FR3045802A1 - THERMAL EXCHANGER, IN PARTICULAR FOR MOTOR VEHICLE - Google Patents

Abstract

The invention relates to a heat exchanger (1) between at least a first fluid and a second fluid, comprising: - a heat exchange bundle (3) with a plurality of heat exchange tubes (5) defining first channels of circulation (7) for the first fluid in the heat exchange tubes (5) and second circulation channels (9) for the second fluid between the heat exchange tubes (5), - at least one manifold (19) ) of the first fluid, and - at least one inlet pipe and an outlet pipe (21) for the second fluid. According to the invention, the heat exchanger (1) comprises an alternating stack of: first frames (13) for receiving the heat exchange tubes (5), the first frames (13) respectively comprising means for placing in communication fluidic fluid (131) between the collecting box (19) and the heat exchange tubes (5), and second frames (15, 15 ') respectively defining at least one second circulation channel (9) for the second fluid and respectively having means for fluid communication (152) between the second circulation channel (9) and the inlet and outlet pipes (21) for the second fluid.

Description

AT

The invention relates to the field of heat exchangers and in particular to heat exchangers intended to be traversed by a fluid under high pressure. In this regard, the invention relates more particularly to heat exchangers able to be traversed by a refrigerant fluid having a relatively high operating pressure, as is the case with natural gases such as carbon dioxide designated by CO2, having an operating pressure higher than the refrigerant gases used in the solutions of the state of the art.

Such heat exchangers find particular application in motor vehicles. They may in particular constitute a gas cooler in which the coolant such as CO2 is cooled by a second fluid, such as liquid. Conversely, the second fluid can be cooled by the first fluid for example in gaseous form, the heat exchanger is then commonly referred to as "Water chiller" in English.

Such heat exchangers can in particular be used in the thermal regulation of one or more batteries of an electric or hybrid vehicle. The thermal regulation of the batteries is an important point because if the batteries are subjected to temperatures too cold, their autonomy can decrease strongly and if they are subjected to too high temperatures, there is a risk of thermal runaway up to to the destruction of the battery, or even the motor vehicle. In order to regulate the temperature of the batteries, it is known to use a coolant, generally coolant comprising a mixture of brine, which circulates in a heat exchanger in contact with the battery or batteries. The coolant can thus bring heat to the battery or batteries to heat them, this heat having been absorbed by the coolant for example during the heat exchange with the CO2 circulating in the gas cooler. The coolant can also, if necessary, absorb the heat emitted by the battery or batteries to cool them and remove this heat at one or more other heat exchangers.

Such heat exchangers can also be used like any other gas cooler in an air conditioning circuit.

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

Heat exchangers are known, for example, comprising a stack of plates allowing the circulation of the first fluid, such as the refrigerant or refrigerant gas, and the second fluid such as the cooling liquid.

However, the use of a refrigerant such as CO2 at a very high pressure, generally greater than 100 bar, with a burst pressure of up to 340 bar, for example, implies that heat exchangers such as coolers gas, must withstand such high pressures.

Plate heat exchangers known from the prior art do not allow to withstand such high pressures.

In order to remedy this, heat exchangers comprising a stack of tubes interconnected by at least one collector of the first fluid, in particular the refrigerant fluid on each side of the tubes, and the second fluid, for example, are known from the prior art. in liquid form, can circulate around the tubes in an envelope connected to a water box.

However, such an architecture is complex to achieve and in particular has drawbacks in terms of sealing, particularly in the case of a brazed heat exchanger for which it proves necessary to provide multiple soldering points for several pieces of the heat exchanger. In addition, with this architecture, the two fluids circulate generally at cross flow. It is not always possible to provide a flow against the current or in several passes of the two fluids, which limits the efficiency of the heat exchanger. In addition, it is difficult to reduce the tube pitch below 3mm due to the known design of the manifold receiving the ends of the tubes, which also limits the efficiency of the heat exchanger. It has also been found that such a heat exchanger does not always have good mechanical strength.

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.

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 providing a heat exchanger simple to achieve and having a small footprint all while having interesting properties to withstand the strong local pressures. For this purpose, the subject of the invention is a heat exchanger between at least a first fluid and a second fluid, in particular for a motor vehicle, said exchanger comprising: a heat exchange bundle comprising a plurality of heat exchange tubes defining first circulation channels for the first fluid in the heat exchange tubes and second circulation channels for the second fluid between the heat exchange tubes, at least one manifold of the first fluid, and at least one inlet and one outlet for the second fluid.

According to the invention, the heat exchanger comprises an alternating stack of: first frames for receiving the heat exchange tubes, second frames respectively defining a second circulation channel for the second fluid, the exchanger further comprising: fluidic communication between the header and the heat exchange tubes; means for placing fluid communication between the second circulation channel and the inlet and outlet pipes for the second fluid.

According to one embodiment of the invention, the first frames may respectively comprise means for placing in fluid communication between the header box and the heat exchange tubes.

According to one embodiment of the invention, the second frames may respectively have means for placing in fluid communication between the second circulation channel and the inlet and outlet for the second fluid. The inlet can be implemented by an inlet manifold.

The outlet can be implemented by an outlet pipe. The heat exchanger thus comprises a stack of simple elements, namely frames and heat exchange tubes in which the first fluid circulates, such as the refrigerant, inserted in the first frames and between which circulates the second fluid such as only coolant.

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 first and second frames.

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

In addition, 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 known solutions.

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.

It is thus possible to allow a countercurrent flow of the two fluids, or even a circulation of the two fluids in several passes and against the current relative to each other.

Such a heat exchanger has a better mechanical strength compared to the solutions of the prior art and very good resistance to high pressures, for example due to the circulation of CO2 as a coolant. 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, the first frames respectively comprise lateral edges extending substantially perpendicularly to the longitudinal direction of the first circulation channels for the first fluid, and at least one of said lateral edges having the means for setting fluid communication .

According to another aspect of the invention, the first frames have a substantially rectangular general shape, and the side edge or edges having the fluidic communication means extend in the direction of the width of the first frames.

According to one embodiment, the fluidic communication means are made in the form of recesses in one of the edges of the first frames, the ends of the heat exchange tubes opening into the recesses, the recesses being arranged in fluid communication with the collector box of the first fluid.

Advantageously, the second frames have guides for the passage of the first fluid, such as through-passage orifices, arranged in alignment with the recesses of the first frames, so as to allow the flow of the first fluid in the stack. first managers and second managers.

According to another aspect of the invention, the second frames have a substantially rectangular general shape, and the passage guides of the first fluid are arranged on at least one of the lateral edges of the second frames extending in the width direction of the second frames.

However, according to other embodiments, it is possible to provide second frames having a general shape that is not rectangular, for example elliptical, or diamond-shaped.

Likewise, according to other embodiments, it would be possible to provide first frames having a general shape that is not rectangular, for example elliptical, or diamond-shaped.

According to yet another aspect of the invention, the second frames respectively have through openings in fluid communication with the input and output, and respectively opening on the inside of a second frame.

The second frames having a substantially rectangular general shape, the through openings are advantageously arranged on the longitudinal edges of the second frames extending parallel to the direction of the first traffic channels.

According to one embodiment, the second frames respectively have at least two handles defining the through openings of fluid communication, with a first loop arranged in fluid communication with the inlet and a second loop arranged in fluid communication with the outlet.

According to one aspect of the invention, the first frames have guides for the passage of the second fluid arranged in the alignment of the through openings for fluidic communication of the second frames.

According to one embodiment, the first frames have handles forming the guides and defining passage openings for the second fluid and arranged in alignment with the handles of the second frames.

According to a further aspect of the invention, the heat exchanger further comprises tabulators of the flow of the second fluid arranged in the second circulation channels, and the second frames have a thickness substantially equal to the thickness of the tabulators, in the stacking direction of said frames.

It is thus possible to increase in a simple manner the exchange surface density with respect to the solutions of the prior art, the size of which is limited by the collectors receiving the ends of the heat exchange tubes.

According to an exemplary embodiment, the heat exchange tubes respectively have on at least one wall deformations forming projections in a second circulation channel for the second fluid, such as corrugations.

According to an alternative embodiment, the heat exchanger comprises perturbation plates arranged in the second frames, the perturbation plates respectively have a plurality of turbulators, for example of substantially crenellated shape, in relief on a disturbance plate.

The heat exchange tubes are received and maintained in dedicated first frames while the turbulators can be received in the second dedicated frames and thus be superimposed on the heat exchange tubes.

According to another aspect of the invention, the second frames respectively have a thickness in the stacking direction of said frames, for example of the order of 2 mm, defining the pitch between the heat exchange tubes.

According to an additional aspect of the invention, the heat exchanger further comprises two closure plates on either side of the stack of first receiving frames of the heat exchange tubes and second frames, and the collecting box. the first fluid is arranged opposite the inlet and outlet for the second fluid, on the same closure plate.

According to one embodiment, the heat exchanger is configured for the circulation of at least one high-pressure fluid, for example of pressure greater than 100 bar, for example of pressure approximately equal to 120 bar.

For example, the first fluid is a refrigerant fluid intended to circulate at high pressure such as CO2.

According to yet another aspect of the invention, the first frames have a thickness, substantially equal to the thickness of the heat exchange tubes, in the stacking direction of said frames.

Thus, the heat exchange tubes can be maintained in the respective first frames before superposition of the different frames.

According to yet another aspect of the invention, the heat exchanger is assembled by brazing.

The superimposed frames make it possible to create the flow path of the first refrigerant fluid, when the frames are brazed together, and likewise the superposed frames make it possible to create the coolant flow path, in particular on two opposite sides of the bundle. heat exchange. 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 perspective view of a heat exchanger according to the invention, - Figure 2a is an exploded partial view of a heat exchange bundle comprising a stack of flat tubes, - Figure 2b is an exploded partial view of an exchange bundle thermal device comprising a stack of substantially corrugated tubes, - Figure 2c is an exploded view of the heat exchanger of Figure 1, - Figure 3 is a top view of the heat exchanger of Figure 1, - Figure 4 is a sectional view from below of a heat exchanger according to one embodiment of the invention; FIG. 5 is a partial perspective view of a stack of first frames and second frames of a FIG. 6 schematically represents a first frame of the heat exchange bundle receiving two heat exchange tubes; FIG. 7 is a view of the first single frame of FIG. FIG. 8a schematically represents a first frame of the heat exchange bundle receiving a heat exchange tube for two-pass circulation of a first fluid; FIG. 8b is a sectional view according to FIG. axis II of FIG. 8a; FIG. 8c is a side view of the end of the heat exchange tube of FIG. 8a; FIG. 9a schematically represents a variant of a first frame of the beam of FIG. heat exchange receiving a heat exchange tube for a two-pass circulation of the first fluid, - Figure 9b is a sectional view along the line II-II of Figure 9a, - Figure 9c is a side view from the end of the tube Figure 10 is a fragmentary sectional view of a first frame showing a recess for the flow of a meltable coating upon soldering, and Figure 11 is a further view in FIG. perspective of a stack of first frames and second frames of a heat exchange bundle according to one embodiment of the invention, - Figure 12 schematically shows a second frame of the heat exchange bundle for circulation in two passes of the second fluid receiving turbulators from the flow of the second fluid, - Figure 13 is a view of the second single frame of Figure 12, - Figure 14 is a partial perspective view showing a reservoir for the flow a coating capable of melting during soldering, provided on a second frame, - Figure 15 is a side sectional view of a second frame having a reservoir on each side, - Figure 16 e there is another partial perspective view of the stack of first frames and second frames of the heat exchange bundle showing a first frame receiving two heat exchange tubes communicating at one end; FIG. 17 is a perspective view of FIG. 18 is a first perspective view of a perturbation plate according to another embodiment, FIG. 19 is a second perspective view of the disturbance plate of FIG. FIG. 18; FIG. 20 is a partial perspective view of the heat exchanger of FIG. 1 showing in more detail a collecting box of the first fluid; FIG. 21 is a partial perspective view of the heat exchange bundle; showing a fastening flange arranged above the stack of first and second frames, and - Figure 22 is a cross-sectional view of the top of the exchanger t hermetic showing the manifold of Figure 20 and the fastening flange of Figure 21.

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 to provide other embodiments.

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 inverted arrangement of the elements in the mounted state in a motor vehicle in particular.

In other words, in a vehicle, the heat exchanger of the invention is mounted "upside down", that is to say that the upper part of Figure 1, for example, is below the lower part of Figure 1, when one places in the frame of reference of a motor vehicle.

AT

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.

It is in particular a heat exchanger 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 during the heat exchange. soldering assembly, as will be detailed later. The heat exchanger 1 according to the invention is particularly suitable for the circulation of at least one fluid having a high operating pressure, in particular greater than 100 bar.

For example, the heat exchanger 1 can be adapted for the circulation of a fluid having a pressure of between 100 bars and 260 bars.

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. The heat exchanger 1 can in particular be a gas cooler in which the cooling fluid such as CO2 is cooled by a second fluid for example in liquid form, such as cooling liquid comprising a mixture of brine. The second fluid such as the cooling liquid can also be cooled by the first fluid such as CO2, such a heat exchanger is then commonly referred to as "Water chiller" in English. 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 circulation of the first and second fluids is advantageously countercurrent in the heat exchange bundle 3. The introduction and the evacuation of the first fluid in the heat exchange bundle 3 or out of the heat exchange bundle 3 is shown by way of example by the arrows Fl [for the introduction and Flo for the evacuation.

Similarly, 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 is shown schematically by way of example by the arrows F2i for the introduction and F2o for evacuation.

Finally, the heat exchanger 1, and more precisely the heat exchange bundle 3, can be configured for circulation in at least two passes of one of the two fluids, or both fluids, as will be described further in detail thereafter.

An example of flow of the two fluids against the current and in two passes is schematically illustrated by arrows F1 and F2 in Figures 1 and 2c.

More specifically, the heat exchange bundle 3, which can be seen more clearly in FIGS. 2a to 2c, comprises a plurality of heat exchange tubes 5 stacked so as to alternately define first circulation channels 7 for the first fluid in the tubes. heat exchange 5 and second circulation channels 9 for the second fluid between the heat exchange tubes 5.

The heat exchange tubes 5 can be made in the form of flat tubes, advantageous in terms of space.

The flat tubes 5 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. In other words, it is the thickness in the direction of stacking heat exchange tubes 5.

Each heat exchange tube 5 defines a predetermined number of first circulation channels 7 for the first fluid, in particular circulating microchannels 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 allow the flow of the first fluid respectively extend in a direction parallel to the longitudinal direction of the heat exchange tubes 5.

The first fluid can follow a circulation in a so-called "I" flow but also a two-pass circulation called "U" circulation as will be described later.

Similarly, the second circulation channels 9 for the second fluid may be shaped to allow circulation in a so-called "I" flow but also a circulation in two passes called "U" circulation as will be described later.

Tabulators 11 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 tabulators 11 may be carried by an element 12 separate from the heat exchange tubes 5 as illustrated in Figure 2a or 2c.

Alternatively, tabulators 11 may be formed on the heat exchange tubes 5, for example by deformations such as corrugations of the heat exchange tubes 5 which project into the second circulation channels 9 for the second fluid, such as illustrated in Figure 2b.

Interlayers are advantageously arranged between the heat exchange tubes 5, and define the pitch between the heat exchange tubes 5.

According to one embodiment, the heat exchange bundle 3 comprises an alternating stack of first frames 13 and second frames 15, 15 '. At least some second frames 15 form the dividers. The stack is here substantially vertically. Each first frame 13 is able to receive at least one heat exchange tube 5 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, 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, 15 'are described in more detail below. By way of example, closure plates 17, 18 (see FIGS. 1 and 2c), in particular at least one bottom closure plate 17 and at least one top closure plate 17, 18, can be arranged on both sides. other of the stacking of the first frames 13 and the second frames 15, 15 'so as to close the heat exchange bundle 3.

Referring to FIGS. 1 and 3, the heat exchanger 1 further comprises at least one manifold 19 of the first fluid arranged in fluid communication with the first circulation channels 7.

The manifold 19 is according to the illustrated example arranged on an upper closure plate 18 disposed at the top of the heat exchange bundle 3. The heat exchanger 1 further comprises at least two inlet and outlet manifolds 21 of fluid allowing the introduction and the evacuation of the second fluid.

In this example, the two tubes 21 are arranged on the same upper closure plate 18 as the manifold 19 for the first fluid.

This upper closure plate 18 arranged at the top of the heat exchange bundle 3 makes it possible to guide the second fluid between the pipes 21 and the heat exchange bundle 3.

Of course, according to a variant not illustrated, it is possible to arrange the two pipes 21 on the bottom plate 17.

According to another variant not illustrated, provision can be made to separately arrange the pipes 21 with a pipe 21 on the upper plate 18 and the other pipe 21 on the bottom plate 17.

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, thus allowing a counter-current circulation of two fluids.

According to the arrangement illustrated in Figures 1 and 3, the manifold 19 is arranged on the left while the pipes 21 are arranged on the right.

First frames called tubes-frames

With reference to FIGS. 2a to 2c and 4 to 10, the first frames 13 for receiving the heat exchange tubes 5 are now described in greater detail.

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

The first frames 13 have two opposite edges 13A, 13B (see FIGS. 6, 7, 8a and 9a) extending perpendicularly to the direction of the first circulation channels 7 of the first fluid, in other words here perpendicularly to the longitudinal direction heat exchange tubes 5, and two other opposite edges 13C, 13D extending parallel to the direction of the first flow channels 7 of the first fluid, in other words here parallel to the longitudinal direction of the heat exchange tubes 5.

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

The general direction of flow of the first fluid means the direction of the flow in "I" in the case of a flow in one pass of the first fluid, or the direction of the branches of the "U" in the case of a circulation in two passes of the first fluid.

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. The longitudinal axis of the first frames 13 and heat exchange tubes 5 is here confused.

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

As before, the thickness is considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the first frames 13. In other words, it is the thickness in the direction of stacking frames 13, 15, 15 '.

According to a first embodiment illustrated in Figures 2a and 2b, each first frame 13 is adapted to receive a single heat exchange tube 5 allowing a flow in one pass of the first 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 means for placing in fluid communication 131 the first circulation channels 7 of the heat exchange tubes 5 with the manifold 19.

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

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

Of course, the number of recesses 131 is adapted as a function of the number of first circulation channels 7 of the heat exchange tubes 5.

These recesses 131 are here provided on two opposite edges 13A, 13B of the first frames 13 which are opposite the ends of the heat exchange tubes 5. This is the lateral edges of the first frames 13. Only a lateral edge 13A is visible in Figures 2a and 2b.

The first frames 13 are arranged so that their recesses 131 are in fluid communication with the recesses 131 of the other first frames 13.

Here, the recesses 131 of the first frames 13 are aligned in the direction of the height of the heat exchange bundle 3. In addition, on one side of the first frames 13, the recesses 131 are aligned with the manifold 19.

According to the preferred embodiment, at least one side 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 131 is delimited by an arch, in other words each recess 131 is made between two adjacent arch feet 133 and is delimited by these two arches 133 and the arch vault 132 connecting them .

When a heat exchange tube 5 is arranged in the housing 130 of a first frame 13, the space remaining between one end of the heat exchange tube 5 and an arch 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, each first frame 13 advantageously comprises at least one stress absorption zone on at least one lateral edge 13A, 13B opposite one end of a heat exchange tube 5.

Such a stress absorption zone is able to withstand mechanical stresses, in particular due to pressure.

The stress absorption zones may be made by a predetermined number of stress absorption legs formed on at least one lateral edge 13A, 13B of a first frame 13 opposite one end of a heat exchange tube 5.

These stress absorption legs extend towards the end of the heat exchange tube 5.

In the illustrated example, the arches 133 provide this function of stress absorption legs.

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 brazing, the arches 133 still make it possible to define brazing areas with the second frames 15, 15 'as will be described later.

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. By way of illustration, in the figures, various embodiments of the loops 134, in particular FIGS. 1, 2a to 2c, 13, illustrate a first embodiment of loops 134 of substantially rounded shape, while FIGS. 7, 8a, 9a, 11, 16 illustrate a second embodiment of the handles 134 whose contour is more rectilinear shape.

Of course, any other form of the handles 134 may be considered.

The handles 134 allow to define the guides for the passage of the second fluid. For example, this through opening has a diameter of the order of 2mm.

The ratio between the diameter of a passage opening of the second fluid and the diameter of a through opening 131 of fluidic communication allowing the flow of the first fluid is in this example of the order of 4.

The loops 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.

Figures 2c and 4 to 7 show a second embodiment of the first frames 13. The description of the first embodiment with reference to Figures 2a and 2b applies to the identical components, only the differences are now described.

The second embodiment differs from the first embodiment in that each first reception frame 13 is able to receive two heat exchange tubes 5. The heat exchange bundle 3 then has two rows of heat exchange tubes 5 : first heat exchange tubes and second heat exchange tubes.

Similarly, the fluid communication means 131 define two rows respectively associated with a row of heat exchange tubes 5. Thus, first communication means 131 ensure the fluid communication of the first heat exchange tubes 5 or in other words a first row of first heat exchange tubes with the manifold 19.

And, second means of communication 131 ensure the fluidic communication of the second heat exchange tubes 5 or in other words the second row of second heat exchange tubes with the manifold 19.

In this case, a succession of arches may be provided on a lateral edge of the first frame 13 over the entire width of the set of heat exchange tubes 5 that the first frame 13 can receive, here two heat exchange tubes 5.

In addition, two adjacent tubes in a first frame 13 communicate with each other at one end so as to allow two-pass circulation of the first fluid.

The heat exchange bundle 3 thus has at least one reversal zone of the first fluid, that is to say, allowing the first fluid having circulated in a heat exchange tube 5 to circulate to another heat exchange tube 5, namely the adjacent heat exchange tube 5 received in the same first frame 13.

Of course, more than two heat exchange tubes 5 can be provided for a circulation of the first fluid in addition to two passes in a first frame 13. The fluidic communication at one end of two adjacent heat exchange tubes 5 received in a first frame 13 is advantageously provided by a second frame 15 as will be described in more detail later.

Each first reception frame 13 has in this case 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.

In the illustrated example, each first receiving frame 13 has a partition wall 135, for example substantially central, which compartmentalizes the first receiving frame 13 in two housings 130 to each receive a heat exchange tube 5.

The partition wall 135 is thus arranged between two heat exchange tubes 5 when they are placed in the first frame 13. The partition wall 135 extends in this example over the entire length of the exchange tubes thermal 5 received in the first frame 13.

The partition wall 135 of a first frame 13 can be made in one piece with this first frame 13. Such a first frame 13 can be made by cutting stamping in a simple manner.

Figure 8a shows a first frame 13 according to a third embodiment. The description of the first embodiment with reference to FIGS. 2a and 2b applies to the identical components, only the differences are now described.

According to this third embodiment illustrated in FIG. 8a, each first frame 13 is able to receive a single heat exchange tube 5 allowing a two-pass circulation of the first fluid.

Circulation in at least two passes with a single heat exchange tube 5 instead of the two heat exchange tubes 5 of the preceding solution with reference to FIGS. 2c and 4 to 7, makes it possible to limit the number of parts to be produced and to assemble, while allowing good resistance to pressure. For this purpose, each heat exchange tube 5 defines at least two groups 70, 72 of channels or microchannels 7 for circulating fluid communicating with each other at one end 50 of the heat exchange tube 5, here a longitudinal end, and not communicating with each other at the opposite end 52.

In this case, the heat exchange bundle 3 has at least one reversal zone of the first fluid, that is to say, allowing the first fluid having circulated through a group 70 of circulation channels 7 to flow to another group 72, at the end 50 of the heat exchange tube 5.

Of course, it can be provided that each heat exchange tube 5 is shaped to define more than two groups 70, 72 of circulation channels 7 communicating in pairs at one end, so as to allow circulation of the first fluid in addition to two passes.

In order to prevent fluid communication between the two groups 70, 72 of the first circulation channels 7, at the other end 52 of the heat exchange tube 5, the heat exchange bundle 3 further comprises at least one means of blocking the passage of the first fluid.

According to this third illustrated embodiment, the means for blocking the fluid passage is formed by shape cooperation between a first frame 13 and the heat exchange tube 5 received in this first frame 13, more precisely between a lateral edge 13B of the first frame 13 and the end 52 vis-à-vis the heat exchange tube 5.

In this example, the locking means comprises at least one tongue 136 formed on a lateral edge 13B of a first frame 13 extending towards the end 52 of the heat exchange tube 5 vis-à-vis .

The tongue 136 here extends longitudinally towards the end 52 opposite the heat exchange tube 5. This tongue 136 is for example provided substantially in the middle of the lateral edge 13B of the first frame 13.

As best seen in Figure 8b, the tongue 136 has a base 136a integral with the edge 13B of the first frame 13. More specifically, in this example the tongue 136 is formed by the extension of an archway 133 towards the end 52 of the heat exchange tube 5.

In this case, the base 136a of the tongue 136 extends an arch foot 133. In addition, the base 136a of the tongue 136 has a thickness substantially equal to the thickness of the heat exchange tube 5 vis-à- screw, more precisely the end 52 of the heat exchange tube 5.

The base 136a of the tongue 136 bears against the end 52 of the heat exchange tube 5 in facing relation between the two groups 70, 72 of the first circulation channels 7, thus blocking the passage of the first fluid. a group 70 of circulation channels 7 to another group 72 of circulation channels 7.

The tongue 136 further has a termination 136b in the extension of the base 136a and thinner than the base 136a. The thickness of the termination 136b of the tongue 136 is for example reduced by half compared to the thickness of the first frame 13, and may in this example be of the order of 0.5mm.

The termination 136b of the tongue 136 therefore extends from the base 136a of the tongue 136 towards the end 52 of the heat exchange tube 5. In particular, according to the third illustrated embodiment, the termination 136b extends substantially from the center of base 136a.

The heat exchange tube 5 comprises an assembly orifice 54 at its end 52 opposite the lateral edge 13B of a first frame 13 having the tongue 136. The assembly orifice 54 is arranged so that the termination 136b of the tongue 136 can be inserted into the assembly hole 54. To do this, the assembly hole 54 has a cross section complementary to the termination 136b.

Thus, at the assembly, a heat exchange tube 5 is inserted in a first receiving frame 13 and then a translation of the heat exchange tube 5 is carried out so that the heat exchange tube comes to go on the tongue. 136. This has the effect of allowing the maintenance of a heat exchange tube 5 in the first receiving frame 13, especially before crimping.

The termination 136b of the tongue 136, cooperating with the assembly orifice 54, thus serves as a holding element of the heat exchange tube 5 in the first receiving frame 13. The orifice 54 is here realized more large than the first channels or microchannel circulation 7 for the first fluid, as best seen in Figure 8c, thus facilitating the fitting of the heat exchange tube 5 on the tongue 136.

Figure 9a shows a first frame 13 according to a fourth embodiment. The description of the third embodiment with reference to FIGS. 8a to 8c applies to the identical components, only the differences are now described.

The fourth embodiment illustrated in FIG. 9a differs from the third embodiment in that each first frame 13 comprises, not only a tab 136 opposite the end 52 of the heat exchange tube 5, where the passage of the first fluid from a group of channels 70 to another group 72 is prohibited, but two tabs 137, 138. Namely, each first frame 13 comprises: a first tongue 137 arranged on the side edge 13A vis-à-vis the end 50 of the heat exchange tube 5 with fluid communication between the two groups 70, 72 of the circulation channels 7, and a second tongue 138 arranged on the opposite side edge 13B opposite the end 52 opposite of the heat exchange tube 5 without fluid communication between the two groups 70, 72 of the circulation channels 7.

According to this fourth illustrated embodiment, only the second tab 138 forms the means for blocking the passage of fluid between the two groups 70, 72 of circulation channels 7.

Similarly to tab 136 of the third embodiment, each tab 137, 138, respectively, may be formed on a side edge 13A, respectively 13B, of a first frame 13 extending toward the end 50, respectively 52, the heat exchange tube 5 vis-à-vis.

The first tongue 137 here extends longitudinally toward the end 50 opposite the heat exchange tube 5.

Similarly, the second tongue 138 extends here longitudinally toward the end 52 opposite the heat exchange tube 5.

The two tabs 137 and 138 may be provided substantially in the middle of the respective lateral edge 13A, 13B of the first frame 13.

The two tabs 137 and 138 are arranged in this example symmetrically with respect to each other.

As best seen in Figure 9b, the first tongue 137 has a base 137a integral with the side edge 13A of the first frame 13. More specifically, in this example the first tongue 137 is formed by the extension of a foot 133 to the end 50 of the heat exchange tube 5. In this case, the base 137a extends a foot of arch 133.

The base 137a of the first tongue 137 may have a thickness substantially equal to the thickness of the heat exchange tube 5 vis-à-vis, more precisely of the end 50 of the heat exchange tube 5.

In addition, the base 137a of the first tongue 137 is arranged recessed with respect to the end 50 of the heat exchange tube, so that the first fluid can circulate in the space between the base 137a of the first tongue 137 and the end 50 of the heat exchange tube 5 vis-à-vis.

The first tongue 137 further has a termination 137b in the extension of the base 137a and thinner than the base 137a. The termination 137b thus extends from the base 137a towards the end 50 of the heat exchange tube 5 vis-a-vis.

The termination 137b of the first tab 137 extends here substantially from the edge of the base 137a and not from the center as the termination 136b of the tab 136 of the third embodiment.

As seen on the cross section of Figure 9b, the tongue 137 has the general shape of a shoe.

As regards the second tongue 138, it has a base 138a formed integrally with the edge 13B of the first frame 13. More precisely, in this example the second tongue 138 is formed by the extension of an arch foot 133 into direction of the end 52 of the heat exchange tube 5. In this case, the base 138a extends a foot of arch 133.

The base 138a of the second tongue 138 may have a thickness substantially equal to the thickness of the heat exchange tube 5 vis-à-vis, specifically the end 52 of the heat exchange tube 5. In a similar manner at the tongue 136 of the third embodiment, the base 138a of the tongue 138 abuts against the end 52 of the heat exchange tube 5 in facing relation between the two groups 70, 72 of the first circulation channels 7, thus blocking the passage of the first fluid from a group 70 of circulation channels 7 to another group 72 of circulation channels 7.

The second tongue 138 further has a termination 138b in the extension of the base 138a and of smaller thickness than the base 138a, which therefore extends from the base 138a towards the end 52 of the heat exchange tube 5 in a screw -a-vis. Similarly to the first tab 137, the termination 138b of the second tab 138 extends in this example from the edge of the base 138a.

As seen on the cross section of Figure 9b, the tongue 139 also has a general shape of a shoe.

The heat exchange tube 5 has a notch 56 visible in Figure 9c. As the heat exchange tube 5 is preferably made by extrusion, the notch 56 can be made at the same time, in this case the notch 56 is formed over the entire length of the heat exchange tube 5.

The termination 137b of the first tongue 137 may be inserted into the notch 56 at the end 50 opposite the heat exchange tube 5, and likewise the termination 138b of the second tongue 138 may be inserted in the notch 56 at the end 52 opposite the heat exchange tube 5. Thus, on assembly, it is no longer necessary to provide a step of translation of the tube of heat exchange 5 after the insertion of the latter in a first receiving frame 13, then simply position the heat exchange tube 5 so that the ends 137b and 138b of the tabs 137 and 138 of the first receiving frame 13 are arranged in the corresponding slots 56 of the heat exchange tube 5, to ensure the maintenance of the heat exchange tube 5, especially before crimping.

An enlarged portion of a first frame 13 according to a fifth embodiment is illustrated in FIG. 10. The description of the first embodiment with reference to FIGS. 2a and 2b applies to the identical components, only the differences are now described.

As said before the heat exchanger 1 is in particular assembled by brazing. For this purpose, it is expected that the elements of the heat exchange bundle 3, and in particular the first frames 13 and the second 15, 15 ', have at least partially a coating capable of melting when the assembly passes into the oven for the brazing and migrate so as to close the gaps between the parts of the heat exchanger 1. The coating is commonly referred to as "cladd" in the field of brazing of metal parts, including aluminum.

In particular, the coating is added to the core of the parts, such as the first frames 13 and second frames 15, 15 ', during manufacture, for example by cold rolling. It may be a non-limiting example of a coating comprising aluminum and silicon.

The percentage of the coating is for example of the order of 5% to 10% of the material of a frame 13, 15, 15 'for example.

Of course, the percentage of the coating is chosen small enough not to weaken the elements of the heat exchange bundle 3, including the first frames 13 and the second 15, 15 'after brazing.

The fifth embodiment differs from the first embodiment in that the first frames 13 respectively have at least one recess 139 at an inner corner receiving a corner of a heat exchange tube 5, that is to say on a corner of the inner edge of a first frame 13, which is opposite with a heat exchange tube 5 when the latter is arranged in the first receiving frame 13.

Such a recess 139 is provided to allow the flow of the coating during brazing of the heat exchanger 1, thus preventing the coating from clogging the first channels or microchannel circulation 7 of the heat exchange tubes 5.

Of course, the design of this roughening 139 takes into account a compromise not to weaken the first frame 13 while being able to collect a sufficient amount of the coating that migrated during soldering.

In a particular example, the width of this recess 139 is substantially equal to the width of a groove 154 provided for a similar purpose on a second frame 15, 15 'as described below.

Advantageously, the first frames 13 respectively have four recesses 139 respectively arranged at each of the four inner corners of a first frame 13.

In addition, the recess or recesses 139 are arranged close to the fluid communication connection means 131.

In addition, as can be seen more clearly in FIG. 4, according to the illustrated example in which at least one edge of a first frame 13 is shaped with a succession of arches, at least one recess 139 is made in the extension of an extreme arch, that is to say of the first or last arch of the succession of arches.

Of course, such recesses 139 may advantageously be provided on the first frames 13 indifferently according to one or other of the previously described embodiments.

Second frames

With reference to FIGS. 2b, 2c and 11 to 15, the second frames 15, 15 'are now described in more detail.

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

When the second frames 15, 15 'receive turbulators 11, the second frames 15, 15' are said frames-turbulators or turbulators frames.

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

It is also possible to define the second frames 15, 15 'with respect to the general direction of flow of the first fluid, namely that the second frames 15, 15' have: two opposite edges extending parallel to the general direction of flow of the first fluid, and two other opposite edges extending perpendicular to the general direction of flow of the first fluid.

In addition, according to the embodiments described, it is still possible to define the second frames 15, 15 'with respect to the general direction of flow of the second fluid flowing against the current of the first fluid, namely that the second frames 15, 15 'have two opposite edges extending parallel to the general direction of flow of the second fluid, and two other opposite edges extending perpendicular to the general direction of flow of the second fluid.

The general direction of flow of the second fluid means the direction of the circulation in "I" in the case of a circulation in a pass of the second fluid, or the direction of the branches of the "U" in the case of a circulation in two passes of the second fluid.

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

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

According to the embodiments described, the second frames 15, 15 'extend over the same length and the same width as the first frames 13. In particular, the outer contours of the first frames 13 and second frames 15, 15' are substantially identical so that the alternating stack of the first frames 13 and second frames 15, 15 'form a block.

More particularly, each second frame 15 defines an internal width and an internal length L (see FIG.

By "internal width" is meant 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 of the second frames 15, 15 'may be slightly larger than the lateral edges of the first frames 13, so that, as best seen in FIG. 14, the ends of the heat exchange tubes 5 received in the first frames 13 stacked with the second frames 15, 15 ', rest on the peripheral edge of the lateral edges of the second frames 15, 15'.

The second frames 15, 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, 15 'have a thickness Th (see FIG. 14) which is of the order of a few millimeters, for example of the order of 0.5 mm to 4 mm, preferably of the order of 2 mm. The thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the second frames 15, 15 '. In other words, it is the thickness in the stacking direction of the frames 13, 15, 15 '.

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

A plurality of second so-called interposed 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.

According to a non-limiting embodiment, the heat exchange bundle 3 may furthermore comprise a second end frame 15 'optionally arranged between a first frame 13 and a closure plate 17, in particular the bottom closure plate 17 , according to the example illustrated in Figure 2c.

Such a second end frame 15 'can be put in place for reasons of mechanical strength.

Of course, it is advantageous to provide a stack of first frames 13 and second frames 15 without such an end frame 15 '.

According to a first embodiment illustrated in FIG. 2a or 2b, each second frame 15, 15 'is shaped for circulation in one pass of the second fluid. For this purpose, each second frame 15, 15 'defines a second circulation channel 9 for the second fluid. The second circulation channel 9 here extends in a substantially "I" shape.

Figures 2c and 11 to 13 show a second embodiment of the second frames 15, 15 'allowing a two-pass circulation of the second fluid. For this purpose, the second frames 15, 15 'each comprise a bar 150 arranged inside the second frame 15, 15' respectively so as to separate two flow passes for the second fluid. It is therefore an internal bar 150.

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

Of course, it would be possible to provide a circulation of the second fluid in addition to two passes in a second frame 15, 15 'and for this purpose more than one bar 150 inside the second frame 15, 15' which would be non-limiting example, arranged in an offset manner and opposite to each other.

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

To do this, the bar 150 does not extend over the entire internal length L of the second frame 15, 15 ', as can be seen more clearly in FIG. 13. In other words, the bar 150 extends from a lateral edge of a second frame 15, 15 'towards the opposite lateral edge but without reaching this opposite lateral edge.

The bar 150 is thus secured to a lateral edge of a second frame 15, 15 'and projects with its free end towards the internal space of the second frame 15, 15' towards the opposite lateral edge, leaving a space .

The inner bar 150 therefore extends longitudinally from a lateral edge of a second frame 15 over a length l less than the internal length L of the second frame 15.

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 Th of the second frame 15. Thus, on each side of the bar 150, the input and the output of the path are defined. flow for the second fluid.

The bar 150 may also be called tongue.

In addition, the bar 150 is substantially of the same thickness as the second frame 15, 15 '.

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, 15 'in the width direction of the second frame 15, 15'. In this way, the bar 150 divides the second frame 15, 15 'into two parts of the same size.

Advantageously, the inner bar 150 extends over a length l at least equal to half the internal length L of a second frame 15, 15 '.

In particular, each second frame 15, 15 'and the inner bar 150 of the second given frame 15, 15' can be shaped so as to verify the following relation (a): (a): 0.49 <£ <0.95 with l = extension length of the bar 150 and L = internal length of the second frame 15,15 '.

Preferably, the upper bound is also defined by a strict relation, so that the second frame 15, 15 'and its inner bar 150 satisfy the following relation (a'): (a '): 0.49 <X- <0.95.

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

Moreover, in the case where the second frames 15, 15 'comprising such an inner strip 150 are stacked with first frames according to the first, the third or the fourth embodiment with reference to FIGS. 2a, 2b, 8a and 9a receiving each a single heat exchange tube 5, the heat exchange tubes 5 or monotubes received in the first frames 13 may rest on the bars 150 of the second frames 15, 15 'vis-à-vis.

As a variant, the inner bars 150 of the second frames 15, 15 'are opposite the partitions 135 of first frames 13 made according to the second embodiment with reference to FIGS. 2c and 4 to 7.

Whatever the embodiment of the second frames 15, 15 'with reference to FIGS. 2b, 2c, 11 to 13, complementary to the first reception frames 13, the second frames 15, in particular the second intermediate frames 15, present guides 151 for the passage of the first fluid allowing its flow in the stack of the first receiving frames 13 and the second frames 15, in particular spacers.

The guides 151 are here made in the form of through-passage orifices 151 arranged in alignment with the recesses 131 forming fluid communication with the first reception frames 13, delimited here by the succession of arches.

The through orifices 151 are thus arranged on at least one lateral edge of a second frame 15, here a second intermediate frame 15.

Of course, the number of throughthrough orifices 151 is adapted as a function of the number of recesses 131 and therefore the number of first circulation channels 7 of the heat exchange tubes 5.

The second end frame 15 ', when present, is similar to a second intermediate frame, except that the second end frame 15' does not have through-holes 151 for the passage of the first fluid.

In addition, the second frames 15, 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, 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, 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, 15 '.

In addition, in the example illustrated in Figures 1, 2c and 13, the through openings 152 are arranged on the same side of a second frame 15, 15 'in the longitudinal direction, that is to say here to left or right, complementary to the arrangement of the tubes 21 on the same side of the heat exchange bundle 3, here to the right with reference to the arrangement shown in Figure 1.

The through openings 152 define a fluid inlet 152 to the inner space of the second frame 15, 15 'on a longitudinal edge, and a fluid outlet 152 out of the second frame 15, 15' on the opposite longitudinal edge.

More specifically, according to the illustrated example, the second frames 15, 15 'have handles 153 which define the through openings 152. The handles 153 of the second frames 15, 15' are made similarly to the handles 134 of the first frames 13 and are aligned with these handles 134 which allow the passage of the second fluid through the heat exchange bundle 3. As an illustration, in the figures there are shown different embodiments of the handles 153, in particular Figures 2c and 13 , illustrate a first embodiment of the loops 153 of substantially rounded shape, while Figures 11 and 12, illustrate a second embodiment of the handles 153 whose contour is more rectilinear shape.

Of course, when the loops 134 of the first frames 13 are made according to the first embodiment, the loops 153 of the second frames 15, 15 'are made similarly according to the first embodiment.

And, when the loops 134 of the first frames 13 are made according to the second embodiment, the loops 153 of the second frames 15, 15 'are made similarly according to the second embodiment.

Of course, any other form of the handles 153 may be considered.

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

In addition, according to the embodiment illustrated in Fig. 13, the fluid inlet 152 extends over a maximum fluid inlet length L1.

This maximum fluid inlet length L1 is, according to the particular embodiment illustrated, defined by the maximum length of the loop 153, at the beginning of its formation on the second frame 15.

In addition, the inner bar 150 is arranged inside a second frame 15, 15 'so that the bar 150 is spaced a lateral distance L2, here in the width direction of the second frame 15, 15 ', a longitudinal edge of the second frame 15, 15' having the fluid inlet 152.

In particular in this example, the central bar 150 is spaced from the same lateral distance L2 of each longitudinal edge of the second frame 15, 15 '.

This lateral distance L2 is considered with respect to the part of the longitudinal edge which extends parallel to the bar 150, and not with respect to the handle 153 formed on the side of this longitudinal edge.

Advantageously, the fluid inlet length L1 is greater than or equal to the lateral distance L2, according to relation (b): (b): L1> L2 with L1 = maximum fluid inlet length and L2 = lateral distance between the bar and the longitudinal edge of the frame.

Preferably, the fluid inlet length L1 is strictly greater than the lateral distance L2 according to the relation (b '): (b'): L1> L2

In addition, the lateral distance L2 is greater than or equal to the remaining length L3 between the free longitudinal end of the inner bar 150 and the lateral edge of the second frame 15, 15 'facing the end of the inner bar 150 s extending substantially perpendicularly to the inner bar 150, that is to say the remaining length L3 without bar 150, according to the relation: (c): L2> L3 = L1 with L3 = remaining length devoid of protuberance.

Preferably, the lateral distance L2 and the remaining length L3 satisfy a strict relation (c '): (c'): L2> L3 = L - 1 By way of nonlimiting example, the lateral distance L2 is within a range of the order of 15mm to 60mm.

Furthermore, each through opening 152 defines a fluid communication connection area SI.

According to a particular embodiment, each through aperture 152 is shaped so that the fluid communication connection area SI is in a range having: an upper limit three times greater than the product of the fluid inlet length L1 with the remaining length L3, and - a lower bound corresponding to one tenth of the product of the fluid inlet length L1 with the remaining length L3.

In other words, each through aperture 152 is shaped so that the fluidic communication setting area SI satisfies the following relation (d): (d): 0.1 x L1 x L3 <S <3 X L1 X L3 with 51 = area setting in fluid communication.

Preferably, each through opening 152 is shaped so that the fluidic communication setting area SI satisfies a strict relation (d '): (d'): 0.1 X L1 X L3 <SI <3 X L1 X L3

Furthermore, as said above, the heat exchanger 1 is preferably assembled by brazing.

The second frames 15, 15 'are intended to be assembled by soldering to the first frames 13.

In particular, the longitudinal edges of the second frames 15, 15 'are intended to be assembled by soldering to the longitudinal edges of the first frames 13 and the lateral edges of the second frames 15, 15' are intended to be assembled by soldering with the feet of 133 provided on the lateral edges of the first frames 13.

For brazing, the second frames 15, 15 'respectively have at least one tank 154, better visible in Figure 14, capable of collecting the coating or "cladd" during brazing of the heat exchanger 1.

Each tank 154 is here arranged on a lateral edge of a second frame 15, 15 '. A reservoir 154 is advantageously provided on each lateral edge of a second frame 15, 15 '.

Each tank 154 is then located facing a lateral edge 13A, 13B of a first receiving frame 13 on which opens an end 50, 52 of a heat exchange tube 5. Thus, during assembly by brazing the heat exchanger 1, the coating disposed on the first frames 13 and the second frames 15, 15 'opposite, melts and migrates so as to plug the gaps between the parts of the heat exchanger 1 and comes s' flow in the tanks 154, thus preventing the coating having melted and migrated to come to block the first channels or micro-channel circulation 7 of the heat exchange tubes 5.

Advantageously, the reservoir or tanks 154 are provided on each side of a second intermediate frame arranged between two first frames 13, as can be seen more clearly in FIG.

In the optional case where a second end frame 15 'is provided as illustrated in FIG. 2c, the tank or reservoirs 154 may be arranged on a single face of this second end frame 15', namely on the face vis-à-vis a heat exchange tube 5, and not on the opposite side of the second end frame 15 ', here vis-à-vis a closure plate 17.

Each tank 154 may be made by local reduction of material of a second frame 15, 15 '.

The depth p of a tank 154 must be chosen large enough to collect the coating, which is for example of the order of 5% to 10% of the material of the second frame 15, 15 ', and small enough not to weaken the mechanical strength of the second frame 15, 15 '. By way of non-limiting example, the tank 154 may have a depth p of the order of 0.5 mm.

According to the particular example illustrated, the tank 154 is in the form of a groove 154 extending substantially perpendicular to the direction of flow of the first fluid in the heat exchange tubes 5, here in the direction of the width of a second frame 15, 15 '.

More specifically in this example, the tank 154 extends facing the entire end of a heat exchange tube 5, in other words over the entire width of a tube or of each heat exchange tube 5.

In particular, in the case where the second frames 15, 15 'are stacked with first receiving frames 13 as previously described according to the fifth embodiment, the width of the groove 154 on a second frame 15, 15' is substantially equal to the width of the recess 139 on a first frame 13.

Furthermore, the second frames 15, in particular the second intermediate frames, may also be shaped to put into fluid communication two heat exchange tubes 5 received in the same first frame 13 according to the second embodiment of the first frames 13 described in FIG. reference to FIGS. 2c and 4 to 7.

It is therefore the second frames 15 which allow circulation in at least two passes of the first fluid in each first frame 13, while ensuring good mechanical strength of the first frames 13 due to the high pressure CO2 circulating in the exchange tubes thermal 5.

More specifically, each second frame 15, in particular the spacer, advantageously has at least one overturning orifice 155 (see FIGS. 11, 13, 16) which is in fluid communication with both a first and a second fluid communication connection means. 131, here first and second recesses 131, first frames 13 on either side of the second spacer frame.

Thus, each turning orifice 155 is arranged between two adjacent heat exchange tubes 5 received in a first frame 13 and in fluid communication with these two heat exchange tubes 5.

In this way, the first fluid which opens out of a first heat exchange tube 5 undergoes a reversal in the overturning orifice 155 and then flows to a second heat exchange tube 5.

The two rows of heat exchange tubes 5 arranged in the first frames 13 then communicate at one end via the overturning orifices 155 provided on the second frames 15, in particular spacers.

Each overturning orifice 155 is here provided between through-through orifices 151 on at least one lateral edge of each second frame 15, in particular a spacer.

Each overturning orifice 155 advantageously has a longitudinal shape extending substantially perpendicular to the general direction of flow of the first fluid in the two heat exchange tubes 5.

In this example, each overturning orifice 155 has a longitudinal shape extending perpendicularly to the longitudinal edges of the second frame 15, especially intermediate.

In particular, each turning orifice 155 arranged facing a first receiving frame 13, extends longitudinally on either side of the partition wall 135 of this first receiving frame 13, as is better visible on 16. By way of example, the turning orifice 155 has a substantially oblong shape.

Furthermore, the turning orifice 155 is dimensioned so as to have a section for the overturning of the first fluid at least equal to the passage section of a heat exchange tube 5.

Furthermore, preferably, a two-pass circulation, referred to as a "U", of the first fluid in a first receiving frame 13 according to the second, third or fourth embodiment, and a two-pass circulation, is additionally provided. said "U" of the second fluid in a second frame 15, 15 'according to the second embodiment. The heat exchanger 1 is then double "U" circulation.

Closing plates

Moreover, with regard to the closure plates 17 arranged on either side of the heat exchange bundle 3, better visible in FIG. 2c, they advantageously have a shape complementary to the shape of the first frames 13 and the second frames 15, 15 '.

In particular, the lower closure plate 17 may have on its sides ears 171 of complementary shape to the shape of the handles 134 and 153, respectively of the first 13 and second 15, 15 'frames, and arranged in the alignment of the handles 134 and 153.

These ears 171 are made in one piece with the bottom closure plate 17 and do not allow to define a through hole for the passage of the second fluid.

The upper closure plate 17, 18 has in turn at least one through orifice 172, 182 arranged in communication with a pipe 21.

The passage orifices delimited by the handles 134 of the first frames 13 and the through openings 152 delimited by the handles 153 of the second frames 15, 15 'are arranged in fluid communication with the through orifices 172, 182 of the upper closure plate or plates 17, 18.

turbulators

As previously mentioned, turbulators 11 of the flow of the second fluid are advantageously arranged in the second circulation channels 9.

As illustrated in FIGS. 2a, 2c, 4, 5, 12, and 17 to 19, disturbance plates 12 may be arranged in the second frames 15, 15 '.

The perturbation plates 12 respectively have a plurality of turbulators 11, for example of substantially crenellated shape, in relief on the perturbation plate 12, forming projections in the second circulation channels 9. The slots can be made by stamping.

In the case of a circulation of the second fluid in a pass, a single disturbance plate 12 can be arranged in a second frame 15, 15 '(see Figure 2a).

The perturbation plate 12 has an edge called an input edge 120a, through which the second fluid comes into contact with the perturbation plate 12 as it circulates in the second circulation channel 9 in which the perturbation plate 12 is arranged, and an edge said output edge 120b, which is the last edge of the perturbation plate 12 with which the second fluid is in contact when leaving the second circulation channel 9.

In the particular case of a circulation in at least two passes, for example substantially in "U" of the second fluid, as illustrated in FIG. 2c, it is possible to arrange two perturbation plates 12 in a second frame 15, 15 ' .

Each of the perturbation plates 12 has an inlet edge 120a, through which the second fluid comes into contact with the perturbation plate 12 and an outlet edge 120b, which is the last edge of the disturbance plate 12 with which the second fluid is in contact when it completes a circulation pass.

In particular, a disturbance plate 12 may be arranged on each side of the bar 150 when it is provided inside the second frame 15, 15 '.

Whether it is a flow in one pass or at least two passes, the input 120a and 120b output edges of the perturbation plate 12 extend substantially parallel to the lateral edges of the second frames 15, 15 ' as shown in Figure 2c.

The input 120a and 120b output edges of the disturbance plate 12 may be substantially straight.

Advantageously, the perturbation plates 12 do not extend over the entire length of a second frame 15, 15 ', so that there are no turbulators 11 at the inlet and / or the fluid outlet, which limits the pressure drop.

In other words, at least one zone Z devoid of turbulators 11 is thus defined in the second circulation channel 9 near the inlet of the second fluid, or even close to the outlet of the second fluid.

In this example with input and / or output edges 120a, 120b substantially straight and parallel to the lateral edges of the second frames 15, 15 ', the or each Z zone without turbulators 11 is substantially rectangular. Of course, any other form can be envisaged.

According to a variant illustrated in Figures 2a, 4, 5 and 12, whether it is a one-pass circulation or at least two passes, at least one input edge 120a or 120b exit, preferably the two input and output edges 120a and 120b of each perturbation plate 12 are no longer parallel to the lateral edges of the second frame 15, 15 'receiving the disturbance plate or plates 12.

Indeed, according to this variant, the input edge (s) 120a and / or 120b of the perturbation plates 12 progress (s) in an oblique direction, for example of the order of 45 °, by relative to the lateral edges of the second frames 15, 15 '. The entry edges 120a and / or exit 120b thus form oblique edges with respect to the lateral edges of the second frame 15, 15 '.

The input and / or output edges 120a and 120b are also oblique with respect to the longitudinal edges of the second frame 15, 15 '.

In particular, the two input and output edges 120a 120b of a perturbation plate 12 extend in parallel oblique directions (see FIGS. 4, 12). In this case, the perturbation plates 12 may respectively have a generally parallelogram-like shape.

Advantageously, the oblique inlet edge 120a is oriented to release the passage for the fluid near the ear 153 defining the opening 152 for the introduction of the second fluid.

In other words, in the vicinity of the inlet for the second fluid, the second circulation channel 9 for the second fluid is free of turbulators 11. This forms in this example a substantially triangular zone Z devoid of turbulators 11. This configuration makes it possible to facilitate the filling of the second circulation channel 9.

Similarly, the oblique outlet edge 120b is oriented to release the passage for the fluid near the ear 153 defining the opening 152 for the evacuation of the second fluid. In other words, in the vicinity of the outlet for the second fluid, the second circulation channel 9 for the second fluid is free of turbulators 11. This forms in this example a substantially triangular zone Z devoid of turbulators 11. This configuration makes it easier to evacuation of the second fluid out of the second circulation channel 9.

Such oblique edges 120a, 120b thus make it possible to improve the flow of the second fluid and therefore the heat exchange performance.

In the particular case of a second frame 15, 15 'having at least one internal strip 150 for separating two circulation passes from the second fluid, the 120a and / or 120b oblique exit edge (s) ( s) progresses (nt) from the inner bar 150 to a longitudinal edge of the second frame 15, 15 ', to define the zone Z, here substantially triangular, devoid of turbulators 11 in the vicinity of the opening or through openings 152.

This particular shape makes it possible even better to limit the pressure drops and to improve the flow of the second fluid.

Alternatively, for a substantially U-shaped circulation of the second fluid, as illustrated in FIGS. 17 to 19, a perturbation plate 12 comprising at least two turbulation zones 121 may be arranged in a second frame 15, 15 ' . Only the differences with respect to the embodiments of the perturbation plate 12 previously described are detailed below.

FIG. 17 illustrates an exemplary embodiment of a perturbation plate 12 comprising at least two turbulation zones 121.

The disturbance plate 12 has a substantially "U" shape with a turbulence zone 121 on each branch of the "U". The two turbulence zones 121 are thus arranged in parallel.

Each turbulence zone 121 has tabulators 11 of the flow of the second fluid.

In this case, the perturbation plate 12 has at each turbulence zone 121 an inlet edge 120a, through which the second fluid comes into contact with the tabulation zone 121 and an exit edge 120b, which is the last edge with which the second fluid is in contact with the tab area 121 when it finishes a pass.

Preferably, the perturbation plate 12 has at each tabulation zone 121 input and output edges 120a 120b oblique with respect to the lateral edges of the second frame 15, 15 'intended to receive the perturbation plate 12. In particular, each turbulence zone 121 has a generally parallelogram-like shape.

The oblique edges 120a, 120b at the output of a tabulation zone 121 and at the inlet of another adjacent turbulation zone 121 are therefore at the level of the upturn of the second fluid and make it possible to facilitate the half-turn of the second fluid.

The disturbance plate 12 furthermore has a substantially central depression 122 between the two turbulence zones 121 extending in the direction of flow of the second fluid, in this example parallel to the longitudinal edges of the second frame 15, 15 '.

During the arrangement of the perturbation plate 12 according to this variant in the second frame 15, 15 ', the bar 150 is found arranged in this recess 122.

In addition, the perturbation plate 12 further comprises a connection zone 123 of the two turbulence zones 121.

This connection zone 123 is advantageously flat and devoid of turbulators 11. The connection zone 123 thus forms a reversal zone or for the half-turn of the second fluid. In addition, according to the illustrated example, the lateral edges delimiting this connection zone 123, which correspond to the outlet edge 120b of one of the turbulence zones 121 and to the entry edge 120a of the other turbulation zone 121, are oblique.

The longitudinal edges of this connection zone 123 extend parallel to the lateral edges of the second frame 15, 15 '. The longitudinal edges of the connecting zone 123 may be substantially straight.

FIGS. 18 and 19 illustrate another variant embodiment in which the perturbation plate 12 no longer has a "U" shape with a connection zone 123 of the two turbulence zones 121 at the level of the overturning of the second fluid, but a zone linkage 125 arranged between the two turbulence zones 121 extending substantially parallel to the flow direction of the second fluid, in this example parallel to the longitudinal edges of the second frame 15, 15 '. In this example, the connecting zone 125 is arranged in place of the recess 122 provided in the previous solution.

The connection zone 125 is then arranged facing the inner bar 150 provided on a second frame 15, 15 'as illustrated in Figures 2c and 11 to 13.

According to another variant not illustrated, the connection zone 125 provided on the perturbation plate 12 of FIGS. 18 and 19 is provided to ensure the separation of two passes for the second fluid, so that it is no longer necessary to provide the bar 150 inside the second frame 15, 15 '.

In this case, the connecting zone 125 is sufficiently high or thick to come into contact with the stage above and the stage below the second frame 15, 15 '.

Collecting box

With reference to FIGS. 1 and 20 to 22, the collecting box 19 for the first fluid and its assembly on the heat exchange bundle 3 are described in more detail.

The same manifold 19 can be compartmentalized, so as to define firstly the introduction of the first fluid schematized by the arrow Fli in Figure 1 and secondly the evacuation of the first fluid schematized by the arrow Flo on the figure 1.

According to a preferred embodiment, the heat exchanger 1 comprises an attachment flange 23 of the manifold 19 forming an interface between the manifold 19 and the heat exchange bundle 3.

Due to its interface position, the fastening flange 23 comprises fluid communication means 231, such as fluidic communication connection orifices 231, between the manifold 19 and the first circulation channels 7 defined by the exchange tubes 5, and therefore between the manifold 19 and the recesses 131 of the first frames 13 and the through holes 151 provided on the second frames 15, in particular on the second intermediate frames.

In addition, as can be seen more clearly in FIG. 22, the fastening flange 23 has: an assembled lower face, preferably by soldering, to the heat exchange bundle 3, and an upper face opposite to the lower and assembled face, preferably by brazing, to the manifold 19.

Advantageously, a form-fitting is provided between the manifold 19 and the fastening flange 23. In particular, the manifold 19 has a base 191 of complementary shape to the fastening flange 23 and it is this base 191 which is assembled on the mounting flange 23. The base 191 of the manifold box 19 more precisely has a surface, for example substantially flat, in contact with the fastening flange 23 when the heat exchanger 1 is assembled.

According to the particular embodiment illustrated in FIGS. 20 and 21, the fastening flange 23 has a substantially "C" shaped profile with: a body having on a lower surface 233 intended to be assembled, preferably by brazing, to the heat exchange bundle 3 and an upper surface 235 opposite to the lower surface 233, for example substantially flat and able to cooperate with the surface, for example substantially flat, facing the base 191 of the manifold 19, and two ends 237 substantially curved relative to the body 233, 235 of the fastening flange 23 and arranged on either side of the body 233, 235. The two ends 237 are adapted to cooperate with two side flanges 192 of the base 191 of the manifold 19 as visible in Figure 20.

The fastening flange 23, which is inside the heat exchanger 1 when assembled, advantageously has a coating, at least on its upper surface 235 opposite the manifold 19, this coating, as said previously is commonly referred to as "cladd" in the field of brazing metal parts, including aluminum.

According to the illustrated example, the fastening flange 23 also has such a coating on the inner surface of the ends 237 which come into contact with the manifold 19 for assembly.

The manifold 19 as for it does not need to present such a coating and can be made of aluminum without coating or cladd.

The manifold 19 may be mechanically assembled to the fastening flange 23, for example by crimping, prior to brazing to ensure contact between the upper surface 235 of the fastening flange 23 having the coating and the lower surface of the manifold 19 .

During brazing, this assembly is pressurized and then passed to the oven and is heated, for example to a temperature of about 580 ° C. to 590 ° C., and the coating present on the fastening flange 23 melts, thus ensuring the connection between the fastening flange 23 and the manifold 19.

Indeed, the molten coating fills the spaces or interstices present between the surfaces of the fastening flange 23 and the manifold 19. The hardening of the molten coating (by cooling) ensures a tight connection without additional supply material.

In addition, the fastening flange 23 may have such a coating on its lower surface 233 facing a first frame 13 or alternatively facing a second frame 15.

Furthermore, according to a particular non-limiting embodiment illustrated in FIGS. 20 to 22, the fastening flange 23 can be made in one piece with an end frame 25 shaped substantially similar to a second intermediate frame 15. as described above, in particular according to the second embodiment.

The fastening flange 23 then forms a lateral edge of this end frame 25 extending substantially perpendicular to the general flow direction of the first fluid in the heat exchange tubes 5 (not visible in these figures 20 to 22). .

In this example, with a single manifold 19 on one side of the heat exchanger 1, the side edge of the end frame 25 which is opposite the fastening flange 23 does not have through orifices for the passage of the first fluid.

Similarly to the fastening flange 23, the end frame 25 also advantageously has a coating called "cladd", at least on its upper face.

The end frame 25 may also have on its underside facing a first frame 13, or alternatively a second frame 15, such a coating for assembly by soldering.

In addition, as said before the heat exchange bundle 3 may comprise at least one closure plate, here upper 18. In order to allow the assembly of said at least one closure plate 18 and the manifold box 19 above of the heat exchange bundle 3, the closure plate 18 or the closure plates, has (have) an end received between the fastening flange 23 and the manifold 19, as is best seen in Figure 22.

In the example illustrated, on the lower side, that is to say on the side facing the stack of the heat exchange bundle 3, the end of the closure plate 18 is in contact with the fastening flange. 23, and here the peripheral edge of the closure plate 18 is also in contact with the end frame 25 made in one piece with the fastening flange in this example.

In a complementary manner, the manifold 19 has a recess 193 forming a receptacle for receiving the end of the closing plate (s) 18. Thus, the closure plate 18, or the closure plates, extends ( ent) along a length less than the length of the first frames 13 and the second frames 15, 15 'and possibly the length of the assembly formed by the fastening flange 23 and the end frame 25 made in one piece .

The closure plate 18 which is above the whole assembly, therefore at the top of the heat exchange bundle 3, does not have a so-called cladd coating at least on its upper face which gives on the outside of the heat exchanger 1.

This closure plate 18 at the top of the heat exchange bundle 3 can therefore be made solely of aluminum.

It is possible to provide the presence of coating only between the lower face of the closure plate 18 which is inside the heat exchange bundle 3 and the element arranged below this closure plate 18, for example here the fastening flange 23 and the possible end frame 25. The assembly of this closure plate 18 to the rest of the heat exchanger 1 is made possible due to the presence of the coating on the fastening flange 23, and optionally end frame 25, on which or on which there is a coating, so that during the passage to the oven, for example at a temperature of about 580 ° C-590 ° C, the coating melts and the connection is formed between the fastening flange 23 possibly made in one piece with the end frame 25, and both the closure plate 18 and the manifold 19.

Thus, it proves unnecessary to provide additional material or material in addition to the coating already provided on the fastening flange 23 and the possible end frame 25. This part 23, 25 may have a coating in so far as it is located inside the heat exchanger 1.

This solution therefore makes it possible to avoid using, in addition, an additional filler material, such as solder paste, in order to be able to assemble the manifold 19 on the heat exchange bundle 3. The assembly of a heat exchanger thermal 1 as defined above therefore comprises a step of arranging one or more heat exchange tubes 5 in a first frame 13 as described above.

At least two rows of heat exchange tubes 5 can be provided to allow circulation in at least two passes of the first fluid or alternatively a single row of tubes defining at least two groups of circulation channels 70, 72. a stage of the heat exchange bundle 3 for the circulation of the first fluid in the first circulation channels 7 of the heat exchange tubes 5. The assembly may comprise a stage of arrangement of turbulators 11 in a second frame 15 such that previously defined.

The second frame 15 receiving or not perturbation plates 12 for example forms another stage of the heat exchange bundle 3 for the circulation of the second fluid in the second circulation channels 9 between the heat exchange tubes 5. The assembly further comprises a step of stacking a first frame 13 and a second frame 15. This is repeated as many times as necessary depending on the available space and required performance. The stack is here substantially vertically. At the end, here at the bottom of the heat exchange bundle 3, it is possible to envisage a second end frame 15 'as described above. The assembly also comprises the arrangement of a bottom closure plate 17 at the bottom of the heat exchange bundle 3.

Of course, the order of these steps can be reversed.

For example, the lower closure plate 17 may be firstly arranged and stacked over the first 13 and second 15, 15 'frames.

Advantageously, a fixing flange 23 is provided as described above, which can be made in one piece with an end frame 25, above the stack of first frames 13 and second frames 15, 15 '. The assembly further comprises the arrangement of one or more upper closure plates 17, 18 as described above at the top of the heat exchange bundle 3, at least one closure plate being at least partially in contact on the flange. 23 and the end frame 25 if any.

At least one manifold 19 is arranged for the first fluid on the fastening flange 23.

A step of mechanical assembly, for example by crimping, of the manifold 19 on the fastening flange 23 can be provided.

And, it arranges the inlet and outlet pipes 21 for the second fluid.

Finally, the whole can be soldered.

Thus, the heat exchanger 1 comprises a stack of first frames 13 receiving one or more heat exchange tubes 5 and second frames 15 advantageously receiving tabs 11. These are simple elements and can be easily assembled by particular brazing.

In addition, the distribution of the first fluid in the heat exchange tubes 5 can be easily done through the recesses 131 and through holes 151 complementary provided on the ends of the first and second frames 13, 15 and in fluid communication with the manifold 19 .

Similarly, the handles 134 and 153, which can also be designated by complementary ears provided on the sides of the first and second frames 13, 15 can define with the inlet and outlet pipes 21 of the second fluid, two ducts. distribution of the second fluid on each side of the heat exchange bundle 3, so that the second fluid can easily flow into the heat exchange bundle 3.

In addition, the manifold 19 of the first fluid and the inlet and outlet pipes 21 of the second fluid may be arranged to allow a countercurrent flow of the two fluids.

In addition, the first fluid can circulate in at least two passes in a simple manner by shaping the first frames 13 with a 136 or more tabs 137, 138, or alternatively by providing a turning hole 155 for example oblong on the second frames 15 .

The second fluid can also flow in a simple manner in at least two passes by shaping the second frames 15, 15 'accordingly with a bar 150 or alternatively by virtue of a connecting zone 125 shaped for this purpose connecting two turbulence zones 121 a disturbance plate 12 arranged in a second frame 15, 15 '.

Finally, such a heat exchanger 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 CO2, as well as optimized heat exchange performance.

Claims (12)

1. Heat exchanger (1) between at least a first fluid and a second fluid, especially for a motor vehicle, said exchanger (1) comprising: - a heat exchange bundle (3) with a plurality of heat exchange tubes ( 5) defining first circulation channels (7) for the first fluid in the heat exchange tubes (5) and second circulation channels (9) for the second fluid between the heat exchange tubes (5), - at least one manifold (19) of the first fluid, and - at least one inlet and one outlet (21) for the second fluid, characterized in that the heat exchanger (1) comprises an alternating stack of: first receiving frames heat exchange tubes, second frames respectively defining a second circulation channel for the second fluid, the exchanger further comprising: means (131) for setting fluid communication between the manifold and the tubes s heat exchange; means (152) for setting fluid communication between the second circulation channel and the inlet and outlet pipes for the second fluid. 2. Heat exchanger (1) according to the preceding claim, wherein the first frames (13) respectively comprise side edges (13A, 13B) extending substantially perpendicular to the longitudinal direction of the first circulation channels (7) for the first fluid, and at least one of said side edges (13A, 13B) having the fluid communication means (131). 3. Heat exchanger according to one of the preceding claims, wherein the means for placing fluid communication (131) are formed as recesses (131) in one of the edges of the first frames (31), the ends of the tubes d heat exchange (5) opening into the recesses (131), the recesses being arranged in fluid communication with the manifold (19) of the first fluid. 4. Heat exchanger (1) according to the preceding claim, wherein the second frames (15, 15 ') have guides (151) for the passage of the first fluid, arranged in alignment with the recesses (131) 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, 15 '). 5. Heat exchanger (1) according to any one of the preceding claims, wherein the second frames (15, 15 ') respectively have through openings (152) in fluid communication with the inlet and outlet (21), and opening respectively on the inside of a second frame (15, 15 '). 6. Heat exchanger (1) according to the preceding claim, wherein the second frames (15, 15 ') respectively have at least two handles (153) defining the through openings (152) of fluid communication with a first handle ( 153) arranged in fluid communication with the inlet (21) and a second loop (153) arranged in fluid communication with the outlet (21). 7. heat exchanger (1) according to one of claims 4 or 5, wherein the first frames (13) have guides (134) for the passage of the second fluid arranged in alignment with the through openings (152) in fluid communication of the second frames (15, 15 '). 8. Heat exchanger (1) according to any one of the preceding claims, further comprising turbulators (11) of the flow of the second fluid arranged in the second circulation channels (9), and wherein the second frames (15). , 15 ') have a thickness (Th) substantially equal to the thickness of the turbulators (11), in the stacking direction of said frames (13, 15, 15'). 9. Heat exchanger (1) according to any one of the preceding claims, further comprising two closure plates (17, 18) on either side of the stack of first frames (13) for receiving the tubes. heat exchange (5) and second frames (15), and wherein the manifold (19) of the first fluid is arranged opposite the inlet and outlet (21) for the second fluid, on the same closure plate ( 18). 10. Heat exchanger (1) according to any one of the preceding claims, for the circulation of at least one fluid at high pressure, in particular with a pressure greater than 100 bar, for example the first fluid is a refrigerant intended to circulate at a high temperature. pressure such as CO2. 11. Heat exchanger (1) according to any one of the preceding claims, wherein the first frames (13) have a thickness substantially equal to the thickness of the heat exchange tubes (5), in the stacking direction of said frames (13, 15, 15 '). 12. Heat exchanger (1) according to any one of the preceding claims, assembled by brazing.