WO2018100298A1

WO2018100298A1 - Heat exchanger constituting a refrigerant circuit

Info

Publication number: WO2018100298A1
Application number: PCT/FR2017/053300
Authority: WO
Inventors: Jérôme MOUGNIER; Jérémy BLANDIN; Julien Tissot; Patrick LEBLAY; Kamel Azzouz
Original assignee: Valeo Systemes Thermiques
Priority date: 2016-11-30
Filing date: 2017-11-30
Publication date: 2018-06-07
Also published as: FR3061284A1; FR3061284B1

Abstract

The invention relates to a heat exchanger (5) comprising a collector box and a return means (9) between which a first layer (11) of first tubes (10a) and a second layer (12) of second tubes (10b) are inserted. The first tubes (10a) comprise a first end (101) in fluid communication with the return means (9) and a second end (102) in fluid communication with the collector box (8). The second tubes (10b) comprise a third end (103) in fluid communication with the return means (9) and a fourth end (104) in fluid communication with the collector box (8). The collector box accommodates at least one device for homogenising the distribution of a refrigerant along the collector box (8). The return means (9) comprises at least one partition (23a) which subdivides the return means (9) into at least two compartments (24), each compartment (24) being provided with at least one end (101, 103) of a tube (10a, 10b).

Description

Heat exchanger constituting a refrigerant circuit

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

A motor vehicle is commonly equipped with a ventilation, heating and / or air conditioning system for heat 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 circulates a refrigerant fluid. The refrigerant circuit comprises successively a compressor, a condenser or gas cooler, an expansion member and a heat exchanger. The heat exchanger is housed inside the ventilation, heating and / or air conditioning system to allow a heat exchange between the refrigerant and a flow of air circulating inside said installation, previously a delivery of the air flow inside the passenger compartment.

According to a mode of operation of the refrigerant circuit, heat exchanger is used as an evaporator to cool the air flow. In this case, the refrigerant is compressed inside the compressor, then the cooling fluid is cooled inside the condenser or gas cooler, then the refrigerant is expanded inside the organ of relaxation and finally the refrigerant captures calories to the air flow inside the heat exchanger. The refrigerant fluid, at the outlet of the expansion member and at the inlet of the heat exchanger, is in the two-phase state and is present in a liquid phase and a gaseous phase.

The heat exchanger is in particular a heat exchanger inside which the coolant flows in a path arranged in "U". For this purpose, the heat exchanger comprises a header and a gearbox between which a bundle of tubes is interposed. The diverting box is formed of an enclosure that delimits a unit volume that extends from one side to the other of the heat exchanger. The tubes are arranged in two parallel layers that extend between two side edges of the heat exchanger. A first web of first tubes is in fluid communication with the return box and a first chamber housed inside the manifold. A second ply of second tubes is in fluid communication with the return box and a second chamber also housed inside the manifold. During operation of the refrigerant circuit, the coolant is admitted inside the heat exchanger through an inlet mouth that includes the first chamber. Then, the refrigerant flows between the first chamber of the header and the return box by borrowing the first tubes of the first sheet. Then, the coolant flows between the return box and the second chamber through the second tubes of the second sheet. Finally, the refrigerant is discharged from the heat exchanger through an outlet mouth formed through the second chamber.

A general problem posed lies in a difficulty in feeding the tubes of the bundle homogeneously with respect to the different phases of the refrigerant fluid. A first problem lies in a difficulty of supplying the first tubes with refrigerant fluid homogeneously. A second problem lies in a difficulty in supplying the second tubes with refrigerant fluid homogeneously. However, a refrigerant supply heterogeneity of the first tubes and / or the second tubes generates a heterogeneity of the temperature of the air flow which passes successively through the first ply, then the second ply. This heterogeneity is likely to induce untimely and undesired temperature differences between zones of the passenger compartment, which is detrimental.

US2015 / 0121950 proposes to house a conduit provided with a plurality of orifices inside the first chamber of the manifold. The coolant in the liquid phase is thus projected through the orifices in the form of droplets along the length of the conduit. US2015 / 0121950 also proposes to arrange the gearbox in a single enclosure in communication with all the tubes of the beam.

Such an organization is not optimal from the point of view of the homogenization of the coolant distribution inside the heat exchanger, and more particularly within the second layer where the fluid tends to migrate to the tubes of the second sheet closest to the coolant outlet in the header, to the detriment of more distant tubes. This results in a heterogeneity of the temperature of the air flow at the outlet of the heat exchanger, which is unsatisfactory.

An object of the invention is to perfect the homogeneity of the coolant distribution inside the heat exchanger, and in particular inside the second constituent tubes of the second sheet, to finally improve its efficiency and its performance, in order to deliver inside the passenger compartment a flow of air at the desired temperature.

A heat exchanger of the present invention is a heat exchanger comprising a header and a return means between which are interposed a first web of first tubes and a second web of second tubes. The first tubes include a first end in fluid communication with the return means and a second end in fluid communication with the header. The second tubes comprise a third end in fluid communication with the return means and a fourth end in fluidic relationship with the manifold. The collector box houses at least one device for homogenizing the distribution of a refrigerant fluid along the collector box.

According to the present invention, the return means comprises at least one partition which divides the return means into at least two compartments, each compartment being equipped with at least one end of a tube.

The heat exchanger advantageously comprises at least one of the following features, taken alone or in combination:

each compartment connects at least one first end of a first tube and at least one third end of a second tube. It will be understood that each compartment puts in fluid communication at least a first end of a first tube with at least a third end of a second tube,

each compartment connects a first end of a single first tube and a third end of a single second tube,

the partition is a partition of a first type which extends perpendicular to a first plane in which an inlet face of an air flow extends in the heat exchanger,

the partition is an integral part of a plate delimiting at least a first tube and a second tube,

the compartment is delimited by at least one plate delimiting at least one of the tubes,

a thickness of the compartment is greater than or equal to a thickness of the tubes, such thicknesses being measured in a direction parallel to the first plane and perpendicular to a third plane in which are aligned a first tube and a second tube;

at least one fin is interposed between two successive compartments. Such a fin forms a member arranged to increase the heat exchange surface of the tube with the flow of air able to pass through the exchanger,

- The fin interposed between two successive compartments is an integral part of a heat dissipation means disposed between two successive tubes of the same sheet,

a thickness of the compartment is equal to a thickness of the tubes. The compartment is then formed in the extension of the tubes, the coolant passage section being constant at least between the compartment and the first tube and / or the second tube,

- A first compartment connects the first ends of the first tubes together and a second compartment connects the third ends of the second tubes. In such a case, the first compartment and / or the second compartment extend along the return means,

the partition is a partition of a second type which extends parallel to a first plane in which an inlet face of an air flow extends in the heat exchanger, the partition of the second type comprising at least one window that communicates the first compartment with the second compartment,

the device for homogenizing the distribution of a refrigerant fluid comprises at least one duct provided with a plurality of orifices distributed along the duct,

- The duct can receive a refrigerant fluid mixer capable of mixing a liquid portion and a gaseous portion of the refrigerant. Such a mixer extends over the length of the duct. Such a mixer may comprise a series of shapes arranged to guide the cooling fluid from a central axis of the duct towards its inner wall,

- Alternatively, the conduit can accommodate a tube coaxial with the conduit or off-center, and provided with holes along its length, the position of these holes then being offset from the position of the orifices. In such a case, a first mouth through which the fluid enters the exchanger communicates with an internal volume delimited by the tube. In another example, the tube may comprise a linear or stepped reduction of its internal section from one end to the other of the header box,

alternatively again, the duct can house a profile in the form of an endless screw.

The invention also relates to a refrigerant circuit comprising at least one such heat exchanger.

The invention also relates to a use of such a heat exchanger as an evaporator housed inside a housing of a ventilation, heating and / or air conditioning equipment equipping a motor vehicle.

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

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

FIG. 2 is a schematic illustration of the heat exchanger included in the refrigerant circuit illustrated in FIG. 1;

FIG. 3 is a partial view of a first variant embodiment of the heat exchanger illustrated in FIG. 2,

FIG. 4 is a sectional view of a first embodiment of a return means that comprises the heat exchanger illustrated in FIG. 3,

FIG. 5 is a partial view of a second variant embodiment of the heat exchanger illustrated in FIG. 2;

FIG. 6 is a sectional view of a second alternative embodiment of a return means that comprises the heat exchanger illustrated in FIG. 5;

FIG. 7 is a partial view of a third embodiment variant of FIG. the heat exchanger illustrated in FIG.

FIG. 8 is a sectional view of a third embodiment of a return means that comprises the heat exchanger illustrated in FIG. 7,

- Figure 9 is a partial view of a plate constituting the heat exchanger shown in Figures 7 and 8.

FIG. 10 is a detailed view of the heat exchanger shown in FIGS. 3 and 4.

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

In Figure 1, there is shown a closed circuit 1 inside which circulates a refrigerant fluid FR. In the exemplary embodiment illustrated, 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 refrigerant FR, an expansion member 4 within which the cooling fluid FR undergoes expansion and a heat exchanger 5. The heat exchanger 5 is housed inside a housing 6 of a ventilation system 7, heating and / or air conditioning inside which circulates a flow of air. The heat exchanger 5 allows a heat transfer between the refrigerant fluid FR and the flow of air coming into contact with it and / or passing through it, as illustrated in FIG. 2. According to the operating mode of the refrigerant circuit 1 described above, the heat exchanger 5 is used as an evaporator for cooling the air flow, during the passage of the air flow in contact with and / or from one side of the heat exchanger 5.

In FIG. 2, the heat exchanger 5 is a heat exchanger inside which the refrigerating fluid FR flows along a path arranged in "U". For this purpose, the heat exchanger 5 comprises at least one manifold 8 and at least one return means 9 between which a bundle of tubes 10a, 10b is interposed. In its generality, the heat exchanger 5 extends generally parallel to a first plane PI containing the manifold 8, the bundle of tubes 10a, 10b and the return means 9. PI plane is parallel to a plane in which is embedded an inlet face 37 of the heat exchanger, such an inlet face 37 being that which is traversed by the airflow FA to be heat treated. The manifold 8 overhangs the bundle of tubes 10a, 10b, which is itself located above the deflection means 9, in particular in the position of use of the heat exchanger 5 mounted inside the housing 6. In other words, according to this position of use, the manifold 8 is an upper box of the heat exchanger 5. The air flow FA flows through the heat exchanger 5 in a direction preferably orthogonal to the first PI plane, crossing the inlet face 37 of the heat exchanger.

The tubes 10a, 10b are for example rectilinear and extend along a first axis of general extension A1 between the manifold 8 and the return means 9. The manifold 8 extends along a second axis of general extension A2 and the return means 9 extends along a third axis of general extension A3. Preferably, the second axis of general extension A2 and the third axis of general extension A3 are mutually parallel, being orthogonal to the first axis of general extension Al.

The tubes 10a, 10b are arranged parallel to each other by being distributed in two plies 11, 12, including a first ply 11 of first tubes 10a and a second ply 12 of second tubes 10b. The first ply 11 and the second ply 12 are formed inside respective planes which are parallel to each other and parallel to the first plane Pl. The return means 9 allows a circulation of the refrigerant fluid FR from the first tubes 10a to the second tubes 10b. According to various variants of the present invention, described below, the return means 9 is arranged in a manifold housing compartments or in a plurality of compartments disjoined from each other and collectively forming the referral means 9 of the coolant FR from the first tubes 10a to the second tubes 10b.

The first tubes 10a of the first ply 11 extend between a first end 101 which is in fluid communication with the return means 9 and a second end 102 which is in fluid communication with a first chamber 13, which is delimited at inside the manifold 8. The second tubes 10b of the second ply 12 extend between a third end 103 which is in communication fluidic with the deflection means 9 and a fourth end 104 which is in fluid communication with a second chamber 14, also delimited within the manifold 8. The first chamber 13 and the second chamber 14 are contiguous and watertight. one with the other. The first chamber 13 extends along a fourth axis of general extension A4 and the second chamber 14 extends along a fifth axis of general extension A5. Preferably, the fourth axis of general extension A4 and the fifth axis of general extension A5 are parallel to each other and parallel to the second axis of general extension A2. The fourth axis of general extension A4 and the fifth axis of general extension A5 together define a second plane P2, which is preferably orthogonal to the first plane P1. In other words, the return means 9 forms the base of the "U" whereas that the first ply 11 and the second ply 12 of tubes 10a, 10b form the branches of the "U", the first chamber 13 and the second chamber 14 forming the ends of the "U". The bundle of tubes 10a, 10b is provided with fins 15 which are interposed at least between two successive first tubes 10a and between two second successive tubes 10b to promote a heat exchange between the air flow FA and the tubes 10a, 10b, during a passage of the air flow FA through successively the first ply 11 and the second ply 12. According to a variant described below, the fins 15 are capable of extending between two successive compartments that includes the means of return 9.

During an implementation of the refrigerant circuit 1, the refrigerant fluid FR enters the inside of the heat exchanger 5 through a first mouth 16 that includes the first chamber 13. Then, the refrigerant fluid FR flows between the first chamber 13 of the manifold 8 and the return means 9 by borrowing the first tubes 10a of the first ply 11. Then, the refrigerant FR flows between the return means 9 and the second chamber 14 by borrowing the second tubes 10b of the second ply 12. Finally, the refrigerant FR is discharged out of the heat exchanger 5 through a second mouth 17 formed through the second chamber 14.

Preferably, a first tube 10a of the first ply 11 is aligned with a second tube 10b of the second ply 12 inside a third plane P3 which is perpendicular to the first plane PI and which is parallel to the first axis of general extension Al.

According to the invention, the first chamber 13 houses a homogenization device 18 for the distribution of the refrigerant fluid FR inside the first tubes 10a of the first sheet 11. Such a homogenization device 18 is intended to distribute homogeneously the refrigerant fluid FR, in the two-phase liquid-gas state, inside the set of first tubes 10a of the first ply 11. Such a homogenizing device 18 of the distribution of the refrigerant fluid FR extends along the manifold 8, for example along the fourth extension axis A4 so as to channel the coolant towards the bottom of the header, the latter being opposite a mouth through which the coolant enters the manifold 8.

According to the illustrated example, the homogenizing device 18 comprises, for example, a duct 19 extending along a sixth axis of general extension A6 between a first end portion 20 and a second end portion 21 of the duct 19. The sixth axis general extension A6 is preferably parallel to the second axis of general extension A2, and / or to the fourth axis of general extension A4. According to an alternative embodiment, the first end portion 20 is intended to be placed in fluid communication with the first mouth 16 of the heat exchanger 5. According to another embodiment, the first mouth 16 houses the conduit 19, the first end portion 20 is placed in fluid communication with a pipe of the refrigerant circuit 1. According to these two variants, the second end portion 21 is blind and forms a cul-de-sac with regard to the circulation of the refrigerant fluid FR to the Inside the duct 19. Orifices 22 are formed along the duct 19 for the discharge of the refrigerant FR from the duct 19 to the first chamber 13. The orifices 22 are advantageously opposed to the inlet mouths of the first tubes 10a by compared to the sixth extension axis A6. In other words, these orifices 22 are formed in the conduit 24 so that the refrigerant flows from them in a direction opposite to the position of the deflection means 9 relative to the tube bundle.

The homogenizer 18 is likely to be of a different nature in performing the same function of homogenizing the distribution of the refrigerant fluid FR over the length of the first chamber 13, and inside the first tubes 10a of the first ply 11. In FIGS. 3 to 8, and according to the present invention , the return means 9 comprises at least one partition 23, 23a, 23b which divides the return means 9 into at least two compartments 24, 24a, 24b. Each of the compartments 24, 24a, 24b is assigned to at least one tube 10a, 10b of the bundle. In other words, the present invention proposes to divide the return means 9 into a plurality of compartments 24, 24a, 24b via at least one partition 23, 23a, 23b. The return means 9 thus comprises at least two compartments 24, 24a, 24b delimited by at least one partition 23, 23a, 23b. According to a variant shown in Figures 3, 4, 7 and 8, each compartment 24 extends between at least a first tube 10a and at least a second tube 10b. Each compartment 24 is shaped as a subdivision of the return means 9 which forms a fluid communication channel between the first end 101 of the first tube 10a and the third end 103 of the second tube 10b to which the first tube 10a is associated. In other words, each first tube 10a is fluidly associated with a second tube 10b via a dedicated compartment 24 which forms an intermediate fluid flow cell between the first end 101 of said first tube 10a and the third end 103 of the second tube 10b to which the first tube 10a corresponds. The compartments 24 are sealed with each other and two successive compartments 24 are particularly sealed relative to each other.

Each compartment 24 connects a single first tube 10a to a single second tube 10b. As a result, a homogenization of the distribution of the refrigerant fluid FR inside the first tubes 10a, in particular obtained by the presence of the homogenizing device 18, is advantageously retained inside the second tubes

10b, from the partition of the return means 9 into compartments 24 assigned to a first tube 10a and a second tube 10b. These provisions are intended to complete a circulation of the refrigerant fluid FR inside the heat exchanger 5, and in particular between the first tubes 10a and the second tubes 10b.

According to another variant, a compartment connects a plurality of first tubes to a single second tube. According to yet another variant, a compartment connects a single first tube to a plurality of second tubes. According to these variants, the number of partitions is minimized, which allows a lightening of the heat exchanger.

According to another variant illustrated in Figures 5 and 6, a first compartment 24a extends between the set of first tubes 10a and a second compartment 24b extends between the set of second tubes 10b. The first compartment 24a is shaped as a subdivision of the deflection means 9 which forms a fluidic communication channel between the first ends 101 of the first tubes 10a therebetween. The second compartment 24b is shaped as a subdivision of the return means 9 which forms a fluidic communication channel between the second ends 103 of the second tubes 10b therebetween. In other words, the first tubes 10a are fluidly associated with each other via the first compartment 24a and the second tubes 10b are fluidly associated with each other via the second compartment 24b.

According to a variant illustrated in particular in Figures 3 to 6, the return means 9 is arranged in a return box 25 which defines the compartments 24, 24a, 24b. In other words, the return means 9 comprises a return box 25, for example parallelepiped, which forms an enclosure housing the compartments 24. The compartments 24, 24a, 24b are for example parallelepipedic. The gearbox 25 extends longitudinally from a first side edge 26 of the heat exchanger 5 to a second side edge 27 of the heat exchanger 5. The first side edge 26 and the second side edge 27 are of preferably parallel to a third plane P3, orthogonal to the first plane P1 and parallel to the first axis of general extension A1. The junction box 25 extends transversely from a first longitudinal edge 28 of the heat exchanger 5 to a second longitudinal edge 29 of the heat exchanger 5. The first longitudinal edge 28 and the second longitudinal edge 29 are preferably parallel to the first plane Pl. According to an embodiment illustrated in FIGS. 3 and 4, the deflection box 25 houses at least one partition of a first type 23a arranged parallel to the third plane P3. Preferably, the return box 25 houses a plurality of first type partitions 23a. Each first-type partition 23a extends from the first longitudinal edge 28 to the second longitudinal edge 29. The compartments 24 are aligned one after the other along the third axis of general extension A3.

The compartments 24 are aligned between the first side edge 26 of the heat exchanger 5 and the second side edge 27 of the heat exchanger 5. According to another example, the compartments 24 are identical to each other.

Each compartment 24 extends between the first end 101 of any first tube 10a and the third end 103 of the second tube 10b associated therewith. The first tube 10a and the second tube 10b connected by the compartment 24 are two tubes 10a, 10b adjacent to each other and respectively constituting the first ply 11 and the second ply 12, that is to say two tubes 10a, 10b arranged in the same third plane P3. Each compartment 24 extends between the first longitudinal edge 28 and the second longitudinal edge 29. According to an alternative embodiment, this first tube 10a and the second tube 10b are delimited either by the same extruded profile or by the edge-to-edge brazing. -Blank of two stamped plates.

Each compartment 24 has a thickness that is greater than a thickness of the tubes 10a, 10b, the thicknesses being measured between walls delimiting the compartment 24 and the tubes 10a, 10b according to the third axis of general extension A3.

According to an embodiment illustrated in FIGS. 5 and 6, the gearbox 25 houses at least one partition of a second type 23b orthogonally arranged at the third plane P3 and parallel to the first plane P1. Preferably, the gearbox 25 houses a single partition of second type 23b. The second type partition 23b extends from the first side edge 26 of the heat exchanger 5 to the second side edge 27 of the heat exchanger 5. The second type partition 23b comprises at least one window 30 formed therethrough to circulate the refrigerant fluid from the first compartment 24a to the second compartment 24b. Preferably, the second type partition 23b comprises a plurality of windows 30 formed therethrough along the third axis of general extension A3.

The first compartment 24a is equipped with the first ends 101 of the first tubes 10a and the second compartment 24b is equipped with the third ends 103 of the second tubes 10b. Preferably, a window 30 is formed opposite a plurality of first ends 101 and / or third ends 103.

According to an embodiment illustrated in Figures 7 and 8, the fins 15 are also interposed between two successive compartments 24. In other words, the fins 15 interposed between the tubes 10a, 10b are extended to be also interposed between two compartments 24 immediately adjacent . This results in an increase of an exchange surface between the refrigerant fluid FR and the air flow FA. In this case, a thickness of the tubes 10a, 10b is preferably equivalent to a thickness of a compartment 24.

In Figure 9, a plate 32 constituting the heat exchanger 5 shown partially in Figure 7 is shaped as "U". Two plates 32 are abutted two by two by their edges 33 to define the first tube 10a, the second tube 10b and the compartment 24. The edges 33 are for example brazed together.

In FIG. 10, the compartment 24 illustrated in FIGS. 3 and 4 is partially shown and cut away. The compartment 24 extends the third plane P3, perpendicular to the plane of the inlet face of the heat exchanger and orthogonal. to the first axis of general extension Al. As illustrated in FIG. 10, the compartment 24 comprises a passage 34 connecting a first volume 35, in fluid communication with the first end 101, with a second volume 36, itself in fluidic communication with the third end 103. The passage 34 is in particular arranged in a narrowing formed between the first volume 35 and the second volume 36. In this variant, the compartment 24 is generally shaped as an "8" whose loops are formed by the first volume 35 and the second volume 36 and the node is formed by the passage 34 disposed at the intersection of the loops. According to this variant embodiment, the bundle of tubes 10a, 10b is formed by a stack of stamped plates 32 attached in pairs to one another to delimit the first tube 10a and the second tube 10b. Each pair of plates 32 forming two tubes 10a is in contact with an adjacent pair of plates 32, at the level of the first volume 35 and second volume 36. The latter being thicker than the tubes 10a, 10b, a clearance is created where a cooling fin can extend. A septum 23 separating the compartments 24 is then formed by a bottom of a plate 32 defining a tube, or by the bottom of two butt plates 32 and each delimiting a tube 10a, 10b. This first volume 35 and this second volume 36 thus each form a closed eyelet.

Whatever the conformation of the compartment 24, the first tubes 10a of the first ply 11 and the second tubes 10b of the second ply 12 overhang the compartment 24. In the case illustrated in FIG. 10, the first tubes 10a overhang the first volume 35 while the second tubes 10b overhang the second volume 36.

According to the embodiment illustrated in Figures 7 and 8, the compartment 24 is bordered by the two plates 32 which define the tubes 10a, 10b. It follows in particular that the bundle of tubes 10a, 10b and the compartments 24 of the heat exchanger 5 are for example made jointly by a stack of plates 32 superimposed between them and soldered in pairs.

Such a compartmentalization of the return means 9 induces a homogeneous distribution of the refrigerant inside the second tubes 10b of the second ply 12, to finally ensure that the distribution of the refrigerant fluid FR inside the exchanger heat 5 is homogeneous, as a whole. More particularly, the combination of the homogenization device 18 of the distribution of the refrigerating fluid FR inside the first tubes 10a of the first ply 11 and a compartment arrangement 24, 24a, 24b of the return means 9 ensures a homogeneous distribution both inside the first tubes 10a and the second tubes 10b. Such an association provides an improved supply of refrigerant FR of all the tubes 10a, 10b of the heat exchanger 5. It will be noted that the compartmentalisation of the deflection means 9 extends inside the second tubes 10b the homogenization of the distribution of the refrigerant fluid FR obtained by the homogenization device 18 of the distribution of the refrigerant fluid FR inside the first tubes 10a of the first web 11. In other words, the combination of said homogenizer 18 of the distribution and the compartments 24, 24a, 24b ensures a homogeneous distribution of the refrigerant fluid FR between the first chamber 13 and the second chamber 14, and this despite its diphasic nature, liquid and gas. It follows that a temperature of any point of the tubes 10a, 10b is identical to the temperature of any other point of the tubes 10a, 10b, situated inside a plane parallel to the first plane PI and containing these two points. It finally follows that the airflow FA has a homogeneous temperature at the outlet of any point of the heat exchanger 5.

Claims

Heat exchanger (5) comprising a collecting box (8) and a return means (9) between which are interposed a first ply (11) of first tubes (10a) and a second ply (12) of second tubes ( 10b), the first tubes (10a) including a first end (101) in fluid communication with the return means (9) and a second end (102) in fluid communication with the header (8), the second tubes (10b). ) comprising a third end (103) in fluid communication with the return means (9) and a fourth end (104) in fluid connection with the header (8), the manifold (8) housing at least one homogenizing (18) the distribution of a refrigerant (FR) along the header (8), characterized in that the return means (9) comprises at least one partition (23, 23a, 23b) which subdivides the return means (9) in at least two compartments (24, 2 4a, 24b), each compartment (24, 24a, 24b) being equipped with at least one end (101, 103) of a tube (10a, 10b).

2. heat exchanger (5) according to claim 1, wherein each compartment (24) connects at least a first end (101) of a first tube (10a) and at least a third end (103) of a second tube (10b).

Heat exchanger (5) according to any of the preceding claims, wherein the partition (23) is a partition of a first type (23a) extending perpendicularly to a first plane (PI) in which s extends at least one inlet face (37) of the heat exchanger (5) through which an air flow (FA) is able to pass therethrough.

4. Heat exchanger (5) according to any one of the preceding claims, wherein the compartment (24, 24a, 24b) is defined by at least one plate (32) defining at least one of the tubes (10a, 10b). ).

5. Heat exchanger (5) according to the preceding claim, wherein a first tube (10a) and a second tube (10b) are delimited by two plates (32), at least one of the two plates forming the partition (23, 23a). ).

6. heat exchanger (5) according to any one of the preceding claims, wherein a thickness of the compartment (24) is greater than or equal to a thickness of the tubes (10a, 10b).

7. Heat exchanger (5) according to any one of the preceding claims, wherein at least one fin (15) is interposed between two successive compartments (24).

8. heat exchanger (5) according to claim 6, wherein the fin (15) interposed between two successive compartments (24) is an integral part of a heat dissipation means disposed between two successive tubes (10a, 10b) d the same ply (11, 12).

9. Heat exchanger (5) according to claim 6, wherein a thickness of the compartment (24) is equal to a thickness of the tubes (10a, 10b).

10. heat exchanger (5) according to claim 1, wherein a first compartment (24a) connects the first ends (101) of the first tubes (10a) together and a second compartment (24b) connects the third ends (103). second tubes (10b).

Heat exchanger (5) according to claim 10, wherein the partition (23) is a partition of a second type (23b) which extends parallel to a first plane (PI) in which at least an inlet face (37) of the heat exchanger (5) through which an air flow (FA) is able to pass therethrough, the second type partition (23b) comprising at least one window (30) which communicates the first compartment (24a) with the second compartment (24b).

12. heat exchanger (5) according to any preceding claim, wherein the homogenization device (18) of the distribution of a refrigerant (FR) comprises at least one conduit (19) provided with a a plurality of orifices (22) distributed along the conduit (19).

13. Heat exchanger (5) according to the preceding claim, wherein the conduit (19) receives a refrigerant mixer capable of mixing a liquid portion and a gaseous portion of the refrigerant fluid (FR).

14. Refrigerant circuit (1) comprising at least one heat exchanger (5) according to any one of the preceding claims.

15. Use of a heat exchanger (5) according to any one of claims 1 to 13 as an evaporator housed inside a housing (6) of a ventilation installation (7), heating and / or air conditioning equipping a motor vehicle.