Heat exchanger and heat-regulating system comprising such an exchanger

Abstract

The invention relates to a heat exchanger (10) comprising a heat-exchange bundle (30) having a first zone (32) which is configured to allow heat exchange between a refrigerant at a first pressure level referred to as high pressure and the refrigerant at a second pressure level referred to as intermediate pressure and lower than the high pressure, the bundle (30) having a second zone (34) which is configured to allow heat exchange between the high-pressure refrigerant and the refrigerant at a third pressure level referred to as low pressure and lower than the intermediate pressure, the exchanger (10) being configured to allow the high-pressure refrigerant to circulate in the bundle (30) through the first zone (32) and the second zone (34).

Description

[0001] DESCRIPTION

[0002] TITLE: Heat exchanger and thermoregulation system comprising such an exchanger

[0003] The invention relates to a heat exchanger and a thermoregulation system comprising such an exchanger. It will find its applications, in particular, in the field of motor vehicles.

[0004] In this field, it has long been known to use a refrigerant circuit for air conditioning a vehicle passenger compartment, operating in air conditioning mode. More recently, with the development of hybrid or electric engines, it has also been proposed to extend the use of such circuits for heating the passenger compartment, operating in heat pump mode. It has also been proposed to use them for thermal regulation of electrical energy storage devices such as batteries supplying power to the motors used to move the vehicle. Said circuits include compressors whose displacement and speed condition the energy consumed to operate in the desired mode.

[0005] The energy required is likely to be particularly high in certain operating modes. To limit such energy consumption and / or avoid using compressors that are too large, it has already been considered to use refrigerant circuits in which the compressor(s) are supplied at the inlet with refrigerant at two pressure levels, with one portion of the refrigerant introduced into the compressor being at low pressure and the other portion at an intermediate pressure.

[0006] To improve the efficiency of the circuit, it has further been proposed to provide the circuit with a first heat exchanger to carry out a heat exchange between the high-pressure refrigerant and the intermediate-pressure refrigerant and a second heat exchanger to carry out a heat exchange between the high-pressure refrigerant and the intermediate-pressure refrigerant.

[0007] A disadvantage of such circuits is that it multiplies the number of exchangers to be used.The invention aims to at least partially overcome the above drawbacks and to this end proposes a heat exchanger comprising a heat exchange bundle having a first zone configured to allow heat exchange between a refrigerant, at a first pressure level, called high pressure, and said refrigerant, at a second pressure level, called intermediate pressure, lower than the high pressure, said bundle having a second zone configured to allow heat exchange between said high pressure refrigerant and said refrigerant at a third pressure level, called low pressure, lower than the intermediate pressure, said exchanger being configured to allow circulation, in particular in series, of said high pressure refrigerant in said bundle through the first zone and the second zone.

[0008] Thanks to the integrated circulation of the refrigerant at its different pressure levels and more particularly to the passage from one zone to another of the high-pressure refrigerant in said heat exchange bundle, the invention makes it possible to simultaneously carry out the desired heat exchange functions, this in a single exchanger.

[0009] According to various additional characteristics of the invention, which may be taken together or separately and which form as many embodiments of the invention:

[0010] - - said exchanger further comprises an inlet flange for said high pressure refrigerant, in communication with said first zone of the bundle and an outlet flange for said high pressure refrigerant, in communication with said second zone of the bundle,

[0011] - said exchanger further comprises an inlet flange and an outlet flange for said intermediate pressure refrigerant, in communication with said first zone of the bundle,

[0012] - said exchanger further comprises an inlet flange and an outlet flange for said low pressure refrigerant, in communication with said second zone of the bundle, - said bundle comprises a housing and one or more tubes, passing through said housing, said tubes being configured to be traversed by said high pressure refrigerant,

[0013] - said housing comprises a first compartment, configured for circulation of the refrigerant at intermediate pressure, and a second compartment, configured for circulation of the refrigerant at low pressure,

[0014] - said compartments are respectively crossed by a first longitudinal part of said tube(s) and a second longitudinal part of said tube(s),

[0015] - said first zone of the bundle is formed by the first compartment and the first longitudinal part of the tube(s) and said second zone of the bundle is formed by the second compartment and the second longitudinal part of the tube(s),

[0016] - said housing comprises a partition separating said first and second compartments,

[0017] - said partition is crossed by said tube(s),

[0018] - said beam comprises a stack of plates, in one direction, called the stacking direction,

[0019] - said stack of plates defines on either side of the same of said plates, a circulation channel for the high pressure refrigerant, on one side of said plate and, on the other side of said plate, a circulation channel for the intermediate pressure refrigerant, opposite a first part of said plate, and a circulation channel for the low pressure refrigerant, opposite a second part of said plate,

[0020] - said stack of plates has first partitions separating the circulation channel for the intermediate pressure refrigerant fluid and the circulation channel for the low pressure refrigerant fluid,

[0021] - said first partitions are formed by first stampings of certain of said plates, called first plates,

[0022] - said stack of plates has second partitions separating each of the high-pressure refrigerant channels into a first and a second part, connected by a circulation passage for said high-pressure refrigerant, the first and second parts of said high-pressure refrigerant channels being located opposite the first and second parts of the plates of said stack of plates,

[0023] - said passage is positioned so as to cause a change in direction of the high pressure refrigerant between the first and second parts of circulation channels of said high pressure refrigerant,

[0024] - said second partitions are formed by second stampings of the other of said plates, called second plates,

[0025] - said stack of plates has contact zones between neighboring plates,

[0026] - a surface density of said contact zones is greater at the level of the low pressure refrigerant circulation channels than at the level of said intermediate pressure refrigerant circulation channels.

[0027] The invention also relates to a thermoregulation system comprising a refrigerant circuit configured to carry out a thermodynamic cycle, said circuit comprising an exchanger as described above.

[0028] According to various additional characteristics of this aspect of the invention, which may be taken together or separately and which form as many embodiments of the invention:

[0029] - said circuit is configured for circulation of said refrigerant at high pressure, intermediate pressure and low pressure respectively in a first part, called high pressure, a second part, called intermediate pressure and a third part, called low pressure, of said circuit,

[0030] - said circuit comprises a compression system provided with a first inlet of said system, connected to the low pressure part of the circuit,

[0031] - said compression system has a second inlet, connected to said intermediate pressure part of the circuit, - said compression system comprises two compression stages respectively connected to the first inlet and to the second inlet of said system,

[0032] - said circuit comprises a main loop comprising at least, according to the direction of flow of the refrigerant, a low pressure pass of said exchanger and said first inlet of the compression system,

[0033] - said circuit comprises a bypass branch comprising at least, according to the direction of circulation of the refrigerant, an intermediate pressure pass of said exchanger and the second inlet of the compression system,

[0034] - the high pressure part of the circuit is located along the main loop between an outlet of said compressor and a first regulator as well as along the bypass branch between a bypass point, located on the main loop, and a second regulator,

[0035] - the intermediate pressure part of the circuit is located between the second regulator and the second compressor inlet,

[0036] - the low pressure part of the circuit extends between the first regulator and the first compressor inlet,

[0037] - the first zone of said exchanger is integrated into the high pressure part and the intermediate pressure part of said circuit and the second zone of said exchanger is integrated into the high pressure part and the low pressure part of said circuit,

[0038] - said second zone of said exchanger is located downstream of said first zone of said exchanger according to the direction of circulation of said refrigerant in the high pressure part of said circuit.

[0039] The invention will be better understood, and other aims, details, characteristics and advantages thereof will appear more clearly during the detailed explanatory description which follows, of at least one embodiment of the invention given by way of purely illustrative and non-limiting example, with reference to the appended schematic drawings among which:

[0040] [Fig 1] schematically illustrates an exemplary embodiment of the thermoregulation system according to the invention; [Fig 2] schematically illustrates an alternative embodiment of a part marked II in figure 1;

[0041] [Fig 3] schematically illustrates a circulation of a refrigerant fluid in a heat exchanger according to the invention;

[0042] [Fig 4] schematically illustrates in cross-sectional view, a first example of embodiment of the heat exchanger according to the invention;

[0043] [Fig 5] schematically illustrates, in longitudinal section view, the heat exchanger of the previous figure;

[0044] [Fig 6] schematically illustrates, in perspective and in exploded view, plates of a stack of plates of a second exemplary embodiment of the heat exchanger according to the invention;

[0045] [Fig 7] schematically illustrates, in perspective, an alternative embodiment, in accordance with the invention, of one of the plates of the stack of plates in the previous figure.

[0046] It should first be noted that the terms upstream and downstream used in the following description refer to the direction of circulation of the fluid in question. Furthermore, the terms "first", "second", "third", etc. are only used to distinguish the components concerned from each other and do not indicate an order or a possible importance of said components.

[0047] As illustrated in Figure 1, the invention relates to a thermoregulation system. It comprises a refrigerant circuit 1. Said refrigerant is, for example, a subcritical fluid, such as those known as R134a, R1234yf or R290 (Propane). Alternatively, it is a supercritical fluid such as CO2 or R744. Said thermoregulation device is intended, in particular, for motor vehicles.

[0048] Said circuit is configured to carry out a thermodynamic cycle, in particular with a compression phase, a first heat exchange phase, an expansion phase and a second heat exchange phase.

[0049] For this, said circuit preferably comprises a compression system, formed here by a compressor 2 with two inlets, at least one expansion member, here two expansion members 4, 6, and / or heat exchangers, here three heat exchangers, 8, 10, 12. A first 8 of said exchangers is intended to exchange heat with a heat transfer fluid, for example a first air flow, called external, illustrated by the arrow marked 14. Said first heat exchanger 8 is intended to be located, in particular, at the level of a front face of the vehicle to be crossed by said external air flow 14, said external air flow 14 having previously crossed a grille of the vehicle. Said first exchanger 8 is formed, for example, of a condenser.

[0050] A second of said exchangers 10 is said to be internal and will be described in more detail below. It is configured to allow heat exchange between the refrigerant and itself, the refrigerant passing through said second exchanger 10 at different times, according to respective passes, while it is at different pressure levels in each pass.

[0051] A third of said heat exchangers 12 is intended to exchange heat, for example, with a second air flow, illustrated by the arrow marked 16, intended to supply a passenger compartment of the vehicle. Said third exchanger 12 is intended to be located, in particular, at the level of a heating, ventilation and / or air conditioning unit, located under a dashboard of the vehicle. Said third exchanger is formed, for example, of an evaporator.

[0052] Alternatively, the heat transfer fluid with which the refrigerant exchanges heat at the first and / or third exchangers 8, 12 is a liquid such as a mixture of water and / or glycol. Preferably, the heat transfer fluid then exchanges in turn, in particular, with the first and / or second air flow, for example at respective additional heat exchangers. In this variant, the first exchanger 8 is, for example, a water condenser and the third exchanger is, for example, a cooler. Such a variant is used in particular if the refrigerant is R290 in order to have an indirect exchange between the refrigerant and the air flow(s).

[0053] Said circuit 1 is configured so that the refrigerant follows a loop, called the main loop, passing in series through the compressor 2, the first exchanger 8, the internal exchanger 10, in a first passage, a first 4 of said expansion valves, the third exchanger 12 and the internal exchanger 10, in a second passage, before returning to the compressor 2, at a first inlet 18 of said compressor 2. Said circuit 1 further comprises a bypass branch between a bypass point 20 and a second inlet 22 of the compressor 2. Said bypass point 20 is located along the main loop downstream of the first exchanger 8 and upstream of the first passage of the second exchanger 10.Said circuit 1 is configured so that the refrigerant follows said bypass branch from said bypass point 20 by passing in series through a second 6 of the expansion valves and said internal exchanger 10, according to a third passage, before reaching the second inlet 22 of said compressor.

[0054] Said circuit 1 is here configured for circulation of said refrigerant at high pressure, intermediate pressure and low pressure respectively in a first part, called high pressure, a second part, called intermediate pressure and a third part, called low pressure, of said circuit. Said high pressure part is located along the main loop between an outlet 24 of said compressor 2 and the first expander 4. It also extends along the bypass branch from the bypass point 20 to the second expander 6. The intermediate pressure part is located along the remainder of said bypass branch, that is to say, between the second expander 6 and the second inlet 22 of the compressor 2. The low pressure part extends along the remainder of the main loop, that is to say, between the first expander 4 and the first inlet 18 of the compressor 2.

[0055] Said circuit 1 makes it possible to cool the internal air flow 16 using frigories drawn from the external air flow 14 and the energy supplied by the compressor 2. The bypass branch supplying the compressor with the refrigerant at intermediate pressure makes it possible to limit the energy to be supplied to the compressor, at constant efficiency. The same is true of the second exchanger 10 thanks to the heat exchanges carried out between the refrigerant and itself, at different pressure levels, which make it possible to obtain sub-cooling and / or superheating effects of the refrigerant without having to oversize the other exchangers.

[0056] As illustrated in Figure 2, alternatively, the compression system comprises two compressors 2', 2” each forming a compression stage. An inlet 18' of a first 2' of said compressors is connected to the low pressure part of the circuit, downstream of the third exchanger. An outlet 24' of a second 2” of said compressors is connected to the high pressure part of the circuit upstream of said first exchanger. The first and second compressors 2', 2” are connected to each other by placing an outlet 26 of the first compressor 2' and an inlet 28 of said second compressor 2” in communication. The bypass branch opens downstream of the third pass of said second exchanger 10 at a collection point 22' of the circuit, located between the outlet 26 of the first compressor 2' and the inlet 28 of said second compressor 2”. Such an alternative allows the use of compressors with a single inlet and reduced displacement.

[0057] As is more clearly seen in Figures 3 and following, the invention also relates to the second exchanger or internal exchanger 10 itself.

[0058] It comprises a heat exchange bundle 30 having a first zone 32, configured to allow heat exchange between the high-pressure refrigerant and said intermediate-pressure refrigerant, and a second zone 34, configured to allow heat exchange between said high-pressure refrigerant and said low-pressure refrigerant. Said exchanger 10 is configured to allow circulation of said high-pressure refrigerant in said bundle 30 through the first zone 32 and the second zone 34, according to the arrow marked HP. The circulation of said high-pressure refrigerant in said bundle 30 takes place here in series between the first zone 32 and the second zone 34. In the first zone 32, said exchanger 10 is configured to allow circulation of said refrigerant in said intermediate-pressure bundle 30, according to the arrow marked IP.In the second zone 34, said exchanger 10 is configured to allow circulation of said refrigerant fluid in said bundle 30 at low pressure, according to the arrow marked BP.

[0059] By providing a heat exchange bundle allowing such integrated circulation of the refrigerant at its different pressure levels, in particular of the high-pressure refrigerant, the heat exchanger according to the invention allows both the exchange of heat between, on the one hand, the high-pressure refrigerant and the intermediate-pressure refrigerant, and, on the other hand, between the high-pressure refrigerant and the low-pressure refrigerant, this in a single component.

[0060] Said exchanger 10 further comprises an inlet flange 36 for said high-pressure refrigerant, in communication with said first zone 32 of the bundle and an outlet flange 38 for said high-pressure refrigerant, in communication with said second zone 34 of the bundle. It also comprises an inlet flange 40 and an outlet flange 42 for said intermediate-pressure refrigerant, in communication with said first zone 32 of the bundle. It further comprises an inlet flange 44 and an outlet flange 48 for said low-pressure refrigerant, in communication with said second zone 34 of the bundle.

[0061] As illustrated in Figure 4, according to a first embodiment, said bundle 30 comprises a housing 50 and one or more tubes 52, here a single tube 52, passing through said housing 50.

[0062] Said tubes 52 are configured to be traversed by said high-pressure refrigerant fluid. They are, for example, of circular section.

[0063] As illustrated in Figure 5, said housing 50 comprises a first compartment 54, configured for circulation of the refrigerant at intermediate pressure, and a second compartment 56, configured for circulation of the refrigerant at low pressure. Said compartments 54, 56 are respectively crossed by a first part 58 and a second part 60 of longitudinal extension of said tube 52.

[0064] Said first zone 32 of the bundle is formed by the first compartment 54 and the first longitudinal extension part 58 of the tube 52. Said second zone 34 of the bundle is formed by the second compartment 56 and the second longitudinal extension part 60 of said tube 52.

[0065] Said housing 50 here comprises a partition 64 separating said first and second compartments 58, 63. Said partition 64 is crossed by the tube 52. Said partition 64 has an annular configuration. It is pierced with an orifice 66 for the passage of said tube 52.

[0066] It should be noted that the pressure resistance conditions are more severe for the tube 2 in the second compartment 56 than in the first compartment 54 due to the greater pressure differential between the high-pressure refrigerant and the low-pressure refrigerant than between the high-pressure refrigerant and the intermediate-pressure refrigerant. A material thickness of said tube is, however, advantageously constant along the entire length of the tube while being configured to withstand the conditions imposed by the greater pressure differential. As illustrated in FIG. 6, according to a second embodiment, said bundle 30 comprises a stack of plates 70, 70' in a direction, called the stacking direction 72.

[0067] Said plates have, for example, a substantially rectangular shape. They comprise raised edges 71 in order to define a circulation basin for the refrigerant fluid, the raised shape of the edges 71 not being illustrated in the drawings. In the stack, the plates 70, 70' are connected to the neighboring plates by their raised edges 71 in order to define between them passages for the refrigerant fluid according to the different passes associated with each pressure level of said refrigerant fluid. Said plates are formed, in particular, by stamping.

[0068] Preferably, said stack of plates 70, 70' defines on either side of the same one of said plates, a circulation channel 74 for the high-pressure refrigerant, on one side of said plate and, on the other side of said plate, a circulation channel 76 for the intermediate-pressure refrigerant, opposite a first part 78 of said plate, and a circulation channel 77 for the low-pressure refrigerant, opposite a second part 82 of said plate.

[0069] Said stack of plates further has first partitions 84 separating the circulation channel 76 for the intermediate pressure refrigerant and the circulation channel 77 for the low pressure refrigerant. Said first partitions 84 are advantageously formed by first stampings of certain 70 of said plates, called first plates. Here, they separate the first plates 70 into two zones of substantially identical surfaces. They are oriented parallel to opposite sides of said plates 70, in particular their short side.

[0070] Said first plates 70 have at their first part 78 an inlet orifice 76a and an outlet orifice 76b for said intermediate pressure refrigerant. Said inlet orifices 76a and outlet orifices 76b for said intermediate pressure refrigerant are here diagonally opposite in order to maximize the path of the fluid in said circulation channel 76 for the intermediate pressure refrigerant. Said first plates 70 also have at their second part 78 an inlet orifice 80a and an outlet orifice 80b for said low pressure refrigerant. Said inlet orifices 80a and outlet orifices 80b for said low pressure refrigerant are here diagonally opposite in order to maximize the path of the fluid in said circulation channel 77 for the low pressure refrigerant.

[0071] The other plates 70' of said stack of plates, called second plates, have an inlet orifice 74a and an outlet orifice 74b for said high-pressure refrigerant. Said inlet orifices 74a and outlet orifices 74b for said high-pressure refrigerant are here diagonally opposite in order to maximize the path of the fluid in said circulation channel 74 for the high-pressure refrigerant.

[0072] Said first plates 70 are further provided with first and second orifices 74c, 74d for the passage of the high-pressure refrigerant fluid so that it can be distributed over the entire height of the stack in the corresponding circulation channels 74. Said inlet orifices 74a, formed in the second plates 70', and said first passage orifices 74c for the high-pressure refrigerant fluid, formed in the first plates 70, alternate with each other along the stacking direction 72. Said outlet orifices 74b, formed in the second plates 70', and said second passage orifices 74d for the high-pressure refrigerant fluid, formed in the first plates 70, alternate with each other along the stacking direction 72.Said passage orifices 74c, 74d for the high-pressure refrigerant fluid are illustrated in dotted lines and formed, for example, at the level of stampings in order to put said channels 74 for circulation of the high-pressure refrigerant fluid into communication with each other.

[0073] Said second plates 70' are further provided with third, fourth, fifth and sixth orifices 76c, 76d and 80c, 80d for the passage of the intermediate and low pressure refrigerant fluid so that it can be distributed over the entire height of the stack in the corresponding circulation channels 76, 77. Said inlet orifices 76a for the intermediate pressure refrigerant fluid, formed in the first plates 70, and said third passage orifices 76c for the intermediate pressure refrigerant fluid, formed in the second plates 70', alternate with each other along the stacking direction 72. The same is true for the inlet orifices 80a for the low pressure refrigerant fluid and said fifth passage orifices 80c for said low pressure fluid.Said outlet ports 76b for the intermediate pressure fluid, formed in the first plates 70, and said fourth passage ports 76d for the intermediate pressure refrigerant, formed in the second plates 70', alternate with each other along the stacking direction 72. The same is true for the outlet ports 80b for the low pressure refrigerant and said sixth passage ports 80d for said low pressure fluid. Said third, fourth, fifth and sixth passage ports 76c, 76d and 80c, 80d for the passage of the intermediate pressure and low pressure refrigerant are illustrated in dotted lines and formed, for example, at the level of stampings in order to respectively put into communication said channels 76 for circulation of the intermediate pressure refrigerant and said channels 77 for circulation of the low pressure refrigerant.

[0074] As illustrated in Figure 7, according to a variant of this second embodiment, said stack of plates has second partitions 86 separating each of the high-pressure refrigerant channels 74 into a first and a second part 88, 90, connected by a passage 92 for circulation of said high-pressure refrigerant. Said passage 92 formed in the second partitions 86 is positioned so as to cause a change in direction of the high-pressure refrigerant between the first and second parts 88, 90 of the high-pressure refrigerant circulation channels 74.

[0075] The first and second parts 88, 90 of said high-pressure refrigerant channels 74 are respectively located opposite the first part 78 and the second part 82 of the first plates 70. A position of the orifices 76c, 76d and 80c, 80d for the passage of the refrigerant at intermediate pressure and low pressure in said second plates 70' is adapted with respect to the variant of FIG. 6, if applicable. Said second partitions 86 are formed, for example, by second stampings of the second plates 70'.

[0076] Although this is not shown, in said second embodiment illustrated in Figures 6 and 7, said stack of plates has contact zones between neighboring plates along said channels 74, 76, 77 for circulation of the refrigerant fluid, additional to those formed by the raised edges 71, the stampings of the passage orifices 74c, 74d, 76a, 76b, 80a, 80b, the first or second stampings 84, 86. These are, for example, third stampings and / or internal spacers. They make it possible to reinforce the resistance to internal pressure in the channels 74, 76, 77. Advantageously, a surface density of said contact zones is greater at the level of the channels 77 for circulation of the low pressure refrigerant fluid than at the level of said channels 76 for circulation of the intermediate pressure refrigerant fluid.As already mentioned above in the context of the first embodiment, this makes it possible to take into account the greater pressure differential between the high-pressure refrigerant and the low-pressure refrigerant than between the high-pressure refrigerant and the intermediate-pressure refrigerant.

[0077] If we return to circuit 1 of figure 1, as will have been understood, the first zone 32 of said exchanger is integrated into the high pressure part and the intermediate pressure part of said circuit 1 and the second zone 34 of said exchanger is integrated into the high pressure part and the low pressure part of said circuit 1.

[0078] Said second zone 34 of said exchanger 1 is located here downstream of said first zone 32 of said exchanger according to the direction of circulation of said refrigerant in the high pressure part of said circuit. Although this is not illustrated, said refrigerant circuit 1 is configured, as a variant, to alternately allow the circulation of the fluid in different other branches. It can thus be used in other operating modes.

Claims

CLAIMS 1. Heat exchanger (10) comprising a heat exchange bundle (30) having a first zone (32) configured to allow heat exchange between a refrigerant, at a first pressure level, called high pressure, and said refrigerant, at a second pressure level, called intermediate pressure, lower than the high pressure, said bundle (30) having a second zone (34) configured to allow heat exchange between said high pressure refrigerant and said refrigerant at a third pressure level, called low pressure, lower than the intermediate pressure, said exchanger (10) being configured to allow circulation of said high pressure refrigerant in said bundle (30) through the first zone (32) and the second zone (34).

2. Heat exchanger (10) according to the preceding claim further comprising an inlet flange (36) for said high pressure refrigerant, in communication with said first zone (32) of the bundle (30) and an outlet flange (38) for said high pressure refrigerant, in communication with said second zone (34) of the bundle (30), an inlet flange (40) and an outlet flange (42) for said intermediate pressure refrigerant, in communication with said first zone (32) of the bundle (30) and / or an inlet flange (44) and an outlet flange (48) for said low pressure refrigerant, in communication with said second zone (34) of the bundle (30).

3. Heat exchanger (10) according to any one of the preceding claims wherein said bundle (30) comprises a housing (50) and one or more tubes (52), passing through said housing (50), said tubes (52) being configured to be traversed by said high pressure refrigerant fluid.

4. Heat exchanger (10) according to the preceding claim wherein said housing (50) comprises a first compartment (54), configured for circulation of the refrigerant at intermediate pressure, and a second compartment (56), configured for circulation of the refrigerant at low pressure, said housing (50) comprising a partition (64) separating said first and second compartments (54, 56), said partition (64) being crossed by said tube(s) (52).

5. Heat exchanger (10) according to any one of claims 1 or 2 wherein said bundle (30) comprises a stack of plates (70, 70'), in a direction (72), called the stacking direction.

6. Heat exchanger (10) according to the preceding claim wherein said stack of plates defines on either side of the same one of said plates (70, 70'), a circulation channel (74) for the high pressure refrigerant, on one side of said plate and, on the other side of said plate, a circulation channel (76) for the intermediate pressure refrigerant, opposite a first part (78) of said plate, and a circulation channel (77) for the low pressure refrigerant, opposite a second part (82) of said plate (70, 70').

7. Heat exchanger (10) according to the preceding claim, said stack of plates (70, 70') has first partitions (84) separating the circulation channel (76) for the intermediate pressure refrigerant and the circulation channel (77) for the low pressure refrigerant.

8. Heat exchanger (10) according to any one of claims 6 or 7 wherein said stack of plates has contact zones between neighboring plates (70, 70'), a surface density of said contact zones being greater at the level of the circulation channels (77) of the low pressure refrigerant than at the level of said circulation channels (76) of the intermediate pressure refrigerant.

9. Thermoregulation system comprising a refrigerant circuit (1) configured to perform a thermodynamic cycle, said circuit comprising an exchanger (10) according to any one of the preceding claims.

10. System according to the preceding claim in which said second zone (34) of said exchanger (10) is located downstream of said first zone (32) of said exchanger (10) according to a direction of circulation of said refrigerant fluid in a high pressure part of said circuit (1).

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