HEAT EXCHANGER FOR REFRIGERANT LOOP

TECHNICAL FIELD

The invention relates to the field of refrigerant loops that are intended for the circulation of a refrigerant and are applied to a heating, ventilation and/or air-conditioning installation for a motor vehicle, and more particularly concerns a heat exchanger which is arranged in the front face of the vehicle and forms part of such refrigerant loops.

BACKGROUND OF THE INVENTION

An electric or hybrid vehicle has a refrigerant loop in order to vary the temperature in the vehicle interior, and notably to heat the latter through the winter and cool it through the summer. The temperature in the vehicle interior is notably modified by means of the refrigerant circulating in the refrigerant loop, the refrigerant travelling through a heating, ventilation and/or air-conditioning installation in order to exchange heat with a stream of air intended to be sent to the vehicle interior. In order for the heating, ventilation and/or air-conditioning installation to work properly, the refrigerant loop also comprises a heat exchanger in contact with the ambient air, in the front face of the vehicle. Thus, the refrigerant circulating in the refrigerant loop absorbs or gives up heat energy in the heat exchanger depending on the cooling or heating requirements of the vehicle interior.

The heat exchanger in the front face of the vehicle allows the exchange of heat energy between the refrigerant, which circulates in the tubes disposed one above another and spaced apart from one another by fins, and a stream of air which comes from outside the vehicle and passes through said heat exchanger between the tubes at the fins.

In electric or hybrid vehicles, it is known to configure the refrigerant loop and the heat exchanger in the front face so as to form a reversible heat pump within which the heat exchanger is able to operate in condenser mode, in summer, to ensure the cooling of the vehicle interior via the heat exchange device forming an evaporator in the heating, ventilation and/or air-conditioning installation, and to operate in evaporator mode, in winter, to ensure the heating in the vehicle interior via the heat exchange device forming a condenser.

One problem with such a heat exchanger positioned in the front face of the vehicle then resides in its operation in evaporator mode, when the temperature difference tends to heat the stream of humid air and create droplets of condensation which are deposited on the surface of the heat exchanger. If the temperature of the refrigerant circulating in the tubes is too low, and the fins between the tubes are too cold owing to thermal conduction, the cooling of the droplets of condensation can cause the local formation of frost on the fins between the tubes of the heat exchanger. Such a presence of frost generates obstacles to the passage of air through the heat exchanger and thus tends to reduce the thermal capacity of the heat exchanger.

SUMMARY OF THE INVENTION

The present invention makes it possible to bypass such a problem by proposing a heat exchanger for a refrigerant loop, comprising a heat exchange surface with a plurality of tubes extending from one longitudinal end of the heat exchange surface to the other, each of the tubes being configured to form part of at least a first refrigerant circuit or a second refrigerant circuit through which one and the same refrigerant flows, characterized in that at least two refrigerant manifolds are disposed at each of the longitudinal ends of the heat exchange surface such that two of these refrigerant manifolds are connected to the first refrigerant circuit and two other ones of these refrigerant manifolds are connected to the second refrigerant circuit.

By virtue of the presence of multiple refrigerant manifolds, it is then possible to position various refrigerant circuits within the heat exchange surface, and it is then possible to form refrigerant inlets and outlets in diverse zones of the heat exchange surface, if appropriate by providing a circulation of a portion of the refrigerant in a tube which is in an opposite direction to the direction of circulation of another portion of the same refrigerant in an adjacent tube. Since the temperature of the refrigerant is intended to change between the inlet and the outlet in the exchange surface, owing to the refrigerant exchanging heat energy with a stream of air passing through the heat exchanger, such a feature makes it possible to avoid the creation of cold zones at a location of the heat exchange surface, and thus avoid the appearance of frost following the formation of droplets as the stream of air condenses.

The heat exchanger can, for example, be installed in a front face of the vehicle so that the heat exchange surface is installed across the stream of air in order to promote the exchange of heat. The heat exchange surface is formed by the tubes making up the heat exchanger, which extend along a main elongation dimension from one longitudinal end to the other of the heat exchange surface and within which the refrigerant circulates.

The tubes can notably be stacked one on another so as to form a single row of tubes stacked along a stacking direction perpendicular to the main elongation dimension of said tubes. The tubes are stacked such that a passage for air is formed, so that a stream of air can pass through the heat exchange surface.

The main elongation direction of the tubes and their stacking direction define a plane of extent of the heat exchange surface, a main direction of the stream of air being perpendicular to said plane of extent.

The tubes are stacked in a single row of tubes, leaving a space between each tube to allow the stream of air traversing the heat exchanger to pass. In other words, all of the tubes are aligned along the same row of tubes, thus limiting the mechanical bulk of the heat exchange surface. The manifolds are arranged at the longitudinal ends of the heat exchange surface, that is to say on either side of the ends of the tubes along their main elongation direction.

The first refrigerant circuit and the second refrigerant circuit form part of the refrigerant loop. The tubes of the heat exchanger each form part of one of the refrigerant circuits. Within the heat exchanger, the refrigerant loop is divided into multiple refrigerant circuits, which are respectively formed by manifolds and some of the plurality of tubes of the heat exchanger. More particularly, a refrigerant circuit comprises two refrigerant manifolds respectively intended to distribute, in the tubes of the exchange surface, that portion of the stream of refrigerant that is associated with this circuit and to collect this same portion of the stream of refrigerant that has circulated in these tubes. The heat exchanger according to the invention comprises as many pairs of refrigerant manifolds as refrigerant circuits formed within the heat exchanger.

According to one feature of the invention, the tubes can be connected to each of the pairs of connectors, i.e. an inlet connector and an associated outlet connector, so as to form, in the row of tubes, an alternating sequence of separate tubes associated with the first refrigerant circuit that are interposed between tubes associated with the second refrigerant circuit.

According to one feature of the invention, the same number of refrigerant manifolds is disposed at each of the longitudinal ends of the heat exchange surface.

According to one feature of the invention, each refrigerant circuit comprises a refrigerant inlet manifold communicating with at least one tube of the heat exchange surface and a refrigerant outlet manifold communicating with the at least one tube of the heat exchange surface, wherein the refrigerant inlet manifolds of each refrigerant circuit are configured for connection to one and the same refrigerant inflow, and the refrigerant outlet manifolds of each refrigerant circuit are configured for connection to one and the same refrigerant outflow. The refrigerant inlet manifolds and the refrigerant outlet manifolds are structurally identical, with only the circulation of fluid enabling a distinction to be made between the two types of refrigerant manifolds. In other words, for any of the refrigerant circuits, the refrigerant circulates first of all within a fluid inlet manifold, then within one or more tubes communicating with said refrigerant inlet manifold, and subsequently flows within a refrigerant outlet manifold communicating with said one or more tubes.

The inflow of refrigerant can, for example, correspond to a branch of the refrigerant loop which is divided into the plurality of refrigerant circuits before entering the heat exchanger. At the outlet of the heat exchanger, the refrigerant circuits meet at a convergence point corresponding to the refrigerant outflow.

According to one feature of the invention, each of the refrigerant inlet manifolds is arranged at a first longitudinal end of the heat exchange surface, each of the refrigerant outlet manifolds being arranged at a second longitudinal end of the heat exchange surface. In other words, the refrigerant circulates within all the tubes of the heat exchange surface in one and the same direction of circulation.

According to one feature of the invention, each longitudinal end of the heat exchange surface comprises at least one refrigerant inlet manifold and at least one refrigerant outlet manifold. Such a configuration makes it possible to implement alternating circulation of the refrigerant, with one portion of the stream of refrigerant circulating from a first longitudinal end to the opposite second end and another portion of the stream of refrigerant circulating from the second longitudinal end to the first longitudinal end.

According to one feature of the invention, the refrigerant inlet manifolds have one and the same passage cross section and/or the refrigerant outlet manifolds have one and the same passage cross section. An identically or substantially identically dimensioned passage cross section makes it possible to streamline the circulation of the refrigerant in each of the refrigerant circuits.

According to one feature of the invention, the refrigerant manifolds arranged at one and the same longitudinal end are aligned relative to one another along a direction parallel to the main elongation dimension of the tubes.

Here and in the rest of the description, it should be understood that the alignment of the manifolds is to be considered with respect to a center of gravity of each of the manifolds in a sectional plane intersecting each of the manifolds in question.

According to another feature of the invention, the refrigerant manifolds arranged at one and the same longitudinal end are aligned relative to one another along a direction perpendicular to the main elongation dimension of the tubes.

According to an alternative feature of the invention, the refrigerant manifolds disposed at one and the same longitudinal end are disposed concentrically with one another.

The alignment of the refrigerant manifolds can differ depending on the space available at the heat exchanger. The fluidic connections to the tubes can differ depending on said alignment of the fluid manifolds. When the refrigerant manifolds are concentric, this means that at least one refrigerant manifold is disposed within the passage cross section of another refrigerant manifold arranged at the same longitudinal end of the heat exchange surface.

According to one feature of the invention, the refrigerant manifolds have a cylindrical shape, the refrigerant manifolds disposed at one and the same longitudinal end being mutually arranged with a smaller bulk owing to the complementing respective shapes of the manifolds. The cross sections of the cylindrical shapes can vary, for example be circular, semicircular or polygonal. In order to limit the mechanical bulk of the refrigerant manifolds arranged at one and the same longitudinal end of the heat exchange surface, the refrigerant manifolds can have an identical cylindrical cross section and be arranged head-to-tail relative to one another. The complementing cylindrical shapes thus promote the reduction in mechanical bulk of the heat exchanger.

BRIEF DESCRIPTION OF DRAWINGS

Other features and advantages of the invention will become more clearly apparent both from the following description and from multiple exemplary embodiments, which are given by way of non-limiting indication with reference to the attached schematic drawings, in which:

FIG. 1 is an overall view of a heat exchanger according to a first embodiment of the invention,

FIG. 2 shows the heat exchanger according to the invention, within which a refrigerant circulates in alternating circulation,

FIG. 3 shows the heat exchanger according to the invention, within which the refrigerant circulates in concurrent circulation,

FIG. 4 schematically shows a heat exchanger according to a second embodiment of the invention, in which a plurality of refrigerant manifolds are aligned along a longitudinal direction,

FIG. 5 schematically shows a heat exchanger according to a third embodiment of the invention, illustrating an alternative position for the plurality of refrigerant manifolds,

FIG. 6 schematically shows a heat exchanger according to a fourth embodiment of the invention, illustrating an alternative position for the plurality of refrigerant manifolds,

FIG. 7 schematically shows a heat exchanger according to a fifth embodiment of the invention, illustrating an alternative position for the plurality of refrigerant manifolds, and

FIG. 8 schematically shows a heat exchanger according to a sixth embodiment of the invention, illustrating an alternative position for the plurality of refrigerant manifolds.

DETAILED DESCRIPTION OF THE INVENTION

To describe the features of the heat exchanger according to the invention in detail, the trihedron LVT present in the figures will make it easier to understand the orientation of the various elements in the detailed description. The longitudinal direction L corresponds to an axis parallel to a main elongation direction of tubes of the heat exchanger, whereas the vertical direction V corresponds to an axis parallel to a main elongation dimension of refrigerant manifolds of the heat exchanger. The transverse direction T, for its part, corresponds to an axis perpendicular to the longitudinal direction L and to the vertical direction V.

FIG. 1 shows an overall view of a heat exchanger 1 according to a first embodiment of the invention, forming part of a refrigerant loop for a vehicle. The heat exchanger 1 notably comprises a heat exchange surface 3 which extends mainly along a longitudinal direction L and a vertical direction V. The heat exchange surface 3 is formed by a plurality of tubes 4 within which a refrigerant circulates. The tubes 4 have a main elongation dimension parallel to the longitudinal direction L, and are stacked with one another along a vertical direction V, resulting in the heat exchange surface 3 extending mainly along the longitudinal direction L and along the vertical direction V. The tubes 4 are stacked such that the stack forms just one single row of tubes 4 arranged one above another, leaving a passage between them so that a stream of air can pass through the heat exchanger between two adjacent tubes.

The heat exchanger 1 is configured for installation across a trajectory of a stream of air 2 in order to exchange heat between said stream of air 2 and the refrigerant circulating in the tubes 4. As a result, the stream of air 2 circulates mainly along a transverse direction T, in order to pass through the heat exchange surface 3, between two adjacent tubes, perpendicularly or substantially perpendicularly. In order that such an exchange of heat can be brought about, the heat exchanger 1 can, for example, be installed in a front face of the vehicle. When the vehicle is running, the stream of air 2 rushes into the front face of the vehicle and passes through the heat exchange surface 3. Depending on the ambient temperature outside the vehicle, the stream of air 2 can give up its heat energy to the refrigerant or even take in heat energy from the refrigerant.

The function of the refrigerant loop that comprises the heat exchanger 1 is notably to cool or heat a vehicle interior as required. The heat exchanger 1 according to the invention has a function which depends on an operating mode of the refrigerant loop. When the function of the refrigerant loop is to cool the vehicle interior, the stream of air 2 takes in heat energy from the refrigerant and condenses the latter. The role of the heat exchanger 1 is then to condense the refrigerant. When the function of the refrigerant loop is to heat the vehicle interior, the stream of air 2 gives up its heat energy to the refrigerant and evaporates the latter. The role of the heat exchanger 1 is then to evaporate the refrigerant. In this case, the stream of air tends to condense and droplets can form on the heat exchange surface, between the tubes notably when fins are disposed between two adjacent tubes so as to increase the contact surface area of the air with the heat exchanger.

In order to avoid the formation of frost, which might result from a negative outside temperature and the presence of such droplets, the aim of the invention is to organize the circulation of the refrigerant within the exchange surface of the heat exchanger.

To this end, the heat exchanger 1 comprises a plurality of refrigerant manifolds 5 arranged at the longitudinal ends of the heat exchange surface 3. In the first embodiment illustrated in FIG. 1, two refrigerant manifolds 5 are installed at each longitudinal end of the heat exchange surface 3, but it is conceivable, as will be discussed below with reference to other embodiments, to install as many refrigerant manifolds 5 as desired at each longitudinal end of the heat exchange surface.

The refrigerant manifolds 5 ensure a fluidic connection between the tubes 4 and a refrigerant loop which comprises the heat exchanger 1. The heat exchanger 1 according to the invention is configured so as to comprise two times as many refrigerant manifolds 5 as there are refrigerant circuits circulating within the heat exchanger 1. By way of example, according to FIG. 1, the heat exchanger 1 illustrated comprises four refrigerant manifolds 5, disposed such that there are two refrigerant manifolds 5 at each end of the heat exchange surface 3, and two refrigerant circuits are thus formed within the heat exchanger 1.

The manifolds are respectively connected to a refrigerant inflow or outflow portion of the refrigerant loop, such that the same refrigerant circulates within all of the circuits.

By virtue of the fact that multiple refrigerant circuits pass through the heat exchanger 1, it is possible to arrange these refrigerant circuits, whether at the refrigerant manifolds 5 or the tubes 4, in order to limit the aforementioned temperature gradient which might be observed from one end of the heat exchanger to the other. In the evaporator mode of the heat exchanger, the temperature of the refrigerant increases as it flows through the heat exchanger 2, and arranging multiple refrigerant circuits within the heat exchanger can make it possible to limit the temperature gradient mentioned by bringing a hot zone of one circuit and a cold zone of another circuit close together.

It can be seen in FIG. 1 that each refrigerant manifold 5 located at one and the same longitudinal end of the heat exchange surface 3 is fluidically connected to half of the tubes 4 making up the heat exchange surface, the manifolds connected to the same tubes contributing to the formation of one of the aforementioned circuits. In addition, the heat exchanger is such that, with reference to the vertical direction V, the refrigerant manifolds 5 of one and the same longitudinal end of the heat exchange surface 3 are alternately connected to the tubes 4. Such an alternating disposition of the tubes 4 and the corresponding circuits is advantageous for a more uniform temperature of the components of the heat exchanger when the refrigerant circulates within the various circuits formed in the heat exchange surface.

In the example illustrated, owing to the alternating tubes over the entire heat exchange surface, the heat exchange surface is evenly distributed between both the tubes that are connected to one refrigerant manifold disposed at a longitudinal end of the heat exchange surface and form a first circuit and the tubes that are connected to another refrigerant manifold disposed at this same longitudinal end and form a second circuit.

It is possible to provide that the heat exchange surface is distinctive in that multiple tubes associated with one circuit are adjacent within the stack of tubes so as to form sets of tubes which are evenly distributed and separated by a single tube associated with the other circuit, and therefore the proportion of one circuit in relation to the other within the heat exchange surface is increased. By way of non-limiting example, it is possible to provide that the first circuit represents two thirds of the heat exchange surface area and that the second circuit represents one third of the heat exchange surface area, and for this it is necessary to provide a repeatable pattern in the stack of tubes in which two successive tubes associated with the first circuit follow a single tube associated with the second circuit.

As can be seen in FIG. 1, the refrigerant manifolds 5 disposed at one and the same longitudinal end of the heat exchange surface 3 are aligned relative to one another along the transverse direction T. This is an exemplary disposition of the refrigerant manifolds 5 that makes it possible to limit the longitudinal mechanical bulk of the heat exchanger. The refrigerant manifolds 5 of one and the same longitudinal end of the heat exchange surface 3 can, however, have a different mutual arrangement, as will be described in detail below.

It is also possible to see that the set of refrigerant manifolds 5 have one and the same passage cross section. The passage cross section corresponds to that zone of the refrigerant manifold 5 within which the refrigerant flows. Setting up identical passage cross sections makes it possible to homogenize the circulation of the refrigerant and ensure an equal or substantially equal flow rate between each of the refrigerant circuits.

FIG. 2 shows the heat exchanger 1, which is structurally identical to that shown in FIG. 1, and part of the refrigerant loop 10 on which the heat exchanger is disposed, and thus makes it possible to describe an example of circulation of the refrigerant within multiple circuits formed in the heat exchanger 1 in detail.

As addressed above, a heat exchanger 1 according to the invention comprising two refrigerant manifolds 5 per longitudinal end of the heat exchange surface 3 allows the refrigerant to circulate via two refrigerant circuits. As a result, the refrigerant loop 10 comprises a first refrigerant circuit 8 and a second refrigerant circuit 9, each coming from a junction formed on an inflow channel 11, such that the refrigerant circulating within the two refrigerant circuits 8, 9 is from one and the same inflow. In other words, the refrigerant loop 10, upstream of the heat exchanger 1 with respect to a direction of circulation of the refrigerant, splits into two branches corresponding to the first refrigerant circuit 8 and the second refrigerant circuit 9.

The first refrigerant circuit 8 and the second refrigerant circuit 9 ensure the circulation of the refrigerant to the refrigerant manifolds 5, and more particularly to the inlet manifolds for supplying refrigerant to the heat exchange surface, which are specific to each circuit. In other words, the heat exchanger 1 comprises two refrigerant inlet manifolds 6, through one of which the refrigerant circulating in the first refrigerant circuit 8 passes and through the other one of which the refrigerant circulating in the second refrigerant circuit 9 passes.

In FIG. 2, the two refrigerant inlet manifolds 6 are arranged at opposite longitudinal ends relative to one another and are each fluidically connected to half of the tubes 4 making up the heat exchange surface 3, as can be seen in FIG. 1, a first half of the tubes being connected to a first inlet manifold and forming part of the first refrigerant circuit 8 and a second half of the tubes being connected to a second inlet manifold and forming part of the second refrigerant circuit 8.

The tubes forming part of the first refrigerant circuit 8 and the tubes 4 forming part of the second refrigerant circuit 9 alternate with one another along the stacking direction of the tubes 4, that is to say along the vertical direction V. Given that the two refrigerant inlet manifolds 6 are arranged so as to be at opposite longitudinal ends, the refrigerant circulating in the first refrigerant circuit 8 and the refrigerant circulating in the second refrigerant circuit 9 circulate within the tubes 4 along the longitudinal direction L but in mutually opposite directions of circulation. The refrigerant, according to FIG. 2, circulates at least in one zone of the exchange surface in a circulation which alternates from one tube to the next, that is to say with some of the refrigerant circulating from a first end to the opposite second end and with some of the refrigerant circulating from the second end to the first end.

Such a configuration, associated with the alternating tubes 4 along the vertical direction V, ensures a uniform distribution in terms of the temperature of the refrigerant over the entire heat exchange surface. This limits the risk of formation of a cold zone, which thus reduces the risk of frosting of the droplets formed as the stream of air 2 condenses on the heat exchange surface 3.

Within each refrigerant circuit, after having circulated in the tubes 4, while being evaporated by the input of heat energy from the stream of air 2 passing through the exchange surface, the refrigerant reaches a refrigerant outlet manifold 7. The number of outlet manifolds is equal to the number of circuits and is equal to two in the example illustrated. The refrigerant outlet manifold 7 is structurally identical to the refrigerant inlet manifold 6, with only the direction of circulation of the refrigerant, which circulates from an inlet manifold to an outlet manifold, enabling a distinction to be made between the two types of refrigerant manifolds 5. The refrigerant outlet manifolds 7 collect the refrigerant coming from the tubes 4 to enable it to subsequently circulate out of the heat exchanger 1.

In FIG. 2, each longitudinal end of the heat exchange surface is provided with a refrigerant inlet manifold 6 and a refrigerant outlet manifold 7. In addition, the tubes 4 fluidically connected to a refrigerant inlet manifold 6 arranged at one longitudinal end of the heat exchange surface 3 are also fluidically connected to a refrigerant outlet manifold 7 arranged at the opposite longitudinal end to this refrigerant inlet manifold 6 mentioned above. In other words, the refrigerant circulating in the first refrigerant circuit 8 or in the second refrigerant circuit 9 leaves the heat exchanger 1 via the opposite longitudinal end to that where the refrigerant entered. This is an example of a configuration of the refrigerant inlet manifolds 6 and refrigerant outlet manifolds 7. It is, for example, conceivable to have the refrigerant leave via the same longitudinal end as that where it entered, if the fluidic connection between the refrigerant manifolds 5 and the tubes 4 allows it, notably by providing, at one longitudinal end, return manifolds which collect the refrigerant circulating in one direction in certain tubes so as to return it in the other direction in other tubes.

At the outlet of the heat exchanger, the portion of the stream of refrigerant circulating in the first refrigerant circuit 8 and the portion of the stream of refrigerant circulating in the second refrigerant circuit 9 meet at a junction which is arranged downstream of the heat exchanger and allows the refrigerant to go to an outflow channel 12 of the refrigerant loop.

FIG. 3 shows the heat exchanger 1 comprising two refrigerant manifolds 5 at each longitudinal end of the heat exchange surface 3 which are aligned along the transverse direction T, like in the preceding figures.

The heat exchanger 1 shown in FIG. 3 is, however, distinguished from that described above by the direction of circulation of the refrigerant. Specifically, by contrast to the alternating circulation of the refrigerant described with reference to FIG. 2, the refrigerant circulates within the heat exchanger 1 illustrated in FIG. 3 in the same direction from one refrigerant circuit to the next. More particularly, the refrigerant inlet manifolds 6 are all arranged at one and the same longitudinal end of the heat exchange surface 3, and the refrigerant outlet manifolds 7 are all arranged at the opposite longitudinal end.

The portion of the stream of refrigerant circulating in the first refrigerant circuit 8 and the portion of the stream of refrigerant circulating in the second refrigerant circuit 9 thus enter the heat exchanger 1 via a single longitudinal end of the latter and these portions of the stream of refrigerant circulate in the same direction toward the outlet manifolds disposed at the opposite longitudinal end, before going to the junction at the outlet of the heat exchanger and the outflow channel 12.

Such an arrangement can notably make it possible to reduce the pressure drops in the manifolds since, by having two manifolds, the passage cross section is doubled and the pressure drops are thus reduced. This improves the thermal performance, since the pressure drops have an adverse effect on the performance in evaporator mode.

FIG. 4 shows a second embodiment of the heat exchanger 1, which differs from that described above by the arrangement of the refrigerant manifolds 5. More particularly, in this second embodiment, the refrigerant manifolds 5 disposed at one and the same longitudinal end of the heat exchange surface 3 are aligned relative to one another along the longitudinal direction L. In other words, the refrigerant manifolds 5 are aligned in the continuation of the longitudinal dimension of the heat exchange surface. Such a disposition is, for example, conceivable when it is not possible to align the refrigerant manifolds 5 along the transverse direction, in accordance with what was shown in FIGS. 1 to 3, owing to a lack of space around the heat exchanger 1. It is furthermore possible for the refrigerant manifolds 5 disposed at one end to be aligned along the transverse direction and for the refrigerant manifolds 5 disposed at the other end to be aligned along the longitudinal direction L.

Aligning the refrigerant manifolds 5 along the longitudinal direction L does not limit the possible ways the refrigerant can circulate within various circuits that can be set up. It is thus possible to set up circulation which alternates from one circuit to the next, as described with regard to FIG. 2, or circulation in the same direction from one circuit to the next, as described with regard to FIG. 3.

FIGS. 5 to 8 are diagrams of the heat exchanger 1 viewed from above which illustrate the diverse arrangements of cylindrical shapes 13 of the refrigerant manifolds 5. The cylindrical shapes 13 of the refrigerant manifolds 5 notably make it possible to define the passage cross sections for the refrigerant within said refrigerant manifolds 5. In FIGS. 1 to 4, the cylindrical shapes 13 of the refrigerant manifolds 5 have a circular cross section, but it is possible to vary the cylindrical shapes 13 and their arrangement so as to optimize the mechanical bulk of the refrigerant manifolds 5.

In FIG. 5, the refrigerant manifolds 5 still have a cylindrical shape 13 of circular cross section. However, the refrigerant manifolds 5 disposed at the same longitudinal end of the heat exchange surface 3 are not aligned with one another along a particular direction, but are disposed relative to one another so as to exhibit a concentric arrangement. In other words, the refrigerant manifolds 5 each have a circular cross section, but with a different diameter to that of the other manifolds, and they are disposed such that a refrigerant manifold 5 having a circular cross section with a first diameter can be inserted into a refrigerant manifold 5 having a circular cross section with a second diameter greater than the first diameter. In FIG. 5, four concentrically arranged refrigerant manifolds are disposed at each longitudinal end of the heat exchange surface 3. The diameters of the circular cross sections can be calculated such that the passage cross sections of the refrigerant manifolds 5 are equal or substantially equal relative to one another, notably relative to the manifold disposed at the center of the arrangement.

In FIG. 6, the refrigerant manifolds 5 disposed at each longitudinal end of the heat exchange surface 3 are disposed with a transverse offset relative to one another, along the transverse direction T, and they each have a cylindrical shape 13 of triangular cross section.

The cylindrical shapes 13 of each manifold can thus be arranged head-to-tail relative to one another, such that their complementing shapes allow an alignment of at least two refrigerant manifolds 5 along the transverse direction T, while still limiting the mechanical bulk along the transverse direction that could result from such an alignment. Here, there are three manifolds at each end of the heat exchange surface.

In FIG. 7, two refrigerant manifolds 5 are aligned with one another along the longitudinal direction L and they have a cylindrical shape 13 of semicircular cross section with a mirrored arrangement relative to one another, still with the aim of minimizing the mechanical bulk resulting from the presence of multiple manifolds.

Lastly, in FIG. 8, three refrigerant manifolds 5 are disposed at each longitudinal end of the heat exchange surface 3 and are aligned with one another along the longitudinal direction L. Of these three refrigerant manifolds 5, two of these refrigerant manifolds 5 have a cylindrical shape 13 of semicircular cross section and the third refrigerant manifold 5 has a cylindrical shape 13 of rectangular cross section. The two refrigerant manifolds 5 of semicircular cross section have a mirrored arrangement relative to one another with the refrigerant manifold 5 of rectangular cross section, which is interposed between the two refrigerant manifolds 5 of semicircular cross section. In such a configuration, the mechanical bulk is also limited, and the arrangement is optimized.

In each of the examples described above, it should be noted that the number of manifolds disposed at one longitudinal end of the heat exchange surface is equal to the number of manifolds disposed at an opposite longitudinal end of the heat exchange surface. Such a feature is notably advantageous in a refrigerant circulation arrangement in accordance with what was described with reference to FIG. 2, that is to say alternating circulation of refrigerant from one circuit to the next, with the number of manifolds disposed at each longitudinal end being equal to the number of circuits formed in the heat exchange surface.

The examples described are not exhaustive and the refrigerant manifolds 5 can have cross sections of varying shapes. Furthermore, according to the examples described, the cylindrical shapes 13 of the refrigerant manifolds 5 are the same for each longitudinal end of the heat exchanger 1, but it is possible to have a different arrangement between said longitudinal ends. The arrangements of the refrigerant manifolds 5 are moreover compatible with each of the refrigerant circulation modes described above with regard to FIGS. 2 and 3.

The invention as has just been described indeed achieves the object set for it, and makes it possible to propose a heat exchanger having a plurality of refrigerant manifolds at each longitudinal end of said heat exchanger, preventing the manifestation of a temperature gradient on the surface of the heat exchanger. Of course, the invention is not limited to the examples that have just been described and numerous modifications can be made to these examples without departing from the scope of the invention.

HEAT EXCHANGER FOR REFRIGERANT LOOP

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