WO2023030971A1

WO2023030971A1 - Heat exchanger for refrigerant loop

Info

Publication number: WO2023030971A1
Application number: PCT/EP2022/073512
Authority: WO
Inventors: Gael Durbecq; Kamel Azzouz; Jeremy Blandin
Original assignee: Valeo Systemes Thermiques
Priority date: 2021-09-03
Filing date: 2022-08-23
Publication date: 2023-03-09
Also published as: FR3126764A1

Abstract

The invention relates to a heat exchanger (2) for a refrigerant loop of a vehicle, which comprises an exchange surface (12) through which an air flow (102) is intended to pass and a plurality of tubes (20), the heat exchanger further comprising at least a first refrigerant circuit (24) consisting of a first portion (28a) of the plurality of tubes (20) and a first inlet manifold (16a) fluidically connected to said first portion (28a) of the plurality of tubes (20), and at least a second refrigerant circuit (26) consisting of a second portion (28b) of the plurality of tubes (20) and a second inlet manifold (16b) fluidically connected to the second portion (28b) of the plurality of tubes (20), the first inlet manifold (16a) and the second inlet manifold (16b) being opposite each other in a main elongation direction (A) of the tubes (20).

Description

TITLE: HEAT EXCHANGER OF A REFRIGERANT LOOP.

The present invention relates to a refrigerant loop intended for the circulation of a refrigerant fluid and applied to a heating, ventilation and/or air conditioning installation for a motor vehicle, and more particularly for electric cars or hybrid cars.

An electric or hybrid car has a refrigerant fluid loop in order to vary the temperature inside its passenger compartment, and in particular to heat it in winter and to cool it in summer. The temperature of the passenger compartment is modified in particular by means of the refrigerant fluid circulating in the refrigerant fluid loop between a heat exchange device arranged in the vehicle in the vicinity of the passenger compartment, and a heat exchanger located in contact with the ambient air, in front of the vehicle. Thus, the coolant circulating in the coolant loop absorbs or releases calories at the heat exchanger or the heat exchange device depending on the heating or cooling needs of the passenger compartment. The use of a compressor and, where appropriate, of an expansion valve is in particular necessary to modify the pressure of the refrigerant fluid in the refrigerant fluid loop in order to thermodynamically modify the temperature of the refrigerant fluid subsequently caused to pass through the device. heat exchanger and heat exchanger.

The heat exchanger located on the front of the vehicle enables the exchange of calories between the coolant which circulates in tubes arranged one above the other and spaced from one another by spacers, and a flow of air, coming from from outside the vehicle and passing through said heat exchanger between the tubes at the spacers.

In electric or hybrid vehicles, it is known to configure the refrigerant loop and the heat exchanger on the front face to form a reversible heat pump in which the heat exchanger is able to operate in condenser mode, in summer, to ensure the cooling of the passenger compartment 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 heating in the passenger compartment via the device heat exchange forming a condenser.

A problem with such a heat exchanger placed on the front of the vehicle then lies in its operation as an evaporator, when the temperature differential tends to heat the flow of humid air and create droplets of condensation which are deposited on the surface of the heat exchanger. 'heat exchanger. If the temperature of the refrigerant circulating in the tubes is too low, and the spacers between the tubes are too cold by thermal conduction, the cooling of the condensation droplets may form frost locally on the spacers between the heat exchanger tubes. heat. Such presence of frost generates obstacles to the passage of air through the heat exchanger and therefore tends to reduce the thermal capacities of the heat exchanger.

The present invention aims to remedy this drawback, by proposing a refrigerant loop, and more particularly a heat exchanger, making it possible to limit the formation of frost on the latter. The invention therefore makes it possible to increase the thermal capacities of the heat exchanger and therefore of the refrigerant fluid loop.

The invention therefore relates to a heat exchanger for a refrigerant loop, comprising a heat exchange surface, the heat exchange surface comprising a plurality of tubes, the heat exchanger being characterized in that it comprises at least a first refrigerant circuit consisting of a first part of the plurality of tubes, a first inlet manifold fluidly connected to the first part of the plurality of tubes and a first outlet manifold fluidly connected to the first part of the plurality of tubes, the heat exchanger comprising at least a second refrigerant circuit consisting of a second part of the plurality of tubes, a second inlet manifold fluidly connected to the second part of the plurality of tubes and a second outlet manifold fluidly connected to the second part of the plurality of tubes, the first part of the plurality of tubes and the second part of the plurality of tubes being fluidly distinct from each other, the first inlet manifold being disposed at a first end of the heat exchange surface and the second manifold input being disposed at a second end of the heat exchange surface opposite the first end.

The refrigerant fluid loop can be arranged within a vehicle, for example electric or hybrid, in order to heat or cool a passenger compartment of said vehicle, in particular via an exchange of calories within the heat exchanger between the refrigerant fluid and an external air flow, the heat exchange surface being intended to be traversed by this external air flow.

The refrigerant fluid loop may consist of a reversible heat pump and the heat exchanger may be an evapo-condenser within which the refrigerant fluid circulates. More specifically, the heat exchanger comprises the heat exchange surface within which heat exchanges take place between the flow of air passing through said exchange surface, and the refrigerant fluid circulating within the plurality of tubes of said exchange surface, the coolant capturing or transferring calories to the air flow depending on the configuration of the coolant loop, intended to heat or cool the passenger compartment.

The tubes are stacked along a stacking direction, with a space left between two neighboring tubes to allow airflow through the heat exchange surface. These tubes are configured to channel the refrigerant fluid along a direction of main elongation of the tubes and they are each fluidly connected to inlet chambers allowing the supply of refrigerant fluid and outlet chambers allowing the evacuation of this coolant.

The first inlet manifold and the second inlet manifold respectively of the first circuit and of the second circuit are fluidically connected to a first portion of the refrigerant fluid loop, said first portion being to be considered as the portion connecting a heat exchanger, which may consist of a condenser or an evaporator depending on the operating configuration of the control loop, to the heat exchanger and borrowed in this direction by the refrigerant fluid. This first portion may in particular comprise at least one compressor or one expansion member. A branch is formed on the first portion of the refrigerant loop and the refrigerant therein circulates is split into two flows directed respectively towards the first inlet collector and towards the second inlet collector.

The first outlet manifold and the second outlet manifold respectively of the first circuit and of the second circuit are fluidically connected to a second portion of the refrigerant fluid loop, the second portion of the refrigerant fluid loop being to be considered as the portion connecting the heat exchanger to the previously mentioned heat exchanger, which may consist of a condenser or an evaporator depending on the operating configuration of the control loop, and borrowed in this direction by the refrigerant fluid. This second portion may in particular comprise at least one compressor or one expansion device. A connection is formed between the two outlet manifolds and the second portion of the refrigerant fluid loop so that the two flows leaving the outlet manifolds converge towards the second portion of the refrigerant fluid loop.

When the coolant loop is in a configuration where it heats the passenger compartment, the coolant entering the heat exchanger is colder than the flow of air passing through said heat exchanger, said coolant having been expanded by the expansion device upstream of the heat exchanger inlet. Thus, although the flow of air coming from outside the vehicle has a low temperature, it is understood that said flow of air is intended to transfer its calories to the refrigerant in order to heat it. The refrigerant fluid is heated as it circulates through the plurality of tubes, from the inlet manifold to the outlet manifold.

Advantage is then taken of the first inlet collector and the second inlet collector, and in particular of their particular arrangement at opposite ends of the exchange surface, in that they make it possible to avoid significant temperature gradients d one end to the other of the heat exchange surface, the portion of refrigerant intended to enter the exchange surface via the first inlet manifold being intended to circulate in the opposite direction to that of the circulation of the portion of refrigerant fluid intended to enter the exchange surface via the second inlet manifold. More precisely, the circulation of the refrigerant fluid in the first circuit and the circulation of the fluid refrigerant in the second circuit are in opposite directions, allowing a better distribution of the temperature gradient of the refrigerant fluid in the exchange surface. The temperature of the exchange surface is thus more homogeneous, so that the formation of frost on said exchange surface of the heat exchanger is limited.

According to a characteristic of the invention, at least one tube of the first circuit is arranged between two tubes of the second circuit along the stacking direction of the tubes.

It is understood that the tubes of the first part of the plurality of tubes and the tubes of the second part of the plurality of tubes are mixed within the stack of tubes forming the heat exchange surface. This allows a better distribution of the temperature of the refrigerant fluid within the exchange surface of the heat exchanger.

According to a feature of the invention, the tubes of the first part of the plurality of tubes are arranged alternately with the tubes of the second part of the plurality of tubes in the stacking direction of the tubes. In other words, a tube from the first part of the plurality of tubes is placed between two tubes from the second part of the plurality of tubes in the stacking direction, and vice versa.

Alternatively, at least two tubes of the first part of the plurality of tubes, successive along the stacking direction of the tubes, are separated from each other along the stacking direction of the tubes, by at least two tubes of the second part of the plurality of tubes.

According to one characteristic of the invention, the first outlet manifold is arranged at the second end of the heat exchange surface and the second outlet manifold is arranged at the first end of the heat exchange surface opposite the second end along the direction of main elongation of the plurality of tubes.

It is then understood that the input collector and the output collector of the first circuit, respectively the input collector and the output collector of the second circuit, are at ends opposite each other of the surface of exchange, along the direction of main elongation of the plurality of tubes. According to one characteristic of the invention, the first input manifold and the second output manifold form an assembly disposed at the first end of the exchange surface, the assembly formed by the first output manifold and the second output manifold entry being disposed at the second end of the exchange surface.

According to one characteristic of the invention, the collectors of the first circuit face each other along the main direction of elongation of the tubes and the collectors of the second circuit face each other along the direction of main elongation of the tubes.

According to a characteristic of the invention, the collectors positioned at the same end of the heat exchange surface are aligned along a line secant to a main plane of the heat exchange surface. More precisely, the collectors positioned at the same end of the heat exchange surface are aligned along a straight line perpendicular to the main plane of the heat exchange surface.

According to one characteristic of the invention, the heat exchanger comprises a plurality of heat dissipation members extending along the main direction of elongation of the tubes, each heat dissipation member being placed between at least two tubes of the plurality of tubes along their stacking direction. The heat dissipation members can be, for example and in a non-limiting way, fins, making it possible to increase, by heat conduction between the tubes and these fins, the calorie exchange surface for the air flow passing through the exchanger heat.

According to one characteristic of the invention, the first inlet manifold and the second inlet manifold are configured to be fluidically connected in a common manner to an expansion member of the first portion of the refrigerant fluid loop. It is understood that the branch formed on the first portion of the refrigerant fluid loop which is connected to each of the inlet manifolds to supply an equivalent quantity of refrigerant fluid to the first circuit and the second circuit, can be arranged downstream of the expansion member, that is to say between this expansion member and the heat exchanger, so that the portions of refrigerant circulating in each circuit is evenly expanded.

The invention also relates to a refrigerant fluid loop comprising at least one compressor, at least one heat exchanger, at least one heat exchanger according to any one of the preceding characteristics, an outlet of the compressor being fluidly connected to the heat, at least one outlet of the heat exchanger being fluidly connected to the heat exchanger or to an inlet of the compressor, and at least one first expansion member is arranged between the heat exchanger and the heat exchanger and to the at least one second expansion member is arranged between the compressor and the heat exchanger.

According to a feature of the refrigerant loop, the latter comprises at least one refrigerant inlet channel in the heat exchanger and an outlet channel for the refrigerant fluid from the heat exchanger, the inlet manifolds of the heat exchanger being fluidically connected to the coolant fluid inlet channel and the heat exchanger outlet manifolds being fluidically connected to the coolant fluid outlet channel.

It is also understood that the inlet channel for the coolant in the first inlet manifold and in the second inlet manifold is arranged at the outlet of the expansion device present on the first portion of the coolant loop. The outlet channel, fluidically connected to the first outlet manifold and to the second outlet manifold, is fluidically connected to the compressor or to the heat exchanger depending on the configuration of use of the refrigerant fluid loop.

Other characteristics, details and advantages of the invention will emerge more clearly on reading the description given below by way of indication in relation to the drawings in which:

[Fig i] is a schematic view of a refrigerant loop according to a first configuration;

[Fig 2] is a schematic view of the refrigerant loop of Figure i according to a second configuration; [Fig 3] is a schematic representation of a heat exchanger of the refrigerant loop of Figures 1 and 2, comprising a first circuit and a second circuit and a heat exchange surface comprising a plurality of tubes distributed in a first part and a second part;

[Fig 4] is a perspective view of an embodiment of the heat exchanger of Figure 3, comprising the first circuit and the second circuit and a heat exchange surface comprising a plurality of tubes distributed in a first part and a second part;

[Fig 5] is a close-up view of the heat exchange surface illustrating several neighboring tubes and several heat dissipation devices respectively arranged between two tubes.

It should first be noted that if the figures expose the invention in detail for its implementation, these figures can of course be used to better define the invention, if necessary. It should also be noted that these figures only show exemplary embodiments of the invention. Finally, the same references designate the same elements in all the figures.

Figures 1 and 2 illustrate a refrigerant fluid loop 1 according to one aspect of the invention intended to equip a vehicle, electric or hybrid, in order to heat or cool a passenger compartment of the vehicle, by means of a first flow of air 101 directed towards the passenger compartment of the vehicle.

The refrigerant loop 1 comprises at least one heat exchanger 2 specific to the invention, and here comprises, in the example illustrated in FIGS. 1 and 2, a compressor 4, a heat exchanger 6, an evaporator 8 and at least at least one expansion member 10. The heat exchanger 2 is advantageously arranged at the front of the vehicle in order to be crossed by a second flow of air 102 coming from outside the vehicle.

In a first configuration of the refrigerant fluid loop 1, intended to cool the passenger compartment of the vehicle and illustrated here in FIG. 1, the refrigerant fluid passes through the heat exchanger 2 within which it transfers calories to the second flow of air 102 passing through said heat exchanger 2, such that the refrigerant fluid leaves the heat exchanger 2 in the liquid state whereas it entered the gaseous state. Subsequently, the refrigerant is directed to a first organ of expansion ioa of the refrigerant loop i, for example an expansion valve, ensuring the expansion of the refrigerant fluid and the lowering of its temperature. Thus, the refrigerant fluid is colder at the outlet of the first expansion member ioa than at the inlet. Following its passage through the first expansion device ioa, the refrigerant fluid passes through the evaporator 8 and exchanges calories with the first law air flow passing through said evaporator 8. More precisely, the evaporator 8 is integrated into a casing of a heating installation of the vehicle which is configured to direct the first flow of law air which passes through the evaporator towards the passenger compartment of the vehicle, and the refrigerant fluid circulating in the evaporator is colder than the first flow law air flow when it passes through the evaporator so that the refrigerant fluid is able to capture the calories of the first law air flow in order to cool it before it enters the passenger compartment. During the exchange of calories in the evaporator 8, the refrigerant fluid therefore changes to the gaseous state when it captures the calories of the first law air flow, in particular by lowering its temperature change point. state by the first trigger member ioa.

Subsequently, at the outlet of the evaporator 8, the refrigerant fluid in gaseous form is directed to the compressor 4 which increases the pressure of the refrigerant fluid and therefore increases its temperature. The refrigerant fluid then passes through the heat exchanger 6 without carrying out any heat exchange, said heat exchanger 6 not being, in this configuration of the refrigerant fluid loop 1, crossed by the first air flow 101. At the outlet of the heat exchanger 6, the coolant is directed to a second expansion member 10b which, in this configuration of the coolant loop 1, is inactive, the coolant being directed to the heat exchanger 2 at the outlet of the second expansion device 10b.

In a second configuration of the refrigerant loop 1, intended to heat the passenger compartment of the vehicle and illustrated here in FIG. 2, the refrigerant passes through the compressor 4 in the gaseous state so that the latter increases the pressure and the temperature refrigerant fluid. Subsequently, the refrigerant passes through the heat exchanger 6 within which it exchanges calories with the first air flow 101 which in this configuration passes through the heat exchanger 6 before being directed towards the passenger compartment of the vehicle. More precisely, the refrigerant transfers these calories to the first air flow 101, then colder, so that said first law air flow is hotter after passing through the heat exchanger 6 so as to heat the vehicle interior.

At the outlet of heat exchanger 6, the refrigerant has become liquid but is colder than at the inlet of heat exchanger 6 and it is caused to pass through the second expansion device lob so that the latter further lowers the pressure and the temperature. refrigerant fluid. Subsequently, the refrigerant passes through the heat exchanger 2 in which it exchanges calories with the second air flow 102 passing through it. More precisely, the second air flow 102 is hotter than the refrigerant fluid, and the refrigerant fluid therefore picks up calories from said second air flow 102 during its passage through the heat exchanger 2 and comes out of this last in a gaseous state. Subsequently, the refrigerant, in gaseous state, is redirected to compressor 4.

It is also understood that during the use of the refrigerant loop 1 in the second configuration, which heats the passenger compartment of the vehicle, the cold refrigerant which passes through the heat exchanger 2 captures calories from the second flow of air 102 from outside the vehicle, so that the temperature of the refrigerant increases as it progresses through the heat exchanger 2 from an inlet manifold to an outlet manifold. In addition, it should be considered that when using the refrigerant fluid loop 1 in the second configuration which heats the passenger compartment, that is to say in the winter period, the second air flow 102 is at a low temperature, so that the temperature of the refrigerant fluid may present a negative temperature at the inlet of the heat exchanger and the temperature of the components of this heat exchanger is particularly cold, liable to create frost if droplets of condensation from the second air flow is formed on the surface of the heat exchanger.

The heat exchanger 2 according to the invention, particularly visible in Figures 3 to 5, comprises a heat exchange surface 12, which extends in a main plane 14 longitudinal L and vertical V, and which is intended to be crossed by the second air flow 102 from outside the vehicle. The heat exchanger 2 also comprises at least one inlet manifold 16 and at least one outlet manifold 18 of the refrigerant fluid connected to the surface exchange 12 so as to respectively allow the entry of the refrigerant into the exchange surface and the exit of the refrigerant from this exchange surface.

The heat exchange surface 12 comprises a plurality of tubes 20 stacked along a stacking direction E, here vertical V, and within which the refrigerant fluid circulates. More specifically, the plurality of tubes 20 is configured to channel the refrigerant fluid between the at least one inlet manifold 16 and the at least one outlet manifold 18 along a main elongation direction A of the tubes 20, here longitudinal L.

The exchange surface 12 of the heat exchanger 2 also comprises a plurality of heat dissipation members 22, visible in FIG. 5. Each of these heat dissipation members 22 extends parallel to the direction of elongation main A of the tubes 20, from the at least one inlet manifold 16 to the at least one outlet manifold 18. Each of the heat dissipation members 22 extends between two neighboring tubes 20 of the plurality of tubes 20 and makes it possible to increase the contact surface for the second air flow passing through the exchange surface 12, so as to increase the heat exchange performance. According to an example of the invention, the plurality of heat dissipation members 22 can take the form of spacers or fins.

According to the invention, the heat exchanger 2 comprises at least a first refrigerant circuit 24 and a second refrigerant circuit 26, visible in Figures 3 and 4.

The first refrigerant circuit 24 comprises in particular a first part 28a of the plurality of tubes 20, as well as a first inlet manifold 16a and a first outlet manifold 18a which are fluidically connected to the first part 28a of the plurality of tubes 20. It is understood that the first inlet manifold 16a makes it possible to distribute the refrigerant fluid in each of the tubes of the first part 28a, while the first outlet manifold 18a makes it possible to evacuate the refrigerant fluid once it has circulated through the tubes of the first part 28a.

More specifically, the first inlet manifold 16a is fluidically connected to a first portion 30a of the refrigerant fluid loop 1, visible in Figures 1 and 2, arranged between the heat exchanger 6, here in the form of a condenser, and the heat exchanger, and comprising the second expansion member lob, mentioned above. Furthermore, the first outlet manifold 18a is fluidically connected to a second portion 30b of the refrigerant fluid loop 1, connected to the evaporator 8 or to the compressor 4 depending on the configuration of the thermal regulation loop.

The second refrigerant circuit 26 comprises a second part 28b of the plurality of tubes 20 of refrigerant fluid, as well as a second inlet manifold 16b and a second outlet manifold 18b which are fluidly connected to the second part 28b of the plurality of tubes 20. In accordance with what has been described previously, the second inlet manifold 16b makes it possible to distribute the refrigerant fluid in each of the tubes of the second part 28b, while the second outlet manifold 18b makes it possible to evacuate the refrigerant fluid once it has circulated through the tubes of the second part 28b.

The second inlet manifold 16b is fluidically connected to the first portion 30a of the refrigerant fluid loop 1 previously described and visible in Figures 1 and 2, while the second outlet manifold 18b is fluidically connected to the second portion 30b of the refrigerant loop 1.

The first part 28a of the plurality of tubes 20 and the second part 28b of the plurality of tubes 20 are fluidically distinct from each other. The first inlet manifold 16a and the second inlet manifold 16b being configured to be fluidically connected to the same first portion 30a of the refrigerant loop, it is understood that this first portion comprises a branch with two branches to which are connected the first input collector 16a and the second input collector 16b. The refrigerant fluid circulating in the first portion 30a of the refrigerant fluid loop is split on passing this branch into two flow portions circulating, one in the first circuit via the first inlet manifold and the other in the second circuit. via the second input collector.

The first inlet manifold 16a and the second inlet manifold 16b are configured to be fluidically connected in a common manner to the second expansion device of the refrigerant fluid loop. More precisely, we defines an inlet channel 32 for the coolant in the heat exchanger 2, visible in FIG. 3, and an outlet channel 34 for the coolant in the heat exchanger 2. The inlet manifolds 16a, 16b are then fluidly connected to the inlet channel 32 of the refrigerant fluid while the outlet manifolds 18a, 18b are fluidically connected to the outlet channel 34 of the refrigerant fluid. In other words, the inlet channel 32 of the refrigerant fluid extends between the second expansion member 10b and the inlet manifolds 16a, 16b, while the outlet channel 34 extends between the outlet manifolds 18a, 18b and the compressor 4 or the evaporator 8 depending on the configuration of the refrigerant loop 1.

As is particularly visible in Figures 3 and 4, the first inlet manifold 16a and the second inlet manifold 16b are arranged opposite one another along the main direction of elongation A of the tubes 20. More specifically, a first end 36a of the exchange surface 12 and a second end 36b of the exchange surface 12 are defined, opposite each other along the main direction of elongation A of said tubes 20, and the first inlet manifold 16a is arranged at the first end 36a of the exchange surface 12 while the second inlet manifold 16b is arranged at the second end 36b of the exchange surface 12.

Similarly, the first outlet manifold 18a is arranged at the second end 36b of the heat exchange surface 12 while the second outlet manifold 18b is arranged at the first end 36a of the exchange surface 12. then comprises that the first inlet collector 16a and the second outlet collector 18b form a set arranged at the first end 36a of the exchange surface 12 and that another set formed by the first outlet collector 18a and the second inlet collector 16b is arranged at the second end 36b of the exchange surface 12.

According to the example of the invention in FIG. 4, the first input collector 16a and the first output collector 18a of the first circuit 24 face each other in the direction of main elongation A of the tubes 20. Similarly, the second inlet manifold 16b and the second outlet manifold 18b of the second circuit 26 face each other in the direction of main elongation A of the tubes 20. Furthermore, and still according to an example of the invention, the first inlet collector 16a and the second outlet collector 18b positioned at the first end 36a of the exchange surface 12 are aligned along a line I secant to the main plane 14 of the exchange surface 12, said line I being for example perpendicular to said main plane 14. It should be considered that this characteristic applies mutatis mutandis to the first outlet collector 18a and to the second inlet collector 16b positioned at the second end 36b of the exchange surface 12.

Other arrangements of the inlet and outlet manifolds can be implemented according to the invention, since two inlet manifolds allowing two distinct supply zones of the same refrigerant are arranged at opposite ends of the heat exchange surface. By way of example not shown here, the inlet and outlet collectors forming an assembly arranged at one end of the heat exchange surface can be arranged so as to be aligned in the direction of main elongation.

It is understood from the above that the circulation of the refrigerant fluid within the heat exchanger 2, and more particularly within the exchange surface 12, is crossed. In other words, during the operation of the refrigerant fluid loop, the refrigerant fluid is caused to circulate in the plurality of tubes 20 of the exchange surface 12 of the heat exchanger 2 according to two opposite directions of circulation. More precisely, a first direction Si of circulation corresponds to a circulation from the first end 36a of the exchange surface 12 towards the second end 36b of the exchange surface 12, that is to say from the first collector of inlet 16a to the first outlet collector 18a, while a second direction S2 of circulation corresponds to a circulation from the second end 36b of the exchange surface 12 towards the first end 36b of the exchange surface 12, it that is to say from the second input collector 16b to the second output collector 18b.

It is further understood that the first inlet manifold 16a and the first outlet manifold 18a are fluidly connected only to the inlet channel 32, to the first part 28a of the plurality of tubes 20 and to the outlet channel 34, while the second inlet manifold 16b and the second outlet manifold 18b are fluidically connected only to the inlet channel 32, to the second part 28b of the plurality of tubes 20 and to the outlet channel 34, the inlet channel 32 and the outlet channel 34 being common to these portions of refrigerant fluid caused to circulate in opposite directions within the heat exchange surface.

Such cross-circulation of the refrigerant fluid within the heat exchanger 2 advantageously makes it possible to obtain a better temperature distribution within the exchange surface 12. In other words, the temperature gradient of the refrigerant fluid circulating within the first circuit 24 is opposed to the temperature gradient of the refrigerant fluid circulating within the second circuit 26, thus limiting the concentration of low or negative temperature in a localized zone of the exchange surface 12, which makes it possible to limit the formation of frost on said heat exchange surface 12.

As illustrated schematically in FIG. 3, at least one of the tubes 20 of the first circuit 24 is arranged between two tubes 20 of the second circuit 26 along the stacking direction E of the tubes 20, and/or at least one of the tubes 20 of the second circuit 26 is arranged between two tubes 20 of the first circuit 24 along the stacking direction E of the tubes 20. Such an arrangement of the tubes 20 of the first circuit 24 and the tubes 20 of the second circuit 26, mixed with within the stack of tubes, is advantageous for better homogenizing the temperature of the components of the heat exchanger when the refrigerant fluid circulates within the heat exchange surface.

More particularly, and as illustrated in FIG. 4 and FIG. 5, the tubes 20 of the first part 28a, that is to say of the first circuit 24, can advantageously be arranged alternately with the tubes 20 of the second part 28b, that is to say of the second circuit 26, following the stacking direction E of the tubes 20, in a configuration where a tube of the first part 28a extends into the stack of tubes just after a tube of the second part 28b, and vice versa.

Alternatively, the first and second parts of the plurality of tubes can be arranged with at least two tubes 20 of the first part 28a of the plurality of tubes 20, successive along the stacking direction E of the tubes 20, which are separated from each other along the stacking direction E of the tubes 20, by at least two tubes 20 of the second part 28b of the plurality of tubes 20. It is thus possible to provide that the heat exchange surface is particular in that several tubes associated with a circuit are adjacent within the stack of tubes to form sets of tubes regularly distributed and separated by a single tube associated with the another circuit, so that the proportion of one circuit relative to the other within the heat exchange surface is thus increased. By way of non-limiting example, provision may be made for the first circuit to represent two thirds of the surface area of the heat exchange surface and for the second circuit to represent one third of the surface area of the heat exchange surface, and it is therefore 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.

The invention as it has just been described cannot however be limited to the means and configurations exclusively described and illustrated, and also applies to all means or configurations, equivalents and to any combination of such means or configurations.

Claims

1. Heat exchanger (2) for a refrigerant loop (1), comprising a heat exchange surface (12), the heat exchange surface (12) comprising a plurality of tubes (20), the heat exchanger (2) being characterized in that it comprises at least a first circuit (24) of refrigerant fluid consisting of a first part (28a) of the plurality of tubes (20), a first collector of inlet (16a) fluidly connected to the first part (28a) of the plurality of tubes (20) and a first outlet manifold (18a) fluidly connected to the first part (28a) of the plurality of tubes (20) , the heat exchanger (2) comprising at least a second refrigerant fluid circuit (26) consisting of a second part (28b) of the plurality of tubes (20), a second inlet manifold (16b) fluidly connected to the second part (28b) of the plurality of tubes (20) and a second outlet manifold (18b) fluidly connected to the second part e (28b) of the plurality of tubes (20), the first part (28a) of the plurality of tubes (20) and the second part (28b) of the plurality of tubes (20) being fluidly distinct from one another, the first inlet manifold (16a) being disposed at a first end (36a) of the heat exchange surface (12) and the second inlet manifold (16b) being disposed at a second end (36b ) of the heat exchange surface (12) opposite the first end (36a).

2. Heat exchanger (2) according to the preceding claim, wherein at least one tube (20) of the first circuit (24) is disposed between two tubes (20) of the second circuit (26) along the stacking direction (E) tubes (20).

3. Heat exchanger (2) according to any one of the preceding claims, in which the tubes (20) of the first part (28a) of the plurality of tubes (20) are arranged alternately with the tubes (20) of the second part (28b) of the plurality of tubes (20) following the stacking direction (E) of the tubes (20).

4. Heat exchanger (2) according to any one of claims 1 or 2, wherein at least two tubes (20) of the first part (28a) of the plurality of tubes (20), successive in the direction of stack (E) of the tubes (20), are separated from each other along the stacking direction (E) of the tubes (20), by at least two tubes (20) of the second part (28b) of the plurality of tubes (20).

5. Heat exchanger (2) according to any one of the preceding claims, in which the first outlet manifold (18a) is arranged at the first end (36a) of the heat exchange surface (12) and the second outlet manifold (18b) is disposed at the second end (36b) of the heat exchange surface (12) opposite the first end (36a) along the main elongation direction (A) of the plurality of tubing (20).

6. Heat exchanger (2) according to any one of the preceding claims, in which the first inlet collector (16a) and the second outlet collector (18b) form an assembly disposed at the first end (36a) of the exchange surface (12), the assembly formed by the first outlet collector (18a) and the second inlet collector (16b) being arranged at the second end (36b) of the exchange surface (12).

7. Heat exchanger (2) according to the preceding claim, wherein the collectors (16a, 18a) of the first circuit (24) face each other in the direction of main elongation (A) of the tubes (20) and the collectors (16b, 18b) of the second circuit (26) face each other along the main direction of elongation (A) of the tubes (20).

8. Heat exchanger (2) according to the preceding claim, wherein the collectors (16, 18) positioned at the same end (36a, 36b) of the heat exchange surface (12) are aligned along a line (I) secant to a main plane (14) of the heat exchange surface (12).

9. Heat exchanger (2) according to any one of the preceding claims, comprising a plurality of heat dissipation members (22), each heat dissipation member (22) being arranged in the direction of main elongation (A) tubes (20) between at least two tubes (20) of the plurality of tubes (20) along their stacking direction (E).

10. Heat exchanger (2) according to any one of the preceding claims, in which the first inlet manifold (16a) and the second inlet manifold (16b) are configured to be fluidically connected in a manner 19 common to an expansion member (10, 10a, 10b) of the first portion (30a) of the refrigerant loop (1).

11. Refrigerant fluid loop (1) comprising at least one compressor (4), at least one evaporator (8), at least one heat exchanger (2) according to any one of the preceding claims, an outlet of the compressor (4 ) being fluidically connected to the heat exchanger (2), at least one outlet of the heat exchanger (2) being fluidically connected to the evaporator (8) or to an inlet of the compressor (4), and at least a first expansion member (10a) is arranged between the heat exchanger (2) and the evaporator (8) and at least one second expansion member (10b) is arranged between the compressor (4) and the heat exchanger heat (2).

12. Coolant loop (1) according to the preceding claim comprising at least one inlet channel (32) of the coolant in the heat exchanger (2) and an outlet channel (34) of the coolant of the heat exchanger (2), the inlet manifolds (16) of the heat exchanger (2) being fluidly connected to the inlet channel (32) of the refrigerant fluid and the outlet manifolds (18) of the exchanger heat (2) being fluidly connected to the outlet channel (34) of the refrigerant.