  22   b  is also arranged in a “U”. 
     In  FIG. 9 , which illustrates the second-type exchange plate  105   b , two of the orifices  110  formed along a diagonal D 3  of the second-type exchange plate  105   b  are surrounded by a collar  120 , so that these orifices  110  surrounded by this collar  120  extend in a plane offset from the bottom plane P 1 , parallel to the plane Oyz, in which the bottom  106  is inscribed. The other two orifices  110  situated along the other diagonal of the second-type exchange plate  105   b  extend in the bottom plane P 1 . These arrangements are such that the circulation channel  2   n   1   a ,  211   b ,  221   a ,  221   b  is shaped as an “I”. 
     It follows from these arrangements that the refrigerant/heat transfer liquid heat exchanger  11  obtained from such second-type exchange plates  105   b  is illustrated in  FIG. 11 . In this case, the first passage  31  and the fourth passage  34  form an integral part of the first circulation path for the refrigerant  21   a , which is shown in bold and continuous lines. The first passage  31  is for example an intake of the refrigerant  4  inside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 , while the fourth passage  34  is a discharge of the refrigerant  4  outside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 . The second passage  32  and the third passage  33  form an integral part of the first circulation path for the heat transfer liquid  22   a , which is shown in bold and dotted lines. The second passage  32  is for example an intake of the heat transfer liquid  6  inside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 , while the third passage  33  is a discharge of the heat transfer liquid  6  outside the first heat exchange block  41  of the refrigerant/heat transfer liquid heat exchanger  11 . It is understood in this that inside the first heat exchange block  41 , the first circulation path for the refrigerant  21   a  is arranged in an “I” and that the first circulation path for the heat transfer liquid  22   a  is also arranged in an “I”. 
     The fifth passage  35  and the eighth passage  38  form an integral part of the second circulation path for the refrigerant  21   b , which is shown in bold and solid lines. The fifth passage  35  is for example an intake of the refrigerant  4  inside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 , while the eighth passage  38  is a discharge of the refrigerant  4  outside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 . The sixth passage  36  and the seventh passage  37  form an integral part of the second circulation path for the heat transfer liquid  22   b , which is shown in bold and dotted lines. The sixth passage  36  is for example an intake of the heat transfer liquid  6  inside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 , while the seventh passage  37  is a discharge of the heat transfer liquid  6  outside the second heat exchange block  42  of the refrigerant/heat transfer liquid heat exchanger  11 . It is understood in this that inside the second heat exchange block  42 , the second circulation path for the refrigerant  21   b  is arranged in an “I” and that the second circulation path for the heat transfer liquid  22   b  is also arranged in an “I”. 
     According to one embodiment of the present invention, the first heat exchange block  41  and/or the second heat exchange block  42  comprises an end plate  49  which is interposed between the partition plate  40  and the exchange plate  105   a ,  105   b  furthest from the cheek  23 ,  24  such as the end plate shown in  FIG. 12 . The end plate  49  is similar to an exchange plate, with the notable exception that the end plate  49  is free of an orifice  110 , protuberance  112  and groove  113 . The end plate  49  is, however, shaped like a cup and has a raised edge  107  which surrounds a bottom  106 . The raised edge  107  of the end plate  49  is intended in particular to come into abutment against the bosses  46  of the partition plate  40 . The bottom  106  of the end plate  49  is in particular intended to come into contact with the apex  48  of each boss  46  to allow these elements to be brazed together. 
     All of these arrangements are such that a cooling method according to the present invention for cooling the component  1  by means of the installation  2  described above allows the component  1  to be cooled, according to three appropriate modes, depending on the state of charge of the electrical storage device  1 , and in particular from a choice of activation of the first control member  10  and/or the second control member  15  in which:
         the refrigerant  4  and the heat transfer liquid  6  travel through the first heat exchange block  41  and the second heat exchange block  42  when the component  1  is placed in a rapid charging mode, and   the refrigerant and the heat transfer liquid  6  travel through only the first heat exchange block  41  when the component  1  is placed in an intermediate charging mode,   the refrigerant and the heat transfer liquid  6  travel through only the second heat exchange block  42  when the component  1  is placed in a normal charging mode.