FR3068452A1 - MULTI-PASS HEAT EXCHANGER COMPRISING A REFRIGERANT FLUID CIRCUIT - Google Patents

Abstract

The subject of the invention is a heat exchanger (5) intended to be traversed by a refrigerant fluid. The heat exchanger (5) comprises a first ply (9) of first tubes (10) and a second ply (11) of second tubes (12). The first ply (9) comprises a first collector (21) which is provided with a refrigerant outlet and which has a plurality of upper compartments, a first upper compartment interposed between a second upper compartment and a third upper compartment . The second ply (11) is provided with a refrigerant inlet mouth. The heat exchanger (5) is equipped with means for supplying (80) the refrigerant fluid which is interposed between the intake port and the first upper compartment, the supply means (80) extending to the less partially inside the second upper compartment.

Description

Multi-pass heat exchanger constituting a refrigerant circuit

The field of the present invention is that of multi-pass heat exchangers constituting a refrigerant circuit fitted to a motor vehicle. The invention relates to such a heat exchanger.

A motor vehicle is commonly equipped with a ventilation, heating and / or air conditioning installation for thermally treating the air present or sent inside a passenger compartment of the motor vehicle. To do this, such an installation is associated with a closed circuit inside which a refrigerant circulates. The refrigerant circuit successively comprises a compressor, a gas condenser or cooler, an expansion member and a heat exchanger. The heat exchanger is housed inside the ventilation, heating and / or air conditioning installation to allow heat exchange between the refrigerant and an air flow circulating inside said installation delivery of the air flow inside the passenger compartment.

According to an operating mode of the refrigerant circuit, the heat exchanger is used as an evaporator to cool the air flow. In this case, the refrigerant is compressed inside the compressor, then the refrigerant is cooled inside the condenser or gas cooler, then the refrigerant undergoes expansion inside the organ and finally the refrigerant captures calories from the air flow inside the heat exchanger.

The document W02010073938A1 describes an evaporator comprising two layers of tubes which are arranged parallel to each other between two longitudinal ends of the evaporator. A first ply of tubes is disposed between an inlet box and a first return box while a second ply of tubes is arranged between an outlet box and a second return box. The inlet box is provided with a coolant inlet, while the outlet box is provided with a coolant outlet. A passage is provided between the first deflection box and the second deflection box to allow the refrigerant to flow from the first ply of tubes to the second ply of tubes.

The evaporator is a multi-pass heat exchanger inside which the refrigerant circulates alternately from the inlet box to the first return box, then from the first return box to the entry box, and alternately from the second return box to the exit box, then from the exit box to the second return box. To do this, shutters are housed inside the inlet box, the outlet box as well as inside the first and second return boxes. The shutter housed inside the inlet box is provided with an orifice to allow the coolant to flow through it inside the inlet box.

Inside the ventilation, heating and / or air conditioning installation, the air flow passes successively through the second layer, then the first layer of the multi-pass evaporator.

A first drawback of the arrangement of such an evaporator lies in the fact that the air flow passes first through the second layer, that is to say the hottest layer, then the first layer, it that is to say the coldest tablecloth.

A second drawback of the arrangement of such an evaporator lies in the fact that a central zone of the evaporator is insufficiently supplied with the coldest refrigerant to cool as efficiently as possible an air flow passing through the central zone.

In general, such an organization is not optimal from the point of view of the homogenization of the distribution of refrigerant fluid inside the evaporator. This results in heterogeneity of a temperature of various points of surface of the evaporator which induces a heterogeneity of a temperature of the air flow at the outlet of the evaporator, which is unsatisfactory.

An object of the invention is to perfect the homogeneity of the distribution of refrigerant fluid inside the heat exchanger, and in particular inside the first tubes, in order to finally improve its efficiency and its yield, in view to deliver a flow of air inside the passenger compartment at the desired temperature.

Another object of the invention is to optimize an exchange of calories between the refrigerant circulating inside the first tubes, in particular in a central zone of the heat exchanger, and an air flow circulating through the installation of ventilation, heating and / or air conditioning.

A heat exchanger of the present invention is a heat exchanger intended to be traversed by a refrigerant fluid. The heat exchanger comprises a first layer of first tubes and a second layer of second tubes. The first layer comprises a first collector which is provided with a coolant discharge mouth and which comprises a plurality of upper compartments including a first upper compartment interposed between a second upper compartment and a third upper compartment. The second layer is provided with an inlet for the coolant.

According to the present invention, the heat exchanger is equipped with a means for supplying the coolant which is interposed between the inlet mouth and the first upper compartment, the supply means extending at least partially to the inside the second upper compartment.

One effect of such a combination lies in the possibility of bringing the coolant into a central pass of the heat exchanger while maintaining a conventional connection to the rest of the coolant circuit, that is to say where the pipe coolant inlet and the coolant drain line are side by side.

According to one aspect of the invention, the supply means comprises at least one channel which is housed inside the second upper compartment. It is understood here that at least part of the channel, and advantageously all of it, encroaches on a volume delimited by the second upper compartment. The position of this channel can be coaxial with the second upper compartment, but it can also be offset transversely or laterally in the second upper compartment. Such arrangements make it possible to arrange the channel so as to have as little impact as possible on the circulation of the coolant within the second upper compartment.

The supply means may include at least one chamber interposed between the channel and the intake mouth. Such a chamber transfers the refrigerant, which enters the heat exchanger through a plane which fits from the second layer, to the first layer, for its circulation in the channel.

According to an exemplary embodiment, the chamber comprises a groove connected directly to a cavity, the intake mouth opening directly into the cavity, while the channel opens directly into the groove. The cavity has a section identical, or substantially identical, to the intake mouth. On the other hand, the groove has a volume less than the volume of the cavity. The cavity is for example cylindrical, in particular circular, while the groove is mostly straight.

According to one example, the chamber extends along a straight line which falls within a plane parallel to a lateral plane of the heat exchanger, the latter being orthogonal to a longitudinal plane defining a face inlet of an air flow in the heat exchanger. The line in question can advantageously be perpendicular to the longitudinal plane in which the entry face of the air flow in the heat exchanger is inscribed.

The heat exchanger may include an intermediate piece in the thickness of which the chamber is formed. The groove and the cavity are space zones produced in the intermediate piece, such spaces being intended to be used by the refrigerant. The intermediate piece thus forms an interface between the conduits of the refrigerant fluid circuit and the heat exchanger, such an interface being configured to channel the coolant antrum in the heat exchanger by the second layer and take it into the first tablecloth, especially in the first upper compartment of the first collector.

According to an example, the intermediate part comprises a first orifice and a second orifice which each open out through a first face and a second face of the intermediate part. The first port is contained in a section of the second port. The first orifice is of section equivalent to a section of the channel, while the section of the second orifice is substantially identical to a section of the discharge mouth.

According to this example, the first orifice is in fluid communication with the groove. The second opening is in fluid communication with the exhaust outlet of the heat exchanger. The groove opens onto the second face and is closed at the first face by a first wall. The latter thus forms a bottom for the groove and for the cavity.

According to one aspect of the invention, the intermediate piece carries the channel, at least at one of its ends.

Advantageously, the first opening and the second opening are separated from each other by a flange which receives a first end of the channel housed inside the first opening. The flange thus carries the end of the channel and makes it possible to connect the internal volume of the channel with the internal volume of the groove.

The intake and exhaust vents are provided on the same side of the heat exchanger, and for example at the same corner.

The heat exchanger may include a closing plate which closes the chamber and which carries sleeves delimiting the inlet and the outlet. The closure plate seals the chamber to conduct the refrigerant from the second layer to the first layer.

According to an example of the invention, the first upper compartment is a central compartment of the heat exchanger located equidistant from a first longitudinal end and a second longitudinal end of the heat exchanger. A width of these three compartments is identical, or substantially identical, measured along a straight line which fits into the inlet face of the air flow of the exchanger.

The invention also relates to a use of such a heat exchanger as an evaporator, in particular when it is housed inside a housing of a ventilation, heating and / or air conditioning installation fitted a motor vehicle.

The invention also relates to a refrigerant circuit comprising at least one such heat exchanger, for example a refrigerant circuit of a motor vehicle.

The invention also relates to a ventilation, heating and / or air conditioning installation for a motor vehicle, comprising at least one such heat exchanger and traversed by a flow of air circulating inside the ventilation installation, heating and / or air conditioning system, in which the heat exchanger is arranged in the ventilation, heating and / or air conditioning system so that the air flow enters the heat exchanger first place by the first layer which includes the first upper compartment.

Other characteristics, details and advantages of the invention will emerge on reading the detailed description given below by way of indication in relation to the drawings of the attached plates, in which:

FIG. 1 is a diagrammatic illustration of a refrigerant fluid circuit comprising a heat exchanger of the present invention,

FIG. 2 is a perspective illustration of the heat exchanger illustrated in FIG. 1,

FIG. 3 is a schematic illustration of an upper cross section of the heat exchanger shown in FIG. 2,

FIG. 4 is a diagrammatic illustration of a median cross section of the heat exchanger shown in FIG. 2,

FIG. 5 is a diagrammatic illustration of a lower cross section of the heat exchanger shown in FIG. 2,

FIG. 6 is a diagrammatic illustration of a path for circulation of the refrigerant fluid inside the heat exchanger shown in FIG. 2,

FIG. 7 is a partial illustration in three-quarters view of the heat exchanger shown in FIG. 2,

FIG. 8 is an illustration from the side and from above of the heat exchanger shown in FIG. 2,

FIG. 9 is a perspective view of a plate constituting the heat exchanger shown in FIG. 2,

FIG. 10 is a perspective and partial view of the heat exchanger shown in FIG. 2,

- Figures 11 and 12 are front and rear views of an intermediate piece constituting the heat exchanger shown in Figure 2.

The figures and their description show the invention in detail and according to specific methods of its implementation. They can be used to better define the invention, if necessary.

In Figure 1 is shown a closed circuit 1 inside which circulates a refrigerant FR. In the illustrated embodiment, the refrigerant circuit 1 successively comprises, in a direction SI of circulation of the refrigerant fluid FR inside the refrigerant circuit 1, a compressor 2 for compressing the refrigerant fluid FR, a condenser or a gas cooler 3 for cooling the FR refrigerant, an expansion member 4 inside which the FR refrigerant undergoes expansion and a heat exchanger 5 according to the invention. The heat exchanger 5 is housed inside a housing 6 of a ventilation, heating and / or air conditioning installation 7 inside which a flow of air circulates. The heat exchanger 5 allows thermal transfer between the refrigerant fluid FR and the air flow FA coming into contact with it and / or passing through it, as illustrated in FIG. 2. Depending on the operating mode of the fluid circuit refrigerant 1 described above, the heat exchanger 5 is used as an evaporator to cool the air flow FA, during the passage of the air flow FA in contact and / or right through the heat exchanger 5.

In FIG. 2, the heat exchanger 5 is represented inside an orthonormal reference mark Oxyz. The heat exchanger 5 comprises an inlet face 8 of the air flow FA and an outlet face 25 of this air stream FA which extend along a longitudinal plane PI parallel to the plane Oxy. Fa inlet face 8 is the face of the heat exchanger 5 through which the air flow FA enters the interior of the heat exchanger 5, while the outlet face 25 is the face of the 'heat exchanger 5 by which the air flow FA leaves the heat exchanger, after being heat treated. Fa inlet face 8 and outlet face 25 are in particular the faces of larger dimensions of the heat exchanger 5. The air flow FA flows through the heat exchanger 5 substantially orthogonally to the longitudinal plane Pl.

The heat exchanger 5 comprises two layers 9, 11 of tubes 10, 12, including a first layer 9 of first tubes 10 and a second layer 11 of second tubes 12.

The first ply 9 is delimited by the inlet face 8, so that the first ply 9 is the ply which the air flow LA crosses first during its circulation through the heat exchanger 5. In other words , the air flow LA passes successively through the inlet face 8, then the first ply 9, then the second ply 11 and leaves the heat exchanger by its outlet face 25. The first ply 9 and the second ply 11 are parallel to each other and parallel to the longitudinal plane PI. The first tubes 10 and the second tubes 12 are mutually parallel and extend along a first axis of general extension A1 which is parallel to the longitudinal plane PI, and parallel to the direction Oy of the orthonormal reference frame Oxyz. Each of the first tubes 10 and of the second tubes 12 are associated in pairs by being aligned within the same lateral plane P3, parallel to the plane Oyz.

The first tubes 10 are interposed between a first collector 21 of coolant ER and a second collector 22 of coolant ER. The first collector 21 and the second collector 22 extend parallel to a second axis of general extension A2 which is orthogonal, or substantially orthogonal, to the first axis of general extension A1. The first collector 21 and the second collector 22 are contained inside a plane parallel to the longitudinal plane PI of the heat exchanger 5. The first manifold 21 is provided with an outlet 15 for the coolant ER from the heat exchanger 5. It is understood here that this discharge mouth 15 is contained, partially or totally, in the first ply 9 of the heat exchanger 5.

The second tubes 12 are interposed between a third collector 23 of refrigerant ER and a fourth collector 24 of refrigerant ER. The third collector 23 and the fourth collector 24 extend parallel to the second general extension axis A2. The third collector 23 and the fourth collector 24 are contained within a plane which is parallel to the longitudinal plane PI of the heat exchanger 5. The third collector 23 is provided with an inlet mouth 16 for the fluid ER refrigerant inside the heat exchanger 5. This inlet mouth 16 is contained, partially or totally, in the second layer 11 of the heat exchanger 5.

The first manifold 21 and the third manifold 23 are contiguous with each other in a plane parallel to a transverse plane P2 of the heat exchanger 5, the latter itself being parallel to the Oxz plane. The second collector 22 and the fourth collector 24 are contiguous with each other in a plane parallel to the transverse plane P2 of the heat exchanger 5.

The inlet mouth 16 and the outlet mouth 15 are disposed inside a plane parallel to the transverse plane P2 and are formed through a first longitudinal end 17 of the heat exchanger 5. In other words, the inlet port 16 and outlet port 15 are arranged side by side with one another. It is understood here that the first manifold 21 and the third manifold 23 extend in the transverse plane P2 between the first longitudinal end 17 and a second longitudinal end 18 of the heat exchanger 5. Furthermore, the layers 9, 11 of the heat exchanger 5 extend longitudinally along the second longitudinal axis A2 between a first cheek 19 and a second cheek 20, which respectively border the heat exchanger 5 over its entire height parallel to the transverse plane P2 and which form the longitudinal ends 17, 18.

In FIG. 3 which illustrates an upper cross section of the heat exchanger 5 produced along a plane which crosses the first collector 21 and the third collector 23 and which is parallel to the transverse plane P2, the first collector 21 and the third collector 23 are compartmentalized. The first collector 21 and the third collector 23 comprise a plurality of upper compartments referenced 41, 42, 43, 44 and 45.

All of the description describes as "superior" any element of the heat exchanger 5 situated above a plane which is parallel to the transverse plane P2 and which is equidistant from the first collector 21 and the second collector 22, and any element of the heat exchanger 5 situated below this same plane parallel to the transverse plane P2 is called "lower".

The first manifold 21 comprises at least a first upper compartment 41 which is interposed between a second upper compartment 42 and a third upper compartment 43. According to the variant illustrated in FIG. 3, the first upper compartment 41 is unique so that the first collector 21 comprises three compartments 41, 42, 43 and that the first upper compartment 41 is a central compartment of the heat exchanger 5. In other words, a first distance between a barycenter of the first compartment 41 and the first longitudinal end 17 is equal at a second distance between the barycenter of the first compartment 41 and the second longitudinal end 18.

The first upper compartment 41, the second upper compartment 42 and the third upper compartment 43 are sealed with respect to each other. To this end, the first upper compartment 41 and the second upper compartment 42 are separated from each other by at least one first upper partition 51. To this end again, the first upper compartment 41 and the third upper compartment 43 are separated from each other by at least a second upper partition 52. The second upper compartment 42, the first upper compartment 41 and the third upper compartment 43 are formed successively one after the other along an axis parallel to the second axis of general extension A2.

The third manifold 23 includes a fourth upper compartment 44 and a fifth upper compartment 45. The fourth upper compartment 44 and the fifth upper compartment 45 are sealed relative to one another. To this end, the fourth upper compartment 44 and the fifth upper compartment 45 are separated from each other by a third upper partition 53. The fourth upper compartment 44 and the fifth upper compartment 45 are formed successively one after the other. other along an axis parallel to the second axis of general extension A2.

According to the present invention, the heat exchanger 5 is equipped with a means 80 for supplying the FR refrigerant fluid from the inlet mouth 16 to the first upper compartment 41, so that the FR refrigerant fluid entering the interior of the heat exchanger 5 flows from the inlet mouth 16 to the first ply 9, and more particularly to the first upper compartment 41, which is a central compartment of the heat exchanger 5. In other words, the supply means 80 places the inlet mouth 16 in fluid communication with the first upper compartment 41, the latter being interposed between two other compartments of the first manifold 21.

These arrangements are such that the refrigerant FR admitted inside the heat exchanger 5 is directed towards the first sheet 9, that is to say the one which receives in the first place the air flow FA, although that the intake manifold 16 equips the second tablecloth

11. More particularly, the supply means 80 allows a supply of refrigerant fluid FR to the heat exchanger 5 first of all from the central compartment of the first manifold 21 of the first layer 9.

The supply means 80 comprises a chamber 81 which is in fluid relationship with the inlet mouth 16 via a first opening 80a. The chamber 81 can encroach on the second upper compartment 42 and / or on the fifth upper compartment 45. Alternatively, the chamber 81 can be provided at the end of the first collector 21, for example outside the second upper compartment 42 and / or on the fifth upper compartment 45. The largest dimension of the chamber 81 is formed inside a plane which is parallel to the lateral plane P3. In other words, the chamber 81 allows the refrigerant fluid FR penetrating inside the heat exchanger 5 through the inlet mouth 16 to flow immediately from the second ply 11 to the first ply 9. According to an exemplary embodiment, the chamber 81 takes the form of a cavity and a groove which can in particular extend along a straight line parallel to the axis Oz of the orthonormal coordinate system.

The supply means 80 also comprises a channel 83 which extends inside the second compartment 42 and which fluidly connects the chamber 81 with the first upper compartment 4L In other words, the channel 83 allows the refrigerant fluid FR to pass longitudinally the second upper compartment 42 from the chamber 81 to the first upper compartment 4L The channel 83 extends between the first chamber 81 and the first upper partition 51, crossing the latter.

We can therefore consider that the supply means 80 comprises the channel 83, which is housed inside the second upper compartment 42, and the chamber 81 which extends partly at the level of the second upper compartment 42 and of the fifth compartment. higher 45.

The first chamber 81 is in fluid relation with the channel 83 via a first outlet 80b of the channel 83 .. The channel 83 is also in fluid relationship with the first upper compartment 41 via a second outlet 80c which puts in fluid relation an internal volume of channel 83 with an internal volume of the first upper compartment 4L The first outlet 80b of channel 83 is produced at a first end 83a of channel 83, while the second outlet 80c of channel 83 is produced at a second longitudinal end 83b of the channel 83.

It is noted that the first plate 101 and / or the second plate 102 delimiting the first upper compartment 41 and the second upper compartment 42 has a hole made in the first upper partition 51 constituting one or the other of these plates. Such a hole forms a landing for receiving the second end 83b of the channel 83, so that the second outlet 80c opens in the first upper compartment 41.

The supply means 80 is for example arranged in a square formed in "L". For this purpose, the first chamber 81 forms the base of the "L" and the channel 83 the branch of the "L" which is elongated along the second axis of general extension A2.

As visible in FIG. 4, the channel 83 is for example formed inside a median longitudinal plane P4 of the first ply 9, which transversely separates the first ply 9 in two equal parts. The first outlet 80b and the second outlet 80c are for example formed perpendicular to the second axis of general extension A2. The first outlet 80b and the second outlet 80c are here provided inside the median longitudinal plane P4, but the invention also covers the case where these outlets 80b and 80c, as well as the channel 83, are offset in the second upper compartment 42 being for example closer to the inlet face 8 or closer to the outlet face 25 of the heat exchanger 5.

According to one embodiment, the first chamber 81 is formed in an intermediate part. This first chamber 81 is delimited by a first wall 81a of the intermediate piece and by a closure plate 27 which extends substantially parallel to the lateral plane P3. The intermediate piece is provided with the first opening 80a which is in fluid communication with the inlet mouth 16. According to this embodiment, the first wall 81a extends in a plane which is included inside the second upper compartment 42 and of the fifth upper compartment 45.

In FIG. 4 which illustrates a median cross section of the heat exchanger 5 produced along a plane parallel to the transverse plane P2 and at equal distance from the first collector 21 and the second collector 22 on the one hand, and from the third collector 23 and from the fourth collector 24 on the other hand, the heat exchanger 5 is a multi-pass heat exchanger, the first ply 9 of which comprises a plurality of passes 31, 32, 33 and the second ply of which 11 also comprises a plurality of passes 34, 35, 36. The passes 31, 32, 33 of the first ply 9 are each formed of a plurality of first tubes 10 inside which the refrigerant FR flows in the same direction. Two adjacent passes 31, 32, 33 of the first ply 9 comprise these first tubes 10 inside which the refrigerating fluid FR circulates in opposite directions, from one pass to the other. Likewise, the passes 34, 35, 36 of the second ply 11 are each formed of a plurality of second tubes 12 inside which the refrigerant FR flows in the same direction. Two adjacent passes 34, 35, 36 of the second ply 11 comprise these second tubes 12 inside which the refrigerating fluid FR circulates in opposite directions, from one pass to the other.

According to an exemplary embodiment, each pass 31, 32, 33 of the first ply 9 is placed opposite a respective second pass 34, 35, 36 of the second ply IL The refrigerant fluid FR circulating in the first tubes 10 of any of the passes 31, 32, 33 of the first ply 11 circulates in a direction opposite to that of the refrigerant fluid FR circulating in second tubes 12 of the pass of the adjacent second ply 11 situated in the same parallel plane in the lateral plane P3.

The first ply 9 comprises at least a first pass 31 which is interposed between a second pass 32 and a third pass 33. The second pass 32 can be delimited at least partially by the first cheek 19 and the third pass 33 delimited at least partially by the second cheek 20. According to the variant illustrated in FIG. 4, the first pass 31 is unique so that the first ply 9 comprises three passes 31, 32, 33 and that the first pass 31 is a first central pass of the heat exchanger 5. According to another alternative embodiment, the first passes 31 are in plurality so that the first ply 9 comprises more than three passes, and in particular four passes.

Similarly, the second ply 11 comprises at least a fourth pass 34 which is interposed between a fifth pass 35 and a sixth pass 36. The fifth pass 35 can be delimited at least partially by the first cheek 19 and the sixth pass 36 can be delimited at least partially by the second cheek 20. According to the variant illustrated in FIG. 4, the fourth pass 34 is unique so that the second ply 11 comprises three passes 34, 35, 36 and that the fourth pass 34 is a pass central heat exchanger 5. According to another alternative embodiment, the fourth passes 34 are in plurality so that the second ply 11 comprises more than three passes, and in particular four passes.

Seen in planes parallel to the lateral plane P3, the first pass 31 is opposite the fourth pass 34, while the third pass 33 is opposite the fifth pass 35. Finally, the second pass 32 faces the sixth pass 36 .

The upper compartments 41, 42, 43 of the first ply 9 are in fluid relation with the passes 31, 32, 33 of the first ply 9. More particularly, the first upper compartment 41 is in fluid communication with the upper ends of the first tubes 10 of the first pass 31. The second upper compartment 42 is in fluid communication with the upper ends of the first tubes 10 of the second pass 32. The third upper compartment 43 is in fluid communication with the upper ends of the first tubes 10 of the third pass 33.

The upper compartments 44, 45 of the second ply 11 are in fluid relation with the passes 34, 35, 36 of the second ply 11. More particularly, the fourth upper compartment 44 is in fluid communication with the upper ends of the second tubes 12 of the fifth pass 35. The fifth upper compartment 45 is in fluid communication with the upper ends of the second tubes 12 of the fourth pass 34 and the upper ends of the first tubes 12 of the sixth pass 36.

Finally, the third upper compartment 43 and the fourth upper compartment 44 are in fluid communication with each other via at least one upper passage 54.

In FIG. 5 which illustrates a lower cross section of the heat exchanger 5 produced according to a plane which crosses the second collector 22 and the fourth collector 24 and which is parallel to the transverse plane P2, the second collector 22 and the fourth collector 24 are compartmentalized. The second collector 22 and the fourth collector 24 comprise a plurality of lower compartments 61, 62, 63.

The second manifold 22 includes a first lower compartment 61 and a second lower compartment 62. The first lower compartment 61 and the second lower compartment 62 are sealed relative to one another. To this end, the first lower compartment 61 and the second lower compartment 62 are separated from each other by a first lower partition 71. The first lower compartment 61 and the second lower compartment 62 are formed successively one after the other. other along an axis parallel to the second axis of general extension A2.

The lower compartments 61, 62 are in fluid relation with the passes 31, 32, 33 of the first ply 9. More particularly, the first lower compartment 61 is in fluid communication with the lower ends of the first tubes 10 of the first pass 31 and with the lower ends of the first tubes 10 of the third pass 33. The second lower compartment 62 is in fluid communication with the lower ends of the first tubes 10 of the second pass 32.

The fourth manifold 24 includes a third lower compartment 63 and a fourth lower compartment 64. The third lower compartment 63 and the fourth lower compartment 64 are sealed relative to one another. To this end, the third lower compartment 63 and the fourth lower compartment 64 are separated from each other by a second lower partition 72, the latter being able to be produced in the same plane, and advantageously by the same plate, as the first lower partition 71. The third lower compartment 63 and the fourth lower compartment 64 are arranged successively one after the other along an axis parallel to the second axis of general extension A2.

The lower compartments 63, 64 of the fourth manifold 24 are in fluid relation with the passes 34, 35, 36 of the second ply 11. More particularly, the third lower compartment 63 is in fluid communication with the lower ends of the second tubes 12 of the fourth pass 34 and with the lower ends of the second tubes 12 of the fifth pass 35. The fourth lower compartment 64 is in fluid communication with the lower ends of the second tubes 12 of the sixth pass 36.

Finally, the second lower compartment 62 and the fourth lower compartment 64 are in fluid communication with each other via at least one lower passage 73.

The circulation of the refrigerant fluid within the heat exchanger 5 will now be detailed by referring to FIGS. 3 to 6. The refrigerant fluid FR penetrating inside the heat exchanger 5 is admitted into it by through the inlet mouth 16, then flows from the second layer 11 to the first layer 9 via the chamber 81, then flows through the channel 83 to the first upper compartment 4L The mouth inlet 16 is thus in fluid communication directly via the fluid supply means 80. Then, the refrigerating fluid FR circulates from the first upper compartment 41 to the first lower compartment 61 by borrowing the first tubes 10 of the first pass 31. Then, the refrigerant FR flows inside the first lower compartment 61 to reach the first tubes 10 of the third pass 33 and join the tr third upper compartment 43. Then, the refrigerant FR flows from the third upper compartment 43 to the fourth upper compartment 44 via the upper passage 54. Then, the refrigerant FR flows from the fourth upper compartment 44 to the third lower compartment 63 using the second tubes 12 of the fifth pass 35. Then, the refrigerant FR flows inside the third lower compartment 63 to reach the second tubes 12 of the fourth pass 34 and join the fifth upper compartment 45. Then , the refrigerant FR circulates inside the fifth upper compartment 45 to join the second tubes 12 of the sixth pass 36 and join the fourth lower compartment 64. Then, the refrigerant FR flows from the fourth lower compartment 64 towards the second lower compartment 62 in borrowing the lower passage 73. Then, the refrigerant FR circulates from the second lower compartment 62 to the second upper compartment 42 using the first tubes 10 of the second pass 32. Finally, the refrigerant FR is evacuated from the exchanger of heat 5 by borrowing the discharge mouth 15 which is in direct fluid communication with the second upper compartment 42.

Referring to Figures 7 and 8, the heat exchanger 5 is a plate exchanger which comprises a plurality of first plates 101 and second plates 102 abutted to each other via their respective flanges 101a, 102a to form a first tube 10 and a second tube 12 as well as a cell of the first collector 21, a cell of the second collector 22, a cell of the third collector 23 and a cell of the fourth collector 24. More particularly, a first plate 101 and a second plate 102 are butted by their respective flanges 101a, 102a to jointly form a first tube 10 and a second tube 12, a plurality of pairs of first plates 101 and second plates 102 being stacked on each other to form the plurality of tubes 10, 12, and therefore the heat exchanger 5. The stack of cells also forms the collectors listed above. A dissipation member 26 is also interposed between two pairs of plates 101, 102, so as to promote a heat exchange between this air flow LA and the walls of the plates 101, 102. Such a member takes for example the form of a spacer.

FIG. 8 also shows an example of lateral positioning of the channel 83 inside the second upper compartment 42. In the present case, the channel 83 is not centered on a central longitudinal axis of the first manifold 21. H is thus offset laterally with respect to this central longitudinal axis of the first manifold 21. According to the example visible in FIG. 8, the channel 83 is closer to a median plane passing between the first manifold 21 and the second manifold 22 and between the third collector 23 and fourth collector 24, than from the inlet face 8 of the air flow LA in the heat exchanger 5. In other words, such a median plane passes between the first ply 9 and the second ply 11.

The invention also covers the case where the channel is offset by being closer to the entry face than to the median plane mentioned above.

Such an offset can also be envisaged in the direction Oy of the orthonormal coordinate system of FIG. 2. The channel can thus be closer to a vertex of the first manifold than of the first tubes. Alternatively, the channel can be closer to the first tubes 10 than to the top of the first manifold.

Finally, the invention covers the case where the channel 83 is centered in the second compartment along the Oy axis and the Oz axis of the orthonormal reference frame. In such a case, a central axis of extension of the channel is merged with a central axis of extension of the second compartment.

In FIG. 9, each first plate 101 and / or each second plate 102 constituting the same compartment comprises four holes 104, two holes 104 of which are formed in an upper zone 105 of the first plate 101 and / or of the second plate 102 and two openings 104 are formed in a lower zone 106 of the first plate 101 and / or of the second plate 102, on either side of the median plane mentioned above. The abutment of a first plate 101 with a second plate 102 forms, at its upper zone 105 and at its lower zone 106, cells which, when the stack of first plates 101 and second plates 102 is made, the first, second, third and fourth manifold respectively referenced 21, 22, 23 and 24. Each first plate 101 and / or each second plate 102 separating two adjacent compartments is free of drilling in the upper zone 105 and / or lower 106 It will be noted at this stage of the description that the first upper partition 51, the second upper partition 52, the third upper partition 53, the first lower partition 71 and the second lower partition 72 advantageously come from the first plate 101 or from the second plate. 102 free of piercing.

Referring to FIG. 10, the heat exchanger 5 comprises an intermediate piece 90 which is interposed between a bundle of tubes 10, 12 and dissipating members 26 of the heat exchanger 5 and the intake openings 16 and evacuation

15. According to this example, the intermediate piece 90 is disposed between these inlet 16 and outlet 15 vents and the first cheek 19 which longitudinally ends the bundle of the heat exchanger 5. According to this exemplary embodiment, the plate closure 27 covers the intermediate part 90 so as to seal the chamber 81, in particular its cavity and its groove constituting this chamber 81. It will be noted that this closure plate 27 can wear sleeves 28, 29 which respectively delimit the mouth 16 and the outlet 15.

The intermediate piece 90 is intended to be housed in its thickness the chamber 81 and to carry a first end 83a of the channel 83. The intermediate piece 90 is disposed in the extension along the axis Ox of the first collector 21 and the second collector 22. L the thickness of this intermediate plate 90 is measured along a straight line parallel to the axis Ox of the orthonormal coordinate system shown in FIG. 2.

In FIGS. 11 and 12, the intermediate piece 90 has two parallel faces, including a first face 91 intended to be vis-à-vis the first cheek 19 and a second face 92 which is intended to be vis-à-vis screw of the closing plate 27. The intermediate piece has a groove 93 which opens out through the second face 92 and which is not open through the first face 91. The groove 93 delimits the chamber 81 of the supply means 80 , in particular its groove, the first wall 81a constituting the first face 91 by closing the groove 93 on the first face 91. The intermediate piece 90 also comprises the first opening 80a which opens on the cavity 82, the latter being of section substantially equivalent to the section of the inlet mouth 16. The cavity 82 is fluidly connected to the groove 93 and thus forms the chamber 81. The first opening 80a is provided to be placed in screws opposite the inlet mouth 16, so that the coolant enters the interior of the chamber 81, the first wall 81a preventing the coolant from flowing to the fifth upper compartment 45. The first wall 81a forms a bottom wall of the intermediate piece 90.

The intermediate piece 90 has a first orifice 94 which passes through from the first face 91 to the second face 92, the first orifice 94 being formed at the edge of the groove 93. The first orifice 94 is designed to be in fluid communication with the first outlet 80b of the channel 83. Thus, the refrigerant present inside the chamber 81 borrows the first orifice 94 to reach the first outlet 80b and then circulate inside the channel 83.

The first orifice 94 is partially delimited by a flange 95 inside which the first end 83a of the channel 83 comes to fit together, with a view to securing it. To this end, the first end 83a of the channel 83 includes a diameter restriction to be embedded in the flange 95, inside the first orifice 94.

The flange 95 forms a separating wall between the groove 93 and a second orifice 96 which passes through the intermediate part 90 right through, that is to say from the first face 91 to the second face 92. The second orifice 96 is designed to be placed in fluid communication with the discharge mouth 15, the second orifice 96 allowing evacuation of the refrigerant fluid LR from the second upper compartment 42 towards the discharge mouth 15.

Claims (13)

1. Heat exchanger (5) intended to be traversed by a cooling fluid (FR), the heat exchanger (5) comprising a first ply (9) of first tubes (10) and a second ply (11) of second tubes (12), the first ply (9) comprising a first manifold (21) which is provided with an outlet (15) for the coolant (FR) and which comprises a plurality of upper compartments (41, 42, 43) including a first upper compartment (41) interposed between a second upper compartment (42) and a third upper compartment (43), the second ply (11) being provided with an inlet (16) for the coolant ( FR), characterized in that the heat exchanger (5) is equipped with a means (80) for supplying the coolant (FR) which is interposed between the inlet mouth (16) and the first upper compartment (41), the supply means (80) extending at least partially to the interior the second upper compartment (42). 2. Heat exchanger (5) according to claim 1, wherein the supply means (21) comprises at least one channel (83) which is housed inside the second upper compartment (42). 3. Heat exchanger (5) according to claim 2, wherein the supply means (80) comprises at least one chamber (81) interposed between the channel (83) and the inlet mouth (16). 4. Heat exchanger (5) according to claim 3, in which the chamber (81) comprises a groove (93) connected directly to a cavity (82), the inlet mouth (16) opening directly into the cavity (82 ) while the channel (83) opens directly into the groove (93). 5. Heat exchanger (5) according to claims 3 or 4, wherein the chamber (81) extends along a straight line which fits within a plane parallel to a lateral plane (P3 ) of the heat exchanger (5) which is orthogonal to a longitudinal plane (PI) defining an inlet face (8) of an air flow (FA) in the heat exchanger (5). 6. Heat exchanger (5) according to any one of claims 3 to 5, wherein the chamber (81) is formed inside a thickness of an intermediate piece (90). 7. Heat exchanger (5) according to claim 6, in which the intermediate piece (90) comprises a first orifice (94) and a second orifice (96) which each open out through a first face (91) and a second face. (92) of the intermediate piece (90). 8. Heat exchanger (5) according to claims 4 and 7, wherein the first orifice (94) is in fluid communication with the groove (93) which opens on the second face (92) and which is closed at the level of the first face (91) by a first wall (81a). 9. Heat exchanger (5) according to any one of claims 7 or 8, wherein the first port (94) and the second port (96) are separated from each other by a flange (95) which receives a first end (83a) of the channel (83) housed inside the first orifice (94). 10. Heat exchanger (5) according to any one of claims 3 to 9, comprising a closure plate (27) which closes the chamber (81) and which carries sleeves (28, 29) delimiting the inlet mouth (16) and the discharge mouth (15). 11. Heat exchanger (5) according to claim 11, wherein the first upper compartment (41) is a central compartment of the heat exchanger (5) located equidistant from a first longitudinal end (17) and d 'a second longitudinal end (18) of the heat exchanger (5). 12. Use of a heat exchanger (5) according to any one of claims 1 to 12 as an evaporator. 13. Installation (7) of ventilation, heating and / or air conditioning for a motor vehicle, comprising at least one heat exchanger (5) according to any one of claims 1 to 12 and traversed by an air flow (FA ) circulating inside the ventilation, heating and / or air conditioning installation (7) in which the heat exchanger (5) is arranged in the ventilation, heating and / / installation (7) or air conditioning so that the air flow (FA) enters the heat exchanger (5) firstly by the first layer (9) which comprises the first upper compartment (41).