Connection block for heat exchanger and cooling device comprising same

Abstract

The present invention relates to a connection block (30) which is 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) with the heat exchanger; and - receiving means (380) for receiving the expansion member, which are connected by a branch (310) of the connection block (30) to the refrigerant inlet (370), by a first passage (330) of the connection block (30) to the first refrigerant outlet (320) and by a second passage (350) of the connection block (30) to the second refrigerant outlet (340).

Description

[0001] Connection block for heat exchanger and cooling device comprising them

[0002] The present invention relates to the field of thermodynamics and more specifically concerns a connection block for a heat exchanger, and a cooling device including this connection block, intended in particular to be used for cooling components of a vehicle.

[0003] In an electric or hybrid vehicle, it is common to cool the electric battery, the electric motor and the vehicle's power electronics by a heat transfer fluid such as water, circulating in a heat transfer fluid circuit running through these components to be cooled, the heat transfer fluid itself being cooled by a heat exchanger receiving on the one hand the heat transfer fluid, and on the other hand a refrigerant fluid. The refrigerant fluid undergoes a thermodynamic cycle in a separate refrigerant circuit using for example a compressor, a condenser, an internal heat exchanger and an expansion member.

[0004] When quickly charging the electric battery of an electric or hybrid vehicle, the electric current being high, the thermal power to be dissipated to cool the electric battery is significant, for example in the order of loooo Watts. Similarly, when the electric or hybrid vehicle is traveling at high speed, the thermal power to be dissipated in the electric motor, the power electronics and the electric battery is significant and therefore requires a heat exchanger sized accordingly, called "high performance".

[0005] Since the heat exchanger is made up of a bundle of stacked and brazed plates delimiting channels for the circulation of the refrigerant fluid or the heat transfer liquid, the number of plates in the heat exchanger of the electric or hybrid vehicle is all the more important as it must dissipate a high thermal power.

[0006] However, during less energy-intensive use of the electric or hybrid vehicle, for example during slow charging of the electric battery of the electric vehicle, or when driving at low speed of the electric vehicle, the thermal power of the electric battery to be dissipated is lower, for example of the order of 4000 Watts. However, the efficiency of a "high-performance" heat exchanger is not optimal at medium or low load, because the number of plates and the dimensioning of the channels of such a heat exchanger have been optimized for use at high load. At medium or low load, the distribution of the liquid and gas phases of the refrigerant in the heat exchanger is therefore not homogeneous and is not very efficient.

[0007] There is therefore a need for a high-performance heat exchanger, particularly for an electric or hybrid vehicle, with improved thermal power and efficiency at low and medium loads, allowing the cooling of vehicle components. The vehicle components to be cooled preferably include the electric battery, the electric motor, the power electronics but also the vehicle interior.

[0008] This need for performance is coupled, in electric and hybrid vehicles, with a need for compactness of the cooling system in the vehicle's engine compartment. Indeed, since these vehicles have both an electric motor and a combustion engine, for example, the size of each component must be limited as much as possible to accommodate these two motors and their associated systems in the engine compartment. This means being able to connect the high-performance heat exchanger to the other elements of the cooling system without requiring bulky external tubing.

[0009] The present invention at least partially overcomes the drawbacks of the prior art by providing, on the one hand, a connection block for a high-performance heat exchanger, making it possible to avoid coupling this heat exchanger by pipes to one or more expansion members, and, on the other hand, a compact cooling device. This compact cooling device includes the connection block according to the invention, as well as a high-performance heat exchanger, in which the distribution of the refrigerant fluid is homogenized from an inlet to an outlet of the heat exchanger at low, medium or high load.

[0010] To this end, the invention proposes a connection block configured to tightly connect at least one expansion member to a heat exchanger, the connection block comprising at least:

[0011] - a refrigerant fluid inlet,

[0012] - a branch, a first and a second internal passages to the connection block, the connection block being characterized in that it further comprises:

[0013] - a first and a second refrigerant outlets distinct from each other, the inlet and the first and second refrigerant outlets being arranged on a contact surface with the heat exchanger, and

[0014] - receiving means intended to receive the at least one expansion member, connected by the branch to the refrigerant fluid inlet, by the first passage to the first refrigerant fluid outlet, and by the second passage to the second refrigerant fluid outlet.

[0015] Thanks to the connection block according to the invention, the heat exchanger can be connected to one or more expansion members without specific pipes. Indeed, the connection block has at least as many outlets as expansion members, these outlets being directly arranged on the contact surface with the heat exchanger. The connection block therefore allows the heat exchanger to receive several flows of refrigerant fluid and therefore to distribute them separately in one or more bodies of the heat exchanger, in order to improve the distribution thereof, and in particular to reduce pressure losses.

[0016] In addition, the expansion member(s) are connected to the connection block without tubing, using the receiving means of the connection block. This is preferably a single piece and made of aluminum, but other materials can of course be used, in particular aluminum alloys, and the connection block can also be made in several pieces.

[0017] The branch of the connection block has two or more ends for connecting the input of the connection block to the receiving means, depending on their arrangement, the receiving means possibly comprising one or more receiving chambers.

[0018] The contact surface between the connection block and the heat exchanger is substantially flat, in the sense that it comprises at least one flat surface allowing, by brazing or welding to a cheek of the heat exchanger, to form sealed connections on the one hand between a high-pressure refrigerant fluid outlet arranged on this cheek and the refrigerant fluid inlet of the connection block, and on the other hand between each refrigerant fluid outlet of the connection block and at least one corresponding inlet of the heat exchanger.

[0019] According to an advantageous characteristic of the connection block according to the invention, the receiving means, the passages and the branch take the form of recesses in the connection block, in the form of cylinders whose axes are parallel. These axes are preferably orthogonal to the contact surface of the connection block. This production of the receiving means, the passages and the branch internal to the connection block is simple to machine. It can in particular be done by drilling in the connection block, advantageously parallelepipedal and compact. As a variant, these recesses are produced in the form of right prisms, of height orthogonal to the contact surface of the connection block.

[0020] Advantageously, the receiving means form a first cylindrical recess orthogonal to the contact surface, the first passage forms a second cylindrical recess orthogonal to the contact surface, and the first cylindrical recess joins the second cylindrical recess at a portion of the connection block in which a section of the first cylindrical recess intersects a section of the second cylindrical recess, without completely covering it. This characteristic of the connection block also makes it possible to give it compactness.

[0021] In one embodiment, the receiving means form a receiving chamber comprising a bearing surface capable of receiving an inlet of said at least one expansion member and a closed volume capable of receiving a refrigerant fluid at the outlet of said at least one expansion member, the branch connecting the bearing surface to the refrigerant fluid inlet, the first passage connecting the closed volume to the first refrigerant fluid outlet and the second passage connecting the closed volume to the second refrigerant fluid outlet. 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, the other between one or more outlets of the expansion member and the first and second passages.

[0022] In another embodiment of the invention, said at least one expansion member comprises a first expansion member and a second expansion member, the receiving means comprise a first receiving chamber intended to receive the first expansion member and a second receiving chamber intended to receive the second expansion member, and:

[0023] - the first receiving chamber is connected by the branch to the refrigerant fluid inlet, and by the first passage to the first refrigerant fluid outlet, and

[0024] - the second receiving chamber is connected by the branch to the refrigerant fluid inlet, and by the second passage to the second refrigerant fluid outlet.

[0025] Preferably in this other embodiment:

[0026] - the first receiving chamber comprises a first bearing surface capable of receiving an inlet of the first expansion member, and a first closed volume capable of receiving a refrigerant fluid at the outlet of the first expansion member, the branch connecting the first bearing surface of the first receiving chamber to the refrigerant fluid inlet, and the first passage connecting the first closed volume to the first refrigerant fluid outlet, and

[0027] - the second receiving chamber comprises a second bearing surface capable of receiving an inlet of the second expansion member, and a second closed volume capable of receiving a refrigerant fluid at the outlet of the second expansion member, the branch connecting the second bearing surface of the second receiving chamber to the refrigerant fluid inlet, and the second passage connecting the second closed volume to the second refrigerant fluid outlet.

[0028] In these embodiments, each receiving chamber is for example formed by three coaxial bores of diameter tapering from a surface opposite the contact surface, the smaller diameter bore being configured to receive an inlet of an expansion valve of an expansion member and to form a sealed connection between the inlet of the expansion valve and the branch. The shoulder between the smaller diameter bore and the intermediate diameter bore serves for example as a bearing surface for the inlet of the expansion valve. Alternatively, the inlet of the expansion valve is tightly fitted in the smaller diameter bore or in the branch, so as to achieve this seal.The intermediate diameter bore is configured to form a closed volume between the portion of the expansion member included in the larger diameter bore and the inlet of the expansion valve, the closed volume forming a sealed connection between the outlets of the expansion valve and the first and / or second passages when the expansion member is received in the receiving chamber.

[0029] Advantageously in the other embodiment of the invention, the contact surface of the connection block comprises a first groove forming the refrigerant fluid inlet and a part of the branch, the branch comprising a first conduit starting from the first groove and opening onto the first receiving chamber, and a second conduit starting from the first groove and opening onto the second receiving chamber. This first groove allows efficient distribution of the refrigerant fluid in each receiving chamber of the receiving means.

[0030] Advantageously still in this other embodiment of the invention, the contact surface comprises a second groove supplying the second refrigerant outlet, configured to connect an inlet of the heat exchanger to a first end of the second passage, the second passage being produced in the form of a cylindrical recess and comprising a second end opposite the first end and forming an opening in the second receiving chamber. This second groove makes it possible to efficiently return the refrigerant from the second receiving chamber to the inlet of the heat exchanger.

[0031] The invention also relates to a cooling device comprising a connection block according to the invention, a heat exchanger, and an internal heat exchanger comprising a high pressure outlet manifold and a low pressure inlet manifold on an end plate of the internal heat exchanger, and in which:

[0032] - the contact surface of the connection block is brazed or welded to a cheek of the heat exchanger, an end plate opposite the cheek of which is itself brazed or welded to the end plate of the internal heat exchanger, the high pressure outlet manifold being connected to a pipe passing through the heat exchanger and serving the refrigerant inlet of the connection block, the low pressure inlet manifold being connected to a refrigerant discharge outlet of the heat exchanger on the end plate, and

[0033] - the heat exchanger includes:

[0034] - on the one hand a first distribution chamber serving a first body of the heat exchanger, and a first refrigerant fluid inlet opening onto the first distribution chamber,

[0035] - and on the other hand a second distribution chamber serving a second body of the heat exchanger, and a second refrigerant fluid inlet opening onto the second distribution chamber, the first refrigerant fluid outlet of the connection block being connected to the second refrigerant fluid inlet of the heat exchanger and the second refrigerant fluid outlet of the connection block being connected to the first refrigerant fluid inlet of the heat exchanger. Alternatively, the first refrigerant fluid outlet of the connection block is connected to the first refrigerant fluid inlet of the heat exchanger and the second refrigerant fluid outlet of the connection block is connected to the second refrigerant fluid inlet of the heat exchanger.Thanks to the cooling device according to the invention, the distribution of refrigerant fluid is balanced between the first body of the heat exchanger and the second body of the heat exchanger, which homogenizes this distribution and reduces pressure losses. Thus at low or medium load, the efficiency of the heat exchanger is improved.

[0036] 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 depending on the thermal power to be dissipated. The cooling device according to the invention also has the advantage of being compact.

[0037] The first body of the heat exchanger comprises, for example, a first plurality of plates between which are arranged first channels intended to receive a refrigerant fluid, and the second body of the heat exchanger comprises a second plurality of plates between which are arranged second channels intended to receive the refrigerant fluid, the first distribution chamber and the second distribution chamber being capable of supplying in a sealed manner with respect to each other respectively a first flow rate of refrigerant fluid to the first channels and a second flow rate of refrigerant fluid to the second channels.

[0038] The first and second channels respectively of the first and second bodies are preferably all of identical sections and lengths, and the first flow rate is preferably substantially equal to the second flow rate. The first flow rate may in fact be different from the second flow rate, in particular depending on different pressure losses between the first and second channels, despite an identical structure of the first and second channels.

[0039] In a main embodiment of the invention, the first and second distribution chambers are arranged around a pipe, the latter passing orthogonally through the plates of the first and 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 angular portion of a cylindrical sleeve around the pipe, and having an opening on the cheek of the heat exchanger.

[0040] In a secondary embodiment of the invention, the first and second distribution chambers are at least partly delimited by a first helical spiral and a second helical spiral intermingled with each other around the pipeline.

[0041] In this secondary embodiment of the invention, the cooling device according to the invention comprises, for example, a first sealing barrier between the first distribution chamber and the second body of the heat exchanger, the first sealing barrier being a spiral plug, and a second sealing barrier between the second distribution chamber and the first body of the heat exchanger, formed by a cylindrical casing surrounding the first and second spirals opposite the first channels, the cylindrical casing comprising orifices between the first distribution chamber and each of the first channels. The first and second spirals stop, for example, at the interface between the first channels and the second channels.

[0042] In this secondary embodiment of the invention, the first and second intertwined spirals define, for example, two pitches, the first distribution chamber being defined by a first of said pitches smaller than a second of said pitches, the second pitch defining the second distribution chamber. In this case, the capacity of the first distribution chamber is smaller than the capacity of the second distribution chamber, the number of first channels being less than the number of second channels. The ratio between the number of first channels and the number of second channels, and therefore between the first pitch and the second pitch, is a function of the thermal power that it is desired to dissipate in the first body of the heat exchanger and in the second body of the heat exchanger, these first and second bodies being able to be supplied independently.The dimensioning of the first body is, for example, adapted to the dissipation of low thermal power in a case of low-speed driving of an electric or hybrid vehicle. The dimensioning of the second body is, for example, adapted to the dissipation of medium thermal power in a case of slow charging of an electric or hybrid vehicle. Used together, the first and second bodies make it possible to dissipate high thermal power, particularly in the case of rapid charging of the electric or hybrid vehicle.

[0043] Alternatively, in this secondary embodiment of the invention, the first distribution chamber has a larger capacity than the second distribution chamber, the first pitch being greater than the second pitch and the number of first channels being greater than the number of second channels.

[0044] In yet another implementation, the number of channels of the first body and the second body is the same.

[0045] According to another advantageous characteristic of the cooling device according to the invention, a plate of the heat exchanger arranged 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 chambers, the refrigerant fluid cannot pass from the first body to the second body of the heat exchanger.

[0046] The cooling device according to the invention advantageously further comprises the expansion member or the first and second expansion members.

[0047] Other characteristics and advantages of the invention will become apparent from the following description on the one hand, and from several examples of embodiment given for informational and non-limiting purposes with reference to the attached schematic drawings on the other hand, in which:

[0048] [fig 1] represents a cooling device according to the invention, in a first embodiment of the invention,

[0049] [fig 2] represents a connection block according to the invention, in this first embodiment of the invention,

[0050] [fig 3] represents in section the connection block of figure 2,

[0051] [fig 4] represents a cooling device according to the invention, in a second embodiment of the invention, [fig 5] represents a connection block according to the invention, in the second embodiment of the invention,

[0052] [fig 6] represents in section the connection block of figure 5,

[0053] [fig 7] is a front view of a heat exchanger of the cooling device of figure 1 or 4, in which the cheek of the heat exchanger has been made transparent,

[0054] [fig 8] is a sectional view of the cooling device of figure 1, in a secondary variant embodiment of the invention,

[0055] [fig 9] shows a diagram of a cooling device according to the invention, in a main variant embodiment of the invention,

[0056] [fig 10] schematizes the cooling device of figure 8, and

[0057] [fig 11] represents a cooling system of an electric or hybrid vehicle comprising the cooling device of figure 4.

[0058] In a first embodiment of the invention illustrated in Figure 1, a cooling device 1 according to the invention comprises an expansion member 6, a connection block 30 according to the invention, a heat exchanger 2, and an internal heat exchanger 4.

[0059] The trigger member 6 is electronically controlled.

[0060] The heat exchanger 2 has a heat transfer liquid inlet 26 and a heat transfer liquid outlet 28.

[0061] The internal heat exchanger 4 comprises a free end plate on which are arranged a high pressure inlet manifold 42 for refrigerant fluid and a low pressure outlet manifold 48 for refrigerant fluid. The opposite end plate of the heat exchanger 4 is an end plate brazed to an end plate 211 of the heat exchanger 2, referenced FIG. 9. As shown in this FIG. 9, at the interface between the end plate of the internal heat exchanger 4 and the end plate 211 of the heat exchanger 2, a refrigerant fluid discharge mouth 24 of the heat exchanger 2 is directly in communication with a low pressure inlet manifold 46 of the internal heat exchanger 4. Similarly at this interface, a 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 has a first end 294 opening into an inlet 370 (referenced figure 2) of refrigerant fluid of the connection block 30 while being arranged in an inlet mouth 22 of refrigerant fluid of the heat exchanger 2. The pipe 29 has a second end 292 connected to the high pressure outlet manifold 44 of the internal heat exchanger 4.

[0062] It should be noted that the detail of the refrigerant fluid path in the heat exchanger 2 and the internal heat exchanger 4 will be described in more detail below in relation to figure 9.

[0063] A cheek 251 of the heat exchanger 2, opposite the end plate 211 of the heat exchanger 2, comprising the heat transfer liquid inlet 26 and the heat transfer liquid outlet 28, is brazed to the connection block 30, shown in FIG. 2, on a contact surface 360 ​​of the connection block 30 with the heat exchanger 2.

[0064] The connection block 30 is an aluminum block, in which holes have been made orthogonally to the contact surface 360. In particular, opposite this contact surface 360, means for receiving the expansion member 6 are formed by a receiving chamber 380 made by three coaxial holes 381, 383, 385, of diameter narrowing from the surface of the connection block 30 opposite the contact surface 360. This receiving chamber 380 houses more precisely an expansion valve for the expansion member 6.

[0065] The last bore 385 of smaller diameter of this receiving chamber is itself pierced by a branch 310 giving onto the contact surface 360 ​​of the connection block 30, this branch 310 forming the inlet 370 of refrigerant fluid of the connection block 30. This branch 310 is here also a cylindrical bore, of smaller diameter than the last bore 385 and coaxial with it. The last bore 385 of the receiving chamber 380 has a bearing surface 386, referenced in FIG. 3, enclosing a periphery of the inlet of the expansion valve of the expansion member 6. This bearing surface 386 thus forms a sealed connection between the inlet of the expansion valve of the expansion member 6, and the inlet 370 of refrigerant fluid of the connection block 30. As a variant, the diameter of the branch 310 is identical to that of the last bore 385.In another variant, the inlet of the expansion valve of the expansion member 6 is held against the shoulder between the last bore 385 and the branch 310, to form the sealed connection between the inlet of the expansion valve of the expansion member 6, and the inlet 370 of refrigerant fluid of the connection block 30.

[0066] The part of the expansion member 6 contained in the larger diameter bore 381 of the receiving chamber 380 rests on a shoulder between this larger diameter bore 381 and the intermediate diameter bore 383 of the receiving chamber 380, closing any passage between the larger diameter bore 381 and the intermediate diameter bore 383. The intermediate diameter bore 383 therefore comprises a closed volume 388 between the expansion valve of the expansion member 6 and the cylindrical surface of this intermediate diameter bore 383 housing the part of the expansion valve comprising the refrigerant fluid outlets of this expansion valve. Thus this closed volume 388 receives the refrigerant fluid at the outlet of the expansion valve in a sealed manner.The refrigerant fluid at the outlet of the expansion valve leaves this closed volume 388 through a first passage 330 provided between the cylindrical surface of the bore 383 of intermediate diameter and a first refrigerant fluid outlet 320 of the connection block 30, and also through a second passage 350 provided between the cylindrical surface of the bore 383 of intermediate diameter and a second refrigerant fluid outlet 340 of the connection block 30.

[0067] The first passage 330 is more precisely formed by a first cylindrical bore 322, continued by a second cylindrical bore of smaller diameter which joins the bore 383 of intermediate diameter of the receiving chamber 380 at a portion of the connection block 30. These first and second bores are made orthogonally from the contact surface 360. Seen in section through a plane parallel to the contact surface 360, the portion of the block where the first passage 330 joins the closed volume 388 of the receiving chamber 380 would therefore show the first passage 330 and the receiving chamber 380 in the form of round sections and non-empty intersection but without one being included in the other.In other words, in this parallel plane, the distance between the axis of revolution of the second bore of the first passage 330 and the axis of revolution of the bore 383 of intermediate diameter of the receiving chamber 380 is less than the sum of the radii of the cylinders formed by these bores.

[0068] Alternatively, the first passage 330 opens entirely into the shoulder between the intermediate diameter bore 383 of the receiving chamber 380 and the last smaller diameter bore 385 of the receiving chamber 380.

[0069] The second passage 350 is produced symmetrically to the first passage 330 with respect to a plane orthogonal to the contact surface 360 ​​passing through a diameter of the cylindrical bore forming the branch 310 of the connection block 30.

[0070] Figure 3 also shows the flows followed by a refrigerant fluid FR inside the connection block 30. The refrigerant fluid FR at the outlet of the pipe 29 arrives at high pressure at the inlet 370 of the connection block 30 and enters the expansion valve of the expansion member 6. After expansion in this valve, the refrigerant fluid FR arrives from the outlets of this valve at low pressure in the closed volume 388 and leaves this closed volume 388 through the first passage 330 and through the second passage 350 to the respective outlets 320 and 340 of the connection block 30. This double outlet of the connection block 30 makes it possible to send the low pressure refrigerant fluid FR into the intake mouth 22 via two separate inlets, i.e. a first inlet 221 and a second inlet 223, respectively supplying a first body 25 of the heat exchanger 2 and a second body 27 of the heat exchanger 2, as shown in Figure 8.This separation of the refrigerant fluid FR into two separate flows makes it possible to better control the pressure losses inside the heat exchanger 2 as will be explained below in relation to this figure 8.

[0071] In a second embodiment of the invention illustrated in Figure 4, a cooling device 10 according to the invention comprises a first expansion member 64, a second expansion member 62, a connection block 3 according to the invention as well as the heat exchanger 2 and the internal heat exchanger 4 of the first embodiment of the invention. As in the first embodiment of the invention, the connection block 3 comprises a contact surface 36 (referenced Figure 5) brazed to the cheek 251 of the heat exchanger 2, which is assembled with the internal heat exchanger 4 as in the first embodiment of the invention.

[0072] The expansion members 62 and 64 are electronically controlled. Alternatively, they are thermally controlled.

[0073] The connection block 3 has many similar features to those of the connection block 30 and will therefore be less detailed than the latter. Compared to the connection block 30, the valves of the first and second expansion members 64 and 62 are inserted into the receiving means of the connection block 3, shown in FIG. 5, these receiving means comprising a first receiving chamber 38 housing the expansion valve of the first expansion member 64 and a second receiving chamber 39 housing the expansion valve of the second expansion member 62. These chambers are made in three cylindrical bores in a manner similar to the chamber 380 of the connection block 30. The respective expansion valves of the expansion members 64, 62 are arranged therein in the same manner.

[0074] The refrigerant fluid inlet 37 FR of the connection block 3 is formed by a first groove 31 hollowed out on the contact surface 36. The last bore of smaller diameter of the receiving chamber 38 is itself pierced by a first cylindrical conduit 312 opening into the first groove 31. Similarly, the last bore of smaller diameter of the receiving chamber 39 is itself pierced by a second cylindrical conduit 314 opening into the first groove 31. Thus the receiving chambers 38, 39 are fluidically connected to the refrigerant fluid inlet 37 of the connection block 3 by the same branch internal to the connection block 3, this branch being formed by the first groove 31 and by conduits 312, 314 orthogonal to the contact surface 36 which extend the ends of the first groove 31.

[0075] As in the first embodiment of the invention, a bearing surface 382 (referenced FIG. 6) of the last bore of smaller diameter of the first or second receiving chamber 38, 39 forms a sealed connection between the respective inlet of the expansion valve of the first or second expansion member 64, 62 and respectively the first or second conduit 312, 314, therefore between the inlets of these expansion valves and the inlet 37 of the connection block 3.

[0076] Unlike the first embodiment of the invention, the first receiving chamber 38 is connected to a first outlet 32 ​​only of the connection block 3, by a first passage 33. The first passage 33 is produced in the same way as the first passage 330. In particular, it receives the refrigerant fluid FR at the outlet of the expansion valve of the first expansion member 64, in a sealed manner thanks to a closed volume 384 (referenced figure 6) between this expansion valve and the intermediate diameter bore of the first receiving chamber 38. This sealing is achieved thanks to the tight insertion of this expansion valve in the first receiving chamber 38, in the same way as in the first embodiment of the invention.

[0077] As in the first embodiment, the first passage 33 is formed of a first cylindrical recess 326 followed by a second cylindrical recess of smaller diameter. The first cylindrical recess 326 is arranged opposite the second refrigerant fluid inlet 223 of the heat exchanger 2.

[0078] Likewise, the second receiving chamber 39 is connected to a second outlet 34 only of the connection block 3, by a second passage 35. The second passage 35 is produced in the same way as the second passage 350. In particular, it receives the refrigerant fluid FR at the outlet of the expansion valve of the second expansion member 62, in a sealed manner thanks to a closed volume comprised between this expansion valve and the intermediate diameter bore of the second receiving chamber 39.

[0079] In order to connect the second passage 35 to the first refrigerant fluid inlet 221 of the heat exchanger 2, a second groove is made on the exchange surface 36 of the connection block 3. A first end of this second groove opens into the second passage 35, and a second end of this second groove is arranged opposite the first refrigerant fluid inlet 221 of the heat exchanger 2. Thus the second refrigerant fluid outlet 34 of the connection block 3 is formed by this second groove.

[0080] This second embodiment therefore makes it possible to separately control a first flow of low-pressure refrigerant fluid arriving at the first refrigerant fluid inlet 221 of the heat exchanger 2, from a second flow of low-pressure refrigerant fluid arriving at the second refrigerant fluid inlet 223 of the heat exchanger 2. In fact, the first flow is controlled by the second expansion member 62 while the second flow is controlled by the first expansion member 64.

[0081] The refrigerant fluid flows FR in the connection block 3 are illustrated in dotted lines in Figures 5 and 6.

[0082] Figure 7 shows a part of the heat exchanger 2 at the level of the portion of the cheek 251 of the heat exchanger in contact with the contact surface 36 or 360 of the connection block 3 or 30. In this figure 7, the cheek 251 has been made transparent, only orifices 222 and 224 of this cheek 251 corresponding respectively to the first inlet 221 and to the second inlet 223 of refrigerant fluid of the heat exchanger 2 being represented. In this figure therefore appear in multiple lines the sealing edges of the channels of the heat exchanger 2 as well as in relief the flow disruptors of a first channel of the heat exchanger 2.

[0083] As visible in this figure 7, the first end 294 of the pipe 29 is arranged in the center of the inlet mouth 22 of the heat exchanger 2. This first end 294 projects from the cheek 251 of the heat exchanger 2, so as to be inserted into the cylindrical bore forming the branch 310 of the connection block 30, or into the first groove 31 of the connection block 3, without touching the bottom of the first groove 31 so that the refrigerant circulates towards the first conduit 312 and towards the second conduit 314.

[0084] The first outlet 32, 320 of refrigerant fluid FR of the connection block 3, 30 is placed opposite the orifice 224 of the cheek 251 so as to supply the second inlet 223 of refrigerant fluid of the heat exchanger 2, and the second outlet 34, 340 of refrigerant fluid FR of the connection block 3, 30 is placed opposite the orifice 222 of the cheek 251 so as to supply the first inlet 221 of refrigerant fluid of the heat exchanger 2.

[0085] In order to receive the first flow in the first inlet 221 in a sealed manner relative to the second flow in the second inlet 223, inlet sealing means are arranged at the intake mouth 22.

[0086] As illustrated in Figures 9 and 10, the inlet mouth 22 is itself the end of an inlet manifold 23 passing through the heat exchanger 2, this inlet manifold 23 being surrounded at least in part by a cylindrical casing 235 making it possible to serve in a sealed manner the first body 25 and the second body 27 of the heat exchanger 2. For this purpose, the inlet manifold 23 comprises a first distribution chamber 231 supplied by the first inlet 221 and serving the first body 25 of the heat exchanger 2, and a second distribution chamber 233 supplied by the second inlet 223 and serving the second body 27 of the heat exchanger 2. The first and second distribution chambers 231 and 233 are arranged around the pipe 29, as detailed below.

[0087] When the first and second distribution chambers 231 and 233 are cylindrical angular portions arranged around the pipe 29, as in the main embodiment variant illustrated in FIG. 9, the inlet sealing means comprise the cheek 251 of the heat exchanger 2, as well as walls of an angular portion of cylindrical sleeve 238 around the pipe 29 forming the first distribution chamber 231. These walls, oriented axially, that is to say in the main direction of extension of the pipe 29, are pressed against the cheek 251.Thus the first flow of refrigerant fluid FR coming from the second outlet 34, 340 of the connection block 3, 30 enters the orifice 222 of the cheek 251 and is located in the angular portion of the cylindrical sleeve 238, sealed relative to the second distribution chamber 233 supplied by the second flow of refrigerant fluid FR coming from the first outlet 32, 320 of the connection block 3, 30.

[0088] When the first and second distribution chambers 231 and 233 are partly delimited by the walls of a first helical spiral 234 and a second helical spiral 236 intermingled around the pipe 29, as in the secondary embodiment illustrated in FIGS. 8 and 10, the inlet sealing means visible in FIG. 7 comprise the cheek 251 of the heat exchanger 2, the cylindrical casing 235 as well as a first spiral plug 225 initiating the wall of the first spiral 234 and extending axially towards the cheek 251, and a second spiral plug 227 initiating the wall of the second spiral 236 and extending axially towards the cheek 251. By being pressed against the cheek 251 of the heat exchanger 2, the first and second spiral plugs 225 and 227 separate in a manner seals the respective inlets 221 and 223 of the first and second distribution chambers 231 and 233.

[0089] The first inlet 221 of the first distribution chamber 231 is thus delimited axially on the one hand by a foiled portion 251 comprising the orifice 222 corresponding to this first inlet 221, and on the other hand by the second helical spiral 236, radially on the one hand by the cylindrical casing 235 and on the other hand by the pipe 29, and angularly by the second spiral plug 227 initiating the wall of the second spiral 236.

[0090] The first spiral plug 225 angularly prevents the first flow from joining the second distribution chamber 233 over the axial length of the first spiral plug 225, the first flow being constrained, in this first inlet 221, to flow axially between the first spiral plug 225 and the wall of the second spiral 236, i.e. is constrained to engage between a surface of the wall of the first spiral 234, and a surface of the wall of the second spiral 236, defining the first distribution chamber 231.

[0091] Likewise, the second inlet 223 of the second distribution chamber 233 is delimited axially on the one hand by a cheek portion 251 comprising the orifice 224 corresponding to this second inlet 223, and on the other hand by the first helical spiral 234, radially on the one hand by the cylindrical casing 235 and on the other hand by the pipe 29, and angularly by the first spiral plug 225 initiating the wall of the first spiral 234.

[0092] The second spiral plug 227 angularly prevents the second flow from joining the first distribution chamber 231 over the axial length of the second spiral plug 227, the second flow being constrained, in this second inlet 223, to flow axially between the second spiral plug 227 and the wall of the first spiral 234, i.e. is constrained to engage between another surface of the wall of the second spiral 236, and another surface of the wall of the first spiral 234, defining the second distribution chamber 233.

[0093] In the section of a part of the cooling device 1 shown in Figure 8, illustrating this secondary embodiment of the invention with the connection block 30, the first and second flows of refrigerant fluid FR leaving the expansion valve 6 to reach respectively the first inlet 221 and the second inlet 223 of the intake mouth 22, are represented by arrows. Of course, this secondary embodiment can also be used with the connection block 3.

[0094] In this secondary embodiment of the invention as in the main embodiment of the invention, one of the plates 254 of the bundle of plates forming the heat exchanger 2 and located between the first body 25 of the heat exchanger 2 and the second body 27 of the heat exchanger 2, tightly encloses the inlet manifold 23 in order to prevent the refrigerant fluid from passing from the first body 25 to the second body 27 outside the inlet manifold 23. Figure 9 now schematically describes the path of the refrigerant fluid and a heat transfer liquid H2O in the heat exchanger 2.

[0095] The heat exchanger 2 is formed of a bundle of plates brazed together and between which channels are formed. The bundle of plates forms more precisely an alternation of channels intended for the refrigerant fluid FR and channels intended for the heat transfer fluid H2O.

[0096] The refrigerant fluid FR and the heat transfer fluid H2O enter the heat exchanger 2 through the refrigerant fluid inlet manifold 23 of the heat exchanger 2 and the heat transfer fluid inlet 26 of the heat exchanger 2, respectively. The inlet manifold 23 comprises the refrigerant fluid inlet 22 of the FR.

[0097] Passages between the plates allow the refrigerant FR and the heat transfer fluid H2O to be discharged through the discharge opening 24 of the heat exchanger 2 and the heat transfer fluid outlet 28 of the heat exchanger 2, respectively.

[0098] The plate bundle of heat exchanger 2 comprises:

[0099] - a first plurality of plates 251, 252, 253, 254 between which are arranged first channels intended to receive the refrigerant fluid FR and defining the first body 25 of the heat exchanger 2, and

[0100] - a second plurality of plates 271, 272, 273, 274 between which are arranged second channels intended to receive the refrigerant fluid FR and defining the second body 27 of the heat exchanger 2, arranged opposite the inlet mouth 22 relative to the first body 25, the distribution of refrigerant fluid FR being able to be managed independently in the first channels and the second channels.

[0101] To simplify in Figures 9 and 10, the heat exchanger 2 only has two first channels and two second channels. Of course, the heat exchanger 2 according to the invention generally has many more first and second channels.

[0102] A first refrigerant fluid channel FR is formed between the plates 251 and 252, another first refrigerant fluid channel FR is formed between the plates 253 and 254. In the first body 25 of the heat exchanger 2, a heat transfer liquid channel is formed between the plates 252 and 253 and another heat transfer liquid channel is formed between the plates 254 and 271.

[0103] A second refrigerant fluid channel FR is formed between the plates 271 and 272, another second refrigerant fluid channel FR is formed between the plates 273 and 274. In the second body 27 of the heat exchanger 2, a heat transfer liquid channel H2O is formed between the plates 272 and 273 and another heat transfer liquid channel is formed between the plates 274 and the end plate 211 of the heat exchanger 2 from which the discharge mouth 24 emerges.

[0104] In each channel, the refrigerant fluid FR or the heat transfer liquid H2O is shown arriving in the channel as a solid arrow and leaving, after a U-shaped path in the channel, as a dotted arrow towards the discharge outlet 24 or the outlet 28 of heat transfer liquid H2O.

[0105] As explained previously, in order to homogenize the distribution of refrigerant fluid FR in the heat exchanger 2, the refrigerant fluid FR at the outlet of the expansion member 6, or of the first and second expansion members 64, 62, is separated into two flows. The first flow is brought to the first inlet 221 of the intake mouth 22, serving the first distribution chamber 231 of the first flow of refrigerant fluid FR in the first body 25 of the heat exchanger 2. The second flow is brought to the second inlet 223 of the intake mouth 22, serving the second distribution chamber 233 of the second flow of refrigerant fluid FR in the second body 27 of the heat exchanger 2.

[0106] The first flow is distributed by the first distribution chamber 231 to the first channels in a sealed manner relative to the distribution of the second flow by the second distribution chamber 233 to the second channels. Thus, the inlet manifold 23 is capable of ensuring the supply of a first flow rate to the first channels and a second flow rate to the second channels, of substantially identical values, which homogenizes the distribution of the refrigerant fluid FR in the heat exchanger 2. Depending on the cooling requirements of the vehicle components, only the first body of the heat exchanger or the second body of the heat exchanger 2 is possibly used. In this case, only the first flow or the second flow is sent to the heat exchanger 2.

[0107] In the main embodiment of the invention shown in this figure 9, the first distribution chamber 231 is formed by the walls of the angular portion of cylindrical sleeve 238 around the pipe 29, this angular portion of cylindrical sleeve 238 extending axially from the cheek 251 of the heat exchanger 2 to one end of the first channels at the interface with the second body 27 of the heat exchanger 2, but not beyond. The walls of the angular portion of cylindrical sleeve 238 are closed and sealed except:

[0108] - in contact with the cheek 251 of the heat exchanger 2 so as to receive the refrigerant fluid FR from the first inlet 221 of refrigerant fluid FR of the heat exchanger 2, and

[0109] - opposite the first channels; orifices 237 are arranged on the angular portion of cylindrical sleeve 238 opposite the first channels, so that the refrigerant fluid FR circulates from the first distribution chamber 231 towards the first channels.

[0110] In particular, the base of the angular portion of cylindrical sleeve 238 located between the first channels and the second channels forms a sealing barrier between the first channels and the second channels.

[0111] The second distribution chamber 233 is delimited by the cylindrical casing 235 present all around the pipe 29, except at the level of the angular portion of cylindrical sleeve 238 which delimits the first distribution chamber 231. The cylindrical casing 235 is sealed except:

[0112] - in contact with the cheek 251 of the heat exchanger 2 so as to receive the refrigerant fluid FR from the second inlet 223 of refrigerant fluid FR of the heat exchanger 2, and

[0113] - opposite the second channels; orifices 239 are arranged on this portion of the cylindrical casing 235 so that the refrigerant fluid FR circulates from the second distribution chamber 233 towards the second channels.

[0114] Figure 10 illustrates the secondary embodiment of the invention, in which the distribution chambers 231 and 233 are each formed by a volume comprised between the walls of the first helical spiral 234 and the second helical spiral 236 intermingled around the pipe 29. The spirals 234 and 236 extend radially in the inlets of the first and second channels. These spirals are preferably ribs extending radially around the pipe 29 and made of the same material as the pipe 29.

[0115] More precisely, the first helical spiral 234 conducts the first flow from the first inlet 221 of the intake mouth 22 to first interstices between the first spiral 234 and the second spiral 236 located opposite the first channels. Similarly, the second helical spiral 236 conducts the second flow from the second inlet 223 of the intake mouth 22 to second interstices between the first spiral 234 and the second spiral 236 located opposite the second channels. In this secondary embodiment of the invention, the first and second interstices are, for example, of identical width, in particular when the number of first channels is equal to the number of second channels.

[0116] In order to seal the first body 25 relative to the second body 27 for the distribution of the refrigerant fluid FR, the inlet manifold 23 comprises a first sealing barrier 232 between the first distribution chamber 231 and the second body 27, produced, in this variant embodiment of the invention, in the form of a spiral plug located between the spirals 234 and 236 and blocking the passage of the first flow of refrigerant fluid FR. Thus the first flow cannot reach the second channels.

[0117] The cylindrical casing 235 forms a second sealing barrier 235 between the second distribution chamber 233 and the first body 25, tightly enclosing, in a sealed manner, the spirals 234 and 236. This cylindrical casing 235 blocks the passage of the second flow in the first channels. Orifices 230 in the cylindrical casing 235 nevertheless allow the passage of the first flow in the first channels.

[0118] In this secondary embodiment of the invention, the cylindrical casing 235 extends, for example, axially from the cheek 251 of the heat exchanger 2 to one end of the first channels at the interface with the second body 27 of the heat exchanger 2, but not beyond. If, on the contrary, the cylindrical casing 235 extends axially from the cheek 251 to the level of the second end 292 of the pipe 29 connected to the high-pressure outlet manifold 44 of the internal heat exchanger 4, then orifices similar to the orifices 239 are, for example, arranged in the cylindrical casing 235 to allow the passage of the second flow in the second channels.In this secondary embodiment of the invention, the cylindrical casing 235 is alternatively replaced by a helical casing covering only the gap between the first helical wall 234 and the second helical wall 236 which delimits the second distribution chamber 233, and extending axially only from the cheek 251 of the heat exchanger 2 to one end of the first channels at the interface with the second body 27 of the heat exchanger 2.

[0119] Figure 11 now illustrates a use of the connection block 3 according to the invention and of the cooling device according to the invention, in a cooling system of an electric or hybrid vehicle. The vehicle comprises an electric battery 84, power electronics 86 and an electric machine 82, these components being cooled by a circuit of heat transfer fluid H2O, for example water, the circulation of which is ensured by a pump 80. The heat transfer fluid H2O enters the heat exchanger 2 via the heat transfer fluid inlet 26, and leaves the heat exchanger 2 via the heat transfer fluid outlet 28, being cooled. This cooling takes place in contact with the refrigerant FR also circulating in the heat exchanger 2, in a separate refrigerant circuit.The refrigerant fluid FR having taken calories from the heat transfer liquid H2O, leaves the heat exchanger 2 at low pressure through the discharge opening 24 of the heat exchanger 2, then is sent into the low pressure inlet manifold 46 of an internal heat exchanger 4 from where it leaves through the low pressure outlet manifold 48 of the internal heat exchanger 4 to be sent into a compressor 7. This low pressure branch of the refrigerant fluid FR in the internal heat exchanger 4 makes it possible to cool a high pressure branch of the refrigerant fluid circuit FR as described below.

[0120] The refrigerant fluid FR compressed by the compressor 7 is then condensed by a condenser 9. A portion of the condensed refrigerant fluid FR is directed to an expansion member 11 and then evaporated in an evaporator 5 of an air conditioning system for the passenger compartment of the vehicle. Another portion of the condensed refrigerant fluid FR is sent to the high-pressure inlet manifold 42 of the internal heat exchanger 4, and leaves the internal heat exchanger 4 via the high-pressure outlet manifold 44 of the internal heat exchanger 4. This high-pressure branch of the refrigerant fluid circuit FR is cooled in the internal heat exchanger 4 by the low-pressure branch of the refrigerant fluid circuit mentioned above.The refrigerant fluid FR arriving from the high pressure outlet manifold 44 is then expanded by the first and second expansion members 64 and 62, then enters the refrigerant fluid inlet 22 of the heat exchanger 2 via the connection block 3, to cool the heat transfer liquid H2O also passing through the heat exchanger 2.

[0121] Of course, the invention is not limited to the examples which have just been described and numerous adjustments can be made to these examples without departing from the scope of the invention.

Claims

CLAIMS 1- Connection block (3, 30) configured to tightly connect at least one expansion member (6, 62, 64) to a heat exchanger (2), the connection block (3, 30) comprising at least: - an inlet (37, 370) for refrigerant fluid (FR), - a branch (310), a first and a second passage (33, 35, 330, 350) internal to the connection block (3, 30), the connection block (3, 30) being characterized in that it further comprises: - a first and a second outlet (32, 34, 320, 340) of refrigerant fluid (FR) distinct from each other, the inlet (37, 370) and the first and second outlets (32, 34, 320, 340) of refrigerant fluid (FR) being arranged on a contact surface (36, 360) with the heat exchanger (2), and - receiving means (38, 39, 380) intended to receive the at least one expansion member (6, 62, 64), connected by the branch (310) to the inlet (37, 370) of refrigerant fluid (FR), by the first passage (33, 330) to the first outlet (32, 320) of refrigerant fluid (FR), and by the second passage (35, 350) to the second outlet (34, 340) of refrigerant fluid (FR). 2- Connection block (3, 30) according to claim 1, in which the receiving means (38, 39, 380), the passages (33, 35, 330, 350) and the branch (310) take the form of recesses in the connection block (3, 30), in the form of cylinders whose axes are parallel. 3- Connection block (3, 30) according to claim 1 or 2, in which the receiving means (38, 39, 380) form a first cylindrical recess orthogonal to the contact surface (36, 360), the first passage (33, 330) forms a second cylindrical recess orthogonal to the contact surface (36, 360), and the first cylindrical recess joins the second cylindrical recess at a portion of the connection block (3, 30) in which a section of the first cylindrical recess intersects a section of the second cylindrical recess, without completely covering it. 4- Connection block (30) according to any one of claims 1 to 3, in which the receiving means (380) form a receiving chamber comprising a bearing surface (386) capable of receiving an inlet of said at least one expansion member (6) and a closed volume (388) capable of receiving a refrigerant fluid (FR) at the outlet of said at least one expansion member (6), the branch (310) connecting the support surface (386) to the inlet (370) of refrigerant fluid (FR), the first passage (330) connecting the closed volume (388) to the first outlet (320) of refrigerant fluid (FR) and the second passage (350) connecting the closed volume (388) to the second outlet (340) of refrigerant fluid (FR). 5- Connection block (3) according to any one of claims 1 to 3, wherein said at least one expansion member (62, 64) comprises a first expansion member (64) and a second expansion member (62), the receiving means (38, 39) comprise a first receiving chamber (38) intended to receive the first expansion member (64) and a second receiving chamber (39) intended to receive the second expansion member (62), and wherein: - the first receiving chamber (38) is connected by the branch to the inlet (37) of refrigerant fluid (FR), and by the first passage (33) to the first outlet (32) of refrigerant fluid (FR), and - the second receiving chamber (39) is connected by the branch to the refrigerant fluid (FR) inlet (37), and by the second passage (35) to the second refrigerant fluid outlet (34). 6- Connection block (3) according to claim 5, in which the contact surface comprises a first groove (31) forming the inlet (37) of refrigerant fluid (FR) and a part of the branch, the branch comprising a first conduit (312) starting from the first groove (31) and opening onto the first receiving chamber (38), and a second conduit (314) starting from the first groove (31) and opening onto the second receiving chamber (39). 7- Connection block (3) according to claim 6, in which the contact surface (36) comprises a second groove supplying the second outlet (34) of refrigerant fluid (FR), configured to connect an inlet mouth (22) of the heat exchanger (2) to a first end of the second passage (35), the second passage (35) being produced in the form of a cylindrical recess and having a second end opposite the first end and forming an opening in the second receiving chamber (39). 8- 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) comprising a high pressure outlet manifold (44) and a low pressure inlet manifold (46) on an end plate of the internal heat exchanger (4), and wherein: - the contact surface (36, 360) of the connection block (3, 30) is brazed or welded to a cheek (251) of the heat exchanger (2), an end plate (211) opposite the cheek of which is itself brazed or welded to the end plate of the internal heat exchanger (4), the high pressure outlet manifold (44) being connected to a pipe (29) passing through the heat exchanger (2) and serving the refrigerant fluid (FR) inlet (37, 370) of the connection block (3, 30), the low pressure inlet manifold (46) being connected to a refrigerant fluid (FR) outlet (24) of the heat exchanger (2) on the end plate (211), and - the heat exchanger (2) comprises: - on the one hand a first distribution chamber (231) serving a first body (25) of the heat exchanger (2), and a first inlet (221) of refrigerant fluid (FR) opening onto the first distribution chamber (231), - and on the other hand a second distribution chamber (233) serving a second body (27) of the heat exchanger (2), and a second inlet (223) of refrigerant fluid (FR) opening onto the second distribution chamber (233), the first outlet (32, 320) of refrigerant fluid (FR) of the connection block (3, 30) being connected to the second inlet (223) of refrigerant fluid (FR) of the heat exchanger (2) and the second outlet (34, 340) of refrigerant fluid (FR) of the connection block (3, 30) being connected to the first inlet (221) of refrigerant fluid (FR) of the heat exchanger (2). 9- Cooling device (i) according to the preceding claim, wherein the first body (25) of the heat exchanger (2) comprises a first plurality of plates (251, 252, 253, 254) between which are arranged first channels intended to receive a refrigerant fluid (FR) and the second body (27) of the heat exchanger (2) comprises a second plurality of plates (271, 272, 273, 274) between which are arranged second channels intended to receive the refrigerant fluid (FR), and wherein the first distribution chamber (231) and the second distribution chamber (233) are capable of supplying in a sealed manner with respect to each other respectively a first flow rate of refrigerant fluid (FR) to the first channels and a second flow rate of refrigerant fluid (FR) to the second channels. 10- Cooling device (1) according to the preceding claim, wherein the first and second distribution chambers (231, 233) are arranged around the pipe (29), the latter passing orthogonally through the plates of the first and second plurality of plates (251, 252, 253, 254, 271, 272, 273, 274), and wherein the cooling device (1) comprises a sealing barrier between the first distribution chamber and the second distribution chamber, the sealing barrier forming an angular portion of cylindrical sleeve (238) around the pipe (29), and having an opening on the cheek (251) of the heat exchanger (2). 11- Cooling device (1) according to claim 9, in which the first and second distribution chambers (231, 232) are at least partly delimited by a first helical spiral (234) and a second helical spiral (236) intermingled with each other around the pipe (29). 12- Cooling device (1) according to the preceding claim, comprising 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 spiral plug, and a second sealing barrier (235) between the second ... distribution (233) and the first body (25) of the heat exchanger (2), formed by a cylindrical envelope surrounding the first and second spirals (234, 236) opposite the first channels, the cylindrical envelope comprising orifices between the first distribution chamber (231) and each of the first channels.

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