Thermoregulation device and method, particularly for motor vehicles

Abstract

A thermoregulation device comprising a refrigerant circuit (1) configured to perform a thermodynamic cycle, said circuit (1) comprising a first branch (36) and a second branch (38), extending from the same first point of divergence (40) of said circuit, said first branch (36) comprising a first heat exchanger (12), intended for heat exchange with a first heat transfer fluid, said second branch (38) comprising a second heat exchanger (14), intended for heat exchange with a second heat transfer fluid, said circuit being configured to supply said first and second heat exchangers in parallel with high-pressure refrigerant from said first point of divergence (40) in at least one heat pump mode for heating said first and / or second heat transfer fluids. Figure for the abbreviation: Figure 4

Description

Title of the invention: Thermoregulation device and method, in particular for a motor vehicle

[0001] The invention relates to a thermoregulation device and method, in particular for a motor vehicle.

[0002] In this field, it has long been known to use a refrigerant circuit for air conditioning a vehicle passenger compartment. More recently, with the development of hybrid or electric engines, it has also been proposed to extend the use of such circuits to the thermoregulation of electrical energy storage devices such as batteries supplying power to the motors used to move the vehicle.

[0003] Said circuits must be able to operate in different modes such as cooling modes for air conditioning the passenger compartment and / or cooling the batteries and heat pump modes for heating them. The currently known circuits have a certain complexity, in particular when it comes to operating in heat pump modes. Some of them include electric heaters. Others include heat exchangers through which the refrigerant necessarily passes for the thermoregulation of other components before passing through the heat exchanger for heating the battery, which can be detrimental to the efficiency of the circuit.

[0004] The invention aims to at least partially overcome the above drawbacks and to this end proposes a thermoregulation device comprising a refrigerant circuit configured to perform a thermodynamic cycle, said circuit comprising a first branch and a second branch, extending from the same first point of divergence of said circuit, said first branch comprising a first heat exchanger, intended for heat exchange with a first heat transfer fluid, said second branch comprising a second heat exchanger, intended for heat exchange with a second heat transfer fluid, said circuit being configured to supply in parallel said first and second exchangers with high-pressure refrigerant from said first point of divergence in at least one heat pump mode making it possible to heat said first and / or second heat transfer fluids.

[0005] By "in parallel", we mean that the portion of fluid passing through one of the exchangers does not pass through the other, during the same cycle.

[0006] Thanks to such a configuration in two distinct parallel branches, namely said first and second branches, the circuit makes it possible to pool the calories of the refrigerant in the high pressure part of the circuit by supplying each of the first and second exchangers without having to pass through the other.

[0007] Preferably, said circuit comprises an element for controlling a circulation of a portion of the refrigerant supplying said first exchanger so as to have a different pressure level between the refrigerant entering the first exchanger and the refrigerant entering the second exchanger in at least some of said heat pump mode(s).

[0008] In this way, thanks to said control element, it is possible to adapt the fluid flow rate in each branch and therefore the pressure at the inlet of each exchanger according to the heating requirements.

[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: - said device comprises a thermoregulation circuit, intended for circulation of said first fluid to be thermoregulated, - said thermoregulation circuit comprises said first exchanger, - said thermoregulation circuit further comprises a storage system electrical energy intended to exchange heat with the first fluid to be thermoregulated, - said second heat transfer fluid is an air flow, - said control element is a valve, - said control element is located on said first branch so as to find between said point of divergence and said first exchanger according to the direction of circulation of the refrigerant fluid in said first branch in said heat pump mode(s), - said device is configured for circulation of the refrigerant fluid in said first exchanger in a first direction in said heat pump mode(s) and in a reverse direction, in at least one cooling mode making it possible to cool said first heat transfer fluid, - said first branch comprises a first expansion element for said refrigerant, said first expansion element being located on said first branch so as to be upstream of said first exchanger according to the direction of circulation of the refrigerant in said first branch in said cooling mode(s), - said refrigerant circuit comprises a third exchanger, intended to exchange heat with another heat transfer fluid, said device being configured so that the high-pressure refrigerant circulates alternately, on the one hand, in the first and / or second exchangers in the or said heat pump modes or, on the other hand, in the third exchanger in said cooling mode(s), - said first branch and said second branch comprise a point of convergence, - said circuit comprises a fourth heat exchanger comprising a high pressure pass and a low pressure pass for said refrigerant, said fourth heat exchanger being configured for heat exchange between said refrigerant passes, - said convergence point is located in said circuit so as to be upstream of said high pressure pass, according to the direction of circulation of the refrigerant in said heat pump mode(s).

[0010] The invention also relates to a thermoregulation method, said method implementing a refrigerant circuit, to carry out a thermodynamic cycle, said circuit comprising a first branch and a second branch, extending from the same first point of divergence of said circuit, said first branch comprising a first heat exchanger, intended for heat exchange with a first heat transfer fluid, said second branch comprising a second heat exchanger, intended for heat exchange with a second heat transfer fluid, said method comprising a step of supplying in parallel said first and second exchangers with high-pressure refrigerant from said first point of divergence in at least one heat pump mode making it possible to heat said first and / or second heat transfer fluids.

[0011] Preferably, said method further comprises a step of controlling a circulation of a portion of the refrigerant supplying said first exchanger so as to have a different pressure level between the refrigerant entering the first exchanger and the refrigerant entering the second exchanger in said heat pump mode(s).

[0012] According to various additional characteristics of the invention, which may be taken together or separately and which form as many embodiments of the invention: - a circulation of the refrigerant fluid in said first exchanger takes place in a first direction in said heat pump mode(s) and in a reverse direction, in at least one cooling mode making it possible to cool said first heat transfer fluid, - said refrigerant circuit comprising a third exchanger, intended to exchange heat with another heat transfer fluid, the high pressure refrigerant circulates alternately, on the one hand, in the first and / or second exchangers in said heat pump mode(s) or, on the other hand, in the third exchanger in said cooling mode(s).

[0013] 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:

[0014] [Fig. 1] schematically illustrates a first embodiment of the device according to the invention;

[0015] [Fig.2] schematically illustrates a second embodiment of the device in accordance with the invention;

[0016] [Fig.3] schematically illustrates the device of [Fig.l] according to a first mode of implementation of the method in accordance with the invention;

[0017] [Fig.4] schematically illustrates the device of [Fig.l] according to a second method of implementing the method according to the invention;

[0018] [Fig.5] schematically illustrates the device of [Fig.l] according to a third method of implementing the method according to the invention;

[0019] [Fig.6] schematically illustrates the device of [Fig.l] according to a fourth method of implementing the method according to the invention;

[0020] [Fig.7] schematically illustrates the device of [Fig.l] according to a fifth method of implementing the method according to the invention;

[0021] [Fig.8] schematically illustrates the device of [Fig.l] according to a sixth mode of implementing the method according to the invention.

[0022] 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 either an order or a possible importance of said components.

[0023] In Figures 3 and following, the dotted lines [yellow in the provisional drawings] correspond to parts of the refrigerant circuit illustrated without circulation of the refrigerant. The thicker continuous lines [red in the provisional drawings] correspond to parts of the refrigerant circuit in which said refrigerant circulates at high pressure. The intermediate thickness continuous lines [green in the provisional drawings] correspond to parts of the refrigerant circuit in which said refrigerant circulates at an intermediate pressure. The thinner continuous lines [blue in the provisional drawings] correspond to parts of the refrigerant circuit in which said refrigerant circulates at low pressure.

[0024] As illustrated in [Fig.l], the invention relates to a thermoregulation device comprising a refrigerant circuit 1. Said refrigerant is, for example, a subcritical fluid, such as those known as R134a or R1234yf. Alternatively, it is a supercritical fluid such as CO2 or R744. Said thermoregulation device is intended, in particular, for motor vehicles.

[0025] 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 / or a second heat exchange phase, this by circulating in different branches.

[0026] For this, said circuit preferably comprises a compressor 2, at least one expansion member, here at least five expansion members 4-9, at least two heat exchangers, here five heat exchangers, 12, 14, 16, 18, 20 and an accumulator 24. It also comprises one or more non-return members 25, 26 and / or circulation valves 30-32.

[0027] Said refrigerant circuit 1 is configured to alternately allow the circulation of the fluid in its different branches, in particular using said expansion members 4-9, provided to be controllable, non-return members 25, 26 and / or said circulation valves 30-32. It can thus be used in one or more heat pump modes, making it possible to heat first and second heat transfer fluids, and in various other operating modes, detailed later.

[0028] The first 12 of the heat exchangers is intended to exchange heat with the first heat transfer fluid. Said first exchanger 12 is formed, in particular, of a cooler.

[0029] Although not shown, said device advantageously comprises a first thermoregulation circuit, intended for circulation of said first heat transfer fluid. Said first thermoregulation circuit comprises said first exchanger 12.

[0030] Said first thermoregulation circuit further comprises an electrical energy storage system, in particular one or more batteries, intended to exchange heat with the first heat transfer fluid. In other words, in the event of a need to cool the batteries, in particular during the recharging phase, even more particularly during the rapid recharging phase, the heat released is evacuated into said first heat transfer fluid flowing through the first thermoregulation circuit and said first heat transfer fluid is cooled in said first exchanger 12 by means of the refrigerant of the refrigerant circuit 1. In the event of a need to heat the batteries, calories supplied by the refrigerant to the first heat transfer fluid via said first exchanger 12 are transported in said first thermoregulation circuit by said first heat transfer fluid to the energy storage system electric.

[0031] Said device advantageously comprises means for regulating the flow rate of the first heat transfer fluid in said first thermoregulation circuit. This is, for example, a pump for regulating the flow rate of the heat transfer fluid. It is thus possible to have a heat exchange at said first exchanger 12 when said first heat transfer fluid circulates in said first exchanger 12 or, alternatively, to neutralize it, when the first heat transfer fluid is not circulating in said exchanger 12, the pump being stopped.

[0032] The second heat exchanger 14 is intended to exchange heat with the second heat transfer fluid. According to a first embodiment, it is, for example, a first air flow, represented by the arrow marked 34, intended to supply a passenger compartment of the vehicle. In this embodiment, said second exchanger 14 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. Alternatively or cumulatively, it exchanges heat with a second heat transfer fluid other than the first air flow 34, possibly being integrated into a second thermoregulation circuit, not illustrated, said second thermoregulation circuit comprising a heating radiator intended to heat said first air flow 34 using said second heat transfer fluid.Said second exchanger 14 is formed, for example, of a gas cooler, called internal, in particular when said refrigerant fluid is CO2.

[0033] The third exchanger 16 is intended to exchange heat with another heat transfer fluid, for example a second air flow, called external, illustrated by the arrow marked 35. Said third heat exchanger 16 is intended to be located, in particular, at a front face of the vehicle to be crossed by said second air flow 35, said second air flow 35 having previously crossed a grille of the vehicle. Said third exchanger 16 is formed, for example, of a gas cooler, called external, in particular when said refrigerant fluid is CO2.

[0034] Said device is preferably configured so that the high-pressure refrigerant circulates alternately, on the one hand, in the first and / or second exchangers 12, 14 in said heat pump mode(s) or, on the other hand, in the third exchanger 16 in one or more cooling modes, making it possible to cool, in particular, the first heat transfer fluid and / or the second heat transfer fluid.

[0035] Said fourth heat exchanger 20 comprises a high pressure pass 22a and a low pressure pass 22b for said refrigerant, said fourth heat exchanger 20 being configured for heat exchange between said passes 22a, 22b of refrigerant fluid. Said fourth heat exchanger 20 thus allows an exchange of heat of the refrigerant fluid with itself. Said fourth exchanger 20 is formed, for example, of an internal exchanger.

[0036] The fifth exchanger 18 is intended to exchange heat with, for example, the first air flow 34. Said fifth exchanger 18 is intended to be located, in particular, at the level of the heating, ventilation and / or air conditioning unit, upstream of the second exchanger 14 according to the direction of circulation of said first air flow 34. Said fifth exchanger 18 is formed, for example, of an evaporator.

[0037] The accumulator 24 is configured for phase separation of said refrigerant, for example by allowing accumulation of said refrigerant, in liquid phase, in a lower part, and in gas phase in an upper part. It comprises an inlet 24a of said refrigerant, in particular in a two-phase liquid-vapor state, and an outlet 24b of said refrigerant, capable of delivering said refrigerant in gas phase.

[0038] According to the invention, said circuit comprises a first branch 36 and a second branch 38, extending from the same first point of divergence 40 of said circuit. Said first branch 36 comprises the first heat exchanger 12. Said second branch comprises the second heat exchanger 14. Said circuit is further configured to supply in parallel said first and / or second exchangers 12, 14 with high-pressure refrigerant fluid from said first point of divergence 40 in the or at least one of the heat pump modes. By "in parallel", it is meant that, during the same thermodynamic cycle in said circuit 1, a portion of fluid passing through one of the first or second exchangers 12, 14 does not pass through the other.

[0039] In this way, the calories that can be supplied by the refrigerant fluid in a high-pressure part of the circuit are pooled by supplying, in at least one or some of said heat pump modes, each of the first and second exchangers 12, 14 to simultaneously heat the first and second heat-transfer fluids.

[0040] Said first branch and said second branch here comprise a convergence point 44. Said convergence point 44 is located in said circuit so as to be upstream of said high pressure pass 22a, according to the direction of circulation of the refrigerant fluid in said heat pump mode(s).

[0041] Preferably, said circuit comprises an element for controlling a circulation of a portion of the refrigerant supplying said first exchanger 12 so as to have a different pressure level between the refrigerant entering the first exchanger 12 and the refrigerant entering the second exchanger 14 in said heat pump mode(s). It is thus possible to adapt the fluid flow rate in each of the first and second branches 36, 38 and therefore the inlet pressure of each of the first and second exchangers 12, 14, this depending on the heating requirements. It is furthermore possible to have a passage of the refrigerant in only one of said first and second branches 36, 38.

[0042] Said control element is here a first 30 of the circulation valves. Said control element, in particular said first circulation valve 30, is advantageously located on said first branch 36 so as to be between said point of divergence 40 and said first exchanger 12 according to the direction of circulation of the fluid in said first branch 36 in said heat pump mode(s).

[0043] Preferably, said device is configured for circulation of the refrigerant in said first exchanger 12 in a first direction in said heat pump mode(s) and in a reverse direction, in the cooling mode(s). This makes it possible to use the same heat exchanger, namely the first exchanger 12, for cooling and heating the batteries. For this, here, said first branch 36 comprises a first 4 of the expansion elements of said refrigerant. Said first expansion element 4 is located on said first branch 36 so as to be upstream of said first exchanger 12 according to the direction of circulation of the fluid in said first branch 36 in said cooling mode(s).

[0044] Said refrigerant circuit 1 advantageously has a third branch 39 and a fourth branch 41 extending from a first bifurcation point 42 located at the outlet of the compressor 2. Said third branch 39 extends to the divergence point 40 where it subdivides to form said first and second branches 36, 38. Said fourth branch 41 extends to the convergence point 44. Taken in series with said third branch 39, the first and second branches 36, 38 are each parallel to said fourth branch 41, between said first bifurcation point 42 and said convergence point 44.

[0045] Between the point of divergence 40 and the point of convergence 44, the first branch 36 successively comprises, according to the direction of flow of the refrigerant in this branch, in the heat pump mode(s), the first circulation valve 30, the first exchanger 12 and the first expansion member 4.

[0046] Between the point of divergence 40 and the point of convergence 44, the second branch 38 successively comprises, according to the direction of flow of the refrigerant in this branch, in the heat pump mode(s), the second exchanger 14 and a possible second 5 of said expansion members. As a variant, the second expansion member 5 is replaced by a first 25 of the non-return members. This is illustrated in [Fig.2] but is also applicable to the embodiment of [Fig.l].

[0047] Between the first bifurcation point 44 and the divergence point 40, the third branch 39 comprises a second 31 of said circulation valves.

[0048] Between the bifurcation point 42 and the convergence point 44, the fourth branch 41 successively comprises, according to the direction of flow of the refrigerant in this branch, in the cooling mode(s), a third 6 of said expansion members, the third exchanger 16, a fourth 7 of said expansion members and the high pressure pass 22a of said fourth exchanger 20.

[0049] Said circuit 1 furthermore has here a fifth branch 46, a sixth branch 48 and a seventh branch 50, configured to complete, in particular in series, the preceding branch(es) 36, 38, 39, 41 or portions thereof, with a view to carrying out said thermodynamic cycle in the corresponding operating mode(s).

[0050] Said fifth branch 46 extends between a second bifurcation point 52 and an inlet of the compressor 2. Said second bifurcation point 52 is located on the fourth branch 41 between the third expansion member 6 and the third exchanger 16. Said fifth branch 46 comprises in series, according to the direction of flow of the refrigerant in said heat pump mode(s), a third 32 of said circulation valves, another 26 of the non-return members, the accumulator 24 and the low-pressure pass of said fourth exchanger 20.

[0051] Said sixth branch 48 connects the fourth branch 41 to the fifth branch 46. It is located between the convergence point 44 and a first junction point 54. Said first junction point 64 is located on said fifth branch 46 between said third circulation valve 32 and said other non-return member 26. Said sixth branch 48 comprises successively between the convergence point 44 and the first junction point 54, according to the direction of flow of the refrigerant in the cooling mode(s), a fifth 8 of said expansion members and said fifth exchanger 18.

[0052] Said seventh branch 50 connects said first branch 36 and said fifth branch 46. It extends between a third bifurcation point 56 and a second junction point 58. Said third bifurcation point 56 is located on the first branch 36 between the divergence point 40 and the first exchanger 12. Said second junction point 58 is located on the fifth branch 46 between the non-return member 54 and the accumulator 24. Said seventh branch 50 comprises a sixth 9 of said expansion members.

[0053] According to the embodiment of [Fig.2], as a variant, said point of convergence 44 is located downstream of said high-pressure pass 22a, according to the direction of circulation of the refrigerant in said heat pump mode(s). In this mode, the high-pressure pass 22a of the fourth exchanger 20 passes from said fourth branch 41 to said first branch 36. It is more precisely located between said point of convergence 44 and a fourth bifurcation point 44' connecting said first branch 36 and said sixth branch 48 upstream of said first expansion member 4 according to the direction of circulation of the fluid in the said cooling mode(s). For the rest, the circuit is identical to that mentioned above.

[0054] As illustrated in [Fig.3], according to a first mode of operation, said device operates as a heat pump by passing through the second branch 38 without passing through the first branch 36.

[0055] In this mode, the refrigerant passes through the third branch 39 at the outlet of the compressor 2, the second valve 31 being open and the third expansion member 6 being closed. It then passes into the second branch 38, said first valve 30 being closed. The calories available in the refrigerant which is then at high pressure are transferred to the second heat transfer fluid which is heated, this by means of said second exchanger 14. The first air flow 34 can then heat the passenger compartment of the vehicle. Downstream, said refrigerant passes through the second expansion member 5 which is open and inactive. It then continues its route through the portion of the fourth branch 41 located between the convergence point 44 and the second bifurcation point 52, the first and fifth expansion members 4, 8 being closed.It thus passes into the high pressure pass 22a of the fourth exchanger 20, into the fourth expansion member 7 which is active and causes an expansion of said refrigerant which then passes to low pressure then passes through the third exchanger 16 taking calories from the second air flow 35. Downstream of the second bifurcation point 52, the refrigerant takes the fifth branch 46 to return to the compressor 2 passing through the other non-return member 26, the accumulator 24 and the low pressure pass 22b of the fourth exchanger 20.

[0056] According to this embodiment, the calories taken from the second air flow 35 are transmitted to the first air flow 34 via the thermodynamic cycle described by the refrigerant fluid.

[0057] As illustrated in [Fig.4], according to a second mode of operation, said device operates again as a heat pump, this time passing through both the first branch 36 and the second branch 38.

[0058] In this mode, the refrigerant fluid follows the same circuit as in the first embodiment, the difference being that the fluid divides into a first portion and a second portion at the divergence point 40. Only the second portion passes into the second branch 38 while the first portion passes into the first branch 36, said first circulation valve 30 being open and the sixth expansion member 9 being closed.

[0059] In the first branch 36, the calories available in the first portion of refrigerant fluid, which is then at high pressure, are transferred to the first heat transfer fluid which is heated, this by means of said first exchanger 12. In this way, the batteries can be heated. Downstream, said refrigerant fluid passes by the first expansion member 4 which is open and inactive. It then joins the second portion of refrigerant fluid which has passed through the second branch 38, this at the level of the convergence point 44.

[0060] In the second branch 38, the calories available in the second portion of refrigerant, which is then at high pressure, are transferred to the second heat transfer fluid which is heated, this by means of said second exchanger 14. In the case where the second heat transfer fluid is the first air flow 34, the latter can then heat the passenger compartment of the vehicle. Downstream, said refrigerant passes through the first expansion member 4 which is open and inactive. It then joins the first portion of refrigerant which has passed through the first branch 36, this at the convergence point 44.

[0061] Downstream, the refrigerant follows the same path as in the first embodiment by taking calories from the second air flow 35.

[0062] According to this embodiment, the calories taken from the second air flow 35 are transmitted both to the batteries and to the first air flow 34 via the thermodynamic cycle described by the refrigerant fluid, this by passing through each of the first and second branches 36, 38.

[0063] As already stated above, this heat transfer sharing is advantageously controlled, here using the first circulation valve 30 which, depending on a degree of opening, makes it possible to determine the quantity of refrigerant sent into each of the first and second branches 36, 38. It should be noted that the location of said first valve 30 upstream of said first exchanger 12 and / or of said second exchanger 14 allows more deterministic control than using a control member located downstream, such as the first expansion member 4 and / or the second expansion member 5. Alternatively, the and / or said expansion members 4, 5 are however used for such control, alternatively or in combination with the first circulation valve 30.

[0064] In the operating mode of [Fig.4], the degree of opening of the first valve 30 is configured so that the pressure of the first portion and the second portion of refrigerant fluid is substantially the same.

[0065] In the operating mode of [Fig. 5], the circulation of the refrigerant is the same as in [Fig. 4]. The difference lies in the degree of opening of the first valve 30 which is this time configured so that the pressure of the first portion of refrigerant is higher than the pressure of the second portion of refrigerant. While heating both the first and second heat transfer fluids in this way, it is possible to promote the heating of the first heat transfer fluid. The batteries can thus be strongly heated while continuing to heat the passenger compartment, even if the heating of the passenger compartment is carried out with less power. than in the operating mode of [Fig.4].

[0066] As illustrated in [Fig.6], according to another mode of operation, said device operates in cooling mode of the first heat transfer fluid. As already mentioned above, it passes through the first exchanger 12 in the opposite direction to that taken in the heat pump mode. In the illustrated embodiment, said device also allows here cooling of the first air flow 34 at the fifth exchanger 18.

[0067] More precisely, the refrigerant fluid passes through the fourth branch 41 at the outlet of the compressor 2, the second valve 31 being closed and the third expansion member 6 being open and inactive. It thus passes into the third heat exchanger 16, the third valve 32 being closed. It is then at high pressure and its calories are dissipated in the second air flow 35. Downstream, said refrigerant fluid passes through the fourth expansion member 7 which is open and inactive. It then continues its route by passing through the high pressure pass 22a of the fourth exchanger 20 and passes in parallel through the first branch 36 and the sixth branch 48, this between the point of convergence 44 and the second junction point 58. In other words, at the level of said point of convergence 44, the refrigerant fluid is subdivided into two portions, a first portion passing through the first branch 36 and a second portion passing through the sixth branch 48.

[0068] In the first branch 36, the first portion circulates, as already stated, in the opposite direction to that of the heat pump modes. More precisely, it passes through the first expansion member 4 which is active and causes an expansion of said first portion of the refrigerant fluid. It then passes into the first exchanger 12 where it takes the calories from the first heat transfer fluid which is thus cooled. Said cold heat transfer fluid can thus in turn cool the batteries. At the third bifurcation point 56, said first portion leaves the first branch 36 to pass into said seventh branch 50, said first circulation valve 30 being closed. It then passes into said sixth expansion member 9, which is open and not active, to reach the second junction point 58.

[0069] In the sixth branch 48, the second portion passes through the fifth expansion member 8 which is active and causes an expansion of said second portion of the refrigerant fluid. It then passes into the fifth exchanger 18 where it takes the calories from the first air flow 34 which is thus cooled. Said first air flow 34 can then cool the passenger compartment of the vehicle. Downstream, said second portion joins the fourth branch 46 at the first junction point 54 then the second junction point 58 passing through said other non-return member 26, the third valve 32, as a reminder, being closed.

[0070] At said second junction point 58, the first and second portions of refrigerant fluid join together and the refrigerant fluid continues its route along the remaining portion of said fourth branch 46 to return to the compressor 2 via the accumulator member 24 and the low pressure pass 22b of the fourth exchanger 20.

[0071] According to this embodiment, the calories taken from the first refrigerant fluid and the first air flow 34 are transmitted to the first air flow 35 via the thermodynamic cycle described by the refrigerant fluid.

[0072] According to additional operating modes, not illustrated, said device operates in cooling mode of the first heat transfer fluid or of the first air flow 34 by passing through the first branch 36, as described above, but without passing through the sixth branch 48, or by passing through the sixth branch 48, as described above, but without passing through the first branch 36. In these operating modes, the entirety of the refrigerant fluid and not only a portion passes respectively through the first branch 36 or through the sixth branch 48.

[0073] As mentioned above, it is understood that the high-pressure refrigerant circulates alternately, on the one hand, in the first and / or second exchangers 12, 14 in said heat pump mode(s), as in FIGS. 3 to 5 or, on the other hand, in the third exchanger 16, in said cooling mode(s), as in [Fig. 6]. For this, it uses either the third branch 39 or the fourth branch 41 at the outlet of the compressor 2.

[0074] As illustrated in [Fig.7], according to another mode of operation, said device operates in a hybrid manner with cooling of the first heat transfer fluid via the first exchanger 12 and heating of the second heat transfer fluid via the second exchanger 14. Such a mode of operation can be seen as a heat pump mode making it possible to recover the calories from the second air flow 35 and from the first heat transfer fluid to transfer them to the second heat transfer fluid, in particular said first air flow 34. It is thus possible to recover not only the calories available in the second air flow 35 but also, via the first heat transfer fluid, those coming from the heat released by the batteries.

[0075] In this mode, the refrigerant follows the same circuit as in the first operating mode, illustrated [Fig. 3], up to the convergence point 44. It then divides into a first portion and a second portion. From said convergence point 44, the first portion passes into the first branch 36 according to the same circuit as the corresponding portion according to the operating mode of [Fig. 6] and the second portion follows the same circuit as the refrigerant in the first operating mode.

[0076] The first and second portions meet at said second point of junction 58 and the low pressure refrigerant returns to the compressor as in each of these operating modes already mentioned.

[0077] As illustrated in [Fig.8], according to a complementary operating mode, the refrigerant fluid allows cooling of the first air flow 34 using said fifth exchanger 18 and heating of said first air flow 34 using the second exchanger 14, in particular for demisting the passenger compartment, as well as dissipation of calories in the second air flow 35 at said third exchanger 16, in particular for defrosting it, if necessary.

[0078] In this embodiment, the refrigerant fluid is divided into a first portion and a second portion at the outlet of the compressor 2, said first and second portions circulating in parallel up to the convergence point 44.

[0079] The first portion follows the third branch 39 then the second branch 38, as in the first operating mode of [Fig.3].

[0080] The second portion follows the fourth branch 41 passing through the third expansion member 6, open and active. Said second portion undergoes a slight expansion at the level of said third expansion member and thus passes to an intermediate pressure before passing into said third exchanger 16, said third valve 32 being closed. Said second portion continues downstream passing through said fourth expansion member 7, open and inactive, then the high pressure pass 22a of said fourth exchanger 20 before joining the first portion of refrigerant fluid at the level of the convergence point 44.

[0081] The refrigerant fluid continues downstream in the sixth branch 48, the first valve 30 being closed as well as the first expansion member 4 and / or the sixth expansion member 9. The refrigerant fluid thus passes through the fifth expansion member 8 which is active and causes an expansion of the refrigerant fluid. The latter is then at low pressure. It then passes into the fifth exchanger 18 and joins the fourth branch 46 at the first junction point 54 of which it travels the remaining portion passing through said other non-return member 26, the accumulator 24 and the low pressure pass 22b of the fourth exchanger 20 to return to the compressor 2.This path of the heat transfer fluid is made possible in particular because the third valve 32, as a reminder, is closed and said refrigerant cannot take the seventh branch 50 at the level of said second junction point 58, if only for reasons of the pressure levels involved at each end of said seventh branch 50.

Claims

Claims

1. Thermoregulation device comprising a refrigerant circuit (1) configured to perform a thermodynamic cycle, said circuit (1) comprising a first branch (36) and a second branch (38), extending from the same first point of divergence (40) of said circuit, said first branch (36) comprising a first heat exchanger (12), intended for heat exchange with a first heat transfer fluid, said second branch (38) comprising a second heat exchanger (14), intended for heat exchange with a second heat transfer fluid, said circuit being configured to supply in parallel said first and second exchangers with high-pressure refrigerant from said first point of divergence (40) in at least one heat pump mode making it possible to heat said first and / or second heat transfer fluids.

2. Device according to the preceding claim in which said circuit comprises a control element (30) for the circulation of a portion of the refrigerant supplying said first exchanger (12) so as to have a different pressure level between the refrigerant entering the first exchanger (12) and the refrigerant entering the second exchanger (14) in at least some of said heat pump mode(s).

3. Device according to the preceding claim in which said control element (30) is located on said first branch (36) so as to be between said point of divergence (40) and said first exchanger (12) according to the direction of circulation of the fluid in said first branch (36) in said heat pump mode(s).

4. Device according to any one of the preceding claims, configured for circulation of the refrigerant fluid in said first exchanger (12) in a first direction in said heat pump mode(s) and in a reverse direction, in at least one cooling mode making it possible to cool said first heat transfer fluid.

5. Device according to the preceding claim in which said first branch (36) comprises a first expansion element (4) for said refrigerant fluid, said first expansion element (4) being located on said first branch (36) so as to be upstream of said first exchanger (12) in the direction of circulation of the fluid in said first branch (36) in said cooling mode(s).

6. Device according to any one of the preceding claims in which said refrigerant circuit (1) comprises a third exchanger (16), intended to exchange heat with another heat transfer fluid, said device being configured so that the high pressure refrigerant circulates alternately, on the one hand, in the first and / or second exchangers (12, 14) in said heat pump mode(s) or, on the other hand, in the third exchanger (16) in said cooling mode(s).

7. Thermoregulation method, said method implementing a refrigerant circuit (1), to carry out a thermodynamic cycle, said circuit (1) comprising a first branch (36) and a second branch (38), extending from the same first point of divergence (40) of said circuit, said first branch (36) comprising a first heat exchanger (12), intended for heat exchange with a first heat transfer fluid, said second branch (38) comprising a second heat exchanger (14), intended for heat exchange with a second heat transfer fluid, said method comprising a step of supplying in parallel said first and second exchangers (12, 14) with high-pressure refrigerant from said first point of divergence (40) in at least one heat pump mode making it possible to heat said first and second heat transfer fluids.

8. Method according to the preceding claim further comprising a step of controlling a circulation of a portion of the refrigerant supplying said first exchanger (12) so as to have a different pressure level between the refrigerant entering the first exchanger (12) and the refrigerant entering the second exchanger (14) in said heat pump mode(s).

9. Method according to any one of claims 7 or 8 in which a circulation of the refrigerant fluid in said first exchanger (12) takes place in a first direction in said heat pump mode(s) and in a reverse direction, in at least one cooling mode making it possible to cool said first heat transfer fluid.

10. Method according to any one of claims 7 to 8 wherein, said refrigerant circuit (1) comprising a third exchanger (16), intended to exchange heat with another heat transfer fluid, the high pressure refrigerant circulates alternately, on the one hand, in the first and / or second exchangers (12, 14) in said one or more heat pump modes or, on the other hand, in the third exchanger (16) in said cooling mode(s).

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