EP3394551B1 - Heat exchanger, in particular for a motor vehicle - Google Patents

Description

The invention relates to the field of heat exchangers in particular capable of acting as condensers according to the preamble of claim 1. US 5,884,503 discloses such a heat exchanger.

Such heat exchangers find particular application in motor vehicles. The heat exchanger can in particular be used as a condenser, more precisely as a water condenser and is commonly designated by “Water condenser” in English. In this case, a first fluid, such as a refrigerating fluid, can enter the heat exchanger in the form of a gas, such as carbon dioxide designated as CO ₂ or other refrigerating fluids such as 1,1,1, 2-tetrafluoroethane known in particular in the industrial nomenclature under the acronym R-134a or 2,3,3,3-tetrafluoropropene known under the acronym R-1234yf. A second fluid, such as liquid, in particular a mixture of brine, is intended to pass through the heat exchanger to cool the refrigerant by condensation.

These heat exchangers can in particular be heat exchangers assembled by brazing.

Furthermore, it is known to add a reservoir of fluid, in particular of refrigerant, also called “bottle”, to a heat exchanger such as a condenser in an air conditioning loop.

After the condensation step, the condensed refrigerant is received and kept in a liquid state inside the tank. The reservoir has the function of separating the liquid and gas phases from the refrigerant in order to let out only the refrigerant in its liquid state. Such a reservoir therefore makes it possible to guarantee that, at the outlet, the refrigerant is completely in the liquid phase.

This tank can be connected to the outlet of the heat exchanger able to act as a condenser, hereinafter referred to as "condenser". This reservoir is therefore in fluid communication with the condenser. For this purpose, the reservoir usually comprises an inlet orifice into which the condensed refrigerant coming from the condenser opens. The reservoir is generally also used for the purpose of sub-cooling the refrigerant, that is to say to lower the temperature of the fluid, used in the air conditioning loop, below the saturation temperature corresponding to the set condensing pressure. This sub-cooling process is a process known in the prior art. To this end, the reservoir may include an outlet orifice which opens into a section of the condenser, so as to subject the liquid refrigerant to an additional passage, known as sub-cooling.

The reservoir can also be used to filter the fluid present in the cold loop, thus preventing particles, having a dimension greater than a determined threshold value, from circulating within the air conditioning loop. An additional functionality also consists in absorbing moisture by virtue of the presence of a material such as a suitable gel, or means of dehydration or a desiccator. The moisture-free refrigerant can then circulate in the air conditioning loop.

Furthermore, a constant problem of heat exchangers implemented in a motor vehicle lies in the allocation of a reduced space, in order to meet the requirements of manufacturers.

Yet another problem is linked to the use of a coolant such as CO ₂ under a very high pressure, generally greater than 100 bars, with a burst pressure which can reach for example up to 340 bars, which implies that the heat exchangers must withstand such high pressures.

The present invention aims to improve the solutions of the state of the art and to at least partially resolve the drawbacks set out above by proposing a heat exchanger which is simple to produce and has a reduced bulk while allowing connection in a simple and following manner. different positions a fluid reservoir at the heat exchanger.

• destinés à être parcourus par le premier fluide et
• destinés à être en communication fluidique avec un réservoir de fluide apte à séparer la phase gazeuse et la phase liquide du premier fluide condensé. Selon l'invention,
• les tubes d'échange thermique comprennent :
  • des canaux de circulation pour la condensation du premier fluide définissant une zone de condensation du faisceau d'échange thermique, et
  • des canaux de circulation pour le sous-refroidissement du premier fluide condensé définissant une zone de sous-refroidissement du faisceau d'échange thermique,
• l'échangeur thermique comprend un empilement de cadres dont au moins certains cadres dits cadres de réception des tubes d'échange thermique sont aptes à recevoir les tubes d'échange thermique et sont respectivement conformés de manière à séparer la zone de condensation et la zone de sous-refroidissement du faisceau d'échange thermique, et
• au moins un cadre de raccord fluidique est conformé de manière à mettre en communication fluidique le réservoir
  • d'une part avec les canaux de circulation pour la condensation et
  • d'autre part et de façon distincte avec les canaux de circulation pour le sous-refroidissement.

To this end, the subject of the invention is a heat exchanger, in particular for a motor vehicle, for a heat exchange between at least a first fluid and a second fluid, said exchanger being able to act as a condenser and comprising a bundle of heat exchange with a plurality of heat exchange tubes comprising circulation channels:

• intended to be traversed by the first fluid and
• intended to be in fluid communication with a fluid reservoir capable of separating the gas phase and the liquid phase from the first condensed fluid. According to the invention,
• the heat exchange tubes include:
  • circulation channels for the condensation of the first fluid defining a condensation zone of the heat exchange bundle, and
  • circulation channels for the sub-cooling of the first condensed fluid defining a zone of sub-cooling of the heat exchange bundle,
• the heat exchanger comprises a stack of frames, at least some of which are called frames for receiving the heat exchange tubes, are capable of receiving the heat exchange tubes and are respectively shaped so as to separate the condensation zone and the subcooling of the heat exchange bundle, and
• at least one fluid connection frame is shaped so as to put the reservoir in fluid communication
  • on the one hand with the circulation channels for condensation and
  • on the other hand and separately with the circulation channels for sub-cooling.

The heat exchanger therefore makes it possible to define in a simple manner a condensation zone and a sub-cooling zone distinct from the heat exchange bundle.

In addition, such a heat exchanger can be connected to, and is preferably equipped with a fluid reservoir for separating the gas phase from the liquid phase of the refrigerant before subcooling. The specific design of the fluid connection frame allows fluid communication between the condensation and sub-cooling zones separate from the heat exchange bundle with the tank.

In this way, the fluid having passed through the circulation channels for the condensation circulates towards the reservoir, and the fluid leaving the reservoir circulates towards the circulation channels for sub-cooling. The condensed fluid at the outlet of the condensation zone necessarily circulates towards the reservoir before a new so-called sub-cooling passage in the sub-cooling zone of the heat exchange bundle.

In the invention, the frames designate a part, or an assembly of parts, which can be rigid, delimiting a closed or not space. In this space can be positioned, in our example, heat exchange tubes.

It will be noted that the heat exchange bundle, which comprises a plurality of heat exchange tubes, is distinct from the frames.

The heat exchanger may further comprise one or more of the following characteristics taken alone or in combination.

According to one aspect of the invention, each frame for receiving the heat exchange tubes is configured to receive both circulation channels for condensation and circulation channels for subcooling defined by the heat exchange tubes. , so that the condensation zone of the heat exchange bundle and the sub-cooling zone of the heat exchange bundle are arranged side by side and without direct fluid communication with each other.

The same frame is shaped to receive both channels of the two condensation zones and sub-cooling of the heat exchange bundle while preventing fluid communication within this frame between these two zones.

In the invention, the frames designate a part, or an assembly of parts, which can be rigid, delimiting a central space. In this central space can be positioned, in our example, heat exchange tubes.

It will be noted that the heat exchange bundle, which comprises a plurality of heat exchange tubes, is distinct from the frames.

According to one embodiment, the frames for receiving the exchange tubes are respectively capable of receiving a single heat exchange tube, and each heat exchange tube comprises on the one hand circulation channels for the condensation of the first fluid, and on the other hand circulation channels for the sub- cooling of the first condensed fluid.

The same heat exchange tube defines both channels for the condensation zone and for the sub-cooling zone. The heat exchange tube may not have circulation channels at the separation between the two condensation and sub-cooling zones. This heat exchange tube is for example an extruded tube.

According to an additional aspect, the receiving frames of the heat exchange tubes have respectively opposite each end of the heat exchange tube which it receives, at least one separation portion arranged between the circulation channels for the condensation of the first fluid and the circulation channels for the sub-cooling of the first condensed fluid, so as to prevent fluid communication between the circulation channels for the condensation and for the sub-cooling.

• au moins une première rangée de premiers tubes d'échange thermique comprenant les canaux de circulation pour la condensation du premier fluide, et
• au moins une deuxième rangée de deuxièmes tubes d'échange thermique comprenant les canaux de circulation pour le sous-refroidissement du premier fluide condensé, et

les cadres de réception des tubes d'échange thermique sont respectivement aptes à recevoir au moins deux tubes d'échange thermique dont un premier tube d'échange thermique de la première rangée et un deuxième tube d'échange thermique de la deuxième rangée.According to another embodiment, the heat exchange bundle comprises:

• at least a first row of first heat exchange tubes comprising the circulation channels for the condensation of the first fluid, and
• at least a second row of second heat exchange tubes comprising the circulation channels for the sub-cooling of the first condensed fluid, and

the receiving frames of the heat exchange tubes are respectively adapted to receive at least two heat exchange tubes including a first heat exchange tube of the first row and a second heat exchange tube of the second row.

According to one aspect of the invention, the heat exchange bundle comprises as many first heat exchange tubes as there are second heat exchange tubes.

According to another aspect of the invention, each frame for receiving the tubes heat exchange comprises at least one partition wall disposed between the first heat exchange tube and the second heat exchange tube, so as to prevent fluid communication between the two heat exchange tubes received in the same frame.

In yet another aspect, the partition extends over the entire length of the heat exchange tubes.

According to a further aspect of the invention, the frames for receiving the heat exchange tubes have a thickness at least equal to the thickness of the heat exchange tubes, in the stacking direction of said frames, this allowing the maintenance of the heat exchange tubes in the respective frames before superimposition of the different frames.

In addition, the portion or partition separating the receiving frames of said tubes also has a thickness at least equal to the thickness of said tubes, this preventing fluid communication between the circulation channels for condensation and those for subcooling. , defined by said tubes.

• des moyens de mise en communication fluidique entre l'entrée pour le premier fluide et les canaux de circulation pour la condensation du premier fluide, et
• des moyens de mise en communication fluidique entre la sortie du premier fluide et les canaux de circulation pour le sous-refroidissement du premier fluide condensé.

According to an additional aspect of the invention, the heat exchanger comprises at least one manifold of the first fluid defining an inlet for the first fluid in the heat exchange bundle and an outlet for the first fluid outside the heat exchange bundle, and the frames for receiving the heat exchange tubes respectively comprise:

• means for placing in fluid communication between the inlet for the first fluid and the circulation channels for the condensation of the first fluid, and
• means for placing in fluid communication between the outlet of the first fluid and the circulation channels for the sub-cooling of the first condensed fluid.

The fluid communication means provided on the first frames make it possible to collect the first fluid and distribute it in the heat exchange tubes maintained in these first frames. It is no longer necessary to provide the collectors on each side of the tubes as in the known prior art solutions.

According to an exemplary embodiment, the means for placing in fluid communication are produced in the form of recesses in the first frames in which the ends of the heat exchange tubes open out, and arranged in fluid communication with the manifold of the first fluid.

According to one aspect, the reception frames of the heat exchange tubes respectively have lateral edges extending substantially perpendicular to the direction of the circulation channels for the first fluid, and in which at least one of said lateral edges has the means for placing in fluid communication.

According to a further aspect of the invention, the heat exchanger comprises a fluid reservoir fixed to the heat exchange bundle.

The tank then forms a unitary system with the heat exchanger.

According to yet another aspect of the invention, the heat exchanger comprises a flange for fixing the reservoir to the heat exchange bundle, and the fluid connection frame is shaped so as to put the reservoir and the circulation channels in fluid communication. for condensing on the one hand, and circulation channels for sub-cooling on the other hand, via the fixing flange.

• un canal d'introduction du premier fluide condensé en provenance des canaux de circulation pour la condensation agencé en communication fluidique avec un orifice d'entrée du réservoir, et
• un canal d'évacuation du premier fluide après séparation de phase en direction des canaux de circulation pour le sous-refroidissement agencé en communication fluidique avec un orifice de sortie du réservoir.

According to an exemplary embodiment, the fixing flange comprises:

• a channel for introducing the first condensed fluid from the circulation channels for the condensation arranged in fluid communication with an inlet orifice of the reservoir, and
• an evacuation channel for the first fluid after phase separation in the direction of the circulation channels for sub-cooling arranged in fluid communication with an outlet orifice of the reservoir.

According to an advantageous embodiment, the fluid connection frame is shaped with a predefined number of teeth separated by notches making it possible to put in fluid communication the reservoir and the circulation channels for condensation on the one hand and the circulation channels for sub-cooling on the other hand.

• mettre en communication fluidique le réservoir avec les canaux de circulation pour la condensation d'un côté de la partie pleine et
• mettre en communication fluidique le réservoir avec les canaux de circulation pour le sous-refroidissement de l'autre côté de la partie pleine.

According to a particular aspect, the fluidic connection frame comprises at least one edge on which rests at least one end of the heat exchange tube and having a solid part, said edge is shaped so as to:

• put the tank in fluid communication with the circulation channels for condensation on one side of the solid part and
• put the tank in fluid communication with the circulation channels for sub-cooling on the other side of the solid part.

The solid part is devoid of fluid communication means.

According to an exemplary embodiment, the solid part of the fluid connection frame has a width at least equal to the width of the separation portion of the frames for receiving heat exchange tubes which are arranged in the heat exchange bundle elsewhere than '' opposite the tank and / or the mounting flange.

• premiers cadres de réception des tubes d'échange thermique, et de
• deuxièmes cadres définissant respectivement au moins un deuxième canal de circulation pour le deuxième fluide, les deuxièmes cadres présentant :
  • des guides pour le passage du premier fluide à condenser, agencés dans l'alignement des moyens de mise en communication des premiers cadres, de manière à permettre l'écoulement du premier fluide dans l'empilement des premiers cadres et des deuxièmes cadres pour la condensation du premier fluide, et
  • des guides pour le passage du premier fluide condensé, agencés dans l'alignement des moyens de mise en communication des premiers cadres, de manière à permettre l'écoulement du premier fluide condensé dans l'empilement des premiers cadres et des deuxièmes cadres pour le sous-refroidissement du premier fluide condensé.

According to yet another aspect of the invention, the heat exchanger comprises an alternating stack of:

• first frames for receiving the heat exchange tubes, and
• second frames respectively defining at least one second circulation channel for the second fluid, the second frames having:
  • guides for the passage of the first fluid to be condensed, arranged in alignment with the means for bringing the first frames into communication, so as to allow the flow of the first fluid in the stack of the first frames and of the second frames for the condensation of the first fluid, and
  • guides for the passage of the first condensed fluid, arranged in alignment with the means of communication of the first frames, so as to allow the flow of the first condensed fluid in stacking the first frames and second frames for the sub-cooling of the first condensed fluid.

The heat exchanger thus comprises a stack of simple elements, namely frames and heat exchange tubes in which the first fluid circulates, such as a cooling fluid, inserted in the first frames and between which the second fluid circulates. such as coolant.

Such an architecture allows a simpler realization of the heat exchanger as a whole and very compact.

Likewise, the fluid communication means provided on the second frames make it possible to collect the second fluid and to distribute it between the heat exchange tubes. This offers great flexibility of arrangement of the manifold of the first fluid and the inlet and outlet pipes for the second fluid.

The different superimposed frames allow the flow path of the first refrigerant to be created, when the frames are assembled for example by soldering, and likewise, the different superimposed frames allow the flow of coolant flow to be created, in particular on two opposite sides of the heat exchange bundle.

The heat exchanger can be used for the circulation of at least one high pressure fluid, in particular of a pressure greater than 100 bars, for example the first fluid is a cooling fluid intended to circulate at high pressure such as CO ₂ .

Such a heat exchanger has better mechanical strength compared to the solutions of the prior art and very good resistance to high pressures, especially when a CO ₂ type refrigerant is used.

According to another aspect of the invention, the second frames have a portion devoid of guides for the passage of the first fluid, arranged between the guides for the passage of the first fluid to be condensed on the one hand and the guides for the passage of the first fluid condensed.

According to an exemplary embodiment, the portion devoid of guides for the passage of the first fluid provided on the second frames has a width at least equal to the width of the solid part of the fluid connection frame arranged opposite the reservoir and / or the fixing flange.

According to an additional aspect, the heat exchanger comprises at least one inlet pipe and one outlet pipe for the second fluid, and the second frames respectively have means for placing in fluid communication between the second circulation channel and the pipes d inlet and outlet for the second fluid.

According to one embodiment, the means for placing the second frames in fluid communication are produced in the form of through openings opening respectively onto the interior of a second frame.

According to a particular example, the second frames respectively have at least two handles delimiting the through openings for setting in fluid communication, with a first handle arranged in fluid communication with the inlet manifold and a second handle arranged in fluid communication with the manifold exit.

In one aspect, the first frames have guides for the passage of the second fluid arranged in alignment with the through openings for fluid communication of the second frames.

• la figure 1 est une vue partielle en perspective d'un échangeur thermique comprenant un faisceau d'échange thermique et un réservoir de fluide selon une première variante, montrant en coupe partielle une extrémité du faisceau dans la direction d'empilement du faisceau,
• la figure 2a est une vue en perspective partielle de l'échangeur thermique de la figure 1,
• la figure 2b est une vue en perspective partielle de l'échangeur thermique selon une deuxième variante,
• la figure 3a est une vue partielle en perspective de l'échangeur thermique de la figure 1 montrant un faisceau d'échange thermique comprenant deux rangées de tubes d'échange thermique,
• la figure 3b est une vue partielle en éclaté du faisceau d'échange thermique et d'une bride de fixation de l'échangeur thermique de la figure 3a,
• la figure 4 est une vue partielle en perspective d'un échangeur thermique comprenant un faisceau d'échange thermique avec une rangée de tubes d'échange thermique,
• la figure 5 représente de façon schématique un premier cadre du faisceau d'échange thermique recevant un seul tube d'échange thermique,
• la figure 6 représente de façon schématique un premier cadre du faisceau d'échange thermique recevant deux tubes d'échange thermique,
• la figure 7 représente de façon schématique un deuxième cadre du faisceau d'échange thermique,
• la figure 8 est une première vue agrandie d'une partie de la figure 3a montrant le raccord fluidique entre la bride de fixation et le faisceau d'échange thermique,
• la figure 9 est une vue encore agrandie de la figure 8 montrant le raccord fluidique entre la bride de fixation et le faisceau d'échange thermique et sur laquelle on a ôté un des tubes d'échange thermique du faisceau d'échange thermique reposant sur un cadre spécifique de raccord fluidique, et
• la figure 10 représente de façon schématique un cadre spécifique du faisceau d'échange thermique pour le raccord fluidique avec le réservoir de fluide.

Other characteristics and advantages of the invention will appear more clearly on reading the following description, given by way of illustrative and nonlimiting example, and of the appended drawings among which:

• the figure 1 is a partial perspective view of a heat exchanger comprising a heat exchange bundle and a fluid reservoir according to a first variant, showing in partial section one end of the bundle in the stacking direction of the bundle,
• the figure 2a is a partial perspective view of the heat exchanger of the figure 1 ,
• the figure 2b is a partial perspective view of the heat exchanger according to a second variant,
• the figure 3a is a partial perspective view of the heat exchanger of the figure 1 showing a heat exchange bundle comprising two rows of heat exchange tubes,
• the figure 3b is a partial exploded view of the heat exchange bundle and a mounting flange of the heat exchanger of the figure 3a ,
• the figure 4 is a partial perspective view of a heat exchanger comprising a heat exchange bundle with a row of heat exchange tubes,
• the figure 5 schematically represents a first frame of the heat exchange bundle receiving a single heat exchange tube,
• the figure 6 schematically represents a first frame of the heat exchange bundle receiving two heat exchange tubes,
• the figure 7 schematically represents a second frame of the heat exchange bundle,
• the figure 8 is a first enlarged view of part of the figure 3a showing the fluid connection between the fixing flange and the heat exchange bundle,
• the figure 9 is an enlarged view of the figure 8 showing the fluid connection between the fixing flange and the heat exchange bundle and on which one of the heat exchange tubes has been removed from the heat exchange bundle resting on a specific fluid connection frame, and
• the figure 10 schematically represents a specific frame of the heat exchange bundle for the fluid connection with the fluid reservoir.

In these figures, the substantially identical elements have the same references.

The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the characteristics apply only to a single embodiment. Simple features of different embodiments can also be combined and / or interchanged to provide other embodiments.

In the description one can index certain elements, such as for example first element or second element etc. In this case, it is a simple indexing to differentiate and name similar but not identical elements.

This indexing does not imply a priority of one element over another and one can easily interchange such names without departing from the scope of this description. This indexing does not imply an order in time either.

In the present, the terms upper and lower, or top and bottom, or vertical and horizontal, are designated with reference to the arrangement of the elements in the figures. This arrangement corresponds to the arrangement of the elements in the mounted state in a motor vehicle in particular.

Heat exchanger

With reference to the figure 1 , the invention relates to a heat exchanger 1 in particular for a motor vehicle, for a heat exchange between at least a first fluid and a second fluid.

The first fluid can enter the heat exchanger 1 in gaseous form and the second fluid in liquid form.

It is in particular a heat exchanger 1 assembled by brazing. To do this, the heat exchanger 1 has at least partially, that is to say on at least certain elements or certain parts, a coating intended to melt to ensure the joining of elements of the heat exchanger 1 as well as sealing during assembly by brazing.

The heat exchanger 1 according to the invention is in particular suitable for the circulation of at least one fluid having a high operating pressure, in particular greater than 100 bars.

For example, the first fluid is a cooling fluid intended to circulate at high pressure such as CO ₂ , also designated by R744 according to the industrial nomenclature.

Other refrigerants can be used, such as 1,1,1,2-tetrafluoroethane or 2,3,3,3-Tetrafluoropropene known by the acronym R-1234yf, respectively known in the industrial nomenclature by R134a or R -1234yf.

The heat exchanger 1 is in particular capable of acting as a condenser, in particular a water condenser, in which the refrigerant fluid such as CO ₂ is cooled by a second fluid, for example in liquid form, such as coolant comprising a mixture of glycol water.

The heat exchanger 1 comprises a heat exchange bundle 3 allowing the heat exchange between the first fluid and the second fluid.

In the example illustrated, the heat exchange bundle 3 has a generally substantially parallelepiped shape.

The introduction and evacuation of the first fluid in the heat exchange bundle 3 or out of the heat exchange bundle 3 are shown schematically by way of example by the arrows F1 _I for the introduction and F1 ' _O for the evacuation on Figures 2a and 2b .

The introduction of the second fluid into the heat exchange bundle 3 and the discharge of the second fluid from the heat exchange bundle 3 are shown schematically by way of example by the arrows F2 _I for the introduction and F2 _O for the evacuation on Figures 1 to 2b .

Finally, the heat exchanger 1, and more particularly the heat exchange bundle 3, can be configured for circulation in at least two passes of one of the two fluids, in particular of the second fluid as will be described in more detail. thereafter.

More specifically, with reference to Figures 2a to 4 , the heat exchange bundle 3 comprises a plurality of heat exchange tubes 5; 51, 53. The heat exchange tubes 5; 51, 53 are described in more detail below.

The heat exchange tubes 5; 51, 53 are stacked so as to alternately define first circulation channels 7 for the first fluid in the heat exchange tubes 5; 51, 53 and second circulation channels 9 for the second fluid between the heat exchange tubes 5; 51, 53.

Turbulators 11 (see figures 1 and 3b ) of the flow of the second fluid are advantageously arranged in the second circulation channels 9, thus improving the heat exchange between the two fluids.

The turbulators 11 can be carried by a separate element from the heat exchange tubes 5; 51, 53 as illustrated in the figures 1 and 3 .

The turbulators 11 are, for example, substantially in the form of crenellations, forming projections in the second circulation channels 9.

The slots can be made by stamping.

According to a variant not illustrated, turbulators 11 can be formed on the heat exchange tubes 5; 51, 53, for example by deformations such as undulations of the heat exchange tubes 5 which protrude into the second circulation channels 9 for the second fluid.

Interleaves are advantageously arranged between the heat exchange tubes 5; 51, 53, and define the pitch between the heat exchange tubes 5; 51, 53.

According to an advantageous embodiment visible on the figures 3a , 3b and 4 , the heat exchange bundle 3 comprises a stack of frames 13, 15, 16. The stack of the different frames 13, 15, 16 is done here substantially vertically.

In particular, the heat exchange bundle 3 comprises an alternating stack of first frames 13 and second frames 15.

At least some second frames 15 form the spacers, these spacer frames 15 are arranged between two first frames 13 for receiving the heat exchange tubes 5, thus defining the pitch between two stages of heat exchange tubes 5; 51, 53.

Each first frame 13 is capable of receiving a heat exchange tube 5 or several heat exchange tubes 51, 53, and this assembly forms a stage of the heat exchange bundle 3.

The first frames 13 can be designated by tube frames.

Each second frame 15 can receive turbulators 11 and this assembly forms another stage of the heat exchange bundle 3.

These two sets or stages are repeated as many times as necessary according to the space available and the performance to be achieved. The first frames 13 and the second frames 15 are described in more detail below.

The heat exchange bundle 3 further comprises at least one specific frame called a fluidic connection 16 visible on the Figures 3a to 4 , as described below.

For example, closure plates 17, 18 (see figures 1 to 4 ), in particular at least one lower closing plate 17 and at least one upper closing plate 18, can be arranged on either side of the stack of first frames 13 and second frames 15, so as to close the heat exchange bundle 3.

Each closure plate 17 or 18 is therefore arranged at one end of the heat exchange bundle 3 in the stacking direction of the various elements, in particular of the different frames 13, 15, 16, of the heat exchange bundle 3.

With reference to the provision illustrated on the figures 1 to 4 , the closure plates 17, 18 are arranged at the ends in the height direction of the heat exchange bundle 3, which here corresponds to a substantially vertical axis in the mounted state of the heat exchanger 1 in a motor vehicle by example.

Referring to Figures 2a and 2b , the heat exchanger 1 further comprises at least one manifold 19 of the first fluid arranged in fluid communication with the first circulation channels 7.

The manifold 19 is, according to the example illustrated, arranged on the lower closure plate 17 disposed at the bottom of the heat exchange bundle 3.

More specifically, the manifold 19 of the first fluid defines an inlet 19A for the first fluid in the heat exchange bundle 3 and an outlet 19B for the first fluid outside the heat exchange bundle 3.

The heat exchanger 1 further comprises at least two fluid inlet and outlet pipes 21 allowing the introduction and the evacuation of the second fluid. In this example, the two pipes 21 are arranged in opposite directions on either side of the stack of the heat exchange bundle 3.

Namely, a first tube 21 is arranged on the upper closure plate 18 while the other tube 21 is arranged on the lower closure plate 17 and therefore on the same closure plate as the manifold 19 for the first fluid.

In particular, the manifold 19 can be arranged on one side of the heat exchange bundle 3 and the pipes 21 can be arranged on the other side of the heat exchange bundle 3.

According to the arrangement illustrated on the Figures 1 to 2b , the manifold 19 is arranged on the right while the pipes 21 are arranged on the left.

In the example shown on the Figures 1 to 2b , the pipes 21 are for example of substantially cylindrical shape, and extend longitudinally in the direction of the height of the heat exchange bundle 3, in other words in the direction of stacking of the different elements, in particular of the different frames 13, 15 , 16, of the heat exchange bundle 3, here along a substantially vertical axis in the mounted state in the motor vehicle.

Finally, the heat exchanger 1 able to act as a condenser further comprises a reservoir 22 allowing phase separation of the first fluid after condensation.

This reservoir 22 described in more detail below is for example fixed to the heat exchange bundle 3 by means of a fixing flange 24.

According to a variant not shown, the reservoir 22 could be offset from the heat exchange bundle 3 by being fluidly connected to the heat exchange bundle 3.

Heat exchange tubes

Referring now to figures 1 to 6 , the heat exchange tubes 5 will now be described in more detail; 51, 53.

The heat exchange tubes 5; 51, 53 are preferably produced by extrusion.

The heat exchange tubes 5; 51, 53 can be produced in the form of flat tubes, advantageous in terms of space.

The flat tubes 5; 51, 53 have a generally substantially rectangular general shape, with a length for example of the order of 32 mm and a thickness of the order of a millimeter.

The thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the heat exchange tubes 5; 51.53.

In other words, the thickness is considered in the stacking direction of the heat exchange tubes 5; 51, 53.

According to the exemplary embodiment illustrated with a heat exchange bundle 3 of substantially parallelepiped shape, the heat exchange tubes 5; 51, 53 here extend longitudinally along the longitudinal axis of the heat exchange bundle 3.

The heat exchange tubes 5; 51, 53 are stacked with a predefined pitch between the heat exchange tubes 5; 51, 53, here one above the other in the height direction of the heat exchange bundle 3.

Each heat exchange tube 5; 51, 53 defines a predetermined number of first circulation channels 7 for the first fluid, such as a cooling fluid, in particular of micro-circulation channels 7 for the first fluid.

The first channels or micro-channels 7 here extend substantially longitudinally, in a substantially "I" or rectilinear shape.

The first circulation channels or micro-channels 7 for the first fluid allowing the flow of the first fluid extend respectively in a direction parallel to the longitudinal direction of the heat exchange tubes 5; 51, 53.

More specifically, the heat exchange tubes 5; 51, 53 define on the one hand circulation channels 71 for the condensation of the first fluid, and on the other hand circulation channels 73 for the sub-cooling of the first condensed fluid.

In the figures, the reference 7 generally designates the first channels defined by the heat exchange tubes 5, 51 or 53.

Overall, all the first channels 7 perform the same general function which is to allow the circulation of the first fluid in the heat exchange bundle 3. The references 71 and 73 designate particular classes of the first channels 7.

This is a first class of first channels referenced by 71 which corresponds to the first channels among all of the first channels 7 which are provided for the circulation of the first fluid during the condensation of the first fluid, while the second class of first channels referenced by 73 corresponds to the first channels among all the first channels 7 which are provided for the circulation of the first fluid after condensation during the sub-cooling of the first fluid.

The first fluid can follow a circulation in a so-called “I” or rectilinear circulation pass in the condensation channels 71.

Likewise, the first fluid can follow a circulation in a so-called "I" or rectilinear circulation pass in the sub-cooling channels 73.

On the Figures 1 to 2b , the arrows F1 illustrate the circulation of the first fluid during the condensation, while the arrows F1 'illustrate the circulation of the first fluid after condensation for the sub-cooling.

All of the circulation channels 71 for the condensation define a zone of condensation of the heat exchange bundle 3, and all of the circulation channels 73 for the sub-cooling define a zone of sub-cooling of the exchange bundle thermal 3.

The condensation zone defined by the circulation channels 71 for the condensation can be substantially equal to the sub-cooling zone defined by the circulation channels 73 for the sub-cooling.

Preferably, these two zones are not equal and the condensation zone is provided for larger than the sub-cooling zone.

For example, a distribution of the order of at least 60%, preferably from 70% to 80%, can be provided for the condensation zone, and for example of the order of 40%, preferably from 20% to 30%, for the sub-cooling zone.

First embodiment of the heat exchange tubes

With reference to the figure 4 describes a heat exchange tube 5 according to a first embodiment.

According to this first embodiment, each heat exchange tube 5 defines a stage of the heat exchange bundle 3.

We can also speak in this case of heat exchange monotube 5 to distinguish from the second embodiment described below.

In other words, the heat exchange bundle 3 comprises a stack of heat exchange tubes 5 defining a row of heat exchange tubes 5.

More specifically, each heat exchange tube 5 comprises on the one hand circulation channels 71 for the condensation of the first fluid, and on the other hand circulation channels 73 for the sub-cooling of the first condensed fluid.

The two groups of channels 71, 73 for the condensation on the one hand and for the sub-cooling on the other hand defined by the same heat exchange tube 5 makes it possible to limit the number of parts of the heat exchanger 1 to be produced and to assemble.

The separation between the circulation channels 71 for the condensation and the circulation channels 73 for the sub-cooling is illustrated diagrammatically by dashes on the figure 4 .

According to an advantageous alternative embodiment, provision may be made for an absence of first circulation channels 7 marking the separation between the circulation channels 71 for condensation and the circulation channels 73 for subcooling.

In addition, provision may be made for the circulation channels 71 for the condensation and the circulation channels 73 for sub-cooling define the same passage section.

In particular, as many circulation channels 71 can be provided for condensation as there are circulation channels 73 for sub-cooling. The separation is then substantially central as in the example illustrated.

The passage section for condensation and the passage section for sub-cooling can advantageously be adapted as required.

For example, the passage section for subcooling may be less than the passage section for condensation.

The number of circulation channels 71 for condensation can be different from the number of circulation channels 73 for subcooling.

Advantageously, one can provide more circulation channels 71 for condensation than circulation channels 73 for sub-cooling.

As a variant or in addition, the circulation channels 71 for the condensation can be of different size compared to the size of the circulation channels 73 for the sub-cooling, so as to adapt the passage section for the condensation and for the sub -cooling.

Second embodiment of the heat exchange tubes

With reference to Figures 1 to 3b , heat exchange tubes 51, 53 are described according to a second embodiment.

According to this second embodiment, several, here two, adjacent heat exchange tubes 51 and 53, together define a stage of the heat exchange bundle 3.

Each heat exchange tube 51, respectively 53 comprises circulation channels 71, respectively 73, either for condensation or for sub-cooling. Clearly, first heat exchange tubes 51 include the circulation channels 71 for the condensation of the first fluid and second heat exchange tubes 53, different from the first heat exchange tubes 51, include the circulation channels 73 for the sub-cooling of the first condensed fluid.

• au moins une première rangée A de premiers tubes d'échange thermique 51, et
• au moins une deuxième rangée B de deuxièmes tubes d'échange thermique 53.

The heat exchange bundle 3 comprises in this case:

• at least a first row A of first heat exchange tubes 51, and
• at least a second row B of second heat exchange tubes 53.

The heat exchange bundle 3 comprises as many first heat exchange tubes 51 as there are second heat exchange tubes 53.

In order to facilitate the understanding of Figures 2a and 2b , only certain first heat exchange tubes 51 are shown.

Provision may also be made for the circulation channels 71 for the condensation of the first heat exchange tubes 51 to define the same passage section as the circulation channels 73 for the sub-cooling of the second heat exchange tubes 53.

Of course, the passage section for condensation and for sub-cooling can be advantageously adapted as required.

Optimally, the passage section for sub-cooling can be less than the passage section for condensation.

In particular, the first heat exchange tubes 51 and the second heat exchange tubes 53 can have the same dimensions as in the example illustrated.

As a variant, the dimensions of the first heat exchange tubes 51 and of the second heat exchange tubes 53 may be different, for example the second heat exchange tubes 53 may have a smaller width than the first heat exchange tubes 51.

In general, the dimensions of the heat exchange tubes 51, 53 are advantageously variable in the direction of the width of the heat exchange bundle 3 to adapt the size of the condensation zone and the sub-cooling zone.

As a variant or in addition, the number and / or the size of the circulation channels 71 for condensation may or may be different compared to the circulation channels 73 for sub-cooling.

First frames called tube frames

With reference to Figures 5 and 6 , the first frames 13 are now described in more detail.

The first frames 13 can be at least partially made of aluminum.

The first frames 13 can be produced by stamping cutting in a simple manner.

• deux bords opposés 13A, 13B s'étendant de façon perpendiculaire à la direction des premiers canaux de circulation 7 du premier fluide, autrement dit ici perpendiculairement à la direction longitudinale des tubes d'échange thermique 5 ou 51, 53, et
• deux autres bords opposés 13C, 13D s'étendant parallèlement à la direction des premiers canaux de circulation 7 du premier fluide, autrement dit ici parallèlement à la direction longitudinale des tubes d'échange thermique 5 ou 51, 53.

The first frames 13 present:

• two opposite edges 13A, 13B extending perpendicular to the direction of the first circulation channels 7 of the first fluid, in other words here perpendicular to the longitudinal direction of the heat exchange tubes 5 or 51, 53, and
• two other opposite edges 13C, 13D extending parallel to the direction of the first circulation channels 7 of the first fluid, in other words here parallel to the longitudinal direction of the heat exchange tubes 5 or 51, 53.

• deux bords opposés 13A, 13B s'étendant perpendiculairement à la direction générale d'écoulement du premier fluide, et
• deux autres bords opposés 13C, 13D s'étendant parallèlement à la direction générale d'écoulement du premier fluide.

The first frames 13 can also be defined relative to the general direction of flow of the first fluid, namely that the first frames 13 have:

• two opposite edges 13A, 13B extending perpendicular to the general direction of flow of the first fluid, and
• two other opposite edges 13C, 13D extending parallel to the general direction of flow of the first fluid.

The general direction of flow of the first fluid means the direction of circulation in “I” or rectilinear in the circulation channels 71 for the condensation, respectively in the circulation channels 73 for the sub-cooling.

In the examples illustrated, the first frames 13 are of generally substantially rectangular shape and have two longitudinal edges 13C, 13D, forming long sides, extending substantially parallel to the general direction of flow of the first fluid and two lateral edges. 13A, 13B, forming short sides, extending in the width direction, substantially perpendicular to the direction of flow of the first fluid.

However, according to other embodiments, provision could be made for frames having a general shape which is not rectangular, for example elliptical, or in the form of a diamond.

The longitudinal axis of the first frames 13 and the heat exchange tubes 5 or 51, 53 is here combined.

These first frames 13 have the same thickness as the heat exchange tubes 5; 51, 53 that they receive, in particular of the order of a few millimeters, for example of the order of 1mm.

As before, the thickness is considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the first frames 13. Thus, the heat exchange tubes 5; 51, 53 can be maintained in the first respective frames 13 before the different frames 13, 15, 16 are superimposed.

In addition, each receiving frame 13 of the heat exchange tubes 5; 51, 53 is configured to receive both circulation channels 71 for condensation and circulation channels 73 for sub-cooling defined by the heat exchange tubes 5; 51, 53.

In this way, the condensation zone of the heat exchange bundle 3 and the sub-cooling zone of the heat exchange bundle 3 are arranged side by side.

In addition, the first frames 13 for receiving the heat exchange tubes 5; 51, 53 are respectively shaped so as to separate the condensation zone and the sub-cooling zone from the heat exchange bundle 3.

Thus, the two zones of condensation of the heat exchange bundle 3 and of sub-cooling of the heat exchange bundle 3 side by side are arranged without direct fluid communication with each other.

First embodiment of the first frames

According to a first embodiment illustrated on the figures 4 and 5 , each first frame 13 is able to receive a single heat exchange tube 5 comprising on the one hand the circulation channels 71 for the condensation of the first fluid, and on the other hand the circulation channels 73 for the sub-cooling of the first condensed fluid. To this end, each first frame 13 has a housing 130 for receiving an associated heat exchange tube 5.

In order to allow the flow of the first fluid in the heat exchange bundle 3, the first frames 13 comprise means for putting in fluid communication 131a, 131b of the first circulation channels 7 of the heat exchange tubes 5 with the manifold 19.

The fluid communication means 131a, 131b of each first frame 13 are therefore arranged in fluid communication with the fluid communication means 131a, 131b of the other first frames 13 of the heat exchange bundle 3 and with the manifold 19 .

• des moyens de mise en communication fluidique 131a entre l'entrée 19A (visible sur les figures 2a, 2b) pour le premier fluide et les canaux 71 de circulation pour la condensation du premier fluide, et
• des moyens de mise en communication fluidique 131b (figures 4-5) entre la sortie 19B (visible sur les figures 2a, 2b) du premier fluide et les canaux 73 de circulation pour le sous-refroidissement du premier fluide condensé.

More specifically, the frames 13 for receiving the heat exchange tubes 5 respectively comprise:

• fluid communication means 131a between the input 19A (visible on the Figures 2a, 2b ) for the first fluid and the circulation channels 71 for the condensation of the first fluid, and
• fluid communication means 131b ( figures 4-5 ) between exit 19B (visible on Figures 2a, 2b ) of the first fluid and the circulation channels 73 for the sub-cooling of the first condensed fluid.

According to the example illustrated, the first frames 13 respectively have a predefined number of recesses 131a, 131b forming the means of setting in fluid communication, in which the ends, in particular the longitudinal ends, of the heat exchange tubes 5 open out.

The fluid communication means 131a, 131b can be carried by the lateral edges 13A, 13B of the first frames 13.

In this example, the recesses 131a, 131b are provided on the two opposite edges 13A, 13B of the first frames 13 which are opposite the ends of the heat exchange tubes 5. These are the lateral edges of the first frames 13.

The first frames 13 are arranged so that their recesses 131a are in fluid communication with the recesses 131a of the other first frames 13. Here, the recesses 131a of the first frames 13 are aligned in the direction of the height of the heat exchange bundle 3 , in other words in the stacking direction of the different frames 13, 15, 16.

In addition, on one side of the first frames 13, the recesses 131a, 131b are aligned with the manifold 19 (visible on the Figures 2a, 2b ). More precisely, on one side of the first frames 13, the recesses 131a into which the circulation channels 71 for condensation open out are aligned with the inlet 19A and the recesses 131b into which the circulation channels 73 open for subcooling are aligned with outlet 19B.

Of course, the number of recesses 131a into which the circulation channels 71 for condensation open out is adapted as a function of the number of circulation channels 71 for condensation. Likewise, the number of recesses 131b into which the circulation channels 73 for sub-cooling open out is adapted as a function of the number of circulation channels 73 for sub-cooling.

According to an advantageous embodiment, at least one lateral edge 13A, 13B of a first receiving frame 13, arranged opposite one end of a heat exchange tube 5, is shaped according to a pattern defining a succession of arches. The arches are advantageously arranged over the entire width of the lateral edge 13A, 13B which is opposite the end of a heat exchange tube 5. In other words, the arches are provided over a width substantially equal to the width of the tube heat exchange 5.

The term “arch” is understood to mean the assembly formed by an arch vault 132 connecting two arch legs 133. In this succession of arches, two adjacent arch vaults 132 are connected by a common arch leg 133.

According to the example illustrated, a recess 131a or 131b is delimited by an arch, in other words each recess 131a or 131b is made between two adjacent arch legs 133 and is delimited by these two arch legs 133 and the arch of arch 132 connecting them. When a heat exchange tube 5 is arranged in the housing 130 of a first frame 13, the space remaining between one end of the heat exchange tube 5 and an arch vault 132 makes it possible to define a through opening for placing in fluid communication.

By way of nonlimiting example, the diameter of a through opening is of the order of 0.5 mm.

In addition, the arch legs 133 advantageously provide a stress absorption function, and are capable of withstanding mechanical stresses, in particular due to pressure.

The arches are therefore dimensioned taking into account the mechanical strength of the first frame 13 and the flow of the first fluid through the recesses 131 defined by the arches. In addition, in the case of a heat exchanger 1 assembled by brazing, the arch feet 133 also make it possible to define brazing zones with the second frames 15.

Furthermore, in order to allow the flow of the second fluid in the heat exchange bundle 3, the first frames 13 also have guides 134 for the passage of the second fluid. According to the example illustrated, the first frames 13 are respectively shaped with at least one handle 134 which when a heat exchange tube 5 is arranged in the first frame 13 makes it possible to define a through passage opening allowing the flow of the second fluid. The handles 134 make it possible to define the guides for the passage of the second fluid.

The handles 134 of each first frame 13 are arranged in alignment with the handles 134 of the other first frames 13 of the heat exchange bundle 3 so as to allow the flow of the second fluid through the heat exchange bundle 3. To Illustrative title, in the figures there is shown an embodiment of the handles 134. Of course, any other form of the handles 134 can be envisaged.

Furthermore, with reference to the figure 5 , the frames 13 for receiving the heat exchange tubes 5 have respectively opposite each end of the heat exchange tube 5 which it receives, at least one separation portion 136 arranged between the circulation channels 71 for the condensation of the first fluid and the circulation channels 73 for the sub-cooling of the first condensed fluid.

This separation portion 136 is shaped to prevent fluid communication between the circulation channels 71 for condensation and the circulation channels 73 for sub-cooling defined by the same heat exchange tube 5.

This separation portion 136 therefore acts as a means of blocking the passage of the first fluid from the circulation channels 71 for condensation to the circulation channels 73 for sub-cooling and vice versa.

According to the example illustrated, each separation portion 136 provided on a first frame 13 prevents fluid communication by form cooperation between the first frame 13 and the heat exchange tube 5 received in this first frame 13, more precisely between the edge lateral 13A, respectively 13B, of the first frame 13 and the end opposite the heat exchange tube 5.

In this example, the separation portion 136 is formed on a lateral edge 13A, respectively 13B, of the first frame 13 extending in the direction of the end of the heat exchange tube 5 opposite.

The separation portion 136 advantageously comes integrally with the lateral edge 13A, respectively 13B, of the first frame 13.

More specifically, in this example the separation portion 136 is formed by the extension of an arch foot 133 in the direction of the end opposite the heat exchange tube 5.

The separation portion 136 is produced by an extension 136 or in other words by a tongue 136. The tongue 136 here extends longitudinally towards the end opposite the heat exchange tube 5.

In addition, the separation portion 136 is for example provided substantially in the middle of the lateral edge 13A, respectively 13B, of the first frame 13, when the two groups of circulation channels 71 for the condensation on the one hand and for the sub-cooling 73 on the other hand define the same passage section and are separated substantially at the middle of the heat exchange tube 5.

Of course, the separation portion 136 can be moved according to the arrangement and the passage section defined by the circulation channels 71 for the condensation on the one hand and for the sub-cooling 73 on the other hand.

For example, the separation portion 136 can be moved to the right with reference to the arrangement shown on the figure 5 , when the heat exchange tube 5 has more circulation channels 71 for condensation than circulation channels 73 for sub-cooling.

In addition, the separation portion 136 has a thickness substantially equal to the thickness of the heat exchange tube 5 opposite, more precisely from the end opposite the heat exchange tube 5 .

The separation portion 136 bears against the end of the heat exchange tube 5 vis-à-vis between the two groups 71, 73 of first circulation channels 7, namely here the circulation channels 71 for condensation and the circulation channels 73 for sub-cooling, thereby blocking the passage of the first fluid. According to a particular embodiment, the separation portion 136 can come to bear against the end of the heat exchange tube 5 where this heat exchange tube 5 does not have first circulation channels 7, marking as much plus the separation between the circulation channels 71 for the condensation and the circulation channels 73 for the sub-cooling by this absence of first channels 7.

Second embodiment of the first frames

The Figures 1 to 3b and 6 show a second embodiment of the first frames 13. The description of the first embodiment with reference to figures 4 and 5 applies to identical components, only the differences are now described.

• un premier tube d'échange thermique 51 de la première rangée A définissant les canaux 71 de circulation pour la condensation, et
• un deuxième tube d'échange thermique 53 de la deuxième rangée B définissant les canaux 73 de circulation pour le sous-refroidissement.

The second embodiment differs from the first embodiment in that each first receiving frame 13 is capable of receiving two heat exchange tubes 51 and 53, of which:

• a first heat exchange tube 51 of the first row A defining the circulation channels 71 for the condensation, and
• a second heat exchange tube 53 of the second row B defining the 73 circulation channels for sub-cooling.

In this case, the fluid communication means 131a, 131b define two rows respectively associated either with the first row A of first heat exchange tubes 51 or with the second row B of second heat exchange tubes 53.

Thus, first communication means 131a ensure the fluid communication of the first heat exchange tubes 51 or in other words of the first row A of first heat exchange tubes 51 with the inlet 19A for the first defined fluid here by the manifold 19.

And, second communication means 131b ensure the fluidic communication of the second heat exchange tubes 53 or in other words of the second row B of second heat exchange tubes 53 with the outlet 19B for the first fluid defined here by the same manifold 19.

In this case, a succession of arches can be provided on one or each lateral edge 13A, respectively 13B, of the first frame 13 opposite one end of the two adjacent heat exchange tubes received in the same first frame 13.

This succession of arches then extends over the entire width of all the heat exchange tubes 51, 53 that the first frame 13 can receive, here two heat exchange tubes 51, 53.

Each first receiving frame 13 has, according to this second embodiment, at least one partition 135 which compartments the first receiving frame 13. This partition 135 is here arranged in the extension of an arch foot 133.

According to this second embodiment, the first frames 13 no longer include the separation portions 136, for example produced in the form of a tongue to prevent the passage of the first fluid between the two groups of channels 71 and 73.

In the example illustrated, each first receiving frame 13 has a single partition 135, which partitions the first receiving frame 13 into two housings 130 to each receive a heat exchange tube 51,53.

The partition 135 is therefore found arranged between two heat exchange tubes 51 and 53 when they are put in place in the first frame 13. The partition 135 makes it possible to prevent fluid communication between the two tubes. heat exchange 51 and 53 received in the same first frame 13.

The partition 135 in this example extends over the entire length of the heat exchange tubes 51, 53 received in the first frame 13. The partition 135 of a first frame 13 can be made in one piece with this first frame 13. In addition, the partition 135 is the same thickness as the rest of the first frame 13, and therefore in this example of thickness substantially equal to the thickness of the heat exchange tubes 51 and 53 of on either side of the partition 135.

Furthermore, in the example illustrated on the figure 6 the partition 135 is arranged substantially centrally. This corresponds to an arrangement in which the two heat exchange tubes 51 and 53 received in the same first frame 13 are of the same size.

Of course, the partition 135 can be moved according to the dimensions of the two heat exchange tubes 51 and 53 received in the same first frame 13. For example, the partition 135 can be moved to the right with reference to the layout shown on the figure 6 , when the first heat exchange tube 51 is wider than the second adjacent heat exchange tube 53.

Second frames

With reference to the figure 7 , the second frames 15 are now described in more detail.

The second frames 15 can be at least partially made of aluminum.

When the second frames 15 receive turbulators 11 (see figure 3b ) of the flow of the second fluid, the second frames 15 are called cadresturbators or turbulator-carrying frames.

The second fluid is able to circulate in at least two passes called circulation in "U" in each second frame 15 as will be described later.

• deux bords opposés 15A, 15B s'étendant de façon perpendiculaire à la direction des premiers canaux de circulation 7 du premier fluide, autrement dit ici perpendiculairement à la direction longitudinale des tubes d'échange thermique 5 ou 51 et 53, et
• deux autres bords opposés 15C, 15D s'étendant parallèlement à la direction des premiers canaux de circulation 7 du premier fluide, autrement dit ici parallèlement à la direction longitudinale des tubes d'échange thermique 5.

Similar to the first frames 13, the second frames 15 have:

• two opposite edges 15A, 15B extending perpendicular to the direction of the first circulation channels 7 of the first fluid, in other words here perpendicular to the longitudinal direction of the heat exchange tubes 5 or 51 and 53, and
• two other opposite edges 15C, 15D extending parallel to the direction of the first circulation channels 7 of the first fluid, in other words here parallel to the longitudinal direction of the heat exchange tubes 5.

• deux bords opposés 15A, 15B s'étendant perpendiculairement à la direction générale d'écoulement du premier fluide, et
• deux autres bords opposés 15C, 15D s'étendant parallèlement à la direction générale d'écoulement du premier fluide.

It is also possible to define the second frames 15 with respect to the general direction of flow of the first fluid, namely that the second frames 15 have:

• two opposite edges 15A, 15B extending perpendicular to the general direction of flow of the first fluid, and
• two other opposite edges 15C, 15D extending parallel to the general direction of flow of the first fluid.

• deux bords opposés 15A, 15B s'étendant perpendiculairement à la direction générale d'écoulement du deuxième fluide, et
• deux autres bords opposés 15C, 15D s'étendant parallèlement à la direction générale d'écoulement du deuxième fluide.

In addition, according to the embodiments described, it is also possible to define the second frames 15 with respect to the general direction of flow of the second fluid, namely that the second frames 15 have:

• two opposite edges 15A, 15B extending perpendicular to the general direction of flow of the second fluid, and
• two other opposite edges 15C, 15D extending parallel to the general direction of flow of the second fluid.

The general direction of flow of the second fluid means the direction of the branches of the "U" defining a two-pass circulation of the second fluid.

In the examples illustrated, the second frames 15 are of general shape similar to the first frames 13, here substantially rectangular.

The second frames 15 have two longitudinal edges 15C, 15D, forming long sides, extending substantially parallel to the longitudinal edges 13C, 13D of the first frames 13 and to the general direction of flow. of the second fluid, and two side edges 15A, 15B, forming short sides, extending in the width direction, substantially perpendicular to the direction of flow of the second fluid parallel to the side edges 13A, 13B of the first frames 13.

According to the embodiments described, the second frames 15 extend over the same length and the same width as the first frames 13.

In particular, the outer contours of the first frames 13 and second frames 15 are practically identical so that the alternating stacking of the first frames 13 and second frames 15 forms a block.

More particularly, each second frame 15 defines an internal width and an internal length L. The term "internal width" means the width defined between the internal walls of the opposite longitudinal edges.

Likewise, the term "internal length" means the length defined between the internal walls of the opposite lateral edges.

In addition, the side edges 15A, 15B of the second frames 15 may be slightly larger than the side edges 13A, 13B of the first frames 13, so that the ends of the heat exchange tubes 5; 51, 53 received in the first frames 13 stacked with the second frames 15, rest on the peripheral edge of the lateral edges 15A, 15B of the second frames 15.

The second frames 15 therefore define an internal length L less than the internal length defined by the interior space of the first frames 13.

The second frames 15 have a thickness which is of the order of a few millimeters, for example of the order of 0.5mm to 4mm, preferably of the order of 2mm. The thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the second frames 15.

Similarly to the first frames 13, the second frames 15 can be produced by stamping cutting.

According to the illustrated embodiment, the second frames 15 each comprise a bar 150 arranged inside the respective second frame 15 so to separate two circulation passes for the second fluid. It is therefore an internal bar 150.

In the example illustrated, the bar 150 makes it possible to conform the second circulation channel 9 substantially in a "U" shape.

Of course, one could provide for a circulation of the second fluid in more than two passes in a second frame 15 and for this purpose more than one bar 150 inside the second frame 15 which would be, by way of nonlimiting example, arranged offset and opposite to each other.

The bar 150 extends longitudinally inside a second frame 15. The bar 150 therefore extends in this example substantially parallel to the longitudinal edges 15C, 15D of the second frame 15.

To do this, the bar 150 does not extend over the entire internal length L of the second frame 15. In other words, the bar 150 extends from a lateral edge 15A of a second frame 15 in the direction of the opposite lateral edge 15B but without reaching this opposite lateral edge 15B.

The bar 150 is therefore secured to a lateral edge 15A of a second frame 15 and projects with its free end towards the internal space of the second frame 15 in the direction of the opposite lateral edge 15B, leaving a space. The internal bar 150 therefore extends longitudinally from a lateral edge 15A of a second frame 15 over a length l less than the internal length L of the second frame 15. Advantageously, the internal bar 150 extends over a length l at least equal to half the internal length L of a second frame 15.

According to an exemplary embodiment, each second frame 15 may have an internal length L comprised in a range of the order of 30mm to 500mm.

The internal bar 150 also does not extend over the entire internal width of the second frame 15. More specifically, the internal bar 150 has a width W smaller than the internal width of the second frame 15. The width W of the internal bar 150 may be greater than or equal, preferably strictly greater, than the thickness of the second frame 15.

We thus define on each side of the bar 150, the entry and exit of the path flow for the second fluid. The bar 150 can also be described as a tongue. In addition, the bar 150 is substantially the same thickness as the second frame 15.

The arrangement of the bar 150 for the separation between the passes of the second fluid can be a function of the separation between the condensation zone and the sub-cooling zone.

Advantageously, the bar 150 is arranged so that the first pass of the second fluid is in the sub-cooling zone of the heat exchange bundle 3, and that the second pass of the second fluid is in the condensation region of the bundle of heat exchange 3.

The bar 150 is for example arranged substantially centrally. More specifically, the bar 150 is arranged substantially in the center of a second frame 15 in the width direction of the second frame 15. In this way, the bar 150 divides the second frame 15 into two parts of the same size.

This arrangement is in particular complementary to a configuration in which the two groups of circulation channels 71 for condensing on the one hand and for sub-cooling 73 on the other hand of the same heat exchange tube 5 define the same passage section and are separated substantially at the middle of the heat exchange tube 5.

Alternatively, this arrangement is complementary to a configuration in which the two heat exchange tubes 51 and 53 received in the same first frame 13 are of the same size.

Of course, the internal bar 150 can be moved for example to the right with reference to the arrangement shown on the figure 7 , when the heat exchange tube 5, according to the first embodiment with reference to the figure 4 , has more circulation channels 71 for condensation than circulation channels 73 for sub-cooling or alternatively when the first heat exchange tube 51 is wider than the second heat exchange tube 53 adjacent along the second embodiment described with reference to Figures 1 to 3b .

Generally, the dimensions of each pass of the second fluid are advantageously variable in the direction of the width of the heat exchange bundle 3 as a function of the conformation of the two condensation and sub-cooling zones.

In addition, in the case where the second frames 15 comprising such an internal bar 150 are stacked with first frames 13 according to the first embodiment with reference to the figure 5 each receiving a single heat exchange tube 5, the base of the bar 150 of each second frame 15 is opposite the separation portions 136, for example in the form of tongues 136, provided on the lateral edges 13A of the first frames 13 of on either side of this second frame 15.

Alternatively, in the case where the second frames 15 comprising such an internal bar 150 are stacked with first frames 13 according to the second embodiment with reference to the figure 6 each receiving two heat exchange tubes 51 and 53, the internal bars 150 of the second frames 15 are located opposite the partition walls 135 of the first frames 13 on either side of the second frames 15. The bar 150 may be more as wide as the 135 partition walls facing each other.

In addition, in addition to the first receiving frames 13, the second frames 15 have guides 151a, 151b for the passage of the first fluid allowing its flow in the stack of the different frames 13, 15, 16.

More precisely, each second frame 15 has guides 151a for the passage of the first fluid to be condensed, arranged in alignment with the means for placing in communication 131a of the first frames 13, so as to allow the flow of the first fluid in the area of condensation.

Each second frame 15 further comprises guides 151b for the passage of the first condensed fluid, arranged in alignment with the means of communication 131b of the first frames 13, so as to allow the flow of the first condensed fluid in the area of subcooling.

The guides 151a, 151b are here produced in the form of through orifices 151a, 151b arranged in alignment with the recesses 131a, 131b for placing in communication. fluidics of the first frames 13.

The through holes 151a, 151b are therefore arranged on at least one lateral edge, preferably on the two lateral edges 15A, 15B of a second frame 15 in the width direction.

The number of through orifices 151a for the passage of the first fluid to be condensed is adapted as a function of the number of recesses 131a and therefore as a function of the number of circulation channels 71 for the condensation of the heat exchange tubes 5; 51, 53.

The number of through orifices 151b for the passage of the first condensed fluid is adapted as a function of the number of recesses 131b and therefore as a function of the number of circulation channels 73 for the sub-cooling of the heat exchange tubes 5; 51, 53.

The distribution of the first fluid in the heat exchange tubes 5; 51, 53 can be easily made thanks to the recesses 131a, 131b provided on the ends of the first frames 13 and the complementary through holes 151a, 151b provided on the ends of the second frames 15 and in fluid communication with the manifold 19.

In addition, each second frame 15 may have a portion 154 devoid of guides 151a, 151b for the passage of the first fluid, which is arranged between the guides 151a for the passage of the first fluid to be condensed and the guides 151b for the passage of the first fluid. condensed.

In addition, the second frames 15 respectively present means for placing in fluid communication 152 the second circulation channels 9 between them on the one hand and with the pipes 21 for the second fluid on the other hand.

According to the example illustrated, the second frames 15 respectively have a predefined number of through openings 152 for fluid communication.

These through openings 152 are here arranged on the longitudinal edges of the second frames 15 and are aligned with each other in the height direction of the heat exchange bundle 3.

The through openings 152 lead respectively to the interior of a second frame 15.

The through openings 152 make it possible to define a fluid inlet 152 towards the interior space of the second frame 15 on a longitudinal edge, and a fluid outlet 152 out of the second frame 15 on the opposite longitudinal edge, as shown by the arrows F2 on the figure 7 .

The second fluid first circulates in the sub-cooling zone before circulating in the condensation zone, that is to say that the second fluid makes a first pass between the channels 73 for sub-cooling and then a second passes between channels 71 for condensation.

More precisely, according to the example illustrated, the second frames 15 have handles 153 which make it possible to delimit the through openings 152.

The handles 153 of the second frames 15 are produced in a similar manner to the handles 134 of the first frames 13 and are aligned with these handles 134 which allow the passage of the second fluid through the heat exchange bundle 3.

By way of illustration, in the figures there is shown an embodiment of the handles 153. Of course, any other form of the handles 153 can be envisaged.

Among the two handles 153 of the second frames 15, the opening delimited by a first handle is arranged in fluid communication with a first tube 21 and the opening delimited by a second handle is arranged in fluid communication with a second tube 21.

The additional ears or handles 134 and 153 provided on the sides of the first and second frames 13, 15 make it possible to define, with the pipes 21 for entering and leaving the second fluid, two conduits for distributing the second fluid on each side of the beam d heat exchange 3, so that the second fluid can easily flow in the heat exchange bundle 3.

Fluid connection frame

In the stack of frames 13, 15, 16 (see Figures 3a to 4 , 8, 9 ), at least one specific frame 16 is distinguished from the others in that it is shaped to allow a fluid connection between the reservoir 22 and the heat exchange bundle 3. This specific frame 16 is also designated by “fluid connection frame” or even “specific fluid connection frame”.

• d'une part avec les canaux 71 de circulation pour la condensation et
• d'autre part et de façon distincte avec les canaux 73 de circulation pour le sous-refroidissement.

More precisely, as we can see better on figures 1 , 8 and 9 , the fluid connection frame 16 places the reservoir 22 in fluid communication:

• on the one hand with the circulation channels 71 for condensation and
• on the other hand and separately with the circulation channels 73 for sub-cooling.

In this way, the first fluid which has passed through the circulation channels 71 for the condensation circulates towards the reservoir 22, as illustrated by the arrows F1 on the Figures 1 to 2b , and the condensed fluid after phase separation at the outlet of the reservoir 22 circulates towards the circulation channels 73 for sub-cooling, as illustrated by the arrows F1 'on the Figures 1 to 2b .

In order to limit the pressure drops, two specific frames 16 are advantageously provided to allow the fluid connection with the reservoir 22, as illustrated in the figure 3b . In this case, as is better visible on the figure 9 , the fluid communication is done by two levels, each level being formed by a specific frame 16.

According to the embodiments described, the fluid connection frame (s) 16 is / are placed facing the fixing flange 24 so as to put the reservoir 22 and the circulation channels 71 for fluid communication condensation on the one hand, and the circulation channels 73 for sub-cooling on the other hand and separately, by means of this fixing flange 24.

In addition, the or each fluid connection frame 16 is stacked with two first frames 13.

Furthermore, similarly to the first frames 13 and second frames 15, the specific frames 16 for example have a generally substantially rectangular shape with two opposite side edges forming short sides in the width direction, only a side edge 16A is visible. in the figures, and two edges opposite longitudinal 16C, 16D forming the long sides lengthwise. The outer contours of the fluid connection frame (s) 16 are provided to allow stacking with the first frames 13 and second frames 15 so as to form a block.

Similarly to the second frames 15, the fluid connection frame (s) 16 has (s) a thickness of the order of a few millimeters, for example of the order of 0.5mm to 4mm, preferably l 'order of 2mm. The thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the fluid connection frame (s) 16.

In addition, similarly to the second frames 15, the end of the heat exchange tube 5 or alternatively the ends of the heat exchange tubes 51 and 53 of a stage of the heat exchange bundle 3 above the fluid connection frame 16, partially rests on the lateral edges 16A of this fluid connection frame 16.

One of the lateral edges, here the lateral edge 16A, on which the end (s) of the heat exchange tube (s) 5 rest; 51, 53, is arranged opposite the fixing flange 24.

In addition, the or each fluid connection frame 16 has a plurality of notches 161a, 161b on this lateral edge 16A, opening towards the outside of the fluid connection frame 16, and therefore towards the outside of the heat exchange bundle. 3.

These notches 161a, 161b make it possible to put the reservoir 22 and the first circulation channels 7 in fluid communication for the first fluid in the heat exchange bundle 3, namely the circulation channels 71 for the condensation on the one hand and the 73 circulation channels for sub-cooling on the other hand.

According to the example illustrated, this fluid communication is ensured by means of the fixing flange 24 detailed below, and for this purpose the notches 161a, 161b open into the fixing flange 24 arranged opposite. fluid connection frame screw 16.

More specifically, a first group of notches 161a is intended to be placed in fluid communication with the inlet of the reservoir 22 while a second group of notches 161b is intended to be placed in fluid communication with the outlet of the reservoir 22 .

The notches 161a of the first group of the fluid connection frame 16 form means of placing in fluid communication between the circulation channels 71 for the condensation and the inlet of the reservoir 22. The number of notches 161a of the first group is adapted as a function the number of circulation channels 71 for the condensation of the heat exchange tubes 5; 51, 53.

The notches 161b of the second group of the fluid connection frame 16 form means of placing in fluid communication between the circulation channels 73 for sub-cooling and the outlet of the reservoir 22. The number of notches 161b of the second group is adapted in function of the number of circulation channels 73 for the sub-cooling of the heat exchange tubes 5; 51, 53.

Furthermore, in this example the or each fluid connection frame 16 comprises on this lateral edge 16A a plurality of teeth 162a, respectively 162b separated by notches 161a, respectively 161b.

In other words, the lateral edge 16A is shaped with alternating teeth 162a, 162b and notches 161a, 161b. The teeth 162a, 162b extend longitudinally from the lateral edge 16A towards the outside of the fluid connection frame 16, and therefore towards the outside of the heat exchange bundle 3, here towards the fixing flange 24.

The lateral edge 16A therefore has a general shape substantially in comb with the back of the comb facing inside the fluid connection frame 16.

Of course, the opposite lateral edge (not visible in the figures) of the fluid connection frame 16 can be shaped similarly to this lateral edge 16A.

We can thus consider that the fluidic connection frames 16 are generally similar to the second frames 15 inside the heat exchange bundle, but at least one edge of which rests the end (s) of tube (s). heat exchange 5 or 51 and 53, here at least one side edge 16A in the direction of the width, was opened at the orifices allowing the passage of the first fluid, so as to form the notches 161a, 161b and thus allowing the first condensed fluid having circulated in the circulation channels 71 for the condensation to circulate towards the inlet of the tank 22, here via the fixing flange 24, and allow the first fluid leaving the tank 22 to flow towards the circulation channels 73 for sub-cooling.

In the stack of frames 13, 15, 16, the notches 161a, respectively 161b, are aligned with the recesses 131a, respectively 131b, of the first frames 13, and with the through orifices 151a, respectively 151b, of the second frames 15. From even, the teeth 162a, respectively 162b, are aligned with the arch legs 133 of the first frames 13, when the different frames 13, 15, 16 are stacked.

The length of the teeth 162a, 162b of the fluid connection frames 16 can be greater than the length of the arches of the first frames 13.

Furthermore, the lateral edge 16A has a solid portion 163 which separates the first group of notches 161a and associated teeth 162a separated by these notches 161a, from the second group of notches 161b and associated teeth 162b separated by these notches 161b. In other words, the fluid connection frame 16 is shaped on either side of this solid part 163, so as to put in fluid communication the reservoir 22 with the circulation channels 71 for condensation on one side of the solid part. 163, and so as to put the tank 22 in fluid communication with the circulation channels 73 for sub-cooling on the other side of the solid part 163.

The solid part 163 is therefore arranged at the level of the separation between the condensation zone and the sub-cooling zone of the heat exchange bundle 3.

The term “full part” is understood here to mean a part or portion which is devoid of means for setting up fluid communication, in this example the solid part 163 is devoid of notches 161a, 161b but also of any other means which would allow the first fluid pass or run.

In the stack of different frames 13, 15, 16, the solid part 163 of the or fluidic connection frames 16 is arranged in alignment with the separation portions 136 or separation partitions 135 of the first frames 13.

The solid part 163 is also in alignment with the portions 154 devoid of guides 151a, 151b for the passage of the first fluid, of the second frames 15, when they are provided (see figure 3b ).

Furthermore, this solid part 163 extends in the width direction of the fluid connection frame 16 over a distance l ₁₆₃ (see figure 10 ).

This distance l ₁₆₃ must be dimensioned as accurately as possible, it must not be too large because it would risk hampering the flow of the first fluid, which can generate disturbances.

This distance l ₁₆₃ is advantageously at least equal to the width of the separation portions 136 or to the width of the partition walls 135 of the first frames 13. In addition, this distance l ₁₆₃ is less than or equal to the distance, in the direction of the width, over which the portion 154 extends (see figures 3b and 7 ) without guides 151a, 151b for the passage of the first fluid provided on the second frames 15.

Finally, in the example illustrated on Figures 3a to 4 and 8 to 10 , this solid part 163 is shown substantially in the center of the lateral edge 16A of the fluid connection frame 16.

Similarly to the separation portions 136 or partition walls 135 of the first frames 13 and to the internal bars 150 of the second frames 15, the arrangement of the solid part 163 is adapted as a function of the dimensioning of the condensation zone and of the zone for sub-cooling the heat exchange bundle.

Referring to Figures 8 and 10 , the assembly formed by the first group of notches 161a and the associated teeth 162a, the solid part 163, and the second group of notches 161b and the associated teeth 162b, extends opposite the entire width of the end of a heat exchange tube 5 or of the ends of the two heat exchange tubes 51 and 53 which rest (s) on the lateral edge 16A of the fluid connection frame 16.

Furthermore, similarly to the second frames 15, the fluid connection frame (s) 16 (better visible on the figure 10 ) present (s) fluid communication means 165 arranged on the longitudinal edges 16C, 16D of the fluid connection frame (s) 16, which are similar to the fluid communication means 152 of the second frames 15 and are not described in more detail later. These fluid communication means 165 can be delimited by handles or ears 166 similar to the handles 153 of the second frames 15 and are therefore not described in more detail either.

Finally, the fluid connection frame (s) 16 has (have) an internal bar 167 similar to the internal bar 150 of the second frames 15 and is therefore not described again here.

This internal bar 167 is arranged in the extension of the solid part 163 by extending towards the inside of the fluid connection frame 16, more precisely from substantially the middle of the solid part 163.

Similarly to the first frames 13 and to the second frames 15, the fluid connection frame (s) 16 can be produced by stamping cutting.

Tank or bottle

With reference to Figures 1, 2a , 3a and 4 , the reservoir 22 is now described which is capable of receiving the fluid coming from the heat exchanger 1 and allowing phase separation of this condensed fluid.

Such a reservoir 22 is also called a bottle, or phase separation bottle or else a condenser bottle when the associated heat exchanger 1 is a condenser. We also speak of "receiver drier" in English.

The Figures 1, 2a , 3a and 4 partially illustrate a heat exchanger 1 comprising such a tank 22.

In this example, the reservoir 22 is assembled and fixed to the heat exchange bundle 3. The reservoir 22 as shown therefore forms a unitary system with the heat exchanger 1, advantageous in terms of space.

The attachment of the reservoir 22 to the heat exchange bundle 3 can be done by any suitable means, for example by screwing, welding.

According to the illustrated embodiments, the reservoir 22 is fixed to the heat exchange bundle 3 via a fixing flange 24 detailed below, for example by screwing. To this end, additional fixing means 220, 240 are carried on the one hand by the reservoir 22 and on the other hand by the fixing flange 24.

In the example illustrated, the reservoir 22 has an orifice 220 for fixing by screwing. The reservoir 22 can in particular be fixed to the fixing flange 24 after brazing the heat exchanger 1.

According to a first alternative embodiment illustrated on the Figures 1, 2a , 3a and 4 , the reservoir 22 can be assembled and fixed on a lateral flank of the heat exchange bundle 3, namely on one of the short sides of the heat exchange bundle 3 of generally substantially parallelepipedal shape. The tank 22 is in this case arranged by extending substantially vertically in the mounted state in the motor vehicle.

The reservoir 22 is for example of substantially tubular shape and is arranged by extending longitudinally in the height direction of the heat exchange bundle 3, in other words in the direction of stacking of the various elements, in particular frames 13, 15, 16, of the heat exchange bundle 3. This corresponds to a substantially vertical position in the mounted state in the motor vehicle.

According to a second alternative embodiment, the reservoir 22 can be carried by a closure plate 17 or 18 of the heat exchange bundle 3. In this case, the reservoir 22 is carried by one of the long sides of the heat exchange bundle 3 of generally substantially parallelepiped shape.

The reservoir 22 then extends substantially longitudinally in the direction of the length of the heat exchange bundle 3, which corresponds to a substantially horizontal position in the mounted state in the motor vehicle.

According to one or other of these variants, the reservoir 22 is arranged so as to receiving as input a mixture of gas and liquid of the first fluid coming from the heat exchanger 1 able to act as a condenser.

More precisely, the reservoir 22 is arranged so as to receive as input the first fluid which has circulated in the condensation zone of the heat exchanger 1, that is to say in the circulation channels 71 for the condensation in the tubes heat exchange 5 or 51.

To do this, the reservoir 22 defines an interior space capable of receiving the first fluid. The reservoir 22 includes at least one orifice 221, 223 in fluid communication with the heat exchange bundle 3, here two orifices 221 and 223.

A first orifice 221 allows the admission of the first condensed fluid coming from the condensation zone of the heat exchanger 1 into the reservoir 22. A second orifice 223 allows the evacuation of the first fluid in liquid form at the outlet of the reservoir 22 towards the sub-cooling zone of the heat exchanger 1, so that the first liquid fluid undergoes an additional passage, known as sub-cooling, in the heat exchange bundle 3 of the heat exchanger 1.

The two orifices 221, 223 are in the illustrated example arranged on the same end edge of the reservoir 22. The spacing between the orifices 221, 223 of the reservoir is less than or equal to the distance l ₁₆₃ over which the solid part 163 of the specific frame 16.

The reservoir 22 also advantageously comprises a filter (not shown) capable of capturing solid particles of dimensions greater than a predetermined threshold value which circulate in the refrigerant fluid. The filter, not shown, is then arranged in the interior space of the reservoir 22.

Thus in use, when the heat exchanger 1 acts as a condenser, the first fluid, such as a cooling fluid, enters for example in the form of high pressure gas and circulates in the circulation channels 71 for the condensation of the beam d heat exchange 3.

During this journey, the coolant thermally exchanges with the second fluid. The refrigerant is thus cooled with a phase change. The condensed refrigerant then circulates in the reservoir 22 for separation of the gas and liquid phases.

The refrigerant can optionally pass through a desiccator and / or a filter in the reservoir 22. At the outlet of the reservoir 22, the refrigerant is only in the liquid phase and can recirculate through the sub-region. cooling of the heat exchange bundle 3 defined by the circulation channels 73 for sub-cooling.

Clamp

With reference to figures 1 to 4 , 9 and 10 , the fixing flange 24 interposed according to the embodiments described between the heat exchange bundle 3 and the reservoir 22 is described in more detail.

The fixing flange 24 is in fluid communication with the reservoir 22 and with the first circulation channels 7 by virtue of the fluid connection frame (s) 16.

The fixing flange 24 can be assembled with the heat exchange bundle 3 during the brazing of the heat exchanger 1.

As said previously, the assembly between the fixing flange 24 and the tank 22 can be done after brazing, for example by screwing. The fixing flange 24 for this purpose comprises a fixing means 240 complementary to the fixing means 220 of the reservoir, for example for fixing by screwing.

According to the arrangement of the reservoir 22 on a lateral flank of the heat exchange bundle as illustrated in the figure 2a , or on a closure plate, for example at the top of the heat exchange bundle 3, the positioning of the fixing flange 24 is adapted as illustrated in the Figures 2a and 2b . On the figure 2a , the fixing flange 24 extends along the longitudinal axis of the heat exchange bundle 3, corresponding to an arrangement of the reservoir 22 on a lateral flank of the heat exchange bundle 3, while on the figure 2b , the fixing flange 24 extends along the height of the heat exchange bundle 3 or in other words the stacking direction of the different elements of the heat exchange bundle 3, corresponding to an arrangement of the reservoir 22 on a closing plate of the heat exchange bundle 3.

• un canal d'introduction 241 du premier fluide condensé en provenance des canaux 71 de circulation pour la condensation, comme illustré par les flèches F1 sur les figures 1 à 2b, ce canal d'introduction 241 est agencé en communication fluidique avec l'orifice d'entrée 221 du réservoir 22 (figure 1), et
• un canal d'évacuation 243 du premier fluide après séparation de phase en direction des canaux 73 de circulation pour le sous-refroidissement, comme illustré par les flèches F1' sur les figures 1 à 2b, ce canal d'évacuation 243 est agencé en communication fluidique avec un orifice de sortie 223 du réservoir 22 (figure 1).

Furthermore, in the example illustrated, the fixing flange 24 comprises:

• an introduction channel 241 of the first condensed fluid coming from the circulation channels 71 for the condensation, as illustrated by the arrows F1 on the Figures 1 to 2b , this introduction channel 241 is arranged in fluid communication with the inlet orifice 221 of the reservoir 22 ( figure 1 ), and
• an evacuation channel 243 of the first fluid after phase separation in the direction of the circulation channels 73 for sub-cooling, as illustrated by the arrows F1 'on the Figures 1 to 2b , this discharge channel 243 is arranged in fluid communication with an outlet orifice 223 of the reservoir 22 ( figure 1 ).

In this example, the inlet 241 and outlet 243 channels extend parallel to each other.

The inlet 241 and outlet 243 channels are made in the plane formed by the fixing flange 24. As can be seen in the figure 3b , the inlet 241 and outlet 243 channels can lead respectively into other connection channels 242, 244 intended to be connected respectively to the inlet 221 and outlet 223 orifices of the reservoir 22.

These connection channels 242, 244 to the reservoir 22 are produced in the particular example illustrated substantially perpendicular to the plane of the fixing flange 24, extending towards the reservoir 22 when the latter is assembled to the heat exchanger 1.

The diameters of the inlet 241 and discharge 243 channels and the connection channels 242, 244 are chosen to be greater than or equal to the diameters of the inlet 221 and outlet 223 ports of the reservoir 22 so as not to create a pressure drop additional.

The spacing between the channels 241 and 243 of the fixing flange 24 is a function of the spacing of the orifices 221 and 223 of the reservoir 22.

The dimensioning of the distance l ₁₆₃ is also advantageously chosen by function of the spacing between the channels 241 and 243 of the fixing flange 24.

In addition, the fixing flange 24 also comprises, according to the embodiment described, grooves or basins 245, 247 better visible on the Figures 3a, 4 , 8 and 9 , of which a groove 245 makes it possible to bring the first condensed fluid into the reservoir 22 via the introduction channel 241 and another groove 247 makes it possible to bring the first fluid after phase separation at the outlet of the reservoir 22 via the channel evacuation 243 to the sub-cooling zone of the heat exchange bundle 3.

The grooves 245 and 247 have for example a diameter identical to the inlet 241 and outlet 243 channels of the fixing flange 24.

Thus, the fixing flange 24 is arranged so that the notches 161a of the fluid connection frame 16 in fluid communication with the circulation channels 71 for the condensation of the first fluid open into the groove 245 into which the introduction channel 241 opens. of the mounting flange 24.

The fixing flange 24 is also arranged so that the notches 161b of the fluid connection frame 16 in fluid communication with the circulation channels 73 for the sub-cooling of the first condensed fluid 161b open into the groove 247 into which the channel d discharge 243 of the mounting flange 24.

Thus the first fluid after condensation having circulated in the circulation channels 71 for the condensation opens into the groove 245, circulates in the introduction channel 241 of the fixing flange, then enters the reservoir 22.

And, the first fluid after phase separation leaves the reservoir 22 and circulates in the evacuation channel 243 of the fixing flange 24 to be distributed in the circulation channels 73 for sub-cooling via the groove 247.

Thus, the heat exchanger 1 as described above comprises a heat exchange bundle 3 which has both a condensation zone and a sub-cooling zone without direct communication between the two, which are defined in a simple manner by the heat exchange tubes 51, 53 adjacent two by two in the same first frame 13 or alternatively by one and the same tube heat exchange 5 received in a first frame 13.

These are the first frames 13 receiving the monotubes 5 or more heat exchange tubes 51, 53 which make it possible to guarantee the non-fluid communication between the two condensation and sub-cooling zones.

Finally, the particular configuration of the fluid connection frame (s) 16 makes it simple to fluidly connect the reservoir 22 on the one hand to the condensation zone and on the other hand to the sub-cooling zone of the bundle of heat exchange, allowing the tank 22 to be arranged in different positions on the heat exchanger 1.

Furthermore, such a heat exchanger 1 has better mechanical strength compared to the solutions of the prior art and very good resistance to high pressures, in particular due to the circulation of a cooling fluid such as CO ₂ , as well as optimized heat exchange performance.

Claims (17)

1. Heat exchanger (1), notably for a motor vehicle, for an exchange of heat between at least a first fluid and a second fluid, the said exchanger (1) being able to act as a condenser and comprising a heat-exchange core (3) with a plurality of heat-exchange tubes (5; 51, 53) comprising circulation canals (7) :

   - through which the first fluid is intended to pass, and

   - which are intended to be in fluidic communication with a fluid reservoir (22) able to separate the gas phase and the liquid phase of the condensed first fluid,

   such that:

   - the heat-exchange tubes (5; 51, 53) comprise:

   • circulation canals (71) for condensing the first fluid, defining a condensation zone of the heat-exchange core (3), and

   • circulation canals (73) for supercooling the condensed first fluid, defining a supercooling zone of the heat-exchange core (3), characterized in that

   - the heat exchanger (1) comprises a stack of frames (13, 15, 16) among which at least certain frames (13), referred to as receiving frames that receive the heat-exchange tubes (5; 51, 53), are able to receive the heat-exchange tubes (5; 51, 53) and are respectively configured in such a way as to separate the condensing zone and the supercooling zone of the heat-exchange core (3), and in that

   - at least one fluidic coupling frame (16) is configured to place the reservoir (22) in fluidic communication:

   • on the one hand, with the circulation canals (71) for condensing, and

   • on the other hand, and distinctly, with the circulation canals (73) for supercooling.
2. Heat exchanger (1) according to the preceding claim, in which each receiving frame (13) that receives the heat-exchange tubes (5; 51, 53) is configured to receive both circulation canals (71) for condensing and circulation canals (73) for supercooling which are defined by the heat-exchange tubes (5; 51, 53), so that the condensing zone and the supercooling zone of the heat-exchange core (3) are arranged side by side and without direct fluidic communication with one another.
3. Heat exchanger (1) according to one of Claims 1 and 2, in which:

   - the receiving frames (13) that receive the heat-exchange tubes (5) are respectively able to receive one single heat-exchange tube (5), and in which

   - each heat-exchange tube (5) comprises, on the one hand, circulation canals (71) for condensing the first fluid and, on the other hand, circulation canals (73) for supercooling the condensed first fluid.
4. Heat exchanger (1) according to the preceding claim, in which the receiving frames (13) that receive the heat-exchange tubes (5) respectively have, facing each end of the heat-exchange tube (5) that it receives, at least one separation portion (136) arranged between the circulation canals (71) for condensing the first fluid, and the circulation canals (73) for supercooling the condensed first fluid, so as to prevent fluidic communication between the circulation canals (71) for condensing and (73) for supercooling.
5. Heat exchanger (1) according to one of Claims 1 and 2, in which:

   - the heat-exchange core (3) comprises:

   • at least a first row (A) of first heat-exchange tubes (51) comprising the circulation canals (71) for condensing the first fluid, and

   • at least a second row (B) of second heat-exchange tubes (53) comprising the circulation canals (73) for supercooling the condensed first fluid, and in which

   - the receiving frames (13) that receive the heat-exchange tubes (51, 53) are respectively able to receive at least two heat-exchange tubes (51, 53) of which one is a first heat-exchange tube (51) of the first row (A) and one is a second heat-exchange tube (53) of the second row (B).
6. Heat exchanger (1) according to the preceding claim, in which each receiving frame (13) for receiving the heat-exchange tubes (51, 53) comprises at least one separation partition (135) positioned between the first heat-exchange tube (51) and the second heat-exchange tube (53) so as to prevent fluidic communication between the two heat-exchange tubes (51, 53) received in one and the same frame (13).
7. Heat exchanger (1) according to any one of the preceding claims, in which the receiving frames (13) that receive the heat-exchange tubes (5; 51, 53) have a thickness at least equal to the thickness of the heat-exchange tubes (5; 51, 53) in the direction of stacking of the said frames (13, 15, 16).
8. Heat exchanger (1) according to any one of the preceding claims,

   - comprising at least one header tank (19) for the first fluid, defining an inlet (19A) for the first fluid into the heat-exchange core (3) and an outlet (19B) for the first fluid from the heat-exchange core (3), and

   - in which the receiving frames (13) that receive the heat-exchange tubes (5; 51, 53) respectively comprise:

   • means (131a) of establishing fluidic communication between the inlet (19A) for the first fluid and the circulation canals (71) for condensing the first fluid, and

   • means (131b) for establishing fluidic communication between the outlet (19B) for the first fluid and the circulation canals (73) for supercooling the condensed first fluid.
9. Heat exchanger (1) according to the preceding claim, in which the means (131a, 131b) for establishing fluidic communication are produced in the form of cut-outs in the first frames (31) into which the ends of the heat-exchange tubes (5; 51, 53) open, and which are arranged in fluidic communication with the header tank (19) for the first fluid.
10. Heat exchanger according to one of Claims 8 and 9, in which the receiving frames (13) that receive the heat-exchange tubes (5; 51, 53) respectively comprise lateral edges (13A, 13B) extending substantially perpendicular to the direction of the canals (7, 71, 73) for the circulation of the first fluid, and in which at least one of the said lateral edges (13A, 13B) has the means (131a, 131b) for establishing fluidic communication.
11. Heat exchanger (1) according to any one of the preceding claims, comprising a reservoir (22) of fluid fixed to the heat-exchange core (3).
12. Heat exchanger (1) according to the preceding claim, comprising a fixing flange (24) for fixing the reservoir (22) to the heat-exchange core (3), and in which the fluidic coupling frame (16) is configured in such a way as to establish fluidic communication between the reservoir (22) and the circulation canals (71) for condensing, on the one hand, and the circulation canals (73) for supercooling, on the other hand, via the fixing flange (24).
13. Heat exchanger (1) according to the preceding claim, in which the fixing flange (24) comprises:

    - an inlet canal (241) for introducing the condensed first fluid (F1) coming from the circulation canals (71) for condensing and arranged in fluidic communication with an inlet orifice (221) of the reservoir (22), and

    - a discharge canal (243) for discharging the first fluid after phase separation (F1') in the direction of the circulation canals (73) for supercooling and arranged in fluidic communication with an outlet orifice (223) of the reservoir (22).
14. Heat exchanger (1) according to one of the preceding claims, the fluidic coupling frame (16) being configured with a predefined number of teeth (162a, 162b) separated by slots (161a, 161b) allowing fluidic communication to be established between the reservoir (22) and the circulation canals (71) for condensing, on the one hand, and the circulation canals (73) for supercooling, on the other hand.
15. Heat exchanger (1) according to one of the preceding claims, in which the fluidic coupling frame (16) comprises at least one edge (16A) on which there rests at least one end of a heat-exchange tube (5; 51, 53) and which has a solid part (163), the said edge (16A) being configured in such a way as to:

    - establish fluidic communication between the reservoir (22) and the circulation canals (71) for condensing on one side of the solid part (163), and

    - establish fluidic communication between the reservoir (22) and the circulation canals (73) for supercooling on the other side of the solid part (163).
16. Heat exchanger (1) according to Claim 4, considered in combination with the preceding claim, in which the solid part (163) of the fluidic coupling frame (16) has a width at least equal to the width of the separation portion (136) of the receiving frames (13) that receive heat-exchange tubes (5; 51, 53) which are arranged in the heat-exchange core (3) elsewhere than facing the reservoir (22) and/or the fixing flange (24).
17. Heat exchanger (1) according to Claim 8 considered in combination with any one of the preceding claims, comprising an alternating stack of:

    - first receiving frames (13) that receive heat-exchange tubes (5; 51, 53), and

    of

    - second frames (15) respectively defining at least a second circulation canal (9) for the second fluid, the second frames (15) having:

    • guides (151a) for the passage of the first fluid that is to be condensed, these being arranged in alignment with the communication-establishing means (131a) of the first frames (13), so as to allow the first fluid to flow in the stack of first frames (13) and second frames (15) in order to condense the first fluid, and

    • guides (151b) for the passage of the condensed first fluid, these being arranged in alignment with the communication-establishing means (131b) of the first frames (13), so as to allow the condensed first fluid to flow in the stack of first frames (13) and second frames (15) in order to supercool the condensed first fluid.

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