Connecting block for heat exchanger and cooling device comprising

Abstract

The present invention relates to a connection block (30) configured to sealingly connect an expansion member to a heat exchanger, the connection block (30) comprising: a refrigerant inlet (370); first and second refrigerant outlets (320, 340), the refrigerant inlet (370) and the first and second refrigerant outlets (320, 340) being arranged on a contact surface (360) in contact with the heat exchanger; and a receiving device (380) for receiving the expansion member, connected to the refrigerant inlet (370) by a branch (310) of the connection block (30), to the first refrigerant outlet (320) by a first flow channel (330) of the connection block (30), and to the second refrigerant outlet (340) by a second flow channel (350) of the connection block (30).

Description

Field of the Invention

[0001] The present invention relates to the field of thermodynamics and, more particularly, to a connection block for a heat exchanger and to a cooling device including such a connection block, which is specifically intended for cooling components of a vehicle. Background Art

[0002] In an electric or hybrid vehicle, the vehicle's battery, electric motor, and power electronics are typically cooled by a heat transfer fluid (such as water) circulating in a heat transfer fluid circuit that passes through these components to be cooled. The heat transfer fluid itself is cooled by a heat exchanger that receives the heat transfer fluid on one hand and a refrigerant fluid on the other hand. The refrigerant fluid is subjected to a thermodynamic cycle in a separate refrigerant fluid circuit using, for example, a compressor, a condenser, an internal heat exchanger, and an expansion member.

[0003] During rapid charging of the battery of an electric or hybrid vehicle, due to the high current, the thermal power to be dissipated to cool the battery is significant, for example, approximately 10,000 watts. Similarly, when an electric or hybrid vehicle is traveling at high speed, the thermal power to be dissipated in the electric motor, power electronics, and battery is significant, and thus a heat exchanger of correspondingly determined size, called a high-performance heat exchanger, is required.

[0004] Since the heat exchanger is formed by a stack of brazed plates defining channels for circulating the refrigerant fluid or the heat transfer fluid, the number of plates of the heat exchanger of an electric or hybrid vehicle is all the greater when it has to dissipate a high thermal power.

[0005] However, when an electric or hybrid vehicle is used in a manner that consumes less energy, such as during slow charging of the battery of an electric vehicle, or when an electric vehicle is operating at low speed, the thermal power to be dissipated by the battery is lower, for example, approximately 4,000 watts. However, the efficiency of a "high-performance" heat exchanger is not optimal under medium or light loads because the number of plates and the size of the channels of such a heat exchanger have been optimized for high-load use. Under medium or light loads, the distribution of the liquid and gas phases of the refrigerant fluid in the heat exchanger is thus uneven and inefficient.

[0006] Therefore, there is a need for a high-performance heat exchanger, particularly for an electric or hybrid vehicle, which has improved thermal power and improved efficiency under light and medium loads, such that the components of the vehicle can be cooled. The vehicle components to be cooled preferably include the battery, electric motor, and power electronics, but also the interior of the vehicle.

[0007] In electric and hybrid vehicles, this performance requirement is combined with the need for compactness of the cooling system in the engine compartment of the vehicle. Specifically, since these vehicles include both, for example, an electric motor and an internal combustion engine, it is necessary to limit the size of each component as much as possible in order to be able to accommodate the electric motor and the engine and their associated systems in the engine compartment. Thus, there is a particular need to be able to connect a high-performance heat exchanger to the other elements of the cooling system without bulky external piping. Summary of the Invention

[0008] The present invention at least partially remedies the drawbacks of the prior art in the following manner: on the one hand, it provides a connection block for a high-performance heat exchanger, such that it is possible to avoid connecting the heat exchanger to one or more expansion members by means of piping, and on the other hand, it provides a compact cooling device. The compact cooling device includes a connection block according to the present invention and a high-performance heat exchanger, wherein the distribution of the refrigerant fluid is homogenized from the inlet to the outlet of the heat exchanger under low, medium or high loads.

[0009] To this end, the present invention proposes a connection block configured to sealingly connect at least one expansion member to a heat exchanger, the connection block comprising at least:

[0010] An inlet for the refrigerant fluid,

[0011] Branches, a first flow channel and a second flow channel inside the connection block, the connection block being characterized in that it further comprises:

[0012] A first outlet and a second outlet for the refrigerant fluid that are separated from each other, the inlet for the refrigerant fluid and the first and second outlets being arranged on a contact surface in contact with the heat exchanger, and

[0013] Receiving means configured to receive at least one expansion member and connected to the inlet for the refrigerant fluid by means of a branch, to the first outlet for the refrigerant fluid by means of the first flow channel, and to the second outlet for the refrigerant fluid by means of the second flow channel.

[0014] By means of the connection block according to the present invention, the heat exchanger can be connected to one or more expansion members without specific piping. Specifically, the connection block includes at least as many outlets as there are expansion members, and these outlets are directly arranged on the contact surface with the heat exchanger. Thus, the connection block allows the heat exchanger to receive several refrigerant fluid flows and thus distribute them separately in one or more bodies of the heat exchanger in order to improve the distribution and in particular reduce the pressure losses.

[0015] Furthermore, in a receiving device using a connection block, one or more expansion members are connected to the connection block without a pipe. The connection block is preferably one-piece and made of aluminum, but of course other materials, in particular aluminum alloys, can be used, and the connection block can also be made in several pieces.

[0016] The branches of the connection block have two or more ends so as to connect the inlet of the connection block to the receiving device according to their arrangement, and the receiving device can include one or more receiving chambers.

[0017] The contact surface between the connection block and the heat exchanger is substantially planar, in the sense that it has at least one planar surface such that it can be brazed or welded to the end face of the heat exchanger. For a part, a sealed connection is formed between the high-pressure outlet for the refrigerant fluid arranged on the end face and the inlet of the connection block for the refrigerant fluid, and for another part, a sealed connection is formed between each outlet of the connection block for the refrigerant fluid and at least one corresponding inlet of the heat exchanger.

[0018] According to an advantageous feature of the connection block of the present invention, the receiving device, the flow channels and the branches are in the form of incisions in the connection block, which are in the form of cylinders with parallel axes. These axes are preferably orthogonal to the contact surface of the connection block. This implementation of the receiving device, the flow channels and the branches inside the connection block is easy to machine. This can be achieved in particular by holes in the connection block, advantageously parallelepipedal and compact. In a variant, these incisions are made in the form of straight prisms, having a height orthogonal to the contact surface of the connection block.

[0019] Advantageously, the receiving device forms a first cylindrical incision orthogonal to the contact surface, the first flow channel forms a second cylindrical incision orthogonal to the contact surface, and the first cylindrical incision joins the second cylindrical incision at a part of the connection block, where a part of the first cylindrical incision is secant to a part of the second cylindrical incision without completely covering the second cylindrical incision. This feature of the connection block also makes it possible to make it compact.

[0020] In one embodiment, the receiving device forms a receiving chamber, which includes a support surface capable of receiving the inlet of the at least one expansion member and an enclosed volume capable of receiving the refrigerant fluid at the outlet of the at least one expansion member. The branch connects the support surface to the inlet for the refrigerant fluid, the first flow channel connects the enclosed volume to the first outlet for the refrigerant fluid, and the second flow channel connects the enclosed volume to the second outlet for the refrigerant fluid. Thus, the receiving chamber forms at least two sealed connections, one between the inlet of the expansion member and the branch of the connection block, and the other between one or more outlets of the expansion member and the first and second flow channels.

[0021] In another embodiment of the present invention, the at least one expansion member includes a first expansion member and a second expansion member, the receiving device includes a first receiving chamber for receiving the first expansion member and a second receiving chamber for receiving the second expansion member, and:

[0022] The first receiving chamber is connected to the inlet for the refrigerant fluid through a branch and is connected to the first outlet for the refrigerant fluid through a first flow path,

[0023] The second receiving chamber is connected to the inlet for the refrigerant fluid through a branch and is connected to the second outlet for the refrigerant fluid through a second flow path.

[0024] Preferably, in this another embodiment:

[0025] The first receiving chamber includes a first support surface capable of receiving the inlet of the first expansion member and a first enclosed volume capable of receiving the refrigerant fluid at the outlet of the first expansion member. The branch connects the first support surface of the first receiving chamber to the inlet for the refrigerant fluid, and the first flow path connects the first enclosed volume to the first outlet for the refrigerant fluid, and

[0026] The second receiving chamber includes a second support surface capable of receiving the inlet of the second expansion member and a second enclosed volume capable of receiving the refrigerant fluid at the outlet of the second expansion member. The branch connects the second support surface of the second receiving chamber to the inlet for the refrigerant fluid, and the second flow path connects the second enclosed volume to the second outlet for the refrigerant fluid.

[0027] In these embodiments, each receiving chamber is formed, for example, by three coaxial holes, the diameters of which narrow from the surface on the opposite side of the contact surface. The hole with the smaller diameter is configured to receive the inlet of the expansion valve of the expansion member and form a sealed connection between the inlet of the expansion valve and the branch. The shoulder between the hole with the smaller diameter and the hole with the medium diameter serves as a support surface for extending the inlet of the valve, for example. In a variant, the inlet of the expansion valve is closely fitted in the hole with the smaller diameter or in the branch to achieve such a seal. The hole with the medium diameter is configured to form an enclosed volume between the part of the expansion member included in the hole with the larger diameter and the inlet of the expansion valve. When the expansion member is received in the receiving chamber, this enclosed volume forms a sealed connection between the outlet of the expansion valve and the first flow path and / or the second flow path.

[0028] Advantageously, in another embodiment of the present invention, the contact surface of the connection block has a first groove forming the inlet for the refrigerant fluid and a part of the branch. The branch includes a first pipeline starting from the first groove and leading to the first receiving chamber, and a second pipeline starting from the first groove and leading to the second receiving chamber. This first groove enables the refrigerant fluid to be effectively distributed in each receiving chamber of the receiving device.

[0029] Advantageously again, in this further embodiment of the invention, the contact surface has a second groove that supplies refrigerant fluid to a second outlet and is configured to connect an inlet orifice of the heat exchanger to a first end of a second flow channel that is produced in the form of a cylindrical cutout, has a second end opposite the first end, and forms an opening in a second receiving chamber. This second groove enables the refrigerant fluid to be effectively returned from the second receiving chamber to the inlet orifice of the heat exchanger.

[0030] The invention also relates to a cooling device that includes a connection block according to the invention, a heat exchanger, and an internal heat exchanger that includes a high-pressure outlet manifold and a low-pressure inlet manifold on a terminal plate of the internal heat exchanger, and wherein:

[0031] a contact surface of the connection block is brazed or welded to an end face of the heat exchanger, and an end plate on the opposite side of the end face is itself brazed or welded to the terminal plate of the internal heat exchanger, the high-pressure outlet manifold is connected to a pipe that passes through the heat exchanger and serves as an inlet for the refrigerant fluid of the connection block, the low-pressure inlet manifold is connected to a discharge orifice of the refrigerant fluid of the heat exchanger on the end plate, and

[0032] the heat exchanger includes:

[0033] for one part, a first distribution chamber that serves a first body of the heat exchanger, and a first inlet for refrigerant fluid that leads to the first distribution chamber,

[0034] and for another part, a second distribution chamber and a second inlet for refrigerant fluid, the second distribution chamber serving a second body of the heat exchanger, the second inlet leading to the second distribution chamber,

[0035] a first outlet for refrigerant fluid of the connection block is connected to a second inlet for refrigerant fluid of the heat exchanger, and a second outlet for refrigerant fluid of the connection block is connected to a first inlet for refrigerant fluid of the heat exchanger. In a variant, a first outlet for refrigerant fluid of the connection block is connected to a first inlet for refrigerant fluid of the heat exchanger, and a second outlet for refrigerant fluid of the connection block is connected to a second inlet for refrigerant fluid of the heat exchanger.

[0036] By means of the cooling device according to the invention, the distribution of the refrigerant fluid is balanced between a first body of the heat exchanger and a second body of the heat exchanger, thus making the distribution uniform and reducing pressure losses. Therefore, at light or medium loads, the efficiency of the heat exchanger is increased.

[0037] Furthermore, when the distribution chambers of the heat exchanger according to the invention are supplied independently, the invention makes it possible to use the first body and / or the second body according to the thermal power to be dissipated. The cooling device according to the invention additionally has the advantage of being compact.

[0038] The first body of the heat exchanger comprises, for example, a first plurality of plates between which a first channel intended to receive a refrigerant fluid is arranged, and the second body of the heat exchanger comprises a second plurality of plates between which a second channel intended to receive a refrigerant fluid is arranged, the first distribution chamber and the second distribution chamber being able to supply a first flow rate of refrigerant fluid to the first channel and a second flow rate of refrigerant fluid to the second channel, respectively, in a sealed manner relative to each other.

[0039] The first channels and the second channels of the first body and the second body respectively preferably all have the same cross-section and length, and the first flow rate is preferably substantially equal to the second flow rate. Although the structures of the first channel and the second channel are the same, the first flow rate can specifically be different from the second flow rate, in particular depending on the different pressure losses between the first channel and the second channel.

[0040] In a main embodiment variant of the invention, the first distribution chamber and the second distribution chamber are arranged around a pipe that orthogonally passes through the plates of the first plurality of plates and the second plurality of plates, and the cooling device comprises a sealing barrier between the first distribution chamber and the second distribution chamber, the sealing barrier forming an angled cylindrical sleeve portion around the pipe and having an opening in the end face of the heat exchanger.

[0041] In a second embodiment variant of the invention, the first distribution chamber and the second distribution chamber are at least partially delimited by a first helical spiral and a second helical spiral wound around the pipe.

[0042] In this second embodiment variant of the invention, the cooling device according to the invention comprises, for example, a first sealing barrier between the first distribution chamber of the heat exchanger and the second body, the first sealing barrier being a screw plug, and a second sealing barrier between the second distribution chamber of the heat exchanger and the first body, the second sealing barrier being formed by a cylindrical envelope around the first and second spirals facing the first channel, the cylindrical envelope comprising holes between the first distribution chamber and each first channel. The first spiral and the second spiral stop, for example, at the interface between the first channel and the second channel.

[0043] In this secondary embodiment variant of the invention, the first and second intertwined spirals define for example two pitches, with the first distribution chamber being defined by the first pitch of said pitches, the first pitch of the pitches being smaller than the second pitch of said pitches, and the second pitch defining the second distribution chamber. In this case, the capacity of the first distribution chamber is smaller than that of the second distribution chamber, and the number of first channels is smaller than the number of second channels. The ratio of the number of first channels to the number of second channels and thus the ratio of the first spacing to the second spacing depend on the thermal power to be dissipated in the first body of the heat exchanger and the second body of the heat exchanger, which can be supplied independently. The sizing of the first body is for example adapted to dissipate low thermal power in the use case of an electric vehicle or a hybrid vehicle operating at low speed. The sizing of the second body is for example adapted to dissipate medium thermal power in the use case of slow charging of an electric vehicle or a hybrid vehicle. The use of the first body and the second body together enables high thermal power to be dissipated, especially in the case of rapid charging of an electric vehicle or a hybrid vehicle.

[0044] As an alternative, in this second embodiment variant of the invention, the first distribution chamber has a greater capacity than the second distribution chamber, the first spacing is greater than the second spacing, and the number of first channels is greater than the number of second channels.

[0045] In yet another embodiment, the number of channels in the first body and the second body is the same.

[0046] According to another advantageous feature of the cooling device of the invention, the plate of the heat exchanger provided at the interface between the first body and the second body does not allow the refrigerant fluid to pass between the first body and the second body. Thus, even outside the distribution chamber, the refrigerant fluid cannot flow from the first body of the heat exchanger to the second body.

[0047] Advantageously, the cooling device according to the invention further comprises an expansion member or a first expansion member and a second expansion member. Description of the Drawings

[0048] Other features and advantages of the invention will become more clearly apparent from the following description and from the multiple exemplary embodiments provided by way of non-limiting indication with reference to the accompanying schematic drawings, in which:

[0049] Figure 1 A cooling device according to the invention is shown, in a first embodiment of the invention,

[0050] Figure 2 A connection block according to the invention is shown, in this first embodiment of the invention,

[0051] Figure 3 Shown in cross-section Figure 2 the connection block in

[0052] Figure 4 shows a cooling device according to the present invention. In a second embodiment of the present invention,

[0053] Figure 5 shows a connection block according to the present invention. In a second embodiment of the present invention,

[0054] Figure 6 is shown in cross-section Figure 5 the connection block in

[0055] Figure 7 is Figure 1 or Figure 4 a front view of the heat exchanger of the cooling device in

[0056] Figure 8 is Figure 1 a cross-sectional view of the cooling device in a variant of the second embodiment of the present invention,

[0057] Figure 9 schematically shows a cooling device according to the present invention, in a variant of the main embodiment of the present invention,

[0058] Figure 10 schematically shows Figure 8 the cooling device in

[0059] Figure 11 shows a cooling system of an electric or hybrid vehicle including Figure 4 the cooling device in Detailed Description

[0060] In Figure 1 a first embodiment of the present invention shown in

[0061] a cooling device 1 according to the present invention includes an expansion member 6, a connection block 30 according to the present invention, a heat exchanger 2, and an internal heat exchanger 4.

[0062] The heat exchanger 2 includes an inlet 26 for the heat transfer liquid and an outlet 28 for the heat transfer liquid.

[0063] The internal heat exchanger 4 includes a free end plate, a high-pressure inlet manifold 42 for the refrigerant fluid and a low-pressure outlet manifold 48 for the refrigerant fluid are provided on the free end plate. The opposite end plate of the heat exchanger 4 is a terminal plate brazed to the end plate 211 of the heat exchanger 2, as Figure 9 shown. As this Figure 9As shown, at the interface between the terminal plate of the internal heat exchanger 4 and the end plate 211 of the heat exchanger 2, the discharge orifice 24 for the refrigerant fluid of the heat exchanger 2 communicates directly with the low-pressure inlet manifold 46 of the internal heat exchanger 4. Also at this interface, the high-pressure outlet manifold 44 of the internal heat exchanger 4 communicates with a pipe 29 passing through the heat exchanger 2. The pipe 29 includes a first end 294 that leads to an inlet 370 for the refrigerant fluid of the connection block 30 (referred to in Figure 2 ), and is arranged in the intake orifice 22 for the refrigerant fluid of the heat exchanger 2. The pipe 29 includes a second end 292 connected to the high-pressure outlet manifold 44 of the internal heat exchanger 4.

[0064] It should be noted that details regarding the paths of the refrigerant fluid in the heat exchanger 2 and the internal heat exchanger 4 will be described in more detail below in conjunction with Figure 9

[0065] The end face 251 of the heat exchanger 2 is on the opposite side of the end plate 211 of the heat exchanger 2 and includes an inlet 26 for the heat transfer liquid and an outlet 28 for the heat transfer liquid, and is brazed to the connection block 30 on the contact surface 360 of the connection block 30 with the heat exchanger 2, as Figure 2 shown.

[0066] The connection block 30 is an aluminum block in which holes have been produced orthogonally to the contact surface 360. It is noteworthy that on the side opposite to this contact surface 360, means for receiving the expansion member 6 are formed by a receiving chamber 380, which is produced by three coaxial holes 381, 383, 385, the diameters of the holes 381, 383, 385 narrowing from the surface of the connection block 30 on the side opposite to the contact surface 360. This receiving chamber 380 more specifically houses the expansion valve of the expansion member 6.

[0067] The last smaller-diameter hole 385 in this receiving chamber is itself penetrated by a branch 310 to the contact surface 360 of the connection block 30, and this branch 310 forms the inlet 370 for the refrigerant fluid of the connection block 30. In this case, this branch 310 is also a cylindrical hole, the diameter of which is smaller than that of the last hole 385 and is coaxial with it. The last hole 385 of the receiving chamber 380 has a support surface 386, as Figure 3 ​As shown, the support surface 386 encloses the perimeter of the inlet of the expansion valve of the expansion member 6. Thus, the support surface 386 forms a sealed connection between the inlet of the expansion valve of the expansion member 6 and the inlet 370 for the refrigerant fluid of the connection block 30. In a variant, the diameter of the branch 310 is the same as the diameter of the last hole 385. In another variant, the inlet of the expansion valve of the expansion member 6 abuts against the shoulder between the last hole 385 and the branch 310 so as to form a sealed connection between the inlet of the expansion valve of the expansion member 6 and the inlet 370 for the refrigerant fluid of the connection block 30.

[0068] That portion of the expansion member 6 received in the larger diameter hole 381 of the receiving chamber 380 abuts against the shoulder between the larger diameter hole 381 and the intermediate diameter hole 383 of the receiving chamber 380, closing any flow path between the larger diameter hole 381 and the intermediate diameter hole 383. Thus, the intermediate diameter hole 383 includes a closed volume 388 between the expansion valve of the expansion member 6 and the cylindrical surface of the intermediate diameter hole 383, and this cylindrical surface receives the portion of the expansion valve including the outlet for the refrigerant fluid for the expansion valve. Thus, the closed volume 388 receives the refrigerant fluid in a sealed manner at the outlet of the expansion valve. The refrigerant fluid at the outlet of the expansion valve leaves the closed volume 388 via a first flow path 330 provided between the cylindrical surface of the intermediate diameter hole 383 and the first outlet 320 for the refrigerant fluid of the connection block 30, and also via a second flow path 350 provided between the cylindrical surface of the intermediate diameter hole 383 and the second outlet 340 for the refrigerant fluid of the connection block 30.

[0069] More specifically, the first flow path 330 is formed by a first cylindrical hole 322, and the second cylindrical hole has a smaller diameter and connects the intermediate diameter hole 383 of the receiving chamber 380 at a portion of the connection block 30. These first and second holes extend orthogonally from the contact surface 360.

[0070] When observed in a cross-section through a plane parallel to the contact surface 360, the portion of the block where the first flow path 330 engages the closed volume 388 of the receiving chamber 380 will thus show the first flow path 330 and the receiving chamber 380 in the form of a non-empty intersecting circular cross-section, but one not included in the other. In other words, in this parallel plane, the distance between the rotational axis of the first hole of the first flow path 330 and the rotational axis of the intermediate diameter hole 383 of the receiving chamber 380 is less than the sum of the radii of the cylinders formed by these holes.

[0071] In a variant, the first flow path 330 leads entirely to the shoulder between the intermediate diameter hole 383 of the receiving chamber 380 and the last hole 385 of the smaller diameter of the receiving chamber 380.

[0072] The second flow channel 350 is symmetrically produced relative to a plane orthogonal to the contact surface 360, which passes through the diameter of the cylindrical hole forming the branch 310 of the connection block 30.

[0073] Figure 3 Also shown is the flow followed by the refrigerant fluid FR within the connection block 30. The refrigerant fluid FR at the outlet of the pipe 29 is transferred at high pressure to the inlet 370 of the connection block 30 and enters the expansion valve of the expansion member 6. After expanding in this valve, the refrigerant fluid FR enters the closed volume 388 at low pressure from the outlet of this valve, and exits from this closed volume 388 via the first flow channel 330 and via the second flow channel 350 to the respective outlets 320 and 340 of the connection block 30. This dual outlet of the connection block 30 enables the low-pressure refrigerant fluid FR to be conveyed to the intake orifice 22 via two separate inlets (i.e., the first inlet 221 and the second inlet 223) that supply the first body 25 of the heat exchanger 2 and the second body 27 of the heat exchanger 2 respectively, as Figure 8 shown. The separation of the refrigerant fluid FR into two separate flows enables better control of the pressure loss inside the heat exchanger 2, as will be Figure 8 explained below.

[0074] In Figure 4 the second embodiment of the present invention shown, the cooling device 10 according to the present invention includes a first expansion member 64, a second expansion member 62, a connection block 3 according to the present invention, and a heat exchanger 2 and an internal heat exchanger 4 of the first embodiment of the present invention. As in the first embodiment of the present invention, the connection block 3 includes a contact surface 36 brazed to the end face 251 of the heat exchanger 2 (see Figure 5 ), and as in the first embodiment of the present invention, the heat exchanger 2 is assembled with the internal heat exchanger 4.

[0075] The expansion members 62 and 64 are electronically controlled. In a variant, they are thermally controlled.

[0076] The connection block 3 has many features similar to those of the connection block 30 and will thus be described in less detail than the connection block 30. Regarding the connection block 30, the valves of the first expansion member 64 and the second expansion member 62 are inserted into the receiving means of the connection block 3, as Figure 5 shown, and these receiving means include a first receiving chamber 38 for accommodating the expansion valve of the first expansion member 64 and a second receiving chamber 39 for accommodating the expansion valve of the second expansion member 62. These chambers are made as three cylindrical holes in a manner similar to the chambers 380 of the connection block 30. The respective expansion valves of the expansion members 64, 62 are arranged therein in the same way.

[0077] The inlet 37 of the refrigerant fluid FR of the connection block 3 is formed by a first groove 31 engraved on the contact surface 36. The last smaller-diameter hole of the receiving chamber 38 is itself pierced by a first cylindrical pipe 312 leading to the first groove 31. Similarly, the last smaller-diameter hole of the receiving chamber 39 is itself pierced by a second cylindrical pipe 314 leading to the first groove 31. Thus, the receiving chambers 38, 39 are fluid-connected to the inlet 37 of the connection block 3 for the refrigerant fluid through a single branch inside the connection block 3, and the branch is formed by the first groove 31 and the pipes 312, 314, and the pipes 312, 314 are orthogonal to the contact surface 36 and extend the ends of the first groove 31.

[0078] As in the first embodiment of the present invention, the bearing surface 382 (refer to Figure 6 ) of the last smaller-diameter hole of the first receiving chamber 38 or the second receiving chamber 39 forms a sealed connection between the corresponding inlets of the expansion valves of the first expansion member 64 or the second expansion member 62 and the first pipe 312 or the second pipe 314 respectively (and thus between the inlets of these expansion valves and the inlet 37 of the connection block 3).

[0079] Contrary to the first embodiment of the present invention, the first receiving chamber 38 is only connected to the first outlet 32 of the connection block 3 via the first flow channel 33. The first flow channel 33 is made in the same way as the first flow channel 330. It is worth noting that it hermetically receives the refrigerant fluid FR at the outlet of the expansion valve by means of a closed volume 384 (refer to Figure 6 ) included between the expansion valve of the first expansion member 64 and the middle-diameter hole of the first receiving chamber 38. In the same way as in the first embodiment of the present invention, this seal is achieved by tightly inserting the expansion valve into the first receiving chamber 38.

[0080] As in the first embodiment, the first flow channel 33 is formed by a first cylindrical cut 326, followed by a second cylindrical cut with a smaller diameter. The first cylindrical cut 326 is arranged to face the second inlet 223 of the heat exchanger 2 for the refrigerant fluid.

[0081] Similarly, the second receiving chamber 39 is only connected to the second outlet 34 of the connection block 3 via the second flow channel 35. The second flow channel 35 is made in the same way as the second flow channel 350. It is worth noting that it hermetically receives the refrigerant fluid FR at the outlet of the expansion valve by means of a closed volume included between the expansion valve of the second expansion member 62 and the middle-diameter hole of the second receiving chamber 39.

[0082] To connect the second flow channel 35 to the first inlet 221 for the refrigerant fluid of the heat exchanger 2, a second groove is created on the exchange surface 36 of the connection block 3. The first end of the second groove leads to the second flow channel 35, and the second end of the second groove is arranged to face the first inlet 221 for the refrigerant fluid of the heat exchanger 2. Thus, the second outlet 34 for the refrigerant fluid of the connection block 3 is formed by this second groove.

[0083] Thus, this second embodiment enables the separate control of the first flow of the low-pressure refrigerant fluid reaching the first inlet 221 for the refrigerant fluid of the heat exchanger 2 and the second flow of the low-pressure refrigerant fluid reaching the second inlet 223 for the refrigerant fluid of the heat exchanger 2. Specifically, the first flow is controlled by the second expansion member 62, whereas the second flow is controlled by the first expansion member 64.

[0084] The flow of the refrigerant fluid FR in the connection block 3 is shown by Figure 5 and Figure 6 the dashed lines in.

[0085] Figure 7 A part of the heat exchanger 2 is shown at the portion of the end face 251 of the heat exchanger that contacts the contact surface 36 or 360 of the connection block 3 or 30. In this Figure 7 the end face 251 is presented as transparent, where only the holes 222 and 224 corresponding to the first inlet 221 and the second inlet 223 for the refrigerant fluid of the heat exchanger 2 of this end face 251 are shown. In this figure, the sealing edges of the channels of the heat exchanger 2 thus appear as multiple lines, and the turbulators of the first channel of the heat exchanger 2 are presented in a prominent form.

[0086] As visible in this Figure 7 the first end 294 of the pipe 29 is arranged at the center of the intake orifice 22 of the heat exchanger 2. This first end 294 protrudes from the end face 251 of the heat exchanger 2 so as to be inserted into the cylindrical hole of the branch 310 forming the connection block 30, or into the first groove 31 of the connection block 3, without contacting the bottom of the first groove 31, such that the refrigerant fluid circulates to the first pipeline 312 and the second pipeline 314.

[0087] The first outlets 32, 320 for the refrigerant fluid FR of the connection blocks 3, 30 are placed facing the hole 224 of the end face 251 so as to supply the second inlet 223 for the refrigerant fluid of the heat exchanger 2, and the second outlets 34, 340 for the refrigerant fluid FR of the connection blocks 3, 30 are placed facing the hole 222 of the end face 251 so as to supply the first inlet 221 for the refrigerant fluid of the heat exchanger 2.

[0088] To receive the first flow in the first inlet 221 sealingly relative to the second flow in the second inlet 223, an inlet sealing device is arranged at the air inlet orifice 22.

[0089] As Figure 9 and Figure 10 shown, the air inlet orifice 22 itself is the end of an inlet manifold 23 of the heat exchanger 2, which inlet manifold 23 is at least partially surrounded by a cylindrical envelope 235 that sealingly serves the first body 25 and the second body 27 of the heat exchanger 2. For this purpose, the inlet manifold 23 includes a first distribution chamber 231 and a second distribution chamber 233, the first distribution chamber 231 being supplied by the first inlet 221 and serving the first body 25 of the heat exchanger 2, and the second distribution chamber 233 being supplied by the second inlet 223 and serving the second body 27 of the heat exchanger 2. The first distribution chamber 231 and the second distribution chamber 233 are arranged around a pipe 29, as described in detail below.

[0090] When the first distribution chamber 231 and the second distribution chamber 233 are angular cylindrical parts arranged around the pipe 29, as Figure 9 shown in the main embodiment variant, the inlet sealing device includes the end face 251 of the heat exchanger 2 and the wall of an angular cylindrical sleeve part 238 around the pipe 29, forming the first distribution chamber 231. These walls, which are oriented axially, that is, in the main extension direction of the pipe 29, are pressed against the end face 251. Thus, a first refrigerant fluid flow FR from the second outlets 34, 340 of the connection blocks 3, 30 enters the holes 222 of the end face 251 and is located sealingly in the angular cylindrical sleeve part 238 relative to the second distribution chamber 233 supplied by a second refrigerant fluid flow FR from the first outlets 32, 320 of the connection blocks 3, 30.

[0091] When the first and second distribution chambers 231 and 233 are partially delimited by the walls of a first helical coil 234 and a second helical coil 236 wound around the pipe 29, as Figure 8 and 10 shown in the second embodiment variant, Figure 7 the inlet sealing device visible therein includes the end face 251 of the heat exchanger 2, the cylindrical envelope 235, and a first helical plug 225 and a second helical plug 227. The first helical plug 225 originates from the wall of the first helical coil 234 and extends axially towards the end face 251, and the second helical plug 227 originates from the wall of the second helical coil 236 and extends axially towards the end face 251. By pressing against the end face 251 of the heat exchanger 2, the first helical plug 225 and the second helical plug 227 sealingly separate the respective inlets 221 and 223 of the first distribution chamber 231 and the second distribution chamber 233.

[0092] Thus, the first inlet 221 of the first distribution chamber 231 is axially bounded by the part of the end face 251 that includes the hole 222 corresponding to this first inlet 221, and is radially bounded by the second helical spiral 236, and is radially bounded by the cylindrical envelope 235, and is radially bounded by the pipe 29, and is angularly bounded by the second helical plug 227, which triggers the wall of the second spiral 236.

[0093] The first helical plug 225 angularly prevents the first flow from combining with the second distribution chamber 233 along the axial length of the first helical plug 225. The first flow is forced to flow axially between the first helical plug 225 and the wall of the second spiral 236 in this first inlet 221, that is, is forced to engage between the surface of the wall of the first spiral 234 and the surface of the wall of the second spiral 236, thereby defining the first distribution chamber 231.

[0094] Similarly, the second inlet 223 of the second distribution chamber 233 is axially bounded by the part of the end face 251 that includes the hole 224 corresponding to this second inlet 223, and is bounded by the first helical spiral 234 in another part, is radially bounded by the cylindrical envelope 235, and is bounded by the pipe 29 in another part, and is angularly bounded by the first helical plug 225 that triggers the wall of the first spiral 234.

[0095] The second helical plug 227 angularly prevents the second flow from combining with the first distribution chamber 231 along the axial length of the second helical plug 227. The second flow is forced to flow axially between the second helical plug 227 and the wall of the first spiral 234 in this second inlet 223, that is, is forced to engage between the other surface of the wall of the second spiral 236 and the other surface of the wall of the first spiral 234, thereby defining the second distribution chamber 233.

[0096] In Figure 8 In the cross-section of a part of the shown cooling device 1, this second embodiment variant of the present invention with the connection block 30 is shown. The first flow and the second flow of the refrigerant fluid FR leaving the expansion valve 6 to reach the first inlet 221 and the second inlet 223 of the intake orifice 22 respectively are shown by arrows. Of course, this second embodiment variant can also be used with the connection block 3.

[0097] In this secondary embodiment variant of the present invention, as in the main embodiment variant of the present invention, one of the plates 254 forming the plate bundle of the heat exchanger 2 (which is located between the first body 25 and the second body 27 of the heat exchanger 2) tightly surrounds the inlet manifold 23 to prevent the refrigerant fluid from being transferred from the first body 25 to the second body 27 outside the inlet manifold 23.

[0098] Figure 9The refrigerant fluid and the heat transfer liquid H in the heat exchanger 2 are now schematically described. 2 O paths.

[0099] The heat exchanger 2 is formed by a bundle of plates that are brazed together and form channels therebetween. More specifically, the plate bundle forms an alternation of channels for the refrigerant fluid FR and channels for the heat transfer liquid H 2 O.

[0100] The refrigerant fluid FR and the heat transfer liquid H 2 O enter the heat exchanger 2 via the inlet manifold 23 for the refrigerant fluid of the heat exchanger 2 and the inlet 26 for the heat transfer liquid H 2 O of the heat exchanger 2, respectively. The inlet manifold 23 includes an air inlet orifice 22 for the refrigerant fluid FR.

[0101] The flow channels between the plates allow the refrigerant fluid FR and the heat transfer liquid H 2 O to be discharged via the discharge orifice 24 of the heat exchanger 2 and the outlet 28 for the heat transfer liquid of the heat exchanger 2, respectively.

[0102] The plate bundle of the heat exchanger 2 includes:

[0103] A first plurality of plates 251, 252, 253, 254, between which a first channel is arranged for receiving the refrigerant fluid FR and defining a first body 25 of the heat exchanger 2, and

[0104] A second plurality of plates 271, 272, 273, 274, between which a second channel is arranged for receiving the refrigerant fluid FR and defining a second body 27 of the heat exchanger 2, the second channel being arranged on a side opposite to the air inlet orifice 22 with respect to the first body 25, and the distribution of the refrigerant fluid FR can be managed independently in the first channel and the second channel.

[0105] For simplicity, in Figure 9 and Figure 10 the heat exchanger 2 includes only two first channels and two second channels. Of course, the heat exchanger 2 according to the present invention typically includes more first channels and second channels.

[0106] One first channel for the refrigerant fluid FR is formed between the plates 251 and 252, and another first channel for the refrigerant fluid FR is formed between the plates 253 and 254. In the first body 25 of the heat exchanger 2, one channel for the heat transfer liquid is formed between the plates 252 and 253, and another channel for the heat transfer liquid is formed between the plates 254 and 271.

[0107] A second channel for the refrigerant fluid FR is formed between plates 271 and 272, and another second channel for the refrigerant fluid FR is formed between plates 273 and 274. In the second body 27 of the heat exchanger 2, a channel for the heat transfer liquid H 2 O is formed between plates 272 and 273, and another channel for the heat transfer liquid is formed between plate 274 and the end plate 211 of the heat exchanger 2, from which the discharge orifice 24 exits.

[0108] In each channel, the refrigerant fluid FR or the heat transfer liquid H 2 O is shown as entering the channel via a solid-line arrow and, after traveling in a U-shape in the channel, exiting again via a dashed-line arrow towards the discharge orifice 24 or the outlet 28 for the heat transfer liquid H 2 O.

[0109] As described above, in order to equalize the distribution of the refrigerant fluid FR in the heat exchanger 2, the refrigerant fluid FR at the outlets of the expansion member 6 or the first expansion member 64 and the second expansion member 62 is divided into two streams. The first stream is brought to the first inlet 221 of the intake orifice 22, serving the first distribution chamber 231 for distributing the first stream of the refrigerant fluid FR in the first body 25 of the heat exchanger 2. The second stream is brought to the second inlet 223 of the intake orifice 22, serving the second distribution chamber 233 for distributing the second stream of the refrigerant fluid FR in the second body 27 of the heat exchanger 2.

[0110] With respect to the second distribution chamber 233, the second stream is distributed to the second channel, and the first stream is hermetically distributed by the first distribution chamber 231 to the first channel. Thus, the inlet manifold 23 is capable of supplying a first flow rate to the first channel and a second flow rate to the second channel, the flow rates having substantially the same value, thereby equalizing the distribution of the refrigerant fluid FR in the heat exchanger 2. Depending on the cooling requirements of the vehicle components, potentially only the first body of the heat exchanger or the second body of the heat exchanger 2 is used. In this case, only the first stream or the second stream is sent to the heat exchanger 2.

[0111] In the main embodiment variant of the present invention presented in this Figure 9 the first distribution chamber 231 is formed by the wall of an angular cylindrical sleeve portion 238 surrounding the pipe 29, the angular cylindrical sleeve portion 238 axially extending from the end face 251 of the heat exchanger 2 to the end of the first channel at the interface with the second body 27 of the heat exchanger 2, but not exceeding that end face. The wall of the angular cylindrical sleeve portion 238 is closed and sealed, except for:

[0112] contacting the end face 251 of the heat exchanger 2 in order to receive the refrigerant fluid FR from the first inlet 221 of the heat exchanger 2 for the refrigerant fluid FR, and

[0113] The first channel faced; the hole 237 is arranged on the angled cylindrical sleeve part 238 facing the first channel, such that the refrigerant fluid FR circulates from the first distribution chamber 231 to the first channel.

[0114] It should be noted that the base of the angled cylindrical sleeve part 238 located between the first channel and the second channel forms a sealing barrier between the first channel and the second channel.

[0115] The second distribution chamber 233 is defined by a cylindrical envelope 235, which exists around the pipe 29 all the time except for the angled cylindrical sleeve part 238 that defines the first distribution chamber 231. The cylindrical envelope 235 is sealed except for:

[0116] Contacting the end face 251 of the heat exchanger 2 so as to receive the refrigerant fluid FR from the second inlet 223 of the heat exchanger 2 for the refrigerant fluid FR, and

[0117] The second channel faced; the hole 239 is arranged on this part of the cylindrical envelope 235, such that the refrigerant fluid FR circulates from the second distribution chamber 233 to the second channel.

[0118] Figure 10 A second embodiment variant of the present invention is shown, in which the distribution chambers 231 and 233 are each formed by a volume included between the wall of the first helical spiral 234 and the wall of the second helical spiral 236, and the walls of the first helical spiral 234 and the second helical spiral 236 are wound around the pipe 29. The spirals 234 and 236 extend radially in the inlets of the first channel and the second channel. These spirals are preferably ribs that extend radially around the pipe 29 and are integrally manufactured with the pipe 29.

[0119] More specifically, the first helical spiral 234 guides the first flow from the first inlet 221 of the intake orifice 22 to the first gap located between the first spiral 234 and the second spiral 236 and facing the first channel. Similarly, the second helical spiral 236 conducts the second flow from the second inlet 223 of the intake orifice 22 to the second gap between the first spiral 234 and the second spiral 236 and facing the second channel. In this second embodiment variant of the present invention, the first gap and the second gap have the same width, for example, especially when the number of the first channels is equal to the number of the second channels.

[0120] To seal the first body 25 relative to the second body 27 for distributing the refrigerant fluid FR, the inlet manifold 23 includes a first sealing barrier 232 between the first distribution chamber 231 and the second body 27. In this variant of the embodiment of the present invention, the first sealing barrier is produced in the form of a screw plug that is located between the helicoids 234 and 236 and blocks the flow path of the first flow of the refrigerant fluid FR. Thus, the first flow cannot reach the second channel.

[0121] A cylindrical envelope 235 forms a second sealing barrier 235 between the second distribution chamber 233 and the first body 25. The second sealing barrier tightly and sealingly encloses the helicoids 234 and 236. The cylindrical envelope 235 blocks the flow path of the second flow from entering the first channel. However, the hole 230 in the cylindrical envelope 235 allows the first flow to enter the first channel.

[0122] In this second variant of the embodiment of the present invention, the cylindrical envelope 235 axially extends, for example, from the end face 251 of the heat exchanger 2 to the end of the first channel at the interface with the second body 27 of the heat exchanger 2, but does not extend beyond this end. Instead, if the cylindrical envelope 235 axially extends from the end face 251 to the region of the second end 292 of the pipe 29 that is connected to the high-pressure outlet manifold 44 of the internal heat exchanger 4, a hole similar to the hole 239 is arranged, for example, in the cylindrical envelope 235 to allow the second flow to enter the second channel. In this minor variant of the embodiment of the present invention, the cylindrical envelope 235 is replaced in the variant by a helical envelope that only covers the gap between the first helical wall 234 and the second helical wall 236 that defines the second distribution chamber 233 and only axially extends from the end face 251 of the heat exchanger 2 to the end of the first channel at the interface with the second body 27 of the heat exchanger 2.

[0123] Figure 11 The use of the connection block 3 according to the present invention and the cooling device according to the present invention in the cooling system of an electric vehicle or a hybrid vehicle is now shown. The vehicle includes a battery 84, a power electronics unit 86, and an electric motor 82, and these components are cooled by a circuit for a heat transfer liquid H 2 O (such as water), and the circulation of this circuit is ensured by a pump 80. The cooled heat transfer liquid H 2 O enters the heat exchanger 2 via the inlet 26 for the heat transfer liquid and is discharged from the heat exchanger 2 via the outlet 28 for the heat transfer liquid. This cooling is achieved by contacting the refrigerant fluid FR that also circulates in the heat exchanger 2 in a separate refrigerant fluid circuit.

[0124] The heat transfer liquid H 2The refrigerant fluid FR that obtains heat energy exits the heat exchanger 2 at a low pressure through the discharge orifice 24 of the heat exchanger 2, and is then conveyed to the high-pressure inlet manifold 46 of the internal heat exchanger 4. The refrigerant fluid FR exits the high-pressure inlet manifold 46 through the low-pressure outlet manifold 48 of the internal heat exchanger 4 so as to be conveyed to the compressor 7. This low-pressure branch for the refrigerant fluid FR in the internal heat exchanger 4 enables the cooling of the high-pressure branch of the circuit for the refrigerant fluid FR, as described below.

[0125] The refrigerant fluid FR compressed by the compressor 7 is then condensed by the condenser 9. A part of the condensed refrigerant fluid FR is guided to the expansion member 11 and then evaporates in the evaporator 5 of the air-conditioning system for the vehicle interior. Another part of the condensed refrigerant fluid FR is sent to the high-pressure inlet manifold 42 of the internal heat exchanger 4 and exits the internal heat exchanger 4 through the high-pressure outlet manifold 44 of the internal heat exchanger 4. This high-pressure branch of the circuit for the refrigerant fluid FR is cooled in the internal heat exchanger 4 by the above-mentioned low-pressure branch of the circuit for the refrigerant fluid. The refrigerant fluid FR from the high-pressure outlet manifold 44 then expands through the first expansion member 64 and the second expansion member 62, and then enters the intake orifice 22 for the refrigerant fluid of the heat exchanger 2 through the connection block 3 so as to cool the heat transfer liquid H that also passes through the heat exchanger 2. 2 O.

[0126] Of course, the present invention is not limited to the embodiments just described, and many modifications can be made to these embodiments without departing from the scope of the present invention.

Claims

1. A connection block (3, 30), the connection block (3, 30) being configured to sealingly connect at least one expansion member (6, 62, 64) to a heat exchanger (2), the connection block (3, 30) at least comprises: an inlet (37, 370) for a refrigerant fluid (FR), branches (310), a first flow channel and a second flow channel (33, 35, 330, 350) inside the connection block (3, 30), The connection block (3, 30) is characterized in that the connection block further comprises: a first outlet and a second outlet (32, 34, 320, 340) for the refrigerant fluid (FR) that are separated from each other, an inlet (37, 370) for the refrigerant fluid (FR), and the inlet (37, 370) and the first outlet and the second outlet (32, 34, 320, 340) are arranged on a contact surface (36, 360) in contact with the heat exchanger (2), and receiving means (38, 39, 380) configured to receive the at least one expansion member (6, 62, 64), and connected to the inlet (37, 370) for the refrigerant fluid (FR) through the branch (310), connected to the first outlet (32, 320) for the refrigerant fluid (FR) through the first flow channel (33, 330), and connected to the second outlet (34, 340) for the refrigerant fluid (FR) through the second flow channel (35, 350).

2. The connection block (3, 30) according to claim 1, wherein the receiving means (38, 39, 380), the flow channels (33, 35, 330, 350) and the branch (310) are in the form of cuts in the connection block (3, 30), and the form of the cuts is in the form of axially parallel cylinders.

3. The connection block (3, 30) according to claim 1 or 2, wherein the receiving means (38, 39, 380) forms a first cylindrical cut orthogonal to the contact surface (36, 360), the first flow channel (33, 330) forms a second cylindrical cut orthogonal to the contact surface (36, 360), and the first cylindrical cut joins the second cylindrical cut at a part of the connection block (3, 30), and at this part, a part of the first cylindrical cut is secant to a part of the second cylindrical cut without completely covering the second cylindrical cut.

4. The connection block (30) according to any one of claims 1 to 3, wherein the receiving device (380) forms a receiving chamber, the receiving chamber including a support surface (386) capable of receiving an inlet of the at least one expansion member (6) and an enclosed volume (388) capable of receiving refrigerant fluid (FR) at an outlet of the at least one expansion member (6), the branch (310) connecting the support surface (386) to an inlet (370) for the refrigerant fluid (FR), the first flow channel (330) connecting the enclosed volume (388) to a first outlet (320) for the refrigerant fluid (FR), and the second flow channel (350) connecting the enclosed volume (388) to a second outlet (340) for the refrigerant fluid (FR).

5. The connection block (3) according to any one of claims 1 to 3, wherein the at least one expansion member (62, 64) includes a first expansion member (64) and a second expansion member (62), the receiving devices (38, 39) include a first receiving chamber (38) for receiving the first expansion member (64) and a second receiving chamber (39) for receiving the second expansion member (62), and wherein: the first receiving chamber (38) is connected to an inlet (37) for the refrigerant fluid (FR) through the branch and is connected to a first outlet (32) for the refrigerant fluid (FR) through the first flow channel (33), and the second receiving chamber (39) is connected to an inlet (37) for the refrigerant fluid (FR) through the branch and is connected to a second outlet (34) for the refrigerant fluid (FR) through the second flow channel (35).

6. The connection block (3) according to claim 5, wherein the contact surface has a first groove (31) forming the inlet (37) for the refrigerant fluid (FR) and a part of the branch, the branch including a first pipeline (312) starting from the first groove (31) and leading to the first receiving chamber (38) and a second pipeline (314) starting from the first groove (31) and leading to the second receiving chamber (39).

7. The connection block (3) according to claim 6, wherein the contact surface (36) has a second groove that supplies the second outlet (34) with the refrigerant fluid (FR) and is configured to connect an air inlet orifice (22) of the heat exchanger (2) to a first end of the second flow channel (35), the second flow channel (35) being formed in the form of a cylindrical cut, having a second end opposite to the first end and forming an opening in the second receiving chamber (39).

8. A cooling device (1) comprising a connection block (3, 30) according to any one of claims 1 to 7, a heat exchanger (2) and an internal heat exchanger (4), the internal heat exchanger (4) including a high-pressure outlet manifold (44) and a low-pressure inlet manifold (46) on a terminal plate of the internal heat exchanger (4), and wherein: The contact surfaces (36, 360) of the connection blocks (3, 30) are brazed or welded to the end face (251) of the heat exchanger (2), and the end plates (211) of the connection blocks on the opposite side of the end face are themselves brazed or welded to the terminal plates of the internal heat exchanger (4). The high-pressure outlet manifold (44) is connected to a pipe (29) that passes through the heat exchanger (2) and serves as an inlet (37, 370) for the refrigerant fluid (FR) of the connection blocks (3, 30). The low-pressure inlet manifold (46) is connected to a discharge orifice (24) for the refrigerant fluid (FR) of the heat exchanger (2) on the end plate (211), and The heat exchanger (2) comprises: - For one part, a first distribution chamber (231) and a first inlet (221) for the refrigerant fluid (FR), the first distribution chamber (231) serving the first body (25) of the heat exchanger (2), and the first inlet (221) leading to the first distribution chamber (231), - For another part, a second distribution chamber (233) and a second inlet (223) for the refrigerant fluid (FR), the second distribution chamber (223) serving the second body (27) of the heat exchanger (2), and the second inlet (223) leading to the second distribution chamber (233), The first outlet (32, 320) for the refrigerant fluid (FR) of the connection blocks (3, 30) is connected to the second inlet (223) for the refrigerant fluid (FR) of the heat exchanger (2), and the second outlet (34, 340) for the refrigerant fluid (FR) of the connection blocks (3, 30) is connected to the first inlet (221) for the refrigerant fluid (FR) of the heat exchanger (2).

9. The cooling device (1) according to claim 8, wherein the first body (25) of the heat exchanger (2) comprises a plurality of first plates (251, 252, 253, 254) between which a first channel for receiving the refrigerant fluid (FR) is arranged, and the second body (27) of the heat exchanger (2) comprises a plurality of second plates (271, 272, 273, 274) between which a second channel for receiving the refrigerant fluid (FR) is arranged, and wherein, the first distribution chamber (231) and the second distribution chamber (233) are able to supply a first flow rate of the refrigerant fluid (FR) to the first channel and a second flow rate of the refrigerant fluid (FR) to the second channel, respectively, in a sealed manner relative to each other.

10. The cooling device (1) according to claim 9, wherein the first distribution chamber (231) and the second distribution chamber (233) are arranged around the pipe (29), the pipe (29) orthogonally passing through the plates of the plurality of first plates (251, 252, 253, 254, 271, 272, 273, 274) and the plurality of second plates (251, 252, 253, 254, 271, 272, 273, 274), and wherein, the cooling device (1) includes a sealing barrier between the first distribution chamber and the second distribution chamber, the sealing barrier forming an angled cylindrical sleeve portion (238) around the pipe (29) and having an opening in the end face (251) of the heat exchanger (2).

11. The cooling device (1) according to claim 9, wherein the first distribution chamber (231) and the second distribution chamber (232) are at least partially defined by a first helical coil (234) and a second helical coil (236) wound around the pipe (29).

12. The cooling device (1) according to the preceding claim, including a first sealing barrier (232) between the first distribution chamber (231) and the second body (27) of the heat exchanger (2), the first sealing barrier being a screw plug, and a second sealing barrier (235) between the second distribution chamber (233) and the first body (25) of the heat exchanger (2), the second sealing barrier being formed by a cylindrical envelope around the first and second helical coils (234, 236) facing the first channel, the cylindrical envelope including holes between the first distribution chamber (231) and each of the first channels.

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