EP3548827B1 - Device for distributing a refrigerant inside a collector box of a heat exchanger for an air-conditioning installation of a vehicle - Google Patents

Description

The field of the present invention is that of heat exchangers equipping air conditioning installations for a vehicle, in particular an automobile. The invention relates more specifically to methods of distributing a refrigerant fluid inside a manifold box that such a heat exchanger comprises. In particular, the present invention relates to a device for dispensing a refrigerant fluid according to the preamble of claim 1, and as disclosed by document US 2013/192808 .

A vehicle is currently equipped with an air conditioning installation for thermally treating the air present or sent into the passenger compartment of the vehicle. Such an installation comprises a closed circuit inside which circulates a refrigerant fluid. Successively depending on the direction of circulation of the refrigerant fluid through it, the circuit essentially comprises a compressor, a condenser, an expansion valve and at least one heat exchanger.

The heat exchanger commonly comprises a bundle of tubes interposed between a manifold box and a coolant return box. The refrigerant fluid is admitted through an inlet port inside a manifold, circulates in successive paths in the tubes of the bundle between the manifold and a return box, then is discharged out of the exchanger thermal through an outlet. The outlet mouth is likely to be formed through the collector box or through the return box.

The heat exchanger is for example an evaporator providing heat exchange between the refrigerant fluid and an air flow passing therethrough. In this case, the refrigerant fluid circulates inside the tubes of the bundle and the air flow circulates along the tubes of the bundle for its cooling.

A problem posed resides in the fact that the refrigerant fluid is in the liquid / gaseous two-phase state when it is admitted inside the heat exchanger. Due to the difference between the physical properties between liquid and gas, the refrigerant tends to separate between its liquid phase and its gas phase.

This results in a heterogeneity of the supply to the tubes of the bundle with regard to the different phases of the refrigerant fluid, depending on their position relative to the inlet of the refrigerant fluid inside the manifold box. More particularly, the tubes of the bundle located closest to the inlet mouth are mainly supplied with liquid and conversely the tubes of the bundle furthest from the inlet mouth are mainly supplied with gas.

This phenomenon generates a heterogeneity in the temperature of the air flow which has passed through the heat exchanger in operation. This heterogeneity complicates the thermal management of the device which receives the heat exchanger and ultimately involves temperature differences between two areas of the passenger compartment, while the same air flow temperature is required.

It is known to house a duct provided with a plurality of orifices inside a manifold box. The refrigerant in liquid phase is thus projected through the orifices in the form of droplets over the entire length of the duct, as shown in the document. EP 2 998 137 (DELPHI TECH INC). According to this document, it is proposed to cross the jets of refrigerant liquid projected through two adjacent orifices.

Such an organization is however not optimal from the point of view of the homogenization of the temperature of the air flow at the outlet of the heat exchanger.

The present invention relates to a device for distributing a refrigerant fluid inside a manifold box of a heat exchanger. The subject of the invention is also a heat exchanger equipped with a device for distributing a refrigerant fluid in accordance with the invention. The heat exchanger is in particular designed to equip an air conditioning installation of a vehicle, in particular an automobile.

An object of the invention is to improve the temperature uniformity of the heat exchanger in operation and finally to improve its efficiency.

It is more specifically targeted by the invention to improve the distribution of the refrigerant fluid in the header box in a homogeneous manner between its liquid phase and its gas phase.

It is still more specifically targeted by the invention to provide a homogeneous supply of coolant to the tubes of the bundle interposed between the manifold box and the return box of the heat exchanger.

Another object of the invention is to provide a device for distributing the refrigerant fluid which can be obtained industrially at lower costs.

In particular, it is sought to obtain lower costs and efficiency of the distribution device, making it possible to obtain efficient homogenization of the refrigerant between its liquid phase and its gas phase, and a homogeneous distribution of the refrigerant within each of the heat exchanger bundle tubes

Another aim of the invention is to provide a device for distributing the refrigerant fluid, the organization of which allows it to be easily and inexpensively adapted to heat exchangers of various structures.

Such a diversity of structures of heat exchangers is to be appreciated in particular with regard to the number of tubes of the bundle that they comprise, the modes of circulation of the refrigerant fluid inside the heat exchanger and / or the relative positions between the mouth. inlet and outlet of the refrigerant fluid that comprises the heat exchanger.

The dispensing device of the invention is defined in claim 1.

Thus, the refrigerant fluid is provided to be admitted inside the first duct at its first end comprising the inlet mouth, the first duct being closed at its second end to force the passage of the refrigerant fluid through the orifices.

According to the invention, the dispensing device is mainly recognizable in that at least two orifices immediately adjacent along the longitudinal axis of the first duct are inclined towards the second end of the first duct, their outlet towards the inside of the first duct being closer to its first end than their outlet to the outside of the first duct.

Ideally, all of the orifices of the first duct are inclined orifices. However, various variants can be implemented depending on the configuration of the heat exchanger and its performance obtained.

For example, the first duct may include at least one group of inclined orifices in a number greater than two.

For example again, at least two groups of inclined orifices can be separated from one another by at least one intermediate orifice oriented differently with respect to the inclination of the inclined orifices. The intermediate orifice can for example be oriented perpendicular to the longitudinal axis of the first duct. For example again, the intermediate orifice may be inclined towards the first end of the first duct, its opening towards the inside of the first duct being further from its first end than its opening towards the outside of the first duct.

The velocity of the refrigerant fluid circulating inside the first conduit and discharged successively through the inclined orifices drives the refrigerant fluid, in particular the liquid phase thereof, towards the second end of the first conduit. The inclination of the inclined orifices thus promotes homogeneous evacuation of the refrigerant fluid through them between its liquid phase and its gas phase along the entire first conduit.

The tubes of a bundle of tubes fitted to a heat exchanger are typically successively arranged along the longitudinal axis of the first duct so as to lead to a manifold box. The driving of the refrigerant fluid towards the second end of the first duct thus makes it possible to homogenize the supply of refrigerant fluid to all the tubes of the tube bundle.

The performance of the heat exchanger is increased. For example, the temperature of the air passing through the heat exchanger is found to be considerably balanced along all the tubes of the tube bundle. For example again, the temperature of a cooling liquid circulating through a hydraulic cooling circuit extending at least in part along the heat exchanger, is also considerably balanced during its passage along the assembly. tubes of the tube bundle.

In addition, the mechanical stresses to which the heat exchanger is liable to be subjected due to locally differentiated temperatures are limited, which makes it possible to increase its service life.

It should be noted that the angles of inclination of the inclined orifices are less than 90 ° with respect to the longitudinal axis of the first duct, in order to cause the refrigerant fluid, in particular its liquid phase, to be driven towards the second end of the first duct. The angle of inclination of the inclined orifices is measured between the longitudinal axis of the first duct and the direction of inclination of the inclined orifices towards the second end of the first duct.

The inclination of the inclined orifices is liable to vary within this angular range of less than 90 °, for example according to the individual position of the inclined orifices relative to the ends of the first duct, as a function of their number and / or of their position on along the first duct, and / or as a function of the longitudinal extension of the first duct or also of its transverse extension.

The number and position of the inclined orifices are also liable to vary along and / or around the first duct as a function of the quantity of the coolant liquid entrained as far as the second end of the first duct.

In other words, the number and position of the inclined orifices along and / or around the first duct are adapted according to a specific configuration of a heat exchanger receiving the distribution device, to evacuate the refrigerant fluid. homogeneously between its liquid phase and its gas phase along the first conduit.

According to one embodiment providing a satisfactory compromise, the angles of inclination of the inclined orifices are between 30 ° and 60 ° relative to the longitudinal axis of the first duct.

Such a compromise is considered with regard to the performance obtained from the heat exchanger. An angle of inclination of the inclined orifices of less than 30 ° tends to affect a projection of the coolant through the orifices inclined in a direction providing an optimized supply of coolant to all the tubes of the bundle of tubes of the exchanger. An inclination angle of the inclined orifices greater than 60 ° can make a homogeneous supply of refrigerant fluid to the tubes of the bundle random.

According to a first embodiment, the angles of inclination of at least two inclined orifices are different.

For example, the angles of inclination of at least two inclined orifices vary progressively from the first end towards the second end of the first duct.

More particularly, the angles of inclination of at least two inclined orifices increase from the first end towards the second end of the first duct.

The variation of the angles of inclination of the inclined orifices is preferably carried out successively for each of the inclined orifices. The successive variation of the angles of inclination of the inclined orifices is preferably carried out regularly, in particular in the case where the inclined orifices are equidistant along the first duct.

According to one embodiment, the variation of the angles of inclination of the inclined orifices is carried out successively by group of at least two inclined orifices.

According to a second embodiment, the angles of inclination of the inclined orifices are identical.

In this case, the angle of inclination of each of the inclined orifices is preferably 45 ° to promote uniform delivery of the refrigerant fluid to the second end of the first duct.

It also avoids a suction effect of the refrigerant fluid by the tubes of the tube bundle located closest to the first end of the first duct. Such a suction effect can be induced due to a possible vacuum generated in this zone extending close to the first end of the first duct, in particular in the case where an outlet for the refrigerant fluid outside the heat exchanger. is arranged close to the inlet.

According to one embodiment, the inclined orifices are aligned along a straight line parallel to the longitudinal axis of the first duct. According to one variant, the orifices can be distributed on either side of a straight line parallel to the longitudinal axis of the first duct. The inclined orifices are nevertheless preferably formed along a half-volume of the first duct considered along its longitudinal axis.

According to one embodiment, the inclined orifices are preferably arranged equidistant from each other along the first duct.

According to a variant, two adjacent groups of at least two inclined orifices can be placed along the first duct at a distance of separation from each other different from that separating at least two other groups from one another. adjacent to at least two inclined orifices.

The angles of inclination of at least two inclined holes of a first group of inclined holes may vary from the angles of inclination of the inclined holes of a second group of at least two inclined holes adjacent to the first group of. 'inclined orifices. The variation in the angle of the inclined orifices between the inclined orifices of the first group and those of the second group is in particular dependent on the separation distance between the first group of inclined orifices and the second group of inclined orifices.

According to the invention, the distribution device comprises at least one second longitudinally extended duct, advantageously closed at each of its longitudinal ends. The second duct accommodates the first duct along its longitudinal extension, leaving between them a channel surrounding the first duct. The second duct is provided with passages for discharging the refrigerant fluid out of the channel to the outside of the distribution device.

In other words, the second duct forms an enclosure inside which the first duct extends longitudinally, a transverse gap being formed between the first duct and the second duct to form the channel. The refrigerant fluid evacuated through the orifices of the first duct is able to circulate inside the channel at least in part around the first duct prior to its evacuation outside the distribution device through the passages.

A first step of homogenization of the refrigerant between its liquid phase and its gas phase is carried out during the evacuation of the refrigerant fluid through the orifices towards the channel. A second step of homogenization of the refrigerant between its liquid phase and its gas phase is then carried out during its circulation inside the channel.

The channel is able to house at least one permeable body structured as a mixer to increase the mixing of the refrigerant fluid between its liquid phase and its gaseous phase prior to its evacuation out of the distribution device through the passages. Such a mixer is a device generating a disturbance of a linear flow of the refrigerant fluid flowing through it. The mixer in particular provides obstacles to the linear flow of the refrigerant fluid inside the channel. The homogenization of the refrigerant between its liquid phase and its gas phase during its circulation inside the channel is thus obtained efficient.

It should also be noted that the configuration of the orifice through which the refrigerant fluid is discharged out of the duct can be advantageously differentiated from the configuration of the passage through which the refrigerant fluid is distributed outside the distribution device to the tubes of the bundle. included in the heat exchanger.

Thus the configuration, the number and / or the distribution of orifices along the first duct can be determined independently of the configuration, the number and / or the distribution of passages along the second duct.

The orifices can be specifically configured to optimize the mixture obtained between the liquid phase and the gas phase of the refrigerant fluid discharged through the first duct. The passages can be specifically configured to increase the reliability and improve the homogenization of the distribution of the refrigerant fluid individually to each of the tubes of a bundle of tubes of the heat exchanger.

A combination between the specific characteristics of the orifices and passages can be chosen to improve obtaining a homogeneous supply of coolant to the tubes of the bundle, depending on the specificity of the structural arrangement of the heat exchanger. The specificity of the structural arrangement of the heat exchanger is to be considered in particular with regard to the number and / or the configuration of the tubes of the bundle of tubes that the heat exchanger comprises and / or the methods of circulation of the fluid between the box. manifold and return box.

The characteristics considered for such a combination relate in particular to the cross section, to the number, to the orientation and / or to the positions of the orifices along the first duct and those relating to the cross section, to the number, to the orientation and / or at the positions of the passages along the second duct.

According to a specific form, the passages can be individually assigned to the tubes of the exchanger bundle, being placed in direct communication with their outlet on the manifold box.

• -) soit directement à partir des passages dont la configuration épouse au moins en partie la configuration du débouché à l'intérieur de la boîte collectrices des tubes du faisceau de tubes que comporte l'échangeur thermique,
• -) soit après une circulation du fluide réfrigérant à l'intérieur de la boîte collectrice au moins en partie autour du deuxième conduit.

Thus, depending on the configuration of a heat exchanger receiving the distribution device, the supply of coolant to the tubes of a bundle of tubes that the heat exchanger comprises can be achieved:

• -) either directly from the passages whose configuration at least partially matches the configuration of the outlet inside the manifold box of the tubes of the bundle of tubes that the heat exchanger comprises,
• -) or after circulation of the refrigerant fluid inside the manifold box at least partly around the second duct.

The first duct and the second duct are capable of being mounted eccentric with respect to one another or of being mounted coaxial with one inside the other along the longitudinal axis of the first duct. The first duct and the second duct in particular have an annular conformation centered on the longitudinal axis of the first duct. The cross sections of the first duct and of the second duct can be differentiated from one another, for example being individually circular or oblong in shape.

Preferably, the passages are oriented perpendicular to the longitudinal axis of the first duct.

The homogenization of the quantities of refrigerant fluid successively evacuated through the orifices along the first duct, makes it possible to orient the passages specifically in the direction of the outlets on the manifold box of the tubes of a bundle of tubes that a heat exchanger receiving the distribution device.

According to one embodiment, the orifices are aligned along a first straight line parallel to the longitudinal axis of the first duct and the passages are aligned along a second straight line parallel to the longitudinal axis of the first duct or at d 'other terms parallel to the first line.

The subject of the invention is also a heat exchanger comprising at least one manifold box provided with a distribution device in accordance with the invention. The manifold box is extended in a longitudinal direction by providing a chamber housing the distribution device extending longitudinally inside the chamber following the longitudinal extension of the manifold box.

The chamber communicates with a plurality of tubes of a bundle of tubes of the heat exchanger arranged successively in the longitudinal direction of the header box and interposed between the header box and a fluid return box. refrigerant to the manifold. The orifices of the first duct are inclined towards the bottom of the collector box located opposite the inlet mouth in the longitudinal direction of the collector box.

In other words, the interior volume of the header box is at least partly placed in communication with the tubes of the heat exchanger tube bundle via the chamber housing the distribution device. The tubes are for example grouped together in a first layer of successively adjacent tubes along the longitudinal axis of extension of the manifold. The tubes extend between the header box and the return box in a direction perpendicular to the longitudinal direction of extension of the header box. The inclination of the orifices towards the bottom of the manifold box provides a homogeneous distribution of the refrigerant fluid to all the tubes of the tube bundle.

According to one embodiment, in a transverse direction and with respect to the longitudinal axis of the first duct, the orifices open out out of the first duct opposite the outlet of the tubes of the bundle of tubes onto the chamber, to constrain a circulation of the tube. refrigerant fluid at least partially around the first conduit prior to supplying the tubes of the bundle with refrigerant fluid.

According to one embodiment, a second duct provided with passages opening onto the chamber is interposed between the first duct and a wall of the manifold box delimiting the chamber. A channel is formed between the second duct and the first duct and a space is formed between the second duct and the wall of the manifold delimiting the chamber.

The refrigerant fluid is discharged from the first duct through the orifices inclined towards the channel, circulates inside the channel at least in part around the first duct, and then is discharged out of the channel through the passages to said space. The refrigerant fluid circulates inside the space prior to the supply of refrigerant fluid to the tubes of the tube bundle in order to increase the homogeneous mixture of the refrigerant fluid between its liquid phase and its gas phase.

The passages are in particular oriented perpendicular to the longitudinal axis of the first duct and parallel to a direction of extension of the tubes of the bundle of tubes between the manifold box and the return box.

In a transverse direction and with respect to the longitudinal axis of the first duct, the passages open into the chamber opposite the outlet of the tubes of the bundle of tubes on the chamber and the orifices open out from the first duct on the side of the outlet of the tubes. beam tubes on the chamber.

Thus, the refrigerant fluid is evacuated out of the first duct through the orifices inclined towards the channel in a first zone of the collector box disposed on the side of the tubes of the bundle. Then the refrigerant fluid circulates at least in part around the first duct through the channel, out of which the refrigerant fluid is discharged through the passages to space in a second zone of the header box further away from the tubes of the bundle than the first. zoned. The refrigerant then circulates inside the space at least partly around the second duct towards the outlet of the tubes of the bundle in the manifold box.

The circulations of the coolant on the one hand inside the channel at least partly around the first duct and on the other hand inside the space at least partly around the second duct are thus optimized to increase the flow rate. 'obtaining a homogeneous mixture of the refrigerant between its liquid phase and its gas phase.

According to one embodiment, the chamber is longitudinally compartmentalized by partitions into a plurality of cells each communicating with at least one tube of the bundle of tubes, and advantageously with a single tube of the bundle of tubes. It is therefore associated with a cell with a tube. At least one passage opens into each of the cells. Each of the cells is thus individually supplied with refrigerant fluid from its individual communication with at least one passage.

Thus, the tubes of the tube bundle are individually supplied with refrigerant fluid from a cell which is assigned to them. The distribution of the refrigerant fluid to the tubes of the tube bundle is made more reliable and is obtained efficient.

Preferably, each of the cells communicates with a single tube to promote the homogeneous supply of refrigerant fluid to all the tubes of the tube bundle and to enhance the performance of the homogeneous supply of the tubes of the tube bundle with refrigerant fluid.

The partitions are advantageously formed by the walls of the tubes leaving between them eyelets participating in the formation of the wall of the collecting chamber delimiting the chamber.

The heat exchanger is used in particular as an evaporator, in particular organized to equip an air conditioning installation of a vehicle. The heat exchanger can be used to cool an air flow passing through it or to cool a liquid dedicated to the cooling of an organ, such as at least one battery of a vehicle supplying the energy necessary at least in part to its propulsion.

A further subject of the invention is a refrigerant fluid circuit comprising at least one compressor, a gas condenser or cooler, an expansion device, and a heat exchanger in accordance with the invention, through which a refrigerant fluid flows.

The subject of the invention is also a ventilation, heating and / or air conditioning installation, or air conditioning installation, configured to equip a vehicle, in particular a motor vehicle, comprising at least one heat exchanger in accordance with the invention.

• la figure 1 est une illustration schématique d'un circuit de circulation d'un fluide réfrigérant participant d'une installation de conditionnement d'air d'un véhicule.
• la figure 2 est une illustration schématique d'un échangeur thermique que comporte le circuit schématisé sur la figure 1.
• la figure 3 est une illustration partielle d'un premier conduit participant d'un dispositif de distribution conforme à l'invention.
• la figure 4 est une illustration partielle d'une forme de réalisation d'un échangeur thermique non conforme à l'invention, dans la zone d'une boîte collectrice qu'il comporte.
• la figure 5 est une illustration partielle d'une forme de réalisation d'un échangeur thermique conforme à l'invention, dans la zone d'une boîte collectrice qu'il comporte.
• la figure 6 est une illustration partielle d'une forme de réalisation d'un échangeur thermique conforme à l'invention, dans la zone d'une boîte collectrice qu'il comporte.

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

• the figure 1 is a schematic illustration of a circuit for circulating a refrigerant fluid participating in an air conditioning installation of a vehicle.
• the figure 2 is a schematic illustration of a heat exchanger included in the circuit shown schematically on the figure 1 .
• the figure 3 is a partial illustration of a first duct participating in a dispensing device according to the invention.
• the figure 4 is a partial illustration of an embodiment of a heat exchanger not in accordance with the invention, in the area of a header box that it comprises.
• the figure 5 is a partial illustration of an embodiment of a heat exchanger according to the invention, in the area of a header box that it comprises.
• the figure 6 is a partial illustration of an embodiment of a heat exchanger according to the invention, in the area of a header box that it comprises.

The figures and their description set out the invention in detail and according to particular methods of its implementation. They can of course serve to better define the invention.

On the figure 1 , an air conditioning installation for a vehicle, in particular a motor vehicle, comprises a closed circuit 1 inside which circulates a refrigerant fluid FR. In the exemplary embodiment illustrated, the circuit 1 essentially comprises, successively following the direction SI of circulation of the refrigerant fluid FR, a compressor 2, a condenser 3 or gas cooler, an expansion member 4 and at least one heat exchanger 5 .

The illustrated example of a minimum architecture of circuit 1 is given as an indication and is not restrictive as regards the scope of the invention with regard to various potential architectures of circuit 1.

The heat exchanger 5 is for example dedicated to cooling an air flow FA passing through it, as illustrated on the figure 2 . Such an air flow FA is used in particular to heat treat the air in the passenger compartment of the vehicle or for example also to cool a component of the vehicle in operation. For example again, the heat exchanger 5 can be used for cooling a liquid used to cool a component of the vehicle in operation, such as one or more batteries supplying electrical energy to a propulsive electric motorization of the vehicle.

On the figure 1 and the figure 2 , the heat exchanger 5 comprises a bundle 6 of tubes 12 interposed between a collector box 7 and a return box 8. The collector box 7 extends in a longitudinal direction D1 oriented perpendicularly to a direction D3 of extension of the tubes 12 of the bundle 6 of tubes 12 between the collector box 7 and the return box 8.

The manifold 7 delimits a chamber 9 supplied with refrigerant fluid FR through an inlet 10. The refrigerant fluid FR circulates inside the heat exchanger 5 to cool at least the tubes 12 of the bundle 6 of tubes 12 , then is discharged out of the heat exchanger 5 through an outlet 11.

In the example illustrated, the outlet 11 is provided through the manifold 7, which implies that the heat exchanger 5 is a circulating heat exchanger in “U”. According to a variant, the outlet 11 can be formed through the return box 8, which then implies that the heat exchanger 5 is a heat exchanger with circulation in “I”.

On the figure 2 , the heat exchanger 5 is of the U-type circulation of the refrigerant fluid FR. In the example illustrated, the heat exchanger 5 is intended for cooling an air flow FA. The tubes 12 of the bundle 6 of tubes 12 typically comprise fins 13 promoting heat exchange between the air flow FA and the tubes 12 of the bundle 6 of tubes 12. The air flow FA passes through the bundle 6 of tubes 12 transversely to the general plane P1 of the heat exchanger 5, flowing along the tubes 12.

The refrigerant fluid FR circulates from the header box 7 to a first layer 12a of tubes 12 of the bundle 6 of tubes 12 dedicated to supplying the return box 8 with refrigerant fluid FR. Then the refrigerant FR circulates from the return box 8 to the manifold 7 through a second layer 12b of tubes 12 of the bundle 6. The first layer 12a and the second layer 12b are superimposed in the direction of flow of the flow of air FA through the heat exchanger 5.

Such a configuration of the heat exchanger 5 makes it particularly useful obtaining a homogeneous distribution of the refrigerant fluid FR between its liquid phase and its gas phase and a homogeneous distribution of the refrigerant fluid FR along the manifold 7 towards each of the tubes 12 of the first layer 12a of the bundle 6 of tubes 12.

The example described of the architecture of the heat exchanger 5 and of the methods of circulation of the refrigerant fluid FR between the manifold 7 and the return box 8, are given as an indication and are not restrictive as regards the scope of invention.

On the figure 1 and the figure 2 , the chamber 9 houses a distribution device 18 extending along a longitudinal direction D2 parallel to the longitudinal direction D1 of extension of the manifold 7. The distribution device 18 comprises a first duct 14 extending along a longitudinal axis A1 between a first end 15 and a second end 16 of the first duct 14. The first duct 14 is intended in particular to provide a homogenization of the refrigerant fluid FR between its liquid phase and its gas phase when it is discharged from the first duct 14.

The longitudinal axis A1 of the first duct 14 is oriented parallel to the direction D1 of extension of the manifold 7 and defines the longitudinal direction D2 of extension of the distribution device 18. The distribution device 18 is potentially centered at the center. inside the collector box 7 as shown on the figure 1 . Alternatively, it can be eccentric inside the manifold 7 with respect to a median longitudinal axis A2 of extension of the manifold 7, as illustrated in the figure. figure 2 .

A first longitudinal end 15 of the first duct 14 comprises the inlet mouth 10 for the supply of refrigerant fluid FR to the distribution device 18 via the first duct 14. The inlet mouth 10 is capable of receiving the refrigerant fluid FR from the outside of the distribution device 18 either directly or via a junction member of the heat exchanger 5 with the fluid circuit 1 illustrated in figure 1 . The second end 16 of the first duct 14 is closed by a shutter formed for example by a bottom wall 16 ′ incorporated into the first duct 14 as illustrated in FIG. figure 3 . Note that the bottom wall can also form part of the manifold 7.

At least one orifice 17 is formed through the first duct 14 for the discharge of the refrigerant fluid FR from the first duct 14 to the chamber 9. The first duct preferably comprises a plurality of orifices 17 formed on at least part of the duct. its length to promote the homogenization of the refrigerant fluid discharged along the first conduit 14 between its liquid phase and its gas phase.

On the figures 3 to 6 , various embodiments of a dispensing device 18 are illustrated.

Referring also to the figure 1 and at the figure 2 , the distribution devices 18 illustrated on the figures 3 to 6 are arranged to be housed in the collector box 7 from which the tubes 12 of the first sheet 12a that the heat exchanger 5 comprises are supplied with refrigerant fluid FR. The distribution devices 18 comprise at least the first duct 14 provided with a plurality of orifices 17 through which the refrigerant fluid FR admitted inside the first duct 14 is discharged.

On the embodiments illustrated on the figures 3 to 6 , the first duct 14 comprises orifices 17 which are as a whole inclined towards its second end 16. As referenced on the figure 3 , the inclination of the orifices 17 is such that their outlet 17a towards the inside of the first duct 14 is closer to its first end 15 than their outlet 17b towards the outside of the first duct 14.

In general, it should be considered that at least two adjacent orifices 17 are inclined. The adjacency between two inclined orifices 17 is an arrangement immediately side by side of the two inclined orifices 17, in particular along the longitudinal direction D2 of the dispensing device.

The velocity of the refrigerant fluid FR flowing through the first duct 14 from its first end 15 to its second end 16 is used to promote entrainment of the refrigerant fluid FR, in particular its liquid phase, towards the second end 16 of the first duct 14 .

It emerges that the jets of refrigerant fluid FR evacuated out of the inclined orifices 17 generate a displacement of the vapor phase and of the liquid phase of the refrigerant fluid FR outside the first duct 14 in the direction of the second end 16 of this first duct 14. The supply of refrigerant fluid FR, homogeneous between its liquid phase and its vapor phase, of each of the tubes 12 of the bundle 6 which the heat exchanger 5 comprises, is obtained efficient, which thus promotes the homogenization of the temperature of the air flow FA on an outlet surface of the heat exchanger 5.

In the example illustrated, the inclined orifices 17 as a whole are aligned along a first straight line L1 parallel to the longitudinal axis A1 of the first duct 14. The inclined orifices 17 are arranged equidistant from each other and are inclined in particular by an angle of 45 ° with respect to the longitudinal axis A1 of the first duct 14. The inclined orifices 17 may however be distributed differently along and / or around the first duct 14.

For example, the inclined orifices 17 can be distributed while being aligned along at least two straight lines parallel to the longitudinal axis A1 of the first duct 14. The inclined orifices 17 can be arranged staggered along the first duct 14. For example again, the inclined orifices 17 may be distributed along at least one portion of the helix extending along the longitudinal axis A1 of the first duct 14.

• -) le nombre d'orifices 17 inclinés d'un même groupe d'orifices 17 inclinés peut varier, en étant supérieur à deux orifices 17 inclinés,
• -) le nombre de groupes d'orifices 17 inclinés peut varier. Un groupe d'orifices 17 inclinés est identifiable dans le cas où au moins un orifice intermédiaire est interposé entre au moins deux groupes d'orifices 17 inclinés. Un tel orifice intermédiaire est par exemple orienté perpendiculairement par rapport à l'axe longitudinal A1 du premier conduit 14 ou plus généralement est orienté différemment par rapport à l'orientation des orifices 17 inclinés vers la deuxième extrémité 16 du premier conduit 14,
• -) un angle B1 d'inclinaison individuel de deux orifices 17 inclinés peut varier dans une plage angulaire inférieure à 90°. L'angle B1 d'inclinaison des orifices 17 inclinés est mesuré entre l'axe longitudinal A1 du premier conduit 14 et la pente d'inclinaison des orifices 17 inclinés vue de la deuxième extrémité 16 du premier conduit 14,

• -) l'angle B1 d'inclinaison individuel des orifices 17 inclinés peut varier progressivement depuis la première extrémité 15 vers la deuxième extrémité du premier conduit 16. Plus particulièrement, l'angle B1 d'inclinaison individuel des orifices 17 est susceptible d'augmenter progressivement depuis la première extrémité 15 vers la deuxième extrémité du premier conduit 16,
• -) une distance D4 de séparation entre deux orifices 17 immédiatement adjacents de l'ensemble des orifices 17 du premier conduit 14 peut varier suivant la longueur du premier conduit 14. Par exemple, la distance D4 de séparation entre deux orifices 17 immédiatement adjacents peut augmenter progressivement depuis la première extrémité 15 du premier conduit 14 vers la deuxième extrémité 16 du premier conduit 14. Une telle variation de distance peut être réalisée entre deux orifices 17 adjacents, que l'un au moins des deux orifices 17 adjacents soit incliné ou être un orifice intermédiaire orienté différemment de l'orientation des orifices inclinés, tel que par exemple perpendiculairement à l'axe longitudinal A1 du premier conduit 14,
• -) les orifices 17, inclinés ou non, de l'ensemble des orifices 17 du premier conduit 14 peuvent être diversement répartis le long du premier conduit 14, en étant alignés ou en étant diversement répartis autour du premier conduit 14, tel que par exemple en quinconce ou le long d'une portion d'hélice enroulée au moins en partie autour du premier conduit 14.

Depending on the desired performance of the heat exchanger 5, in particular depending on its configuration and the number of tubes 12 of the bundle 6 of tubes 12 that it comprises:

• -) the number of inclined orifices 17 of the same group of inclined orifices 17 may vary, being greater than two inclined orifices 17,
• -) The number of groups of inclined orifices 17 may vary. A group of inclined orifices 17 can be identified in the case where at least one intermediate orifice is interposed between at least two groups of inclined orifices 17. Such an intermediate orifice is for example oriented perpendicularly with respect to the longitudinal axis A1 of the first duct 14 or more generally is oriented differently with respect to the orientation of the orifices 17 inclined towards the second end 16 of the first duct 14,
• -) An individual angle B1 of inclination of two inclined orifices 17 may vary within an angular range of less than 90 °. The angle B1 of inclination of the inclined orifices 17 is measured between the longitudinal axis A1 of the first duct 14 and the inclination slope of the inclined orifices 17 seen from the second end 16 of the first duct 14,

• -) the angle B1 of individual inclination of the inclined orifices 17 may vary progressively from the first end 15 to the second end of the first duct 16. More particularly, the angle B1 of individual inclination of the orifices 17 is liable to increase. progressively from the first end 15 to the second end of the first duct 16,
• -) a separation distance D4 between two orifices 17 immediately adjacent to the set of orifices 17 of the first duct 14 can vary according to the length of the first duct 14. For example, the separation distance D4 between two immediately adjacent orifices 17 can increase progressively from the first end 15 of the first duct 14 towards the second end 16 of the first duct 14. Such a variation in distance can be made between two adjacent orifices 17, whether at least one of the two adjacent orifices 17 is inclined or be one intermediate orifice oriented differently from the orientation of the inclined orifices, such as for example perpendicular to the longitudinal axis A1 of the first duct 14,
• -) the orifices 17, inclined or not, of the set of orifices 17 of the first duct 14 can be variously distributed along the first duct 14, being aligned or being variously distributed around the first duct 14, such as for example staggered or along a portion of the helix wound at least in part around the first duct 14.

It will be noted that the inclined orifices 17 are formed along the same longitudinal portion of the first duct 14, the transverse profile of which is shaped as a half-section of the first duct 14. For example in the case where the transverse section of the first duct 14 is circular, the longitudinal portion of the first duct 14 comprising the orifices 17 has a transverse section shaped as a semicircle.

On the figures 4 to 6 , a distribution device 18 comprising a first duct 14 is housed inside the chamber 9 formed inside the manifold 7. The chamber 9 is delimited by a wall 7a of the manifold 7 formed by eyelets 25 successively butted in the direction D1 of extension of the manifold 7. The eyelets 25 are formed as an extension of the tubes 12 of the bundle 6 of the heat exchanger 5.

The first duct 14 is preferably mounted on the manifold 7 by being centered inside the chamber 9 along the longitudinal axis A2 of the manifold 7. According to a variant, the first duct 14 can be mounted on the manifold 7 eccentrically with respect to the chamber 9 along the axis longitudinal A2 of the manifold 7.

On the figure 4 , it is considered a transverse direction DT to the longitudinal axis A1 of the first duct 14, parallel to the direction D3 of extension of the tubes 12 of the bundle 6 of tubes 12 between the manifold 7 and the return box 8. The orifices 17 inclined open onto the chamber 9 opposite the outlet 24 of the tubes 12 on the chamber 9 for supplying the tubes 12 with refrigerant fluid FR.

The refrigerant fluid FR admitted into the first duct 14 is successively evacuated to the chamber 9 through the inclined orifices 17, in substantially homogeneous fractions between the liquid phase and the vapor phase of the refrigerant fluid FR. The refrigerant fluid FR then circulates inside the chamber 9 at least in part around the first duct 14 towards the tubes 12 of the bundle 6 of tubes 12 for their individual supply of refrigerant fluid FR.

On the figure 5 and the figure 6 , the first duct 14 is surrounded by a second duct 19 interposed between the first duct 14 and the wall 7a of the manifold 7 delimiting the chamber 9. The second duct 19 surrounds the first duct 14 at a transverse distance, leaving a channel between them 22 for circulating the refrigerant fluid FR evacuated from the orifices 17. The second duct 19 comprises passages 20 for evacuating the refrigerant fluid FR from the distribution device 18 from the channel 22 to the tubes 12 of the bundle 6 of tubes 12.

In the examples illustrated, the second duct 19 is centered inside the chamber 9 and / or centered relative to the first duct 4. The second duct is mounted on the manifold 7 by traversing longitudinally the eyelets 25 forming the wall 7a. of the collector box 7 delimiting the chamber 9. The second conduit 19 is placed at a transverse distance from the wall 7a of the collector box 7 delimiting the chamber 9, leaving between them a space E1 onto which the passages 20 open.

The space E1 forms a space for circulating the refrigerant fluid FR inside the chamber 9 at least in part around the second duct 19 towards the outlets 24 of the tubes 12 of the bundle 6 of tubes 12 on the chamber 9.

The passages 20 are oriented perpendicular to the longitudinal axis A1 of the first duct 14 while being aligned along a straight line L2 parallel to the first straight line L1. The first straight line L1 and the second straight line L2 extend parallel on either side of the longitudinal axis A1 of the first duct 14. Transversely to the longitudinal direction D2 of the manifold 7, the inclined orifices 17 open out into the channel 22 opposite the outlet of the passages 20 on the space E1 on either side of the longitudinal axis A1 of the first duct 14.

With respect to the longitudinal axis A1 of the first duct 14, the orifices 17 are formed along a longitudinal portion of the first duct 14 situated on the side of the outlets 24 of the tubes 12 of the bundle 6 of tubes on the chamber 9. The passages 20 are formed through a longitudinal portion of the second duct 19 located opposite the outlet of the tubes 12 of the bundle 6 of tubes 12 on the chamber 9 relative to the longitudinal axis A1 of the first duct 14.

On the figure 5 , the refrigerant fluid FR is admitted inside the first duct 14 and is evacuated out of the first duct 14 towards the channel 22 through the orifices 17. Then the refrigerant fluid FR is evacuated out of the channel 22 through the passages 20 towards the space El, then circulates in the space E1 at least in part around the second duct 19 towards the outlets 24 of the tubes 12 of the bundle 6 of tubes 12 for their supply of refrigerant fluid FR.

According to the example shown on figure 6 , the chamber 9 is compartmentalized by transverse partitions 23 into a plurality of successively adjacent cells E2 along the longitudinal direction D1 of the collector box 7. At least one passage 20 opens onto each of the cells E2. The partitions 23 are formed by the walls of the eyelets 25 extending the tubes 12 of the bundle 6 of tubes 12. Each of the cells E2 is in communication with one of the tubes 12 of the bundle 6 of tubes 12. The partitions 23 are in contact against each other. the peripheral wall of the second duct 19.

The refrigerant fluid FR is admitted inside the first duct 14 and is evacuated out of the first duct 14 through the orifices 17 towards the channel 22. Then the refrigerant fluid FR is evacuated out of the channel 22 through the passages 20 towards each one. cells E2 making up space E1. The refrigerant fluid FR circulates in each of the cells E2 at least in part around the second conduit 19 towards the outlets 24 of the tubes 12 of the bundle 6 of tubes 12 for their supply of refrigerant fluid FR. Each cell can be associated, that is to say in a fluidic relationship, with a single outlet 24 of tube 12 of the tube bundle. Alternatively, a cell can be associated with a plurality of outlets 24 of tubes 12, provided that this number of outlets is less than the total number of outlets 24 of the bundle of tubes 12.

In the embodiments described above, the invention promotes the liquid-gas mixture of the refrigerant while optimizing the supply of refrigerant fluid thus mixed to the tubes furthest from the inlet mouth for the refrigerant fluid inlet. inside the first duct.

Claims (15)

1. Distribution device (18) for distributing a refrigerant fluid (FR) inside a collector tank (7) of a heat exchanger (5), the distribution device (18) comprising at least a first pipe (14) extending along a longitudinal axis (A1) defining the longitudinal direction of extension of the distribution device (18), the first pipe (14) comprising, at a first (15) of the longitudinal ends thereof, an inlet opening (10) for the entry of the refrigerant fluid (FR) into the first pipe (14), the first pipe (14) being closed at its second longitudinal end (16) and comprising, along at least part of its longitudinal axis (A1), a plurality of discharge orifices (17) for removing the refrigerant fluid (FR) from the first pipe (14), wherein at least two orifices (17) which are adjacent along the longitudinal axis (A1) of the first pipe (14) are inclined towards the second end (16) of the first pipe (14), their opening (17a) towards the inside of the first pipe (14) being closer to its first end (15) than their opening (17b) towards the outside of the first pipe (14), characterized in that the device comprises at least one longitudinally extending second pipe (19), the second pipe (19) housing the first pipe (14) along its longitudinal extension, creating between them a canal (22) surrounding the first pipe (14), the second pipe (19) being provided with discharge passages (20) for removing the refrigerant fluid (FR) from the canal (22) towards the outside of the distribution device (18).
2. Distribution device (18) according to Claim 1, wherein angles (B1) of inclination of the inclined orifices (17) are less than 90° with respect to the longitudinal axis (A1) of the first pipe (14).
3. Distribution device (18) according to Claim 2, wherein the angles (B1) of inclination of the inclined orifices (17) are comprised between 30° and 60° with respect to the longitudinal axis (A1) of the first pipe (14) .
4. Distribution device (18) according to either one of Claims 2 and 3, wherein the angles (B1) of inclination of at least two orifices (17) are different.
5. Distribution device (18) according to any one of Claims 2 to 4, wherein the angles (B1) of inclination of at least two inclined orifices (17) vary progressively from the first end (15) towards the second end (16) of the first pipe (14).
6. Distribution device (18) according to Claim 5, wherein the angles (B1) of inclination of at least two inclined orifices (17) increase from the first end (15) towards the second end (16) of the first pipe (14).
7. Distribution device (18) according to either one of Claims 2 and 3, wherein the angles (B1) of inclination of the inclined orifices (17) are identical.
8. Distribution device (18) according to Claim 7, wherein the angle (B1) of inclination of each of the orifices (17) is 45°.
9. Distribution device (18) according to Claim 1, wherein the passages (20) are oriented at right angles to the longitudinal axis (A1) of the first pipe (14).
10. Distribution device (18) according to either one of Claims 1 and 9, wherein the orifices (17) are aligned along a first straight line (L1) parallel to the longitudinal axis (A1) of the first pipe (14), and wherein the passages (20) are aligned along a second straight line (L2) parallel to the longitudinal axis (A1) of the first pipe (14).
11. Heat exchanger (5) comprising at least one collector tank (7) equipped with a distribution device (18) according to any one of the preceding claims, the collector tank (7) extending in a longitudinal direction (D2), creating a chamber (9) housing the distribution device (18), the chamber (9) communicating with a plurality of tubes (12) of a tube (12) bundle (6) of the heat exchanger (5) which are arranged in succession in the longitudinal direction (D2) of the collector tank (7) and interposed between the collector tank (7) and a return tank (8) returning refrigerant fluid (FR) towards the collector tank (7), the orifices (17) of the first pipe (14) being inclined towards the closed end of the collector tank (7) which is situated on the opposite side to the inlet opening (10) in the longitudinal direction (D2) of the collector tank (7).
12. Heat exchanger according to Claim 11, wherein, in a transverse direction (DT) and with respect to the longitudinal axis (A1) of the first pipe (14), the orifices (17) open out of the first pipe (14) on the opposite side to the opening (24) of the tubes (12) of the tube (12) bundle (6) onto the chamber (9).
13. Heat exchanger according to either one of Claims 11 and 12, wherein a second pipe (19) provided with passages (20) opening onto the chamber (9) is interposed between the first pipe (14) and a wall (7a) of the collector tank (7) delimiting the chamber (9), a canal (22) being formed between the second pipe (19) and the first pipe (14) and a space (E1) being created between the second pipe (19) and the wall (7a) of the collector tank (7) delimiting the chamber (9).
14. Heat exchanger (5) according to Claim 13, wherein the passages (20) are oriented at right angles to the longitudinal axis (A1) of the first pipe (14) and parallel to a direction in which the tubes (12) of the tube (12) bundle (6) extend between the collector tank (7) and the return tank (8).
15. Heat exchanger according to either one of Claims 13 and 14, wherein, in a transverse direction (DT) and with respect to the longitudinal axis (A1) of the first pipe (14), the passages (20) open onto the chamber (9) on the opposite side to the opening of the tubes (12) of the bundle (6) onto the chamber (9) and the orifices (17) open out from the first pipe (14) on the same side as the opening of the tubes (12) of the tube (12) bundle (6) onto the chamber (9).

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