FR3045803A1 - THERMAL EXCHANGER, IN PARTICULAR FOR MOTOR VEHICLE - Google Patents

Abstract

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, said exchanger (1) being able to act as a condenser and comprising an exchange beam thermal device (3) with a plurality of heat exchange tubes (5) comprising circulation channels (7) for being traversed by the first fluid. According to the invention, the heat exchange tubes (5) comprise: circulating channels (71) for the condensation of the first fluid defining a condensing zone of the heat exchange bundle (3), and channels (73) for the subcooling of the first condensed fluid defining a sub-cooling zone of the heat exchange bundle (3), - the heat exchanger (1) comprises a stack of frames (13, 15, 16 ) of which: • at least some frames (13) are able to receive the heat exchange tubes (5) and are respectively shaped so as to separate the condensation zone and the subcooling zone from the heat exchange bundle ( 3), and • at least one fluidic connection frame (16) is shaped to fluidly connect a fluid reservoir (22) on the one hand with the circulation channels (71) for condensation and on the other hand part and distinctly with the channels (73) d e circulation for subcooling.

Description

The invention relates to the field of heat exchangers in particular able to act as condensers.

Such heat exchangers find particular application in motor vehicles. The heat exchanger can in particular be used as a condenser, more specifically as a water condenser and is commonly referred to as "Waler condenser" in English. In this case a first fluid such as a coolant can enter the heat exchanger in gu / form, such as carbon dioxide designated CO 2 or other coolants such as 1,1,1, 2-tetrafluoroethane known in particular in the industrial nomenclature under the acronym R-134a or 2,3,3,3-tetrafluoroetopropene known under the acronym R-1234yf. A second fluid, such as liquid, in particular a brine mixture, is intended to pass through the heat exchanger to cool the cooling fluid by condensation.

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

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

After the condensation step, the condensed coolant is received and maintained in a liquid state within the reservoir. The tank has the function of separating the liquid and gaseous phases of the refrigerant fluid in order to let out only the coolant in its liquid state. Such a tank thus makes it possible to guarantee that, at the outlet, the refrigerant fluid is completely in the liquid phase.

This tank can be connected to the output of the heat exchanger able to act as a condenser, hereinafter referred to as "condenser". This reservoir is in fluid communication with the condenser. For this purpose, the tank usually comprises an inlet port into which the condensed refrigerant fluid 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 pressure of condensation defined. This subcooling process is a known method in the prior art. For this purpose, the reservoir may comprise an outlet orifice which opens into a section of the condenser, so as to subject the liquid coolant iluide an additional passage, said subcooling.

The reservoir can also be used to filter the fluid present in the cold loop, thus preventing particles, having a size greater than a predetermined threshold value, from circulating within the air conditioning loop. Additional functionality is still to absorb moisture through the presence of a material such as a suitable gel, or dehydrating means or a deicer. The refrigerant fluid free of moisture can then circulate in the air conditioning loop.

Moreover, 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 related to the use of a refrigerant such as CO2 under a very high pressure, generally greater than 100 bar, with a burst pressure which can reach for example up to 340 bar, 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 solve the disadvantages described above by proposing a simple heat exchanger to achieve and having a footprint, reduced while allowing to connect in a simple and following different positions a fluid reservoir to the heat exchanger. For this purpose, 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 beam of thermal 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 of the first condensed fluid.

According to the invention, the heat exchange tubes comprise: circulation channels for the condensation of the first fluid defining a condensing zone of the heat exchange bundle; and circulation channels for the subcooling of the first fluid. condensate defining a sub-cooling zone of the heat exchange bundle, the heat exchanger comprises a stack of frames, at least some frames known as frames for receiving the heat exchange tubes are able to receive the heat exchange tubes and are respectively shaped so as to separate the condensation zone and the subcooling zone from the heat exchange bundle, and - at least one fluidic connection frame is shaped so as to put in fluid communication the reservoir of a part with the circulation channels for condensation and • secondly and distinctly with the circulating channels. culation for subcooling. The heat exchanger thus makes it possible to define in a simple manner a distinct condensation zone and a subcooling zone of the heat exchange bundle.

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

In this way, the fluid having traveled, the circulation channels for condensation flows to the reservoir, and the fluid leaving the reservoir flows to the circulation channels for subcooling. The condensed fluid leaving the condensing zone necessarily flows to the reservoir before a new so-called subcooling passage in the subcooling 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 space or not. 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 features taken alone or in combination.

According to one aspect of the invention, each receiving frame of 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 condensing zone of the heat exchange bundle and the subcooling zone of the heat exchange bundle are arranged side by side and without direct fluid communication with each other.

The same frame is designed to receive both channels of the two zones of condensation and subcooling of the heat exchange beam while preventing fluid communication within this frame between these two areas.

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 reception frames of the heat 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 secondly circulation channels for subcooling the first condensed fluid.

The same heat exchange tube defines both channels for the condensation zone and for the subcooling zone. The heat exchange tube may not have circulation channels at the separation between the two zones of condensation and subcooling. 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 that it receives, at least one separation portion arranged between the circulation channels for the condensation of the first fluid and the circulation channels for subcooling the first condensed fluid, so as to prevent fluid communication between the circulation channels for condensation and for subcooling.

According to another embodiment, the heat exchange bundle comprises: at least one first row of first heat exchange tubes comprising the circulation channels for the condensation of the first fluid, and at least one second row of second tubes. heat exchange system comprising the circulation channels for the subcooling of the first condensed fluid, and the receiving frames of the heat exchange tubes are respectively able to receive at least two heat exchange tubes including a first exchange tube 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 second heat exchange tubes. According to another aspect of the invention, each frame for receiving the heat exchange tubes comprises at least one separation partition 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 wall extends over the entire length of the heat exchange tubes.

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

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

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 of the first fluid out of the heat exchange bundle, and the receiving frames of the heat exchanger 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 communication fluidic between the outlet of the first fluid and the circulation channels for subcooling the first condensed fluid.

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

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

According to one aspect, the receiving frames of the heat exchange tubes respectively comprise lateral edges extending substantially perpendicularly to the direction of the circulation channels for the first fluid, and wherein at least one of said lateral edges has the means of setting 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 fluidic connection frame is shaped so as to put in fluid communication the tank and the circulation channels. for condensation on the one hand, and the circulation channels for subcooling on the other hand, via the fixing flange.

According to an exemplary embodiment, the fixing flange comprises: - a channel for introducing the first condensed fluid from the condensation circulation channels arranged in fluid communication with an inlet port of the tank, and an evacuation channel of the first fluid after phase separation towards the circulation channels for subcooling arranged in fluid communication with an outlet of the reservoir.

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

According to one particular aspect, the fluidic connection frame comprises at least one edge on which at least one end of a heat exchange tube rests and having a solid portion, said edge is shaped so as to: - put in fluid communication the reservoir with the circulation channels for the condensation of one side of the solid part and put in fluid communication the tank with the circulation channels for the subcooling of the other side of the solid part,

The solid portion is devoid of means for setting fluid communication. According to an exemplary embodiment, the solid portion of the fluidic connection frame has a width at least equal to the width of the separation portion of the heat exchange tube receiving frames which are arranged in the heat exchange bundle elsewhere than 'vis-à-vis the tank and / or the mounting flange.

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 communication means of the first frames, so as to allow the flow of the first fluid in the stack of the first frames and the second frames; frames for the condensation of the first fluid, and • guides for the passage of the first condensed fluid, arranged in alignment with the communication means of the first frames, so as to allow the flow of the first condensed fluid in the stack first and second frames for subcooling 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 refrigerant, inserted in the first frames and between which flows the second fluid. such as coolant.

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

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

The various superimposed frames make it possible to create the flow path of the first refrigerant fluid, when the frames are assembled, for example by soldering, and likewise, the various superposed frames make it possible to create the flow path of the cooling liquid, in particular over 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 with a pressure greater than 100 bar, for example the first fluid is a refrigerant fluid intended to circulate at high pressure such as CO2.

Such a heat exchanger has a better mechanical strength compared to the solutions of the previous part and a very good resistance to high pressures, especially when a CO 2 refrigerant fluid 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 portion of the fluid coupling frame arranged vis-à-vis the reservoir and / or the fixing flange.

According to a further aspect, the heat exchanger comprises at least one inlet pipe and an 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 drains. input cl outlet for the second fluid.

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

In a particular example, the second frames respectively have at least two handles delimiting the through openings for fluidic communication, with a first loop arranged in fluid communication with the inlet manifold and a second loop arranged in fluid communication with the tubing. exit.

In one aspect, the first frames have guides for the passage of the second fluid arranged in alignment with the through openings for fluidic communication of the second frames. Other features and advantages of the invention will appear more clearly on reading the following description, given by way of illustrative and nonlimiting example, and the appended drawings in which: FIG. 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 an end of the bundle in the beam stacking direction, - Figure 2a is a partial perspective view of the FIG. 2b is a partial perspective view of the heat exchanger according to a second variant; FIG. 3a is a partial perspective view of the heat exchanger of FIG. of heat exchange comprising two rows of heat exchange tubes, - Figure 3b is an exploded partial view of the heat exchange bundle 4 is a partial view in perspective of a heat exchanger comprising a heat exchange bundle with a row of heat exchange tubes, FIG. 4 is a fragmentary perspective view of a heat exchanger comprising a heat exchange bundle with a row of heat exchange tubes, FIG. FIG. 5 schematically represents a first frame of the heat exchange bundle receiving a single heat exchange tube, and FIG. 6 schematically represents a first frame of the heat exchange bundle receiving two heat exchange tubes. FIG. 7 schematically represents a second frame of the heat exchange bundle; FIG. 8 is a first enlarged view of a part of FIG. 3a showing the fluid connection between the fastening flange and the bundle of FIG. FIG. 9 is a still enlarged view of FIG. 8 showing the fluidic connection between the fixing flange and the heat exchange bundle and on which a FIG. The thermal exchange tubes of the heat exchange bundle resting on a specific fluid coupling frame, and FIG. 10 schematically shows a specific frame of the heat exchange bundle for the fluid connection with the fluid reservoir.

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

The following achievements 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 features apply only to a single embodiment. Simple features of different embodiments may also be combined and / or interchanged to provide other embodiments.

In the description we can index certain elements, such as first element or second element etc. In this case, it is a simple indexing to denote and denote close but not identical elements.

This indexing does not imply a priority of one element with respect to another and it is easy to interchange such denominations without departing from the scope of the present description. This indexing does not imply an order in time either.

In the present, the terms upper and lower, or high and low, 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 assembled state in a motor vehicle in particular. Heat exchanger

With reference to FIG. 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. This 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 some elements or parts, a coating intended to melt to ensure the joining of elements of the heat exchanger 1 and sealing during assembly by brazing. The heat exchanger 1 scion the invention is particularly suitable for the circulation of at least one fluid having a high operating pressure, especially greater than 100bar,

For example, the first fluid is a refrigerant fluid intended to circulate at high pressure such as CO2, also designated by R744 according to the industrial nomenclature. Other refrigerant fluids may be used, such as 1,1,1,2-tetrafluoroethane or 2,3,3,3-tetrafluoropropene known under the acronym R-1234yf, respectively known in the industrial nomenclature by R 134a or R-1234yf. The heat exchanger 1 is in particular capable of acting as a condenser, in particular a water condenser, in which the cooling fluid such as CO2 is cooled by a second fluid, for example in liquid form, such as a cooling liquid comprising a brine mixture. The heat exchanger 1 comprises a heat exchange bundle 3 for the heat exchange between the first fluid and the second fluid.

In the illustrated example, the heat exchange bundle 3 has a generally parallelepipedal shape. The introduction and the evacuation of the first fluid in the heat exchange bundle 3 or outside the heat exchange bundle 3 are shown schematically by way of example by the arrows Fit for the introduction and Fl'o for the evacuation in Figures 2a and 2b. The introduction of the second fluid into the heat exchange bundle 3 and the evacuation of the second fluid out of the heat exchange bundle 3 are shown schematically by way of example by the arrows F2j for the introduction and F2o for the evacuation. in 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 the second fluid as will be described in more detail thereafter.

More specifically, with reference to FIGS. 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 later.

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 FIGS. 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 may be carried by a separate element of the heat exchange tubes 5; 51,53 as illustrated in Figures 1 and 3.

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

The slots can be made by stamping.

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

Interlayers 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 in FIGS. 3a, 3b and 4, the heat exchange bundle 3 comprises a stack of frames 13, 15, 16. The stacking of the various frames 13, 15, 16 is 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 able to receive 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 depending on 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 fluidic connection 16 visible in Figures 3a to 4, as described below. By way of example, closure plates 17, 18 (see FIGS. 1 to 4), in particular at least one bottom closure plate 17 and at least one top closure plate 18, can be arranged on either side stacking the first frames 13 and the second frames 15, so as to close the heat exchange bundle 3,

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

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

Referring to FIGS. 2a and 2b, the heat exchanger 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 shown in 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 19Λ for the first fluid in the heat exchange bundle 3 and an outlet 19B of the first fluid out of the heat exchange bundle 3. The heat exchanger 1 further comprises at least two fluid inlet and outlet pipes 21 for the introduction and evacuation of the second fluid. In this case, the two pipes 21 are arranged in opposite directions on either side of the stack of the heat exchange bundle 3. Namely, a first pipe 21 is arranged on the upper closure plate 18 while the Another tubing 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 tubes 21 can be arranged on the other side of the heat exchange bundle 3.

According to the arrangement illustrated in 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 in 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, otherwise in the direction of stacking different elements, including different frames 13, 15, 16, 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 for phase separation of the first fluid after condensation.

This tank 22 described in more detail below is for example fixed to the heat exchange bundle 3 via a fastening flange 24.

According to a variant not shown, the tank 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 1-6, the heat exchange tubes 5 are now described in more detail. 51, 53.

Heat exchange tubes 5; 51, 53 are preferably made by extrusion.

Heat exchange tubes 5; 51, 53 can be made in the form of flat tubes, advantageous in terms of size.

Pleasure tubes 5; 51, 53 have a generally rectangular general shape, with a length for example of the order of 32 mm and a thickness of about one 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.

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 direction of the height 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 refrigerant, in particular microchannel circulation 7 for the first fluid.

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

The first circulation channels or microchannels 7 for the first fluid allowing the flow of the first fluid respectively extend 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 subcooling 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.

Globally, all the first channels 7 provide 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. Π here a first class of first channels referenced 71 which corresponds to the first channels among all 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 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 subcooling of the first fluid.

The first fluid can follow a circulation in a so-called "T" flow or rectilinear flow in the condensation watercocks 71.

Likewise, the first fluid can follow a circulation in a so-called "1" or rectilinear flow in the subcooling channels 73.

In FIGS. 1 to 2b, the arrows F1 illustrate the flow of the first fluid during the condensation, while the arrows F1 'illustrate the circulation of the first fluid after condensation for subcooling. The set of circulation channels 71 for condensation define a condensing zone of the heat exchange bundle 3, and the set of circulation channels 73 for the subcooling define a zone of subcooling of the exchange bundle. thermal 3.

The condensing zone defined by the circulation channels 71 for the condensation may be substantially equal to the subcooling zone defined by the circulation channels 73 for subcooling.

Preferentially, two zones are not equal and the zone of condensation is. For example, it is possible to provide a distribution of the order of at least 60%, preferably 70% to 80%, for the condensation zone, for example of the order of 40%, preferably 20% to 30%, for the subcooling zone.

First embodiment of the heat exchange tubes

Referring to Figure 4, there is described 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.

One can also speak in this case of heat exchange monotube 5 to distinguish 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 precisely, each heat exchange tube 5 comprises on the one hand circulation channels 71 for condensing the first fluid, and on the other hand circulation channels 73 for subcooling the first condensed fluid.

The two groups of channels 71, 73 for condensation on the one hand and for subcooling 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 subcooling is schematically illustrated by dashes in FIG. 4.

According to an advantageous embodiment variant, it is possible to provide an absence of first circulation channels 7 marking the separation between the circulation channels 71 for the condensation and the circulation channels 73 for the subcooling.

In addition, it can be provided that the circulation channels 71 for the condensation and the circulation channels 73 for the subcooling define the same passage section.

In particular, it is possible to provide as many circulation channels 71 for condensation as circulation channels 73 for subcooling. The separation is then substantially central as in the example illustrated.

The passage section for the condensation and the passage section for the sub-cooling can be advantageously 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 may be different from the number of circulation channels 73 for subcooling.

Advantageously, more circulation channels 71 for condensation may be provided than circulation channels 73 for subcooling.

Alternatively or additionally, the circulation channels 71 for the condensation may be of different size relative to the size of the circulation channels 73 for subcooling, so as to adapt the passage section for the condensation cl for the sub -cooling.

Second embodiment of the heat exchange tubes

Referring to Figures 1 to 3b, heat exchange tubes 51, 53 are described in a second embodiment.

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

Each heat exchange tube 51, respectively 53 comprises circulation channels 71, 73 respectively, for either condensation or subcooling. Clearly, the first heat exchange tubes 51 comprise the circulation channels 71 for the condensation of the first fluid and the second heat exchange tubes 53, different from the first heat exchange tubes 51, include the circulation channels 73 for circulation. I under-relfoid the first fluid condense.

In this case, the heat exchange bundle 3 comprises: at least one first row A of first heat exchange tubes 51, and at least one second row B of second heat exchange tubes 53.

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

To facilitate the understanding of Figures 2a and 2b, only some first heat exchange tubes 51 are shown.

It can further be provided that the circulation channels 71 for the condensation of the first heat exchange tubes 51 define the same passage section as the circulation channels 73 for the subcooling of the second heat exchange tubes 53.

Of course, the passage section for condensation and for subcooling can be advantageously adapted as needed.

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

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

Alternatively, the dimensions of the first heat exchange tubes 51 and 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 subcooling zone.

Alternatively or additionally, the number and / or size of the circulation channels 71 for condensation may or may be different from the circulation channels 73 for subcooling.

First frames called tubes-frames

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

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

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

The first frames 13 have: - two opposite edges 13A, 13B extending perpendicular to the direction of the first flow channels 7 of the first fluid, in other words. here perpendicularly 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 in parallel with the longitudinal direction of heat exchange tubes 5 or 51,53.

It is also possible to define the first frames 13 with respect to the general direction of flow of the first fluid, namely that the first frames 13 have: two opposite edges 13A, 13B extending perpendicularly to the general direction of flow of the first fluid fluid, and two other opposite edges 13C-, 13D extending parallel to the general direction of flow of the first fluid. Λ.Λ general flow direction of the first fluid means the direction of flow in "I" or rectilinear in the channels 71 for circulation for condensation, respectively in the channels 73 for circulating subcooling.

In the illustrated examples, the first frames 13 are of generally 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 side edges 13A, 13B, extending in the width direction, substantially perpendicular to the direction of flow of the first fluid.

However, in other embodiments, there may be provided frames having a general ton which is not rectangular, for example elliptical, or diamond-shaped. The longitudinal axis of the first frames 13 and heat exchange tubes 5 or 51,53 is here confused.

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

As previously, 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 superposition of the various frames 13,15,16.

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 subcooling defined by the heat exchange tubes 5; 51.53.

In this way, the condensing zone of the heat exchange bundle 3 and the subcooling 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 of the heat exchange bundle 3.

Thus, the two zones of condensation of the heat exchange bundle 3 and subcooling 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 in FIGS. 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 on the other hand, the circulation channels 73 for the subcooling of the first condensed fluid. For this purpose, 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 fluid communication means 131a, 131b of the first circulation channels 7 of the heat exchange tubes 5 with the collecting box. 19.

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

More precisely, the frames 13 for receiving the heat exchange tubes 5 comprise respectively: fluidic communication means 131a between the inlet 19Λ (visible in FIGS. 2a, 2b) for the first fluid and the channels 71 of circulation for the condensation of the first fluid, and fluid communication means 13 Ib (FIGS. 4-5) between the outlet 19B (visible in FIGS. 2a, 2b) of the first fluid and the circulation channels 73 for the sub. -cooling of the first condensed fluid.

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

The fluid communication means 131a, 131b may 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. This is the BoHs'làtérér 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 13a of the first frames 13 are aligned in the direction of the height of the heat exchange bundle 3 that is, in the stacking direction of the various 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 in Figures 2a, 2b). More specifically, on one side of the first frames 13, the recesses 131a into which the circulation channels 71 for the condensation flow are aligned with the inlet 19A and the recesses 131b into which the circulation channels 73 for the subcooling open out are aligned with the output 19B.

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

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.

Arch is understood to mean the group formed by an arch arch 132 connecting two feet of arch 133. In this series of arches, two adjacent arch arches 132 are connected by a common arch foot 133.

According to the illustrated example, a recess 131a or 131b is delimited by an arch, otherwise said each recess 131a or 131b is made between two adjacent feet 133 and is delimited by these two arches 133 and the arch of 132 arch 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 arch 132 makes it possible to define a through opening of setting in fluid communication. By way of non-limiting example, the diameter of a through opening is of the order of 0.5 mm.

In addition, the arches 133 advantageously provide a stress absorption function, and are able to withstand mechanical stresses, in particular due to pressure.

The arches are 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 soldering, the arches 133 still make it possible to define soldering 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 illustrated example, the first frames 13 are respectively shaped with at least one loop 134 which when a heat exchange tube 5 is arranged in the first frame 13 defines a through through opening allowing the flow of the second fluid. The handles 134 allow 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. A As an illustration, the figures show an embodiment of the handles 134. Of course, any other form of the handles 134 may be considered.

In addition, with reference to FIG. 5, the frames 13 for receiving the heat exchange tubes 5 have, respectively, facing each end of the heat exchange tube 5 that 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 subcooling 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 subcooling defined by the same heat exchange tube 5.

This separation portion 136 thus serves as a means of blocking the passage of the first fluid of the circulation channels 71 for condensation to the circulation channels 73 for subcooling and vice versa.

According to the illustrated example, each separation portion 136 provided on a first frame 13 prevents the fluidic communication by shape cooperation between the first frame 13 and the heat exchange tube 5 received in this first frame 13, more precisely between the edge 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 towards the end of the heat exchange tube 5 vis-à-vis.

The separation portion 136 is advantageously integral with the lateral edge 13A, respectively 1313, of the first frame 13.

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

The separation portion 136 is made by an extension 136 or in other words by a tongue 136. The tongue 136 here extends longitudinally toward 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 channels 71 of circulation for the condensation on the one hand and for the subcooling 73 on the other hand define a 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 subcooling 73 on the other hand.

For example, the separation portion 136 can be shifted to the right with reference to the arrangement shown in FIG. 5, when the heat exchange tube 5 has more circulation channels 71 for condensation than circulation channels 73 for circulation. subcooling.

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

The separating portion 136 bears against the end of the heat exchange tube 5 in facing relation between the two groups 71, 73 of the first circulation channels 7, namely here the circulation channels 71 for the condensation and the circulation channels 73 for subcooling, thus blocking the passage of the first fluid. According to a particular embodiment, the separation portion 136 can bear against the end of the heat exchange tube 5 where the heat exchange tube 5 does not have first 7 circulation channels, marking all the the greater the separation between the circulation channels 71 for condensation and the circulation channels 73 for subcooling by the absence of first channels 7.

Second embodiment of the first frames

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 the identical components, only the differences are now described.

The second embodiment differs from the first embodiment in that each first receiving frame 13 is able to receive two heat exchange tubes 51 and 53 including: 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 circulation channels 73 for the subcooling.

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

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

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

In this case, a succession of arches can read provided on one or each lateral edge 13A, respectively 13B, of the first frame 13 vis-à-vis 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 the set of 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 wall 135 which compartmentalizes the first reception frame 13, This partition wall 135 is. here arranged in the extension of a foot of arch 133.

According to this second embodiment, the first frames 13 no longer include the separation portions 136, for example made 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 illustrated example, each first receiving frame 13 has a single partition wall 135, which compartmentalizes the first receiving frame 13 into two housings 130 to each receive a heat exchange tube 51,53.

The partition wall 135 is therefore arranged between two heat exchange tubes 51 and 53 when they are put in place in the first frame 13. The partition wall 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 wall 135 extends in this example over the entire length of the heat exchange tubes 51, 53 received in the first frame 13. The partition wall 135 of a first frame 13 can be made in one piece In addition, the partition wall 135 is of 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 both sides of the partition wall 135.

Furthermore, in the example illustrated in Figure 6 the partition wall 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 wall 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 wall 135 can be moved to the right with reference to the The arrangement shown in FIG. 6, when the first heat exchange tube 51 is wider than the second heat exchange tube 53 adjacent.

Second Ears

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

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

When the second frames 15 receive tabulators 11 (see FIG. 3b) from the flow of the second fluid, the second frames 15 are known as turbulators or turbulators.

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

Similarly to the first frames 13, the second frames 15 have: - two opposite edges 15A, 15B extending perpendicularly to the direction of the first flow channels 7 of the first fluid, in other words here perpendicular to the longitudinal direction of the 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 in parallel with the longitudinal direction of the heat exchange tubes 5.

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

Furthermore, according to the described embodiments, it is still 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 15Λ, 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 flow direction 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 illustrated examples, the second frames 15 are of generally similar shape to the first frames 13, here substantially rectangular.

The second frames 15 have two longitudinal edges 15C, 15D forming large sides, extending substantially parallel to the longitudinal edges 13C, 13D of the first frames 13 and the general direction of flow of the second fluid, and two lateral edges 15A, 15B, forming narrow lengthwise, 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 on the same length and on the same width as the first frames 13.

In particular, the outer contours of the first frames 13 and second frames 15 are substantially identical so that the alternating stack 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", the width defined between the inner walls of the opposite longitudinal edges.

Similarly, the term "internal length", the length defined between the inner walls of the opposite side edges.

In addition, the lateral edges 15A, 15B of the second frames 15 may be slightly larger than the lateral 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, one can also speak of the height of the second frames 15.

Similarly to the first frames 13, the second frames 15 can be made by stamping cut.

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

In the example shown, the ban-ette 150 makes it possible to shape the second circulation channel 9 substantially in a "U" shape.

Of course, one could provide a circulation of the second iluide in addition to 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 non-limiting example, arranged in an offset manner and opposite to each other.

The strip 150 extends longitudinally inside a second frame 15. The strip 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 side edge 15A of a second frame 15 towards the opposite side edge 15B but without reaching this opposite side edge! 5B.

The bar 150 is secured to a side edge 15A of a second frame 15 and projects with its free end towards the internal space of the second frame 15 towards the opposite side edge 15B, leaving a space. The inner bar 150 thus 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 inner 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 in a range of about 30mm to 500mm.

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

The inlet and the outlet of the flow path for the second fluid are thus defined on each side of the bar 150. The bar 150 may also be called tongue. In addition, the bar 150 is substantially of the same thickness as the second frame 15. The arrangement of the bar 150 for the separation between the passes of the second fluid may be a function of the separation between the condensation zone and the sub-zone. reffoidissement.

Advantageously, the strip 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 zone 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 condensation on the one hand and for the subcooling 73 on the other hand of a 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, it is possible to move the inner bar 150 for example to the right with reference to the arrangement shown in FIG. 7, when the heat exchange tube 5, according to the first embodiment with reference to FIG. 4, comprises more circulation channels 71 for condensing circulation channels 73 for subcooling or alternatively when the first heat exchange tube 51 is wider than the second heat exchange tube 53 adjacent according to the second embodiment described with reference to Figures 1 to 3b.

In general, the dimensions of each pass of the second fluid are advantageously variable in the direction of the width of the heat transfer beam 3 according to the conformation of the two zones of condensation and subcooling.

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

Alternatively, in the case where the second frames 15 comprising such an inner bar 150 are stacked with first frames 13 scion the second embodiment with reference to Figure 6 each receiving two heat exchange tubes 51 and 53, the bars internal 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 i 5. The bar 150 may be wider than the partition walls 135 facing.

In addition, in addition to the first reception 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 various frames 13,15, 16.

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

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

The guides 151a, 151b are here made in the form of through-holes 151a, 151b in the alignment of the recesses 131a, 131b of fluid communication with the first frames 13.

The through orifices 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-holes 151a for the passage of the first fluid to be condensed is adapted as a function of the number of recesses 13a 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-holes 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 subcooling of the heat exchange tubes 5; 51.53.

The distribution of the first fluid in the heat exchange tubes 5; 51, 53 can be done easily thanks to the recesses 131a, 131b provided on the ends of the first frames 13 and to the through orifices 151a, 151b complementary 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 have means for fluid communication 152 of 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 illustrated example, the second frames 15 respectively have a predefined number of through-openings 152 for setting into 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 direction of the height of the heat exchange bundle 3.

The through openings 152 open respectively to the inside of a second frame 15.

The through openings 152 make it possible to define a fluid inlet 152 towards the inner space of the second frame 15 on a longitudinal edge, and a fluid outlet 152 outside the second frame 15 on the opposite longitudinal edge, as shown schematically by the arrows. 1 * 2 in Figure 7.

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

More specifically, in the illustrated example, the second frames 15 have handles 153 which define the through openings 152.

The loops 153 of the second frames 15 are made in a manner similar to the loops 134 of the first frames 13 and are aligned with these loops 134 which allow the passage of the second fluid through the heat exchange bundle 3. As an illustration, in the figures There is shown an embodiment of the handles 153. Of course, any other form of the handles 153 may be considered.

Of the two loops 153 of the second frames 15, the opening defined by a first loop is arranged in fluid communication with a first pipe 21 and Γ opening defined by a second loop is arranged in fluid communication with a second pipe 21.

The ears or handles 134 and 153 complementary provided on the sides of the first and second frames 13,15 used to define with the inlet and outlet pipes 21 of the second fluid, two distribution ducts of the second fluid on each side of the beam. 3, so that the second fluid can easily flow into the heat exchange bundle 3.

Fluidic connection frame

In the stack of frames 13, 15, 16 (see FIGS. 3a to 4, 8, 9), at least one specific frame 16 is different from the others in that it is shaped to allow a fluid connection between the tank 22 and the heat exchange bundle 3. This specific frame 16 is also referred to as "fluid connection frame" or "specific fluid coupling frame".

More precisely, as can be seen more clearly in FIGS. 1, 8 and 9, the fluidic connection frame 16 puts the reservoir 22 into fluid communication: - on the one hand with the circulation channels 71 for the condensation and - on the other hand apart and distinctly with the circulation channels 73 for subcooling.

In this way, the first fluid having traveled through the circulation channels 71 for condensation flows towards the reservoir 22, as illustrated by the arrows Fl in FIGS. 1 to 2b, and the condensed fluid after phase separation at the outlet of the tank 22 circulates. to the circulation channels 73 for subcooling, as illustrated by arrows F1 'in FIGS. 1 to 2b.

In order to limit the pressure drops, two specific frames 16 are advantageously provided to allow the fluid connection with the tank 22, as illustrated in FIG. 3b. In this case, as can be seen more clearly in FIG. 9, the fluidic communication is done by two levels, each level being formed by a specific frame 16.

According to the embodiments described, the fluidic connection frame (s) 16 is / are placed opposite the fastening flange 24 so as to put the reservoir 22 and the circulation channels 71 in fluid communication with each other. condensation of a bet, and the circulation channels 73 for subcooling on the other hand and separately, through this fastening flange 24.

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

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

In a similar manner to the second frames 15, the fluidic connection frame (s) 16 has (s) a thickness of the order of a few millimeters, for example of the order of 0.5 mm to 4 mm, preferably order of 2mm. The thickness is here considered in the direction of the height of the heat exchange beam 3, one can also speak of the height of the fluidic connection frame or frames 16.

In addition, similarly to the second frames 15, the end of the heat exchanger tube 5 or alternatively the ends of the heat exchange tubes 51 and 53 of a heat exchange bundle stage 3 over the fluid connection frame 16, restc (nt) partially on the side edges 16A of this fluidic connection frame 16. One of the side edges, here the side edge 16A, on which rest or the ends of tube (s) d heat exchange 5; 51, 53, is arranged vis-à-vis of the fastening flange 24,

In addition, the or each fluidic 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 thus towards the extcricur of the heat exchange bundle 3.

These notches 161a, 161b make it possible to put in fluid communication the reservoir 22 and the first circulation channels 7 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 subcooling on the other hand.

According to the illustrated example, this setting in fluidic communication is ensured by means of the lixation flange 24 detailed thereafter, and for this purpose the notches 161a, 161b open into the fastening flange 24 arranged vis-à- screw of the fluidic connection frame 16.

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

The notches 161a of the first group of the fluidic connection frame 16 form fluidic communication means 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 according to the number of circulation channels 71 for condensing the heat exchange tubes 5; 51, 53.

The notches 161b of the second group of the fluidic connection frame 16 form fluidic communication means between the circulation channels 73 for the under-cooling and the outlet of the tank 22. The number of notches 161b of the second group is adapted in accordance with FIG. a function of the number of circulation channels 73 for the subcooling of the heat exchange tubes 5; 51.53.

In addition, in this example the or each fluidic connection frame 16 comprises on this side 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 an alternation of teeth 162a, 162b and notches 161a, 161b. The teeth I62a, 162b extend longitudinally from the lateral edge 16A towards the outside of the fluid connection frame 16, and thus towards the outside of the heat exchange bundle 3, here to the fastening flange 24.

The side edge 16A thus has a generally comb-like shape with the back of the comb facing the inside of the fluidic connection frame 16.

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

It can thus be considered that the fluidic connection frames 16 are of generally similar shape to the second frames 15 inside the heat exchange bundle, but at least one edge on which the tube end (s) rests. 5 or 51 and 53, here at least one side edge 16A in the direction of ugliness, has been opened at the openings allowing the passage of the first fluid, so as to form the notches 161a, 161b and thus allow the first condensed fluid circulating in the circulation channels 71 for condensation to flow to the inlet of the reservoir 22, here via the attachment flange 24, and to allow the first fluid at the outlet of the reservoir 22 to flow to the channels 73 circulation for subcooling.

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 holes 151a, respectively 151b, second frames 15. From even, the teeth 162a, respectively 162b, are aligned with the arch feet 133 of the first frames 13, when the different frames 13,15,16 are stacked;

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

Furthermore, the lateral edge 16A has a solid part 163 which separates the first group of notches 161a and associated teeth 162a separated by these notches 161a, the second group of notches 161b and associated teeth 162b separated by these notches 161b . In other words, the fluidic connection frame 16 is formed 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 in such a way as to put in fluid communication the reservoir 22 with the circulation channels 73 for the subcooling on the other side of the solid part 163.

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

Here, the term "solid part" is understood to mean a portion or portion that does not have any means for setting fluid communication, in this example the solid portion 163 is devoid of notches 161a, 161b but also of any other means that would allow the first fluid pass or run.

In the stack of the various frames 13, 15, 16, the solid portion 163 of the fluid connection frame (s) 16 is arranged in alignment with the separation portions 136 or partition walls 135 of the first frames 13.

The solid portion 163 is also in alignment with the portions 154 without guides 151a, 151b for the passage of the first fluid, the second frames 15, when provided (see Figure 3b).

Moreover, this solid part 163 extends in the width direction of the fluidic connection frame 16 over a distance (see FIG. 10).

This distance h03 must be dimensioned as accurately as possible, it must not be too big because it could interfere with the flow of the first fiuid, which can generate disturbances.

This distance li63 is advantageously at least equal to the width of the separation portions 136 or the width of the partition walls 135 of the first frames 13. Moreover, this distance li63 is less than or equal to the distance, in the width direction on which extends the portion 154 (see FIGS. 3b and 7) devoid of guides 15a, 151b for the passage of the first fluid provided on the second frames 15.

Finally, in the example illustrated in FIGS. 3a to 4 and 8 to 10, this solid portion 163 is shown substantially at the center of the lateral edge 16A of the fluidic connection frame 16.

Similarly to the separation portions 136 or partition walls 135 of the first frames 13 and the internal bars 150 of the second frames 15, the arrangement of the solid part 163 is adapted according to the dimensioning of the condensation zone and the zone. subcooling of the heat exchange bundle.

Referring to Figures 8 and 10, the assembly formed by the first set of notches 161a and the associated teeth 162a, the solid portion 163, and the second set of notches 161b and the associated teeth 162b, extends into view of the entire width of the end of a heat exchange tube 5 or the ends of the two heat exchange tubes 51 and 53 which reccounts (m) on the side edge 16A of the fluid connection frame 16.

Moreover, similarly to the second frames 15, the (s) eadrc (s) of μidic connection 16 (best seen in Figure 10) has (s) fluid communication establishment means 165 arranged on the longitudinal edges 16C, 16D or 16 of the connecting frames 16, which are similar to the means of fluid communication 152 of the second frames 15 and are not described in more detail later. These means of fluid communication 165 may 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.

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

This inner bar 167 is arranged in the extension of the solid portion 163 extending inwardly of the fluidic connection frame 16, more precisely since substantially the middle of the solid portion 163.

Similarly to the first frames 13 and the second frames 15, the fluidic connection frame or frames 16 can be made by stamping cutting. Tank or bottle

Referring to Figures 1,2a, 3a and 4, there is now described the reservoir 22 adapted to receive the fluid from the heat exchanger 1 and allowing a phase separation of the condensed fluid.

Such a tank 22 is also called a bottle, or phase separation bottle or still condenser bottle when the associated heat exchanger 1 is a condenser. There is also talk of "rcccivcr drier" in English.

FIGS. 1, 2a, 3a and 4 partially illustrate a heat exchanger 1 comprising such a reservoir 22.

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

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

According to the illustrated embodiments, the reservoir 22 is fixed to the heat exchange bundle 3 via a fastening flange 24 detailed subsequently, for example by screwing. Complementary fastening means 220, 240 are at this point gates on the one hand by the reservoir 22 and on the other hand by the fastening flange 24.

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

According to a first variant embodiment illustrated in FIGS. 1, 2a, 3a and 4, the reservoir 22 can be assembled and fixed on a lateral side of the heat exchange bundle 3, namely on one of the short sides of the exchange beam. thermal 3 of substantially parallelepipedal general shape. The reservoir 22 is in this case arranged extending substantially vertically in the mounted state in the motor vehicle.

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

According to a second alternative embodiment, the reservoir 22 may be carried by a closure plate 17 or 18 of the heat exchange bundle 3. In this case, the tank 22 is carried by one of the long sides of the heat exchange bundle 3 generally of substantially parallelepipedal 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 the other of these variants, the reservoir 22 is arranged to receive at the inlet a mixture of gas and liquid of the first fluid from the heat exchanger 1 able to act as a condenser.

More specifically, the reservoir 22 is arranged to receive at its inlet the first fluid having circulated in the condensation zone of the heat exchanger 1, that is to say in the circulation channels 71 for condensation in the tubes. heat exchanger 5 or 51.

To do this, the reservoir 22 defines an interior space capable of receiving the first fluid. The reservoir 22 comprises 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 from the condensing 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 subcooling zone of the heat exchanger 1, so that the first liquid fluid undergoes an additional passage, called subcooling, in the heat exchange bundle 3 of the heat exchanger 1,

The two orifices 221, 233 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]] 63 on which the portion extends. full 163 of the specific frame 16.

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

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

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

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

Clamp

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

The fastening flange 24 is in fluid communication with the reservoir 22 and with the first circulation channels 7 thanks to the (x) frame (s) of fluid connection 16.

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

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

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

In addition, in the illustrated example, the fastening flange 24 comprises: an insertion channel 241 of the first condensed fluid coming from the circulation channels 71 for condensation, as illustrated by the arrows Fl in FIGS. 1 to 2b this inlet channel 241 is arranged in fluid communication with the inlet orifice 221 of the reservoir 22 (FIG. 1), and a discharge channel 243 of the first fluid after phase separation in the direction of the circulation channels 73. for subcooling, as illustrated by the arrows F1 'in FIGS. 1 to 2b, cc exhaust channel 243 is arranged in fluid communication with an outlet port 223 of the reservoir 22 (FIG. 1).

In this example, the introduction 241 and evacuation 243 channels extend parallel to each other.

The introduction 241 and discharge 243 channels are made in the plane formed by the fastening flange 24. As can be seen in Figure 3b, the introduction channels 241 and 243 discharge can lead respectively into other connection channels 242, 244 intended to be respectively connected to the inlet and outlet ports 221 and 223 of the tank 22.

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

The diameters of the introduction 241 and discharge 243 channels and the connection channels 242, 244 are chosen 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 loss of head additional. The spacing between the channels 241 and 243 of the fastening flange 24 is a function of the spacing of the orifices 221 and 223 of the reservoir 22.

The dimensioning of the distance h $ 3 is also advantageously chosen as a function of the spacing between the channels 241 and 243 of the fastening flange 24.

In addition, the fixing flange 24 further comprises, according to the embodiment described, grooves or cuvettes 245, 247 better visible in FIGS. 3a, 4, 8 and 9, a groove 245 of which serves to bring the first condensed fluid. in 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 evacuation channel 243 towards the subcooling zone of the beam of heat exchange 3.

The grooves 245 and 247 for example have a diameter identical to the introduction 241 and discharge 243 channels of the fastening flange 24.

Thus, the fixing flange 24 is arranged so that the notches 161a of the fluidic 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 inlet channel 241 opens. of the fastening flange 24.

The fixing flange 24 is also arranged so that the notches 161b of the fluidic connection frame 16 in fluid communication with the circulation channels 73 for the subcooling of the first condensed fluid 161b open into the groove 247 into which the flow channel opens. discharge 243 of the fastening flange 24.

Thus, the first fluid after condensation circulating in the circulation channels 71 for condensation opens into the groove 245, flows into the insertion channel 241 of the fastening flange and then enters the reservoir 22.

El, the first fluid after phase separation leaves the reservoir 22 and flows in the discharge channel 243 of the fastening flange 24 to be distributed in the circulation channels 73 for subcooling 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 a same first frame 13 or alternatively by a single heat exchange tube 5 received in a first frame 13.

It is the first frames 13 receiving the monotubes 5 or several tubes 51, 53 of heat exchange that ensure the non-fluid communication between the two zones of condensation and subcooling.

Finally, the particular conformation of the fluidic connection frame or frames 16 makes it possible in a simple way to connect the reservoir 22 on the one hand to the condensation zone and on the other hand to the sub-cooling zone of the heat exchange, allowing to arrange in different positions the reservoir 22 on the heat exchanger 1.

Furthermore, such a heat exchanger 1 has a 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 refrigerant such as CÜ2, as well as performance heat exchange optimized.

Claims (17)

1. Heat exchanger (1) in particular for a motor vehicle, for a heat exchange between at least a first fluid and a second fluid, said exchanger (1) being able to act as a condenser and comprising a heat exchange bundle (3). ) with a plurality of heat exchange tubes (5; 51,53) comprising circulation channels (7): - intended to be traversed by the first fluid and - intended to be in fluid communication with a fluid reservoir (22); ) capable of separating the gaseous phase and the liquid phase from the first condensed fluid, characterized in that: - the heat exchange tubes (5; 51, 53) comprise: • circulation channels (71) for the condensation of the first fluid defining a condensing zone of the heat exchange bundle (3), and • circulating channels (73) for subcooling the first condensed fluid defining a sub-cooling zone of the exchange bundle thermal device (3), in that - the heat exchanger (1) comprises a stack of frames (13, 15, 16), at least some frames (13) of which are said frames for receiving the heat exchange tubes (5; 51, 53) are adapted to receive the heat exchange tubes (5; 51, 53) and are respectively shaped so as to separate the condensation zone and the subcooling zone from the heat exchange bundle (3), and in that - at least one fluidic connection frame (16) is shaped to put in fluid communication the reservoir (22) • on the one hand with the circulation channels (71) for condensation and • other separately and separately from the circulation channels (73) for subcooling. 2. Heat exchanger (1) according to the preceding claim, wherein each receiving frame (13) of the heat exchange tubes (5; 51, 53) is configured to receive both channels (71) of circulation for the condensing and circulation channels (73) for subcooling defined by the heat exchange tubes (5; 51,53) so that the condensing zone and the sub-cooling zone of the heat exchange bundle (3) are arranged side by side and without direct fluid communication with each other. 3. Heat exchanger (1) according to one of claims 1 or 2, wherein: - the receiving frames (13) of the heat exchange tubes (5) are respectively able to receive a single heat exchange tube ( 5), and wherein - 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 channels (73) for circulation for the penny. s-cooling of the first condensed fluid. 4. Heat exchanger (1) according to the preceding claim, wherein the receiving frames (13) of the heat exchange tubes (5) respectively facing each end of the heat exchange tube (5) it receives at least one separation portion (136) arranged between the circulation channels (71) for condensing the first fluid and the circulation channels (73) for subcooling the first condensed fluid, so as to prevent fluid communication between the circulation channels (71) for the condensation and for the subcooling (73). 5. Heat exchanger (1) according to one of claims 1 or 2, wherein: - the heat exchange bundle (3) comprises: • at least a first row (A) of first heat exchange tubes (51). ) comprising the circulation channels (71) for condensing the first fluid, and • at least a second row (B) of second heat exchange tubes (53) comprising the circulation channels (73) for the subcooling of the first fluid first condensed fluid, and wherein - the receiving frames (13) of the heat exchange tubes (51, 53) are respectively adapted to receive at least two heat exchange tubes (51, 53) including a first tube of heat exchange (51) of the first row (A) and a second heat exchange tube (53) of the second row (B). 6. Heat exchanger (1) according to the preceding claim, wherein each frame (13) for receiving heat exchange tubes (51, 53) comprises at least one partition (135) disposed between the first exchange tube thermal (51) and the second heat exchange tube (53), so as to prevent fluid communication between the two heat exchange tubes (51, 53) received in the same frame (13). 7. Heat exchanger (1) according to any one of the preceding claims, wherein the receiving frames (13) of the heat exchange tubes (5; 51, 53) have a thickness at least equal to the thickness of the tubes. heat exchanger (5; 51, 53) in the stacking direction of said frames (13, 15, 16). 8. Heat exchanger (1) according to any one of the preceding claims, - comprising at least one manifold (19) of the first fluid defining an inlet (19A) for the first fluid in the heat exchange bundle (3) and an outlet (19B) of the first fluid out of the heat exchange bundle (3), and - in which the receiving frames (13) of the heat exchange tubes (5; 51,53) respectively comprise: placing in fluid communication (131a) between the inlet (19A) for the first fluid and the circulation channels (71) for the condensation of the first fluid, and • fluid communication means (131b) between the outlet (19B). ) of the first fluid and the circulation channels (73) for subcooling the first condensed fluid. 9. Heat exchanger (1) according to the preceding claim, wherein the means of fluid communication (131a, 131b) are formed as recesses of the first frames (31) in which the ends of the heat exchange tubes ( 5; 51, 53) open, and arranged in fluid communication with the manifold (19) of the first fluid. 10. Heat exchanger according to one of claims 8 or 9, wherein the receiving frames (13) of the heat exchange tubes (5; 51, 53) respectively comprise side edges (13A, 13B) extending substantially perpendicularly to the direction of the circulation channels (7, 71, 73) for the first fluid, and wherein at least one of said side edges (13A, 13B) has the fluid communication means (131a, 131b). 11. Heat exchanger (1) according to any one of the preceding claims, comprising a reservoir (22) of fluid attached to the heat exchange bundle (3). 12. Heat exchanger (1) according to the preceding claim, comprising a fastening flange (24) of the reservoir (22) to the heat exchange bundle (3), and wherein the fluidic connection frame (16) is shaped so to put in fluid communication the reservoir (22) and the circulation channels (71) for the condensation on the one hand, and the circulation channels (73) for the subcooling on the other hand, via the fastening flange (24). 13. Heat exchanger (1) according to the preceding claim, wherein the fastening flange (24) comprises: - an introduction channel (241) of the first condensed fluid (Fl) from the channels (71) of circulation for the condensation arranged in fluid communication with an inlet (221) of the reservoir (22), and - a discharge channel (243) of the first fluid after phase separation (F1 ') towards the circulation channels (73) for subcooling arranged in fluid communication with an outlet (223) of the reservoir (22). 14. Heat exchanger (1) according to one of the preceding claims, the fluidic connection frame (16) is formed with a predefined number of teeth (162a, 162b) separated by notches (161a, 161b) for putting in communication fluidic reservoir (22) and the channels (71) for circulation on the one hand and the channels (73) circulation for subcooling on the other. 15. Heat exchanger (1) according to one of the preceding claims, wherein the fluidic connection frame (16) comprises at least one edge (16A) on which rests at least one heat exchange tube end (5; , 53) and having a solid portion (163), said edge (16A) is shaped so as: - to put in fluid communication the reservoir (22) with the circulation channels (71) for condensation on one side of the solid portion (163) and - put in fluid communication the reservoir (22) with the channels (73) of circulation for subcooling the other side of the solid part (163). 16. Heat exchanger (1) according to claim 4 taken in combination with the preceding claim, wherein the solid portion (163) of the fluidic connection frame (16) has a width at least equal to the width of the separation portion ( 136) receiving frames (13) of heat exchange tubes (5; 51,53) which are arranged in the heat exchange bundle (3), other than vis-à-vis the tank (22) and or the fastening flange (24). 17. Heat exchanger (1) according to claim 8 taken in combination with any one of the preceding claims, comprising an alternating stack of: first receiving frames (13) of the heat exchange tubes (5; 51, 53). , and second frames (15) respectively defining at least one second circulation channel (9) for the second fluid, the second frames (15) having: • guides (151a) for the passage of the first fluid to be condensed, arranged in the alignment of the communication means (131a) of the first frames (13), so as to allow the flow of the first fluid in the stack of the first frames (13) and the second frames (15) for condensation of the first fluid, and • guides (151b) for the passage of the first condensed fluid, arranged in alignment with the communication means (131b) of the first frames (13), so as to allow the flow of the first fluid co ndensé in the stack of first frames (13) and second frames (15) for subcooling the first condensed fluid.