Heat transfer fluid circuit for a heat treatment system

Abstract

Heat transfer fluid circuit for a heat treatment system The present invention relates to a heat transfer fluid circuit (2), comprising: a main branch (4) extending between a convergence zone (7) and a divergence zone (8), a first loop (9) comprising a main section (10) and a secondary section (11), the main section (10) being provided with a first control device (14) configured to circulate the heat transfer fluid to the convergence zone (7) or to the secondary section (11), a second loop (23) placed under the control of a second control device (27) configured to circulate the heat transfer fluid to the second loop (23) or to the convergence zone (7), a third loop (31) comprising a third control device (35) configured to circulate the heat transfer fluid to the third loop (31) or to the convergence zone (7). (figure 1)

Description

Title of the invention: Heat transfer fluid circuit for a heat treatment system

[0001] The present invention relates to the field of heat treatment systems for a motor vehicle, and more particularly concerns a heat transfer circuit integrated into such heat treatment systems.

[0002] Motor vehicles are commonly equipped with a refrigerant circuit and at least one heat transfer fluid circuit, both used to participate in a heat treatment of different zones or different components of the vehicle. It is in particular known to use the refrigerant circuit and / or the heat transfer fluid circuit to heat treat a flow of air sent into the passenger compartment of the vehicle equipped with such a circuit. This heat treatment is carried out in particular by means of a circulation of the refrigerant within a ventilation, heating and / or air conditioning installation arranged in the vehicle.

[0003] In another application of this circuit, it is known to use the heat transfer fluid circuit to cool components of the vehicle's powertrain, such as for example an electrical storage device, the latter being used to supply energy to an electric motor capable of setting the vehicle in motion. The heat treatment system thus supplies the energy capable of cooling the electrical storage device during its use in driving phases.

[0004] Several refrigerants have been used for this type of heat treatment system, such as R 134a or R1234yf. However, following new European standards, these refrigerants have been banned from use in Europe due to their environmental harm. For future heat treatment systems, it was therefore decided to use R290 as the refrigerant. However, R290 is pure propane. As a safety measure, it is therefore essential to avoid circulating propane directly in the ventilation, heating and / or air conditioning system. Thus, the heat treatment of the vehicle interior is done indirectly by the refrigerant, and only the heat transfer fluid circulates within the ventilation, heating and / or air conditioning system.

[0005] Such a condition leads to rethinking the configuration of the heat treatment system, in particular in order to design a heat transfer fluid circuit combining compactness, simplicity and multiplicity of heat treatment functions.

[0006] In order to meet these objectives, the present invention proposes a heat transfer fluid circuit for a heat treatment system of a vehicle and intended to be traversed by a heat transfer fluid, comprising: - a main branch comprising a first heat exchanger configured to carry out a heat exchange between the heat transfer fluid and an external air flow, and extending between a convergence zone and a divergence zone, - a first loop comprising a main section and a secondary section, the main section starting at the divergence zone and being provided with a second heat exchanger configured to heat treat an electric motor of the vehicle, a first pumping device and a first control device, the first control device being configured to circulate the heat transfer fluid to the convergence zone or to the secondary section, the secondary section comprising a second pumping device, a third heat exchanger configured to carry out a heat exchange between the heat transfer fluid and a refrigerant circulating in a refrigerant circuit and a fourth heat exchanger configured to heat treat an electrical storage device of the vehicle, - a second loop comprising a fifth heat exchanger configured to carry out a heat exchange between the heat transfer fluid and the refrigerant fluid circulating in the refrigerant circuit, a third pumping device and a sixth heat exchanger configured to carry out a heat exchange between the heat transfer fluid and an interior air flow intended to be sent into the passenger compartment of the vehicle, the second loop being placed under the control of a second control device configured to circulate the heat transfer fluid towards the second loop up to the sixth heat exchanger or towards the convergence zone via a junction branch, - a third loop comprising a seventh heat exchanger configured to carry out a heat exchange between the heat transfer fluid and the refrigerant fluid circulating in the refrigerant circuit, a fourth pumping device, a third control device and an eighth heat exchanger configured to carry out a heat exchange between the heat transfer fluid and the interior air flow intended to be sent into the passenger compartment of the vehicle, the third control device being configured to circulate the heat transfer fluid towards the third loop up to the eighth heat exchanger or towards the convergence zone via a connecting branch.

[0007] A heat transfer fluid circuit configured in this way guarantees a good compromise between multiplicity of functions and simplicity. On the one hand, the heat transfer fluid circuit provides a plurality of functions, without circulating the refrigerant fluid within a ventilation, heating and / or air conditioning installation associated with the heat treatment system in question. On the other hand, the architecture of the heat transfer fluid circuit is implemented in a simple manner, without the need to integrate expensive and / or complex elements.

[0008] The main branch is fluidically connected to all of the loops of the heat transfer fluid circuit. In other words, the heat transfer fluid from the first loop, the second loop or the third loop can subsequently circulate via the main branch. The main branch allows passive thermal treatment of the heat transfer fluid via the first heat exchanger and the outside air flow passing through the latter. By outside air flow, it is meant an air flow that is not intended to be sent to the passenger compartment of the vehicle. In order to be arranged on a path of the outside air flow, the first heat exchanger can for example be arranged at a front face of the vehicle.

[0009] By convergence zone, it should be understood that it is a section of the main branch comprising one or more points of convergence through which the heat transfer fluid from the different loops of the heat transfer fluid circuit circulates.

[0010] The divergence zone corresponds to a section of the main branch comprising one or more divergence points allowing the distribution of the heat transfer fluid within the different loops of the heat transfer fluid circuit. Depending on the need, the divergence zone can supply one or more loops with heat transfer fluid.

[0011] The first loop allows in particular the heat transfer fluid to provide thermal treatment, which may be heating or cooling, of the electric motor via the main section and the second heat exchanger and / or of the electrical storage device via the secondary section and the fourth heat exchanger.

[0012] Such an operation may prove necessary in the event of the temperature of the electric motor or the electrical storage device being too high or too low. For example, the electric motor may reach a high temperature when driving at high speed, for example on the highway, while the electrical storage device may need to be heated when the vehicle is started or to be cooled after a rapid recharge of the vehicle.

[0013] The third heat exchanger participates for example in the cooling of the electric motor and / or the electrical storage device by carrying out a heat exchange between the refrigerant fluid and the heat transfer fluid. The refrigerant fluid being previously expanded before passing through the third heat exchanger, the heat transfer fluid is then cooled within the third heat exchanger before circulating within the second heat exchanger or the fourth heat exchanger. thermal to respectively cool the electric motor or the electrical storage device.

[0014] The first pumping device makes it possible to circulate the heat transfer fluid, in particular in the main section of the first loop. The first control device makes it possible to circulate the heat transfer fluid towards the main branch or towards the secondary section. The second pumping device makes it possible to circulate the heat transfer fluid within the secondary section, for example in order to generate a circulation of fluid independent of any other potential circulation of fluid within the main section.

[0015] The second loop ensures the cooling of the vehicle interior. The third pumping device allows the heat transfer fluid to be circulated within this second loop. Just like the third heat exchanger, the fifth heat exchanger is configured to cool the heat transfer fluid by means of the previously expanded refrigerant.

[0016] The cooled heat transfer fluid then circulates to the sixth heat exchanger, and thus cools the interior air flow which is then sent into the passenger compartment of the vehicle. The second loop therefore contributes to the air conditioning of the passenger compartment of the vehicle. As such, the sixth heat exchanger can be arranged within the ventilation, heating and / or air conditioning system mentioned above. The second control device is arranged downstream of the fifth heat exchanger, and allows either the heat transfer fluid from the fifth heat exchanger to circulate to the sixth heat exchanger, or to circulate it to the main branch via the junction branch.

[0017] The third loop has the particular function of ensuring the heating function within the passenger compartment of the vehicle. The fourth pumping device ensures the circulation of the heat transfer fluid within the third loop. The seventh heat exchanger, just like the third heat exchanger and the fifth heat exchanger, allows a heat exchange with the refrigerant. However, the heat exchange carried out within the seventh heat exchanger is carried out with the refrigerant previously compressed and not expanded. The seventh heat exchanger therefore allows the heat transfer fluid to be heated via the high-pressure refrigerant. Subsequently, the heated heat transfer fluid passes through the eighth heat exchanger in order to heat the interior air flow passing through the latter. The interior air flow thus heated is then sent into the passenger compartment of the vehicle to heat treat it.Like the sixth heat exchanger, the eighth heat exchanger can be arranged within the ventilation, heating and / or air conditioning system. The passenger compartment of the vehicle, via the sixth heat exchanger and / or the eighth exchanger. thermal can thus be heated or air conditioned.

[0018] Just like the first control device and the second control device, the third control device is configured to provide a direct fluid connection between its loop and the main branch. The third loop is thus connected to the main branch via the connecting branch.

[0019] Thus, all of the loops partially constituting the heat transfer fluid circuit comprise at least one fluid connection with the first heat exchanger, via its respective control device. These fluid connections guarantee a multiplicity of functionalities of the heat transfer fluid circuit, whether at the level of the heat treatment of the passenger compartment of the vehicle or the heat treatment of the components of the vehicle's powertrain.

[0020] According to a characteristic of the invention, the first loop comprises a first transfer branch between the main section and the secondary section, the first transfer branch extending between the first control device and the secondary section. This first transfer branch allows the circulation of the heat transfer fluid from the main section to the secondary section or vice versa. Thanks to this first transfer branch, a fluid connection is ensured in particular between the second heat exchanger and the third heat exchanger, allowing cooling of the engine, or between the second heat exchanger and the fourth heat exchanger in order to be able to carry out indirect heat exchanges between the electric motor and the electrical storage device.

[0021] According to a feature of the invention, the first loop comprises a second transfer branch extending between the main section and the secondary section. The second transfer branch makes it possible to complete the first loop and to connect the main section to the secondary section in a closed manner, also thanks to the first transfer branch mentioned above. The second transfer branch is therefore essential for performing the functions mentioned above.

[0022] According to a characteristic of the invention, the secondary section of the first loop comprises an electric heating element. The electric heating element ensures the heating of the heat transfer fluid using an external energy supply to the heat transfer fluid circuit. Depending on the need, the electric heating element is therefore capable of heating the heat transfer fluid circulating in the secondary section.

[0023] According to a characteristic of the invention, the first loop comprises a control member and a bypass branch, the control member being configured to circulate the heat transfer fluid to the fourth heat exchanger or within the bypass branch, the bypass branch being fluidically linked to the control member and being arranged in parallel with the fourth heat exchanger. The bypass branch allows the circulation of the heat transfer fluid in the secondary section of the first loop without the latter passing through the fourth heat exchanger. Thus, when there is no need to heat treat the electrical storage device but the heat transfer fluid is heated via the electric heating element or cooled via the third heat exchanger for a heat treatment purpose other than that of the electrical storage device, the bypass branch prevents the heat transfer fluid from passing through the fourth heat exchanger and disturbing the temperature of the heat transfer fluid.

[0024] According to a characteristic of the invention, the first control device is a three-way valve comprising three ports, at least one port extending the main section to the convergence zone and at least one other port being connected to the secondary section, the third control device being a three-way valve comprising three ports, at least one port extending the third loop to the eighth heat exchanger and at least one other port being connected to the convergence zone via the connecting branch. It is thanks to these three-way valves that the heat transfer fluid circulating in the first loop, respectively in the third loop, can be sent to the convergence zone of the main branch or to the secondary section, respectively to the eighth heat exchanger or to the convergence zone of the main branch. Each of these three-way valves comprises an inlet and two outlets.It is possible that depending on one or more parameters of the heat transfer fluid circuit, certain ports may act as inlets or outlets according to a given circulation mode of the heat transfer fluid circuit.

[0025] According to a characteristic of the invention, the second control device may be a three-way valve comprising three ports, at least one port extending the second loop to the sixth heat exchanger and another port being connected to the convergence zone via the junction branch. In a first embodiment of the heat transfer fluid circuit, the second control device, like the first control device and the third control device, is a three-way valve comprising an inlet and two outlets. It is thanks to this three-way valve that the heat transfer fluid circulating in the second loop can be sent to the sixth heat exchanger or to the convergence zone of the main branch.

[0026] According to a characteristic of the invention, the control member may be a three-way valve comprising three ports, at least one port extending the secondary section to the fourth heat exchanger and at least one other port being connected to the bypass branch. Still in the first embodiment of the heat transfer fluid circuit according to the invention, the control member is also a three-way valve channels comprising one inlet and two outlets, thus ensuring the circulation of the heat transfer fluid so as to pass through the fourth heat exchanger or bypass it.

[0027] According to a characteristic of the invention, the first pumping device and / or the second pumping device and / or the third pumping device may be reversible pumps configured to circulate the heat transfer fluid in a first circulation direction or in a second circulation direction opposite to the first circulation direction. In a second embodiment of the heat transfer fluid circuit, at least one of the pumping devices among the first pumping device, the second pumping device and the third pumping device are reversible. In other words, it is possible for these pumping devices to circulate the heat transfer fluid in two circulation directions opposite to each other, in order to guarantee all of the different functions of the heat transfer fluid circuit according to the invention.

[0028] According to a characteristic of the invention, the control member comprises a first non-return valve arranged on the bypass branch and / or a second non-return valve arranged on a pipe of the secondary section which comprises the fourth heat exchanger. Due to the reversibility of certain pumping devices, the control member is composed of several non-return valves ensuring the control of the circulation of the heat transfer fluid, and this according to the direction of circulation of the latter. It is the first non-return valve and the second non-return valve, associated with the direction of circulation of the heat transfer fluid, which ensure the passage or the bypass of the fourth heat exchanger by the heat transfer fluid. The non-return valves are configured to authorize the circulation of the heat transfer fluid in one direction of circulation and to prohibit the circulation of the heat transfer fluid in the opposite direction of circulation.This configuration of the control member is specific to the second embodiment, as opposed to the three-way valve of the first embodiment.

[0029] According to a characteristic of the invention, the second control device comprises a first non-return device arranged on the second loop and / or a second non-return device arranged in the main branch upstream of the second loop. If the third pumping device is a reversible pump, the first non-return device and the second non-return device are arranged so as to circulate the heat transfer fluid towards the sixth heat exchanger or towards the convergence zone of the main branch instead of a three-way valve, and this depending on the direction of circulation of the heat transfer fluid. Just like the non-return valves, the non-return devices are configured to authorize the circulation of the heat transfer fluid in one direction of circulation and to prohibit the circulation of the heat transfer fluid in the opposite direction of circulation.

[0030] Other characteristics and advantages of the invention will become apparent from the following description on the one hand, and from several examples of embodiment given for informational and non-limiting purposes with reference to the appended schematic drawings on the other hand, in which:

[0031] [Fig. 1] represents a heat treatment system comprising a first embodiment of a heat transfer fluid circuit according to the invention,

[0032] [Fig.2] illustrates a first mode of circulation of the fluid(s) circulating in the heat treatment system,

[0033] [Fig.3] illustrates a second mode of circulation of the fluid(s) circulating in the heat treatment system,

[0034] [Fig.4] illustrates a third mode of circulation of the fluid(s) circulating in the heat treatment system,

[0035] [Fig.5] illustrates a fourth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0036] [Fig.6] illustrates a fifth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0037] [Fig.7] illustrates a sixth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0038] [Fig.8] illustrates a seventh mode of circulation of the fluid(s) circulating in the heat treatment system,

[0039] [Fig.9] illustrates an eighth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0040] [Fig. 10] illustrates a ninth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0041] [Fig. 11] illustrates a tenth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0042] [Fig. 12] illustrates an eleventh mode of circulation of the fluid(s) circulating in the heat treatment system,

[0043] [Fig. 13] illustrates a twelfth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0044] [Fig. 14] illustrates a thirteenth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0045] [Fig. 15] represents the heat treatment system comprising a second embodiment of a heat transfer fluid circuit according to the invention,

[0046] [Fig. 16] is a diagram of a secondary section of a first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in a first direction of circulation,

[0047] [Fig. 17] is a diagram of the secondary section of the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in a second direction of circulation, opposite to the first direction of circulation,

[0048] [Fig. 18] is a diagram of the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in the first direction of circulation,

[0049] [Fig. 19] is a variant of the circulation of the heat transfer fluid in the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in the first direction of circulation,

[0050] [Fig.20] is a diagram of the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in the second direction of circulation, opposite to the first direction of circulation,

[0051] [Fig.21] is a diagram of a second loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in the first direction of circulation,

[0052] [Fig.22] is a diagram of the second loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid circulates in the second direction of circulation, opposite to the first direction of circulation.

[0053] The terms upstream and downstream used in the following description refer to the direction of circulation of the fluid in question, i.e. the refrigerant fluid or the heat transfer fluid.

[0054] In Figures 1 and 15, a heat transfer fluid circuit 2 is illustrated in solid lines and a refrigerant fluid circuit 3 is illustrated in dotted lines. In Figures 2 to 14 and 16 to 22, for each of the circuits, the portions traversed by their respective fluid are in solid lines and the portions without fluid circulation are in short dotted lines. Regarding Figures 2 to 14, the solid lines indicating the circulation of fluid are also of different thicknesses concerning the refrigerant fluid circuit 3 when the latter is used. More precisely, the thickest solid lines correspond to portions where the refrigerant circulates at high pressure and the thinnest solid lines correspond to portions where the refrigerant circulates at low pressure.

[0055] [Fig.l] represents a heat treatment system 1 which can be integrated within a motor vehicle and comprising a first embodiment of a heat transfer fluid circuit 2 according to the invention. This heat treatment system 1 is capable of ensuring heat treatment of the passenger compartment of the vehicle, but also heat treatment of different components of a powertrain of the vehicle.

[0056] To do this, the heat treatment system comprises the heat transfer fluid circuit 2 within which a heat transfer fluid circulates, and the refrigerant fluid circuit 3 within which a refrigerant fluid circulates. The treatment system thermal 1 is configured to operate different interactions between the heat transfer fluid and the refrigerant fluid in order to thermally treat the passenger compartment of the vehicle and / or the various components of the vehicle's powertrain in an optimal manner. The heat transfer fluid can for example be glycolated water, while the refrigerant fluid can advantageously be an R290 type fluid, i.e. propane, meeting European environmental protection standards unlike other types of refrigerant fluid used for thermal treatment.

[0057] The heat transfer fluid circuit 2 is divided into several sections fluidically linked together in order to multiply the functionalities of the heat treatment system 1. Thus, the heat transfer fluid circuit comprises in particular a main branch 4 provided with a first heat exchanger 5. The latter is configured to carry out a heat exchange between the heat transfer fluid which circulates therein and an external air flow 6 passing through the first heat exchanger 5. By external air flow, it is necessary to understand an air flow which is not intended to be sent into the passenger compartment of the vehicle. In order to be positioned at the level of a trajectory of the external air flow 6, the first heat exchanger 5 can for example be arranged at the level of a front face of the vehicle.

[0058] The main branch 4 extends between a convergence zone 7 and a divergence zone 8. The convergence zone 7 corresponds to a zone of the main branch 4 comprising one or more convergence points at which one or more heat transfer fluid flows can flow. The divergence zone 8 corresponds to a zone comprising one or more divergence points at which one or more heat transfer fluid flows can be distributed. Thus, the convergence zone 7 is arranged upstream of the first heat exchanger 5, while the divergence zone 8 is arranged downstream of the first heat exchanger 5.

[0059] The heat transfer fluid circuit also comprises a first loop 9 divided into a main section 10 and a secondary section 11. The main section 10 extends between the divergence zone 8 and the convergence zone 7, and comprises a first pumping device 12, a second heat exchanger 13 and a first control device 14.

[0060] The first pumping device 12 allows the heat transfer fluid to be circulated within the first loop 9. The second heat exchanger 13 allows heat treatment of an electric motor of the vehicle by the heat transfer fluid. By circulating in the second heat exchanger 13, the heat transfer fluid is thus able to heat or cool the electric motor depending on their respective temperatures.

[0061] The first control device 14 is arranged downstream of the first pumping device 12 and the second heat exchanger 13. The first control device 14 is in the form of a three-way valve comprising three ports. In the first embodiment of the heat transfer fluid circuit 2, these three ports are an inlet into which the heat transfer fluid from the second heat exchanger 13 enters, a first outlet which extends the main section 10 to the convergence zone 7 of the main branch 4, and a second outlet allowing a fluid connection between the main section 10 and the secondary section 11. The first loop 9 thus comprises a first transfer branch 15 extending between the second outlet of the first control device 14 and the secondary section 11.

[0062] The secondary section 11 comprises a second pumping device 16, an electric heating element 17, a third heat exchanger 18 and a fourth heat exchanger 19. The second pumping device 16 makes it possible to circulate the heat transfer fluid in the secondary section 11, independently of a potential circulation of fluid in the main section 10. The electric heating element 17 makes it possible to heat the heat transfer fluid via an external energy supply to the heat treatment system 1.

[0063] The third heat exchanger 18 is configured to carry out a heat exchange between the heat transfer fluid circulating in the secondary section 11 and the refrigerant fluid circulating in the refrigerant circuit 3. As will be detailed later, the third heat exchanger 18 makes it possible to cool the heat transfer fluid.

[0064] Finally, the fourth heat exchanger 19 allows heat treatment of an electrical storage device of the vehicle by the heat transfer fluid. By circulating in the fourth heat exchanger 19, the heat transfer fluid is thus able to heat or cool the electrical storage device according to their respective temperatures.

[0065] The first loop 9 also comprises a second transfer branch 20 which, like the first transfer branch 15, ensures a fluid connection within the first loop 9 between the main section 10 and the secondary section 11. The two transfer branches 15, 20 make it possible to form a closed circuit composed at least partially of the main section 10 and at least partially of the secondary section 11. Such a configuration makes it possible to multiply the functions of the heat transfer fluid circuit 2 according to the invention.

[0066] The first loop 9 finally comprises a control member 21 arranged on the secondary section 11 downstream of the third heat exchanger 18 and upstream of the fourth heat exchanger 19. The control member 21 is in the form of a three-way valve comprising three ports. In the first embodiment of the heat transfer fluid circuit 2, these three ports are an inlet through which the heat transfer fluid from the third heat exchanger 18 circulates, a first outlet extending the secondary section 11 to the fourth heat exchanger 19 and a second outlet from which a bypass branch 22 begins. The bypass branch 22 is arranged in parallel with the fourth heat exchanger 19 and makes it possible to bypass it when the heat transfer fluid is not intended to thermally treat the electrical storage device.

[0067] The heat transfer fluid circuit 2 also comprises a second loop 23. Just like the first loop 9, the second loop 23 is connected to the divergence zone 8 of the main branch 4. The second loop 23 comprises a third pumping device 24, a fifth heat exchanger 25 and a sixth heat exchanger 26. In addition, the second loop 23 is placed under the control of a second control device 27.

[0068] The third pumping device 24 circulates the heat transfer fluid in the second loop 23. The fifth heat exchanger 25, just like the third heat exchanger 18 of the first loop 9, is configured to carry out a heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit 3. As will be detailed later, the fifth heat exchanger 25 makes it possible to cool the heat transfer fluid.

[0069] The sixth heat exchanger 26 is configured to carry out a heat exchange between the heat transfer fluid and an interior air flow 28. Unlike the exterior air flow 6, the interior air flow 28 is intended to be sent to the passenger compartment of the vehicle in order to heat treat it. As such, the sixth heat exchanger 26 can be arranged within a ventilation, heating and / or air conditioning installation 29 which makes it possible to direct the interior air flow 28 through in particular the sixth heat exchanger 26 before sending it to the passenger compartment of the vehicle. As will be detailed later, the sixth heat exchanger 26 participates in the air conditioning of the passenger compartment of the vehicle.

[0070] The second control device 27 is arranged downstream of the fifth heat exchanger 25 and upstream of the sixth heat exchanger 26. The second control device 27 is in the form of a three-way valve comprising three ports. In the first embodiment of the heat transfer fluid circuit, these three ports are an inlet within which the heat transfer fluid from the fifth heat exchanger 25 circulates, a first outlet which extends the second loop 23 to the sixth heat exchanger 26 and a second outlet through which the heat transfer fluid can circulate to the convergence zone 7 of the main branch 4. As such, the heat transfer fluid circuit 2 comprises a junction branch 30 which extends between the second outlet of the second control device 27 and the convergence zone 7 of the main branch 4. convergence 7 of the main branch 4. The junction branch 30 therefore ensures the fluid connection between the second loop 23 and the main branch 4.

[0071] The heat transfer fluid circuit 2 further comprises a third loop 31 provided with a fourth pumping device 32, a seventh heat exchanger 33, an eighth heat exchanger 34 and a third control device 35. The third loop 31 can be supplied with heat transfer fluid via the divergence zone 8.

[0072] The fourth pumping device 32 is capable of circulating the heat transfer fluid in the third loop 31 while the seventh heat exchanger 33 is configured to carry out a heat exchange between the heat transfer fluid and the refrigerant fluid. As will be detailed later, the seventh heat exchanger 33 allows the heat transfer fluid to be heated.

[0073] Just like the sixth heat exchanger 26, the eighth heat exchanger 34 is configured to carry out a heat exchange between the heat transfer fluid and the interior air flow 28. The eighth heat exchanger 34 is therefore also advantageously arranged within the ventilation, heating and / or air conditioning installation 29. As will be detailed later, the eighth heat exchanger 34 participates in heating the passenger compartment of the vehicle.

[0074] The third control device 35 is arranged downstream of the seventh heat exchanger 33 and upstream of the eighth heat exchanger 34. The third control device 35 is in the form of a three-way valve comprising an inlet where the heat transfer fluid from the seventh heat exchanger 33 circulates, a first outlet which extends the third loop 31 to the eighth heat exchanger 34 and a second outlet through which the heat transfer fluid can circulate to the convergence zone 7 of the main branch 4. As such, the heat transfer fluid circuit 2 comprises a connecting branch 36 which extends between the second outlet of the third control device 35 and the convergence zone 7 of the main branch 4. The connecting branch 36 therefore ensures the fluid connection between the third loop 31 and the main branch 4.

[0075] The set of loops 9, 23, 31 of the heat transfer fluid circuit therefore comprises a branch connecting them directly to the main branch, upstream of the first heat exchanger 5. This characteristic makes it possible to multiply the possible operating modes of the heat transfer fluid circuit 2, while maintaining a simple architecture.

[0076] The refrigerant circuit 3 comprises a main path 37 provided with a compression device 38 circulating the refrigerant in the refrigerant circuit. The main path 37 extends until it passes through the seventh heat exchanger 33, then separates into a first path 43 comprising a first expansion member 39 and a second channel 40 comprising a second expansion member 41.

[0077] Each of the expansion members 39, 41 ensures an expansion of the refrigerant fluid which then drops in pressure and temperature. Subsequently, the refrigerant fluid can pass through the third heat exchanger 18 or the fifth heat exchanger 25 depending on the path in which the refrigerant fluid circulates. This choice of path is obviously dependent on the objectives that the heat treatment system 1 must fulfill.

[0078] Subsequently, the first path 43 and the second path 40 join to reform the main path 37. The compression device 38 being capable of compressing only refrigerant fluid in the gaseous state, the refrigerant fluid circuit 3 can advantageously comprise an accumulation device 42 arranged on the main path upstream of the compression device 38 in order to retain a liquid fraction of the refrigerant fluid before it passes through the compression device 38 and damages it.

[0079] The refrigerant fluid being advantageously propane, there is no question of circulating it within the ventilation, heating and / or air conditioning installation 29 for safety reasons. Thus, as illustrated in [Fig.l], only the heat transfer fluid circulates within the ventilation, heating and / or air conditioning installation 29.

[0080] [Fig. 2] illustrates a first mode of circulation of the fluid(s) within the heat treatment system 1. In this circulation mode and in each of the following ones, one or more heat treatment objectives are resolved by the heat treatment system. The different circulation modes presented below are not exhaustive and can even be combined with each other in order to accomplish more objectives simultaneously.

[0081] In [Fig.2], the objective is to heat the passenger compartment of the vehicle by means of the interior air flow 28. The heat transfer fluid therefore circulates within at least the third loop 31. The fourth pumping device 32 circulates the heat transfer fluid, and the latter passes through the seventh heat exchanger 33.

[0082] In order to heat the heat transfer fluid so that the latter subsequently releases its calories to the internal air flow 28, the refrigerant circuit 3 is also started using the compression device 38. This compresses the refrigerant at high pressure, which causes its temperature to rise. The refrigerant can thus condense by releasing its calories to the heat transfer fluid within the seventh heat exchanger 33.

[0083] At the outlet of the seventh heat exchanger 33, the hot heat transfer fluid circulates to the third control device 35 which directs the hot heat transfer fluid to the eighth heat exchanger 34. By passing through the latter, the calories of the heat transfer fluid- The air from the carrier is transferred to the interior air flow 28, which is then sent into the passenger compartment of the vehicle to heat the latter.

[0084] The refrigerant having been used to heat the heat transfer fluid within the seventh heat exchanger 33, the thermodynamic cycle of the refrigerant must be continued in order to maintain the effectiveness of the heat treatment. To do this, the at least partially condensed refrigerant continues its circulation within the main path 37, then the first path 43. The refrigerant is then expanded by the first expansion member 39 and passes through the third heat exchanger 18.

[0085] Simultaneously with this, another heat transfer fluid loop is put into circulation, at the secondary section 11 of the first loop 9. The second pumping device 16 puts the heat transfer fluid into circulation, and the electric heating element 17 is activated in order to heat the heat transfer fluid circulating in the secondary section 11. The heated heat transfer fluid then passes through the third heat exchanger 18. The heat exchange occurring in the third heat exchanger 18 therefore makes it possible to complete the thermodynamic cycle of the refrigerant fluid by evaporating the latter thanks to the heated heat transfer fluid.

[0086] The evaporated refrigerant fluid can then circulate to the compression device 38, the accumulation device 42 possibly being able to retain a liquid fraction of the refrigerant fluid. The heat transfer fluid circulates in the secondary section 11 until it reaches the second pumping device 16 again. Since the electrical storage device does not require heat treatment, the control member 21 directs the heat transfer fluid to the bypass branch 22.

[0087] [Fig. 3] illustrates a second mode of circulation of the fluid(s) within the heat treatment system 1. In [Fig. 3], the electrical storage device needs to be heated. This may be necessary, for example, when starting the vehicle and / or in the event of low ambient temperature. [Fig. 3] illustrates a circulation mode ensuring the heating of the electrical storage device, but as will be detailed later, several circulation modes make it possible to meet this objective.

[0088] The electrical storage device is here heated only using the electric heating element 17. This circulation mode therefore does not require circulation of the refrigerant fluid. Only the heat transfer fluid circulates within the secondary section 11 using the second pumping device 16. The heat transfer fluid is therefore heated by the electric heating element 17 and passes through the third heat exchanger 18 without heat exchange, the refrigerant fluid not circulating.

[0089] Subsequently, the control member 21 directs the heat transfer fluid towards the fourth heat exchanger 19 which passes through the latter in order to transfer its calories to the device electrical storage which is then heated. Subsequently, the heat transfer fluid circulates again to the second pumping device 16.

[0090] [Fig.4] illustrates a third mode of circulation of the fluid(s) within the heat treatment system 1. For this circulation mode, the electrical storage device needs to be cooled. As with the previous circulation modes, the heat transfer fluid circulates within the secondary section 11 of the first loop via the second pumping device 16. The heat transfer fluid then passes through the electric heating element 17 but since the latter is inactive, the heat transfer fluid remains at the same temperature.

[0091] The heat transfer fluid is, on the other hand, cooled within the third heat exchanger 18 by means of the refrigerant fluid circulating in the first path 43 and previously expanded by the first expansion member 39. The cooled heat transfer fluid then circulates to the fourth heat exchanger 19 in order to capture the calories from the electrical storage device and thus cool the latter, before being pumped again by the second pumping device 16.

[0092] In order to operate an optimal thermodynamic cycle, the compressed refrigerant fluid must be condensed before being expanded and evaporated to cool the heat transfer fluid circulating in the third heat exchanger 18. To do this, another heat transfer fluid loop must be implemented in order to condense the refrigerant fluid within the seventh heat exchanger 33. The fourth pumping device 32 circulates the heat transfer fluid which then passes through the seventh heat exchanger 33 in order to capture the calories from the high-pressure refrigerant fluid to condense the latter. The heat transfer fluid subsequently circulates to the third control device 35 which this time directs the heat transfer fluid within the connection branch 36 to the convergence zone 7 of the main branch 4.This allows the heat transfer fluid to pass through the first heat exchanger 5 so that the outside air flow 6 dissipates the calories of the heat transfer fluid captured during the heat exchange carried out within the seventh heat exchanger 33.

[0093] At the outlet of the first heat exchanger 5, the heat transfer fluid continues its circulation in the main branch 4 up to the divergence zone 8 and can recirculate within the third loop 31 to be pumped again by the fourth pumping device 32.

[0094] [Fig.5] illustrates a fourth mode of circulation of the fluid(s) within the heat treatment system 1. This fourth circulation mode is similar to the third circulation mode except that it is the passenger compartment of the vehicle that needs to be cooled and not the electrical storage device.

[0095] As a result, there is no circulation of heat transfer fluid within the first loop 9. The refrigerant fluid must, however, also be condensed when passing through the seventh heat exchanger 33 in order to respect the thermodynamic cycle, therefore the circulation of the heat transfer fluid within the seventh heat exchanger 33 and the first heat exchanger 5 as described in [Fig.4] is always implemented and we will refer to the description of [Fig.4] concerning the details of this heat exchange.

[0096] The condensed refrigerant fluid continues its circulation in the main path 37 then within the second path 40 in order to be expanded by the second expansion member 41 and to pass through the fifth heat exchanger 25 to be evaporated there then compressed again by the compression device 38.

[0097] In parallel, the heat transfer fluid is circulated within the second loop 23 by the third pumping device 24 and passes through the fifth heat exchanger 25 to be cooled by the expanded refrigerant. The cooled heat transfer fluid then circulates to the second control device 27 which directs the cooled heat transfer fluid to the sixth heat exchanger 26. By circulating within the sixth heat exchanger 26, the heat transfer fluid then cools the interior air flow 28 and the latter is then sent into the passenger compartment of the vehicle to air-condition it. At the outlet of the sixth heat exchanger 26, the heat transfer fluid is again pumped by the third pumping device 24.

[0098] [Fig.6] illustrates a fifth mode of circulation of the fluid(s) within the heat treatment system 1. The objective of this fifth mode of circulation is to carry out passive cooling of the electric motor by means of the heat transfer fluid and the first heat exchanger 5.

[0099] To do this, the heat transfer fluid circuit 2 is configured so that the heat transfer fluid circulates in a loop in the main section 10 of the first loop 9 and in the main branch 4. The heat transfer fluid is circulated by the first pumping device 12 then captures the calories generated by the electric motor by circulating in the second heat exchanger 13. Subsequently, the heat transfer fluid travels through the entirety of the main section 10 until it reaches the convergence zone 7 to continue its circulation within the main branch 4.

[0100] The heat transfer fluid then circulates within the first heat exchanger 5 and the calories of the electric motor captured by the heat transfer fluid are then dissipated by the flow of external air 6 passing through the first heat exchanger 5. Subsequently the heat transfer fluid circulates to the divergence zone 8 and recirculates in the main section 10 while being pumped again by the first pumping device 12.

[0101] The electric motor is thus passively cooled by transferring its calories to the heat transfer fluid, and said calories are dissipated by the external air flow 6 thanks to the circulation of the heat transfer fluid having stored said calories at the level of the second heat exchanger 13.

[0102] [Fig.7] illustrates a sixth mode of circulation of the fluid(s) within the heat treatment system 1. This sixth circulation mode is actually a combination of the third circulation mode and the fifth circulation mode, i.e. cooling of the electrical storage device using the refrigerant fluid and passive cooling of the electric motor simultaneously.

[0103] At the divergence zone 8, the heat transfer fluid is therefore distributed between the main section 10 of the first loop 9 and the third loop 31. The heat transfer fluid is therefore circulated by the first pumping device 12 and by the fourth pumping device 32. In both cases, calories are captured by the heat transfer fluid, that is to say the calories generated by the electric motor, or the calories of the high-pressure refrigerant fluid compressed by the compression device 38 and circulating in the refrigerant circuit 3. Subsequently, in either case, the heat transfer fluid joins the convergence zone 7 to circulate within the main branch 4 and the first heat exchanger 5 so that the calories captured within the second heat exchanger 13 or the seventh heat exchanger 33 are dissipated by the outside air flow 6.The heat transfer fluid is subsequently redistributed within the main section 10 or the third loop 31 via the divergence zone 8.

[0104] The electrical storage device is cooled by means of the heat transfer fluid circulating in the secondary section 11 of the first loop 9 and previously cooled within the third heat exchanger 18 by the expanded refrigerant. The electric heating element 17 is of course inactive. As described above, the heat exchange ensuring the cooling of the electrical storage device takes place within the fourth heat exchanger 19. The refrigerant fluid operates its cooling function optimally because it has been previously at least partially condensed within the seventh heat exchanger 33 by the heat transfer fluid circulating in the third loop 31.

[0105] Concerning the sixth mode of circulation, one can refer to the description of figures 4 and 6 for further details.

[0106] [Fig.8] illustrates a seventh mode of circulation of the fluid(s) within the heat treatment system 1. The objective of this seventh circulation mode is to heat the passenger compartment of the vehicle. The heat transfer fluid therefore circulates within the third loop 31, is heated within the seventh heat exchanger 33 by the high-pressure refrigerant compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the interior air flow 28 passing through the eighth heat exchanger 34. The interior air flow 28 is thus heated and is sent into the passenger compartment of the vehicle.

[0107] Just like the first mode of circulation whose objective was also to heating the vehicle interior, the refrigerant was used to heat the heat transfer fluid through the seventh heat exchanger 33, and the thermodynamic cycle of the refrigerant must be continued in order to maintain the effectiveness of the heat treatment.

[0108] Unlike the first circulation mode where the expanded refrigerant was evaporated in the third heat exchanger 18 via the heat transfer fluid previously heated using the electric heating element 17, the seventh circulation mode takes advantage of the heat from the electric motor to heat the heat transfer fluid. This makes it possible to avoid an additional energy input to power the electric heating element 17.

[0109] To do this, the first transfer branch 15 and the second transfer branch 20 are used to form a junction between the main section 10 and the secondary section 11 of the first loop 9. The transfer branches 15, 20 thus provide a direct fluid connection between the second heat exchanger 13 and the third heat exchanger 18. The first control member 14 is also used to direct the heat transfer fluid coming from the main section 10 to the first transfer branch 15.

[0110] The heat transfer fluid is circulated by the first pumping device 12 and circulates within the second heat exchanger 13 to capture the calories from the electric motor which emits heat due to its operation. The heat transfer fluid then circulates to the first control device 14 which directs it to the first transfer branch 15. The heat transfer fluid therefore circulates from the main section 10 to the secondary section 11.

[0111] The heat transfer fluid subsequently transfers the calories captured from the electric motor to the refrigerant fluid, during the heat exchange occurring within the third heat exchanger 18. The refrigerant fluid is thus evaporated and its thermodynamic cycle is completed, thus optimizing the thermal performance of the heat treatment system 1. At the outlet of the third heat exchanger 18, the heat transfer fluid circulates in the bypass branch 22 to bypass the fourth heat exchanger 19 because the electrical storage device does not require heat treatment, then circulates within the second transfer branch 20 in order to return to the main section 10 and be pumped by the first pumping device 12.

[0112] [Fig.9] illustrates an eighth mode of circulation of the fluid(s) within the heat treatment system 1. Just as for the seventh mode of circulation, the eighth mode of circulation ensures the heating of the passenger compartment of the vehicle, but instead of subsequently using the heat from the electric motor to evaporate the refrigerant, it is the heat emitted by the electrical storage device which is used.

[0113] The circulation of the heat transfer fluid takes place here entirely in the secondary section 11 and the heat transfer fluid is circulated by the second pumping device 16. The heat transfer fluid captures the calories generated by the electrical storage device by circulating within the fourth heat exchanger 19 and continues its circulation in the secondary section 11 to the third heat exchanger 18 to transfer the calories to the refrigerant fluid. In [Fig.9], the electric heating element 17 is inactive, but it is possible to activate it to further raise the temperature of the heat transfer fluid before it circulates in the third heat exchanger 18.

[0114] In a circulation mode not shown, it is possible to combine the seventh circulation mode and the eighth circulation mode in order to recover both the heat generated by the electric motor and the heat generated by the electrical storage device. In this circulation mode, the heat transfer fluid circulates in the first loop, captures the heat from the electrical storage device by circulating in the fourth heat exchanger 19, and separates into two fractions at the second transfer branch 20. One of the fractions continues its circulation in the secondary section 11 while the other fraction joins the main section 10 via the second transfer branch 20 and circulates in the second heat exchanger 13 to capture the calories generated by the electric motor. The two fractions subsequently join upstream of the third heat exchanger 18.

[0115] [Fig. 10] illustrates a ninth mode of circulation of the fluid(s) within the heat treatment system 1. The objective of this circulation mode is to heat the electrical storage device using the heat emitted by the electric motor. This circulation mode is therefore particularly advantageous because it is thus not necessary to use the refrigerant circuit 3.

[0116] The transfer branches 15, 20 are once again used to form the junction between the main section 10 and the secondary section 11 of the first loop 9. The heat transfer fluid is circulated by the first pumping device 12, captures the calories generated by the electric motor by circulating within the second heat exchanger 13, then circulates in the first transfer branch 15 to reach the secondary section 11.

[0117] The heat transfer fluid then passes through the third heat exchanger 18 without consequences given that the refrigerant circuit 3 is inactive, then circulates to the fourth heat exchanger 19 to transfer said calories to the electrical storage device to heat the latter. Subsequently, the heat transfer fluid reaches the main section 10 thanks to the second transfer branch 20.

[0118] [Fig. 11] illustrates a tenth mode of circulation of the fluid(s) within the heat treatment system 1. The objective here is to defrost the first heat exchanger 5 when the ambient temperature is very low.

[0119] To do this, the heat transfer fluid circulates between the third loop 31 and the main branch 4 via the connecting branch 36. The aim is to heat the heat transfer fluid within the seventh heat exchanger 33 via the refrigerant compressed by the compression device 38. The heated heat transfer fluid then leaves the third loop 31 via the connecting branch 36 and joins the main branch 4 via the convergence zone 7.

[0120] Then, the hot heat transfer fluid circulates in the first heat exchanger 5 in order to defrost it, and again joins the third loop 31 via the divergence zone 8.

[0121] The completion of the thermodynamic cycle of the refrigerant fluid is done as for example for the first circulation mode, that is to say that the evaporation of the expanded refrigerant fluid takes place within the third heat exchanger 18. The heat transfer fluid ensuring the evaporation of the refrigerant fluid circulates in the secondary section 11 of the first loop 9, is preheated using the electric heating element 17 and bypasses the fourth heat exchanger 19 thanks to the bypass branch 22.

[0122] In a circulation mode not shown, the defrosting of the first heat exchanger 5 can be done using the heat generated by the electric motor. This circulation mode is strictly identical to the fifth circulation mode shown in [Fig.6], i.e. the refrigerant circuit 3 is inactive and the heat transfer fluid circulates between the main branch 4 and the main section 10 of the first loop 9.

[0123] Instead of cooling the electric motor using the outside air flow 6 as described in [Fig.6], in this circulation mode not illustrated it is the first heat exchanger 5 which is defrosted using the heat generated by the heat engine and captured by the heat transfer fluid during its circulation within the second heat exchanger 13.

[0124] In another circulation mode not illustrated, it is possible to combine the two defrosting modes previously described, that is to say the tenth circulation mode with the circulation mode not illustrated described above, in order to improve the defrosting of the first heat exchanger 5. The heat transfer fluid thus separates into two fractions, one of which is heated by the refrigerant fluid via the seventh heat exchanger 33, while the other captures the calories generated by the electric motor by circulating within the second heat exchanger 13. The two fractions of heated heat transfer fluid then join at the convergence zone 7 and then carry out defrosting by circulating within the first heat exchanger 5.

[0125] [Fig. 12] illustrates an eleventh mode of circulation of the fluid(s) within the heat treatment system 1. This circulation mode consists of heating the passenger compartment of the vehicle and evaporating the refrigerant fluid using the third heat exchanger 18 while heating the electrical storage device in particular using the heat generated by the electric motor.

[0126] Just as for the circulation modes described previously and having in particular the objective of heating the passenger compartment of the vehicle, the heat transfer fluid circulates within the third loop 31, is heated within the seventh heat exchanger 33 by the high-pressure refrigerant compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the interior air flow 28 passing through the eighth heat exchanger 34. The interior air flow 28 is thus heated and is sent into the passenger compartment of the vehicle.

[0127] The condensed refrigerant fluid then circulates within the first path 43, is expanded by the first expansion member 39 and is evaporated within the third heat exchanger 18 by the heat transfer fluid. The refrigerant fluid then circulates to the compression device 38.

[0128] In order to store enough calories to both evaporate the refrigerant and subsequently heat the electrical storage device, the assistance of the electric heating element 17 and the heat generated by the electric motor is necessary. The heat transfer fluid circulating in the first loop 9 then separates into two fractions. The first fraction circulates in the second transfer branch 20, is pumped by the first pumping device 12 and circulates within the second heat exchanger 13 to capture the calories generated by the electric motor and then join the secondary section 11 via the first transfer branch 15. The second fraction is pumped by the second pumping device 16 and is heated by the electric heating element 17.Subsequently, the two fractions of heat transfer fluid, both heated, join and circulate together within the third heat exchanger 18 to evaporate the refrigerant fluid. Thanks to the contribution of the two fractions of heat transfer fluid and their respective calories captured previously, the heat transfer fluid leaves the third heat exchanger 18 still sufficiently hot to circulate within the fourth heat exchanger 19 and release the remaining calories to heat the electrical storage device. At the outlet of the fourth heat exchanger 19, the heat transfer fluid continues its circulation in the secondary section 11 until it separates again into two fractions.

[0129] The distribution of the heat transfer fluid between the two heat transfer fluid fractions can be regulated to optimize the temperature of the heat transfer fluid. This distribution can for example depend on the temperature of the electric motor, which can encourage send more heat transfer fluid through the second heat exchanger 13 if said temperature is very high. The heating power of the electric heating element 17 can also be modulated according to the need. The regulation of the distribution of the heat transfer fluid can for example be carried out by the pumping devices 12, 16 if the pumping speed of these can be modified.

[0130] [Fig. 13] illustrates a twelfth mode of circulation of the fluid(s) within the heat treatment system 1. The purpose of this twelfth mode of circulation is to dehumidify the interior air flow 28 intended to be sent into the passenger compartment of the vehicle. The dehumidification consists of circulating heat transfer fluid both within the sixth heat exchanger 26 and the eighth heat exchanger 34 in order to dehumidify the interior air flow 28. This method avoids sending a humid air flow into the passenger compartment which can cause several disadvantages such as the formation of fog on the vehicle windows which can impair visibility, or even discomfort for the occupants of the passenger compartment of the vehicle. In [Fig. 13], the dehumidification method is coupled with passive cooling of the electric motor, but the dehumidification can quite easily be implemented alone.

[0131] For this twelfth circulation mode, the heat transfer fluid circulates in particular within the third loop 31. After having been put into circulation by the fourth pumping device 32, the heat transfer fluid is heated within the seventh heat exchanger 33 by the high-pressure refrigerant fluid compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the internal air flow 28 passing through the eighth heat exchanger 34.

[0132] In parallel, heat transfer fluid is also circulated within the second loop 23 by the third pumping device 24 and passes through the fifth heat exchanger 25 to be cooled by the expanded refrigerant. The cooled heat transfer fluid then circulates to the sixth heat exchanger 26. By circulating within the sixth heat exchanger 26, the heat transfer fluid then cools the interior air flow 28.

[0133] Thus, before being sent into the passenger compartment of the vehicle, the interior air flow 28 is first cooled by passing through the sixth heat exchanger 26. The cooling of the interior air flow 28 makes it possible to condense the humidity present therein and to retain it. The interior air flow 28 thus leaves the sixth heat exchanger 26 cold and dry.

[0134] Then, the objective being to heat the passenger compartment of the vehicle while dehumidifying it, the interior air flow 28 passes through the eighth heat exchanger 34 to be heated there. The interior air flow 28 is thus sent into the passenger compartment of the hot and dry vehicle.

[0135] Thanks to the dehumidification method, the management of the refrigerant circuit 3 is simplified. Indeed, after having been compressed by the compression device 38, the refrigerant is condensed within the seventh heat exchanger 33 and transfers its calories to the heat transfer fluid intended to heat the interior air flow 28. The refrigerant then circulates within the second path 40, is expanded by the second expansion member 41, and is evaporated within the fifth heat exchanger 25, making it possible to cool the heat transfer fluid intended to cool the interior air flow 28. The evaporated refrigerant then continues its circulation until it is again compressed by the compression device 38.The dehumidification process is therefore sufficient for the refrigerant fluid to operate a complete thermodynamic cycle and it is therefore not necessary to implement other functions of the heat transfer fluid circuit 2 to complete this thermodynamic cycle.

[0136] Optionally, the heat transfer fluid circuit, in parallel with the dehumidification process, can operate passive cooling of the electric motor. The circulation of the heat transfer fluid is identical to that illustrated in [Fig.6]. The heat transfer fluid circulates in the main section 10 of the first loop 9 and cools the electric motor by capturing its calories within the second heat exchanger. The heat transfer fluid then joins the main branch 4 and circulates within the first heat exchanger 5, where the outside air flow 6 allows the calories of the heat transfer fluid to be dissipated. The heat transfer fluid then joins the main section 10 via the divergence zone 8.

[0137] [Fig. 14] illustrates a thirteenth mode of circulation of the fluid(s) within the heat treatment system 1. This mode of circulation consists of heating the passenger compartment of the vehicle and evaporating the refrigerant fluid using the fifth heat exchanger 25.

[0138] Just as for the circulation modes described previously and having in particular the objective of heating the passenger compartment of the vehicle, the heat transfer fluid circulates within the third loop 31, is heated within the seventh heat exchanger 33 by the high-pressure refrigerant compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the interior air flow 28 passing through the eighth heat exchanger 34. The interior air flow 28 is thus heated and is sent into the passenger compartment of the vehicle.

[0139] To evaporate the refrigerant fluid previously condensed by its heat exchange within the seventh heat exchanger 33, the refrigerant fluid circulates this path within the second path 40, is expanded by the second expansion member 41 and is evaporated within the fifth heat exchanger 25.

[0140] For the evaporation of the refrigerant fluid, another heat transfer fluid loop is formed, said other loop being formed from the main branch 4 and a portion of the second loop 23, the latter and the main branch 4 being fluidically linked by means of the junction branch 30. The heat transfer fluid is thus put into circulation by the third pumping device 24 and captures the calories from the expanded refrigerant fluid by circulating within the fifth heat exchanger 25.

[0141] The heat transfer fluid then circulates to the second control device 27 which guides it within the recovery branch 30. The heat transfer fluid subsequently joins the main branch 4 via the convergence zone 7. The captured calories are then dissipated when the heat transfer fluid circulates within the first heat exchanger 5 and the latter is crossed by the outside air flow 6. As the heating of the passenger compartment is active, this means that the ambient temperature is relatively low. The outside air flow 6 therefore offers a very good means of dissipating the calories of the heat transfer fluid, thus optimizing the thermodynamic cycle of the refrigerant fluid. At the outlet of the first heat exchanger 5, the heat transfer fluid continues its circulation in the main branch 4 and joins the second loop 23 via the divergence zone 8.

[0142] [Fig. 15] represents a heat treatment system 1 comprising a second embodiment of the heat transfer fluid circuit 2. This second embodiment differs from the first embodiment illustrated previously in particular in that the first pumping device 12, the second pumping device 16 and the third pumping device 24 are reversible pumps. In other words, the first pumping device 12, the second pumping device 16 and the third pumping device 24 are capable of circulating the heat transfer fluid in two directions of circulation. Furthermore, the control member 21 is no longer in the form of a three-way valve but in the form of two non-return valves 53, 54. The second control device 27 is in the form of two non-return devices 56, 57 instead of a three-way valve.

[0143] The first control device 14 is still in the form of a three-way valve, but depending on the circulation mode applied to the heat treatment system 1, some of the ports of the first control device 14 can act as inlets or outlets.

[0144] As will be described subsequently, the heat treatment system 1 provided with the second embodiment of the heat transfer fluid circuit 2 is capable of applying all of the circulation modes applicable by the heat treatment system 1 provided with the first embodiment of the heat transfer fluid circuit 2 and described previously. The second embodiment is therefore distinguished from the first embodiment only on a structural level.

[0145] At the level of the secondary section 11 of the first loop 9, the control member 21 comprises a first non-return valve 53 arranged on the bypass branch 22 and a second non-return valve 54 arranged on a pipe 55 at which the fourth heat exchanger 19 is arranged. In this second embodiment, it is the positioning of the non-return valves 53, 54 as well as the direction of circulation of the heat transfer fluid which determines whether, in the case of circulation in the secondary section 11, the heat transfer fluid circulates within the fourth heat exchanger 19 or bypasses the latter by circulating within the bypass branch 22. The direction of circulation of the heat transfer fluid in the secondary section 11 is determined by the first pumping device 12 and / or by the second pumping device 16.

[0146] The first transfer branch 15 and the second transfer branch 20 are structurally identical compared to the first embodiment, but due to the reversibility of the first pumping device 12 and the second pumping device 16, the transfer branches 15, 20 can be traversed by the heat transfer fluid in two directions of circulation, unlike the first embodiment.

[0147] As mentioned previously, the third pumping device 24 is also a reversible pump. The second control device 27, governing the circulation of heat transfer fluid in the second loop 23, comprises a first non-return device 56 arranged on the second loop 23 and a second non-return device 57 arranged on the main branch 4, at the divergence zone 8 upstream of the second loop 23. Just as for the first loop 9, it is the direction of circulation of the heat transfer fluid defined by the third pumping device 24 associated with the positioning of the non-return devices 56, 57.

[0148] The rest of the elements of the heat treatment system 1 being identical to those of the heat treatment system 1 provided with the first embodiment of the heat transfer fluid circuit 2, reference will be made to the description of [Fig.l] concerning the details relating to the elements common to the two embodiments of the heat transfer fluid circuit.

[0149] Figures 16 to 22 illustrate portions of the heat transfer fluid circuit detailing the circulation of the heat transfer fluid as a function of a circulation direction 58, 59 of said heat transfer fluid. For each of Figures 16 to 22, the circulation direction 58, 59 is indicated by an arrow, and by a color code of the pumping device 12, 16, 24 considered. As for Figures 2 to 14, the circulation of heat transfer fluid is represented by solid lines and the portions without circulation of heat transfer fluid are represented by short dotted lines.

[0150] [Fig. 16] is a representation of the secondary section 11 alone. For Figures 16 and 17, the direction of circulation of the heat transfer fluid is defined by the second pumping device 16. In [Fig. 16], the direction of circulation of the heat transfer fluid is defined by the white arrow of the second pumping device 16. The fluid ca- The heat transfer fluid therefore circulates in a first direction of circulation 58 and the non-return valves 53, 54 are arranged so that the heat transfer fluid circulates within the fourth heat exchanger 19. The first non-return valve 53 in fact prevents the circulation of the heat transfer fluid within the bypass branch 22 at the outlet of the third heat exchanger 18 and forces the circulation of the heat transfer fluid within the fourth heat exchanger 19.

[0151] Referring to the circulation modes previously described, as non-exhaustive examples, the circulation direction illustrated in [Fig. 16] is defined to implement the second circulation mode illustrated in [Fig. 3], where the electrical storage device is heated by the electric heating element 17, or to implement the third and sixth circulation modes illustrated respectively in Figures 4 and 7, where the electrical storage device is cooled using the third heat exchanger 18. This circulation direction is also defined to implement the eighth circulation mode illustrated in [Fig. 9], where the heat generated by the electrical storage device is used to evaporate the refrigerant via the third heat exchanger 18.

[0152] [Fig. 17] still illustrates the secondary section 11 of the first loop 9, but this time when the heat transfer fluid circulates in a second direction of circulation 59 opposite to the first direction of circulation 58 illustrated in [Fig. 16].

[0153] When the heat transfer fluid circulates in the secondary section 11 of the first loop 9 in the second direction of circulation 59, the second non-return valve 54 prevents the circulation of the heat transfer fluid within the pipe 55 at the level of which the fourth heat exchanger 19 is arranged. The circulation of the heat transfer fluid is therefore forced within the bypass branch 22 and the heat transfer fluid therefore bypasses the fourth heat exchanger 19.

[0154] Referring to the circulation modes previously described, as non-exhaustive examples, the circulation direction illustrated in [Fig. 17] is defined to implement the first circulation mode illustrated in [Fig. 2] or the tenth circulation mode illustrated in [Fig. 11]. For these two circulation modes, the electric heating element 17 is used to heat the heat transfer fluid which subsequently ensures the evaporation of the refrigerant by circulating within the third heat exchanger 18.

[0155] [Fig. 18] represents the first loop 9 in its entirety, with the main section 10 and the secondary section 11. In Figures 18 to 20, the direction of circulation of the heat transfer fluid is defined at least by the white arrow of the first pumping device 12.

[0156] In [Fig. 18], the heat transfer fluid circulates in the first loop 9 according to the first direction of circulation 58. Just as was described in [Fig.16], the first direction of circulation 58 allows the heat transfer fluid to circulate within the fourth heat exchanger 19 and not in the bypass branch 22.

[0157] For this configuration, the heat transfer fluid circulates in the first transfer branch 15 from the main section 10 to the secondary section 11 and in the second transfer branch 20 from the secondary section 11 to the main section 10. The second pumping device 16 is inactive.

[0158] The configuration illustrated in [Fig. 18] is used to implement in particular the ninth circulation mode illustrated in [Fig. 10], during which the heat generated by the electric motor is captured by the heat transfer fluid circulating in the second heat exchanger 13, then is transmitted to heat the electrical storage device when the heat transfer fluid circulates within the fourth heat exchanger 19.

[0159] [Fig. 19] is a variant of what is illustrated in [Fig. 18], where the second pumping device 16 is also active in addition to the first pumping device 12 and also circulates the heat transfer fluid in the first circulation direction 58. The heat transfer fluid therefore always circulates within the fourth heat exchanger 19.

[0160] The configuration illustrated in [Fig. 19] is used to implement in particular the eleventh circulation mode illustrated in [Fig. 12], during which the heat transfer fluid is divided into two fractions, one of which captures the heat generated by the electric motor by circulating in the second heat exchanger 13 while the other is heated by the electric heating element 17, and this with the aim of both evaporating the refrigerant fluid by circulating within the third heat exchanger 18 and heating the electrical storage device by circulating within the fourth heat exchanger 19.

[0161] [Fig.20] still illustrates the first loop 9 in its entirety, but this time when the heat transfer fluid circulates in the second direction of circulation 59 opposite to the first direction of circulation 58 illustrated in Figures 18 and 19. The second direction of circulation 59 is here imposed by the first pumping device 12.

[0162] With respect to Figures 18 and 19, the heat transfer fluid circulates in the transfer branches 15, 20 in a reverse direction of circulation. In other words, the heat transfer fluid circulates in the second transfer branch 20 from the main section 10 to the secondary section 11 and in the first transfer branch 15 from the secondary section 11 to the main section 10. In addition, with respect to Figures 18 and 19, the ports of the first control device 14 within which the heat transfer fluid circulates reverse their function, that is to say that an inlet port becomes an outlet port and vice versa.

[0163] As described in [Fig.17], when the heat transfer fluid circulates in the secondary section 11 according to the second direction of circulation 59, the heat transfer fluid bypasses the fourth heat exchanger 19 by circulating in the bypass branch 22. The second pumping device 16 is inactive here.

[0164] The configuration illustrated in [Fig.20] is used to implement in particular the seventh circulation mode illustrated in [Fig.8], during which the heat generated by the electric motor by circulating in the second heat exchanger 13 is used to evaporate the refrigerant fluid within the third heat exchanger 18. According to a circulation mode not illustrated, the configuration illustrated in [Fig.20] can also be used to operate cooling of the electric motor via the second heat exchanger 13 using the third heat exchanger 18.

[0165] [Fig. 21] is a representation of the second loop 23 alone. For figures 21 and 22, the direction of circulation of the heat transfer fluid is defined by the third pumping device 24. In [Fig. 21], the direction of circulation of the heat transfer fluid is defined by the white arrow of the third pumping device 24. The heat transfer fluid therefore circulates according to the first direction of circulation 58. It should be noted that the directions of circulation 58, 59 of the heat transfer fluid within the second loop 23 illustrated in figures 21 and 22 are completely independent of the directions of circulation 58, 59 of the heat transfer fluid within the first loop 9 illustrated in figures 16 to 20.

[0166] When the heat transfer fluid circulates within the second loop 23 in the first direction of circulation 58, the non-return devices 56, 57 are arranged so that the heat transfer fluid circulates to the junction branch 30 without passing through the sixth heat exchanger 26. The first non-return device 56 in fact prevents the circulation of the heat transfer fluid within the sixth heat exchanger 26 at the outlet of the fifth heat exchanger 25 and forces the circulation of the heat transfer fluid within the junction branch 30.

[0167] Referring to the circulation modes previously described, as non-exhaustive examples, the circulation direction illustrated in [Fig. 21] is defined to implement the thirteenth circulation mode illustrated in [Fig. 14], where the refrigerant is evaporated using the heat transfer fluid circulating within the fifth heat exchanger 25, the heat transfer fluid subsequently circulating to the main branch via the junction branch 30 so that the calories captured within the fifth heat exchanger 25 are dissipated by the flow of outside air within the first heat exchanger, as illustrated in [Fig. 14].

[0168] [Fig.22] still illustrates the second loop 23, but this time when the heat transfer fluid circulates in the second direction of circulation 59 opposite to the first direction of circulation 58 illustrated in [Fig.21].

[0169] When the heat transfer fluid circulates in the second loop 23 in the second direction of circulation 59, the second non-return device 57 prevents the circulation of the heat transfer fluid within the main branch via the divergence zone 8. The circulation of the heat transfer fluid is therefore forced within the second loop 23 up to the sixth heat exchanger 26.

[0170] The circulation of the heat transfer fluid in the second direction of circulation 59 within the second loop 23 allows circulation of the heat transfer fluid within the sixth heat exchanger 26 in order to operate air conditioning of the passenger compartment of the vehicle or to participate in dehumidification of the interior air flow 28. The direction of circulation illustrated in [Fig. 22] is therefore defined to implement, by way of example, the fourth circulation mode illustrated in [Fig. 5], or the twelfth circulation mode illustrated in [Fig. 13].

[0171] Of course, the invention is not limited to the examples which have just been described and numerous adjustments can be made to these examples without departing from the scope of the invention.

[0172] The invention, as just described, achieves the aim it set itself, and makes it possible to propose a heat transfer fluid circuit meeting the condition of avoiding circulation of refrigerant fluid within a ventilation, heating and / or air conditioning installation, while combining structural simplicity and multiplicity of functions. Variants not described here could be implemented without departing from the context of the invention, provided that, in accordance with the invention, they comprise a heat transfer fluid circuit in accordance with the invention.

Claims

Claims

1. Heat transfer fluid circuit (2) for a heat treatment system (1) of a vehicle and intended to be traversed by a heat transfer fluid, comprising: - a main branch (4) comprising a first heat exchanger (5) configured to carry out a heat exchange between the heat transfer fluid and an external air flow (6), and extending between a convergence zone (7) and a divergence zone (8), - a first loop (9) comprising a main section (10) and a secondary section (11), the main section (10) starting at the divergence zone (8) and being provided with a second heat exchanger (13) configured to heat treat an electric motor of the vehicle, a first pumping device (12) and a first control device (14), the first control device (14) being configured to circulate the heat transfer fluid to the convergence zone (7) or to the secondary section (11), the secondary section (11) comprising a second pumping device (16), a third heat exchanger (18) configured to carry out a heat exchange between the heat transfer fluid and a refrigerant circulating in a refrigerant circuit (3) and a fourth heat exchanger (19) configured to heat treat an electrical storage device of the vehicle, - a second loop (23) comprising a fifth heat exchanger (25) configured to carry out a heat exchange between the heat transfer fluid and the refrigerant fluid circulating in the refrigerant circuit (3), a third pumping device (24) and a sixth heat exchanger (26) configured to carry out a heat exchange between the heat transfer fluid and an interior air flow (28) intended to be sent into the passenger compartment of the vehicle, the second loop (23) being placed under the control of a second control device (27) configured to circulate the heat transfer fluid towards the second loop (23) up to the sixth heat exchanger (26) or towards the convergence zone (7) by via a junction branch (30), - a third loop (31) comprising a seventh heat exchanger (33) configured to carry out a heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit (3), a fourth pumping device (32), a third control device (35) and an eighth heat exchanger (34) configured to carry out a heat exchange between the heat transfer fluid and the interior air flow (28) intended to be sent into the passenger compartment of the vehicle, the third control device (35) being configured to circulate the heat transfer fluid towards the third loop (31) to the eighth heat exchanger (34) or towards the convergence zone (7) via a connection branch (36).

2. A heat transfer fluid circuit (2) according to claim 1, wherein the first loop (9) comprises a first transfer branch (15) between the main section (10) and the secondary section (11), the first transfer branch (15) extending between the first control device (14) and the secondary section (11).

3. Heat transfer fluid circuit (2) according to claim 2, in which the first loop (9) comprises a second transfer branch (20) extending between the main section (10) and the secondary section (11).

4. A heat transfer fluid circuit (2) according to any preceding claim, wherein the secondary section (11) of the first loop (9) comprises an electric heating element (17).

5. Heat transfer fluid circuit (2) according to the preceding claim, in which the first loop (9) comprises a control member (21) and a bypass branch (22), the control member (21) being configured to circulate the heat transfer fluid to the fourth heat exchanger (19) or within the bypass branch (22), the bypass branch (22) being fluidically linked to the control member (21) and being arranged in parallel with the fourth heat exchanger (19).

6. Heat transfer fluid circuit (2) according to any one of the preceding claims, in which the first control device (14) is a three-way valve comprising three ports, at least one port pro- running along the main section (10) to the convergence zone (7) and at least one other port being connected to the secondary section (11), the third control device (35) being a three-way valve comprising three ports, at least one port extending the third loop (31) to the eighth heat exchanger (34) and at least one other port being connected to the convergence zone (7) via the connecting branch (36).

7. Heat transfer fluid circuit (2) according to any one of the preceding claims, in which the second control device (27) is a three-way valve comprising three ports, at least one port extending the second loop (23) to the sixth heat exchanger (26) and another port being connected to the convergence zone (7) via the junction branch (30).

8. A heat transfer fluid circuit (2) according to any preceding claim, in combination with claim 5, wherein the control member (21) is a three-way valve comprising three ports, at least one port extending the secondary section (11) to the fourth heat exchanger (19) and at least one other port being connected to the bypass branch (22).

9. Heat transfer fluid circuit (2) according to any one of claims 1 to 6, wherein the first pumping device (12) and / or the second pumping device (16) and / or the third pumping device (24) are reversible pumps configured to circulate the heat transfer fluid in a first circulation direction (58) or in a second circulation direction (59) opposite to the first circulation direction (58).

10. Heat transfer fluid circuit (2) according to the preceding claim, in combination with claim 5, in which the control member (21) comprises a first non-return valve (53) arranged on the bypass branch (22) and / or a second non-return valve (54) arranged on a pipe (55) of the secondary section (11) which comprises the fourth heat exchanger (19).

11. Heat transfer fluid circuit (2) according to claim 9 or 10, in which the second control device (27) comprises a first non-return device (56) arranged on the second loop (23) and / or a second non-return device (57) arranged in the main branch (4) upstream of the second loop (23).

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