Thermal storage system using a phase change material

Abstract

The invention relates to a thermal storage system (1) implementing a phase change material (2), comprising a heat exchanger (11) having a bundle (111) of at least three conduits (14a), (14b) and (14c), configured, for a conventional PCM, to receive a single-pass, downward flow of the heat transfer fluid during charging and a multi-pass flow during discharging of the thermal storage system, and for a "water" type PCM, to receive a multi-pass flow of the heat transfer fluid during charging and a single-pass, upward flow during discharging of the thermal storage system. Figure for the abstract: Fig. 5

Description

Title of the invention: Thermal storage system implementing a phase change material

[0001] The invention relates to a thermal storage system (TSS) comprising a heat exchanger, for example of shell and tube type, or tank type, or plate type, and implementing a phase change material (called "PCM").

[0002] The invention finds application, for example, in urban, rural, or industrial heating and / or cooling networks, or in solar energy storage. The invention also finds applications in housing, off-grid thermal transport (trucks, boats, etc.), and in the thermal management of embedded (electric batteries) or stationary systems.

[0003] One particularly interesting envisaged application is for example the substation of heat networks, which presents an important challenge of compactness and offers significant potential replication (several tens of thousands of substations in France).

[0004] A very common heat exchanger technology is, for example, the so-called "shell and tube" type. In such a system, a shell through which a fluid flows is traversed by a bundle of tubes through which another fluid flows. The two fluids exchange heat energy by conduction through the tube walls.

[0005] For thermal storage, this technology is suitable: there is no longer an exchange between two moving fluids, but between a heat transfer fluid (HTF) circulating in the tubes (which is therefore in motion) and a phase change material (PCM) contained in the shell. The phase change material is then considered stagnant, i.e., static (apart from natural convection movements in the liquid phase of the phase change material).

[0006] During a charge, the heat transfer fluid reaches a temperature that is higher than a phase change temperature of the phase change material, for example its melting temperature, and gives up energy to it, which causes a phase change of the phase change material, for example, its melting.

[0007] During a discharge, the heat transfer fluid reaches a temperature lower than a phase change temperature of the material undergoing a phase change, for example its melting temperature (or here solidification) or even its crystallization temperature, and recovers the previously stored energy, causing a phase change of the material undergoing a phase change, for example its solidification or its crystallization.

[0008] Generally speaking, the choice of the direction of flow, upward or downward, depends on the desire to promote the establishment of thermal stratification in the MCP during charging or discharging (although sensible heat is often low compared to latent heat to justify this interest).

[0009] To promote the establishment of thermal stratification in the PCM during discharge of the thermal storage system, it is preferable to have an upward flow of the heat transfer fluid. However, if achieving thermal stratification in the PCM during discharge of the thermal storage system is not a design criterion of the thermal storage system (for example, during operation with a small temperature differential), then the flow of the heat transfer fluid can be downward.

[0010] In a thermal storage system with a PCM, it is the thermomechanical stresses that can occur in the PCM that will generally impose the direction of flow.

[0011] Such a problem arises from the change in density of the MCP during the change of state.

[0012] Most PCMs have a higher density in the solid state than in the liquid state; therefore, in the liquid state, a PCM expands, i.e., occupies more volume, for example, about 10-15% more volume. However, some materials that can be used as PCMs have the opposite behavior, for example, water or lithium.

[0013] For PCMs where the density in the solid state is greater than the density in the liquid state, it is necessary to ensure downward flow of the heat transfer fluid during charging (PCM melting). Indeed, when heat is supplied to the system from below, the PCM melts and can expand, while it is trapped in a solid state higher up the surface, generating thermomechanical stresses on the system. During discharging, however, there is less stress.

[0014] For PCMs where the density in the solid state is less than the density in the liquid state, the constraint relates to the direction of flow during discharge (solidification of the PCM), which must be upward. For the loading, on the other hand, there is less of a constraint.

[0015] Thus, with a "classical" PCM, that is to say having a higher density in the solid state than in the liquid state, therefore expanding in the liquid state, i.e. taking up more space, for example about 10-15% more space, it is generally preferable that the charge be downward, while for a PCM having an inverse behavior, for example such as water or lithium, it is then preferable to favor an upward discharge.

[0016] With a conventional PCM, a discharge could be downward, whereas with water, a charge could be upward.

[0017] However, for convenience, the directions of flow of the heat transfer fluid for a charge and a discharge are generally reversed with respect to each other, regardless of the PCM.

[0018] Such a thermal storage system with a PCM makes it possible to store a relatively large quantity of thermal energy in a relatively small volume, while also allowing for relatively short charging and discharging times, typically a few hours. Generally, heat storage times can range from a few hours (so-called daily storage) to a few days (so-called weekly storage) and up to a few months (so-called inter-seasonal storage).

[0019] However, apart from a few prototypes and demonstrators, few latent heat storage systems (with phase change material) have been built and are currently being operated on an industrial scale.

[0020] One of the obstacles to their large-scale deployment is their low profitability, inherent in large part to the high cost of the heat exchanger at the interface between the heat transfer fluid and the phase change material.

[0021] There are latent heat storage systems based on the same design scheme, in which a bundle of tubes, inside which the heat transfer fluid flows, is arranged in a shell containing the phase change material, the tubes being provided with fins.

[0022] Such fins make it possible in particular to improve thermal conduction on the side of the phase change material (phase change materials generally being poor conductors of heat).

[0023] The dimensions of these finned tubes are standardized, and largely conditioned by the petrochemical sector.

[0024] One advantage of finned tube technology is that it can offer a generally very attractive price.

[0025] On the other hand, a major drawback lies in the maximum diameter of the fins which remains relatively small (about 5-6 cm maximum), which leads to the use of many finned tubes in a latent heat storage system to diffuse the heat efficiently within the phase change material.

[0026] This drawback considerably increases the final cost of the latent heat storage system and also leads to other disadvantages, including: - A significant number of finned tube assemblies on an upper collector plate and a lower collector plate, which assembly is often carried out by welding or expansion, generating a second strong constraint on the cost of the system; - A very low flow velocity of the heat transfer fluid in the tubes, given the low partial flow rate of heat transfer fluid circulating in each tube. This constraint implies, in order to improve the heat exchange between the heat transfer fluid and the phase change material, the use of solutions such as the addition of internal hydraulic inserts in the tubes, which results in a further significant additional cost due to the purchase and assembly of these inserts (which can be done by brazing, crimping, or other means) in the finned tubes.

[0027] Furthermore, to limit the volume of free phase-change material (i.e., contained in thermally inactive areas), it is preferable to incorporate a large number of tubes. This arrangement may imply that, to ensure a downward flow of the heat transfer fluid under pressure (generally due to the expansion of phase-change materials during their melting), all the tubes are traversed in parallel by the heat transfer fluid, which results in low partial flow rates of heat transfer fluid per tube, and consequently a low flow velocity of the heat transfer fluid in each of the tubes.

[0028] This low flow velocity results in a low convective exchange coefficient of the heat transfer fluid in the wall of a tube and therefore a low overall exchange coefficient between the phase change material and the heat transfer fluid, which ultimately results in a low heat exchange power between the phase change material and the heat transfer fluid.

[0029] This situation is particularly encountered on urban or industrial heat networks when the availability and value of the available flow rate are low, leading to or even accentuating the consequences mentioned above.

[0030] Furthermore, the operation of thermal storage systems generally leads to considering very different power profiles between the charging and discharging phases of the thermal storage system. In most cases, the thermal power available for charging is lower than the power required during discharging.

[0031] This situation is also particularly encountered on urban heating networks where usage profiles lead to managing peak demand, such as morning and evening power demands to meet domestic hot water needs, and trough consumption such as at night.

[0032] In addition, instability of the convection mode of the heat transfer fluid (HTF) may occur.

[0033] French patent application FR2996631 proposes to reduce the number of tubes in a thermal storage system by adding external aluminum inserts with a snowflake-shaped geometry around the finned tubes. This design optimizes conduction in the phase-change material. However, a gap remains between the outside of the tube and the insert, resulting in significant thermal resistance that negatively impacts system performance. Therefore, placing an aluminum insert directly around a steel tube can be detrimental to heat transfer. For this reason, a finned tube was retained, with the aluminum insert positioned around the fins. While the gap still exists, it is less problematic due to the larger heat exchange surface area. This device thus improves conduction in the phase-change material but could be further enhanced by eliminating the gap between the fins and the inserts—a gap that hinders heat transfer—or ideally, by eliminating the fins altogether and achieving direct contact between the aluminum insert and the tube.

[0034] Patent application EP2510302 proposes to improve heat exchange in the phase-change material using the same aluminum insert principle as described above, but without a fin around the tube, for example, by adding aluminum inserts made of two parts clipped around the steel tube. The clipping of this system does not allow for perfect contact with the tube, and some play between the tube and the insert always remains. Furthermore, this design increases the number of parts and assembly steps.

[0035] Several technical problems are therefore encountered in latent heat storage systems using a phase change material.

[0036] The present invention aims to resolve at least in part the aforementioned disadvantages, leading in addition to other advantages.

[0037] To this end, a thermal storage system is proposed according to a first aspect, implementing a phase change material, the thermal storage system comprising the phase change material, and a heat exchanger having an upper and a lower terminal configured to form an inlet or outlet of a heat transfer fluid in the thermal storage system,

[0038] the heat exchanger comprising a bundle of conduits extending between the upper and lower terminals, the bundle of conduits comprising at least three conduits including a first conduit, a second conduit and a third conduit, each of the conduits being configured to receive a flow of the heat transfer fluid, at least a part of each of the conduits being in contact with the phase change material.

[0039] The at least three conduits are configured in particular, for a conventional PCM, to receive the flow of the heat transfer fluid in a single, downward pass during a charge and in multiple passes during a discharge of the thermal storage system.

[0040] For another type of PCM, for example a "water" type PCM, the at least three conduits are then configured in particular to receive the fluid flow multi-pass heat transfer during charging and single-pass, upward, during discharging of the thermal storage system.

[0041] For example, the thermal storage system comprising an upper distributor extending between the upper terminal and the duct bundle, and a lower distributor extending between the duct bundle and the lower terminal,

[0042] and the upper distributor comprising an upper partial distribution box and an upper fluid distribution box, and the lower distributor comprising a lower partial fluid distribution box and a lower fluid distribution box,

[0043] at least the first conduit opening on the one hand into the upper partial distribution box outside the upper fluid distribution box, and on the other hand into the lower fluid distribution box outside the lower partial fluid distribution box, at least the second conduit opening on the one hand into the upper fluid distribution box and on the other hand into the lower fluid distribution box outside the lower partial fluid distribution box, and at least the third conduit opening on the one hand into the upper fluid distribution box and on the other hand into the lower partial fluid distribution box,

[0044] the lower distributor further comprising a lower partial hydraulic tube configured to allow flow of the heat transfer fluid between the lower partial fluid distribution box and the lower terminal,

[0045] the upper fluid distribution box comprising an upper hydraulic valve device, and the lower fluid distribution box comprising a lower hydraulic valve device,

[0046] the upper hydraulic valve device and the lower hydraulic valve device being configured to be open when heat transfer fluid flows in through the upper terminal and closed when heat transfer fluid flows in through the lower terminal.

[0047] Such a thermal storage system therefore has a hydraulic configuration which varies according to the direction of circulation of the heat transfer fluid between its terminals.

[0048] Such a thermal storage system is generally used in a vertical arrangement. However, such a thermal storage system can also be implemented in a horizontal or inclined arrangement, so that the terms "upper / lower" should then be understood as referring to the laterality of the device, for example "left / right" or "upstream / downstream". Similarly, a flow designated here as upward / downward then refers to a flow in one direction, or in another direction, for example, a reverse direction.

[0049] The upper partial distribution box is separate from the upper fluid distribution box; they are, for example, separated from each other by a shared wall.

[0050] Generally, the flow is preferably downward to change the PCM from a solid state to a liquid state.

[0051] To change the MCP from the liquid state to the solid state, the flow can be either upward or downward.

[0052] For example, in a storage case involving a PCM whose density in the solid state is greater than its density in the liquid state, it is preferable for the flow during charging to be downward. During discharging, the flow direction has less impact, as the flow can be more freely upward or downward.

[0053] In a storage case involving a PCM whose density in the solid state is lower than its density in the liquid state, it is preferable for the flow to be upward during discharge. There is less constraint on the flow during charging, which can be more freely upward or downward.

[0054] The thermal storage system then includes hydraulic separators, in order to direct the flow of the heat transfer fluid within the bundle of ducts, and hydraulic valve devices which allow the passage of the heat transfer fluid in one direction of flow, and prevent it in the other direction of flow.

[0055] The present invention makes it possible, in particular, to escape a mixed convection zone, and the transient flow regime where applicable, not by placing inserts in tubes, which have the disadvantage of being relatively expensive (because they induce supply and assembly requirements) and are likely to generate fouling zones, but by passively configuring the heat transfer fluid flow in multiple passes during an upward flow, i.e., entering through the lower end, into the thermal storage system to increase the velocity of the heat transfer fluid in the tubes. This configuration thus makes it possible to achieve a higher Reynolds number for the heat transfer fluid flow and an established and stable convection mode (i.e., natural or mixed convection).

[0056] However, according to one embodiment, the thermal storage system may include at least one internal hydraulic insert positioned in at least one of the conduits.

[0057] Using such an insert makes it possible to further increase the speed of the fluid in a conduit, in particular if the conduit is a tube.

[0058] In one embodiment, the thermal storage system is configured to include a single pass of heat transfer fluid during a flow from the upper terminal to the lower terminal.

[0059] In one embodiment, the thermal storage system is configured to include an odd number of passes of heat transfer fluid during a flow from the lower terminal to the upper terminal, and comprising at least three passes.

[0060] In one embodiment, the thermal storage system is configured to distribute a flow of heat transfer fluid, flowing from the upper terminal to the lower terminal, into all the conduits of the conduit bundle.

[0061] In one embodiment, the thermal storage system is configured to make a flow of heat transfer fluid, flowing from the lower terminal to the upper terminal, pass through the third conduit, then the second conduit and then the first conduit.

[0062] In one embodiment, the upper hydraulic valve device includes a passive system configured to be opened by a pressure difference of the heat transfer fluid on either side of the upper hydraulic valve device.

[0063] In one embodiment, the lower hydraulic valve device includes a passive system configured to be opened by a pressure difference of the heat transfer fluid on either side of the lower hydraulic valve device.

[0064] The valves open passively, actuated solely by the pressure difference of the heat transfer fluid across their terminals. If necessary, the pressure difference of the heat transfer fluid across each valve is sufficient to release an optional return spring fitted to each valve.

[0065] In one embodiment, at least one of the upper hydraulic valve device and the lower hydraulic valve device comprises at least one spring-loaded valve.

[0066] In one embodiment, at least one spring-loaded valve includes at least one return spring and a flap attached to the return spring.

[0067] The return spring is configured for example to bring the shutter back to the closed position and in particular to keep the shutter in the closed position when desired, by compensating for its weight when it is subjected to gravity.

[0068] The at least one spring comprises, for example, a helical spring, and / or a flat spring, and / or a leaf spring.

[0069] The helical spring may have a round or flat wire.

[0070] During operation, the forces acting on the flap are: - A downward weight on the flap, - A spring restoring force (upwards), - A pressure difference in the fluid on either side of the flap.

[0071] For the valve to be in the closed position with an upward flow, the spring return force and the fluid flow pressure must therefore be greater than the weight of the flap.

[0072] Conversely, for the valve to be open with downward flow, the weight of the flap and the fluid flow pressure must be greater than the spring return force.

[0073] In the absence of flow, at least one of the upper hydraulic valve device and the lower hydraulic valve device is preferably closed, or even both are closed.

[0074] According to an interesting option, the thermal storage system may include a deflector to direct a jet of fluid arriving from the lower terminal and generate a jet effect which keeps the lower hydraulic valve device closed.

[0075] In one embodiment, the heat exchanger includes an upper collecting plate and / or a lower collecting plate.

[0076] For example, the conduits of the conduit bundle extend from the upper collector plate to the lower collector plate.

[0077] Such a system allows the use of standard ducts, or of any desired size, which is less restrictive, while having a relatively large exchange surface with the MCP.

[0078] In one embodiment, at least one of the conduits in the conduit bundle comprises at least one tube.

[0079] In one embodiment, at least one tube has an outer surface carrying heat exchange fins.

[0080] In one embodiment, at least one of the conduits in the conduit bundle includes at least one plate delimiting a passage of the fluid in a conduit.

[0081] In one embodiment, the thermal storage system includes at least one partition delimiting at least one duct.

[0082] For example, the thermal storage system is configured so that the fluid flow bypasses the partition when a heat transfer fluid flows in through the lower terminal.

[0083] In one embodiment, the heat exchanger includes at least one capsule containing the phase change material.

[0084] In one embodiment, the thermal storage system comprises a shell containing the phase change material, the heat exchanger being disposed in the shell.

[0085] In one embodiment, the thermal storage system includes at least one constriction element.

[0086] A constriction element is configured to increase pressure losses, and therefore reduce the flow rate of the heat transfer fluid.

[0087] Such a constriction element can be disposed, in the thermal storage system, in, before or after at least one of the conduits.

[0088] For example, at least one constriction element is disposed in a part of at least one hydraulic tube.

[0089] In one embodiment, at least one constriction element is disposed in a hydraulic tube of the upper terminal.

[0090] The flow restriction can be obtained by adding an element and / or by deforming a wall forming a conduit or tubing or other, depending on where the constriction element is located.

[0091] In one embodiment, the phase change material comprises any type of material, such as, for example, paraffin, fatty alcohol, fatty acid, sugar alcohol, salt hydrate, or other, or even, for example, water or lithium.

[0092] In one embodiment, the heat transfer fluid may be water, for example in liquid or vapor form.

[0093] The invention is therefore particularly advantageous for energy-dense heat storage (expressed in kWh / m3) for urban or industrial heat networks, with different expectations between power or charging time (low power - long duration) and power or discharging time (high power - short duration).

[0094] Such an energy storage system (with phase change material) thus exhibits satisfactory efficiency and heat transfer performance between the heat transfer fluid and the phase change material.

[0095] The invention, according to an exemplary embodiment, will be better understood and its advantages will become more apparent upon reading the following detailed description, given by way of example and in no way limiting, with reference to the accompanying drawings in which:

[0096] Fig. 1 schematically represents a general principle of a thermal storage system according to an example of an embodiment;

[0097] [Fig.2] illustrates tubes with fins;

[0098] [Fig.3] represents a detail of [Fig.2];

[0099] [Fig.4] presents a graph taken from Martinelli & al. “Experimental study of an externally finned tube with internal heat transfer enhancement for phase change thermal energy storage” 7th European Thermal Scientific Conference (EUROTHERM 2016);

[0100] [Fig.5] represents a thermal storage system according to a first embodiment of the present invention;

[0101] Figure 6 illustrates a hydraulic path of the heat transfer fluid during a flow from the upper limit, here descending, in the thermal storage system of the [Fig.5];

[0102] [Fig.7] illustrates a hydraulic path of the heat transfer fluid during a flow from the lower terminal in the thermal storage system of [Fig.5];

[0103] [Fig.8] represents a bundle of conduits in top view according to an example of an embodiment;

[0104] [Fig.9] represents a thermal storage system according to a second embodiment of the present invention;

[0105] Fig. 10 represents a thermal storage system according to a third example of the realization of the present invention;

[0106] [Fig.1 1] represents a thermal storage system according to a fourth embodiment of the present invention;

[0107] [Fig. 12] illustrates an optional constriction element in a tube hydraulics of a thermal storage system according to an example of an embodiment of the present invention;

[0108] Fig. 13 represents a thermal storage system according to a fifth example of the realization of the present invention;

[0109] [Fig. 14] illustrates a hydraulic path of the heat transfer fluid during a flow from the upper limit in the thermal storage system of [Fig. 13]; and

[0110] [Fig. 15] illustrates a hydraulic path of the heat transfer fluid during a flow from the lower terminal in the thermal storage system of [Fig. 13].

[0111] A latent heat storage system exploiting a phase change material (designated "PCM") operates by harnessing the latent heat of a liquid-solid (or even solid-solid) phase change of a phase change material.

[0112] Thus, such a phase-change material has a phase-change temperature, for example a melting temperature, below which the phase-change material is in a first state, for example a solid state, and above which the PCM is in a second state, for example a liquid state.

[0113] For a solid-liquid phase change material, energy related to latent heat is absorbed by the PCM during the melting of the phase change material and is released by the PCM during the solidification of the phase change material.

[0114] The charging of a latent heat storage is generally characterized by the melting of the phase change material, while the discharging is generally characterized by the solidification of said phase change material.

[0115] By way of example, the opposite phenomenon is considered for a storage of cold (for example, the phase change material is ice or salt hydrate) finding its application on a cold network.

[0116] The amount of stored thermal energy is expressed by the following relationship:

[0117] AQ = m*Ahlv

[0118] Where: m is the mass (in kilograms [kg]) and

[0119] Ahiv is the specific enthalpy of solid-liquid phase change (in kilojoules per kilogram [kJ / kg]).

[0120] One of the major advantages of such a technology is that the phase change takes place at almost constant pressure and temperature.

[0121] Consequently, the discharge of the stored energy can take place at an almost constant temperature and close to the phase change temperature of the material.

[0122] The enthalpy of phase change is relatively important in comparison to the sensible energy variation of a material, over a relatively small temperature difference.

[0123] Consequently, storage systems with phase change material are attractive because the amount of energy stored per unit volume (and mass) is greater than that obtained by a sensitive system over the same temperature range used (i.e. better energy storage density).

[0124] As a result, the volumes of the storage system and the material contained are reduced, which limits the heat losses which are proportional to the external surface of the tank and which may also possibly reduce the price for example for pressurized systems.

[0125] A very widespread phase change material storage technology is the so-called "tube and shell" technology.

[0126] In such a system, a shell containing a phase-change material is traversed by a bundle of tubes through which a heat transfer fluid (HTF) flows. The PCM and the heat transfer fluid exchange energy by conduction through the tube walls.

[0127] The phase-change material is then considered to be stagnant (apart from the natural convection movements in the liquid phase of the phase-change material).

[0128] Fig. 1 illustrates such a thermal storage system 1.

[0129] The thermal storage system 1 comprises a calender 12 containing a phase change material (PCM) 2.

[0130] The thermal storage system 1 further comprises a heat exchanger 11.

[0131] The heat exchanger 11 comprises a bundle 111 of tubes 114 in which a Heat transfer fluid 3 flows during system operation.

[0132] The heat exchanger 11 is disposed in the shell 12 and the PCM 2 envelops at least a part of each of the tubes 114.

[0133] Each of the tubes 114 has a wall of a determined thickness.

[0134] In operation, the phase change material 2 (which surrounds at least part of the tubes 114) and the heat transfer fluid 3 (which flows in the tubes 114) thus exchange energy by conduction through the wall of the tubes 114.

[0135] During a downward flow, for example a charge, schematically [Fig.1] A), the heat transfer fluid 3 reaches a temperature higher than a temperature of change of state of the phase change material 2, for example its melting temperature, and gives up energy to it, which causes it to melt (or more generally a change of state).

[0136] During an upward flow, for example a discharge, schematically represented [Fig.1] B), the heat transfer fluid 3 enters at a temperature lower than a phase change temperature of the phase change material 2, for example its melting temperature, or even its crystallization temperature, and recovers the previously stored energy, causing the solidification of the phase change material (or more generally a change of state).

[0137] Generally, a flow is preferably downward to change the PCM from the solid state to the liquid state. To change the PCM from the liquid state to the solid state, the flow can be either upward or downward.

[0138] This is due to the fact that when a material changes state, its density changes. Most PCMs have a higher density in the solid state than in the liquid state; therefore, in the liquid state, a PCM expands, i.e., occupies more volume, for example, about 10-15% more volume. However, some materials that can be used as PCMs have the opposite behavior, for example, water and lithium.

[0139] For convenience, the present description refers to the general case of PCMs having a higher density in the solid state than in the liquid state.

[0140] Considering a PCM having a lower density in the solid state than in the liquid state, it is preferable that the flow be upward in discharge (crystallization).

[0141] As a result, the arrangement of the collectors / distributors and valves described in the embodiments presented below is then in transverse symmetry, i.e. so that the upward flow is single-pass, and the downward flow is multi-pass.

[0142] As illustrated in [Fig.2], there are latent heat storage systems based on the same design scheme, in which the tubes 114 have fins 115.

[0143] Fig. 3 shows in more detail such a tube 114 provided with fins 115 to improve thermal conduction on the side of the phase change material (phase change materials generally being poor conductors of heat).

[0144] Indeed, commonly used phase change materials (such as hydrated salts, paraffins, fatty alcohols) have low thermal conductivity.

[0145] In order to increase the thermal conductivity in the chosen phase change material, while limiting the costs of manufacturing heat exchangers, it is advantageous to use finned tubes.

[0146] Particularly for reasons of cost and means of production, finned tubes of standardized dimensions are generally used.

[0147] Figure 4, for example, presents a diagram illustrating the Reynolds number on the ordinate (characterizing the flow regime) as a function of Ra*D / L on the abscissa for vertical tubes, where Ra is the Rayleigh number, D is the hydraulic diameter of the flow and L is its characteristic length.

[0148] The dimensionless Rayleigh number (Ra) expresses the predominant mode of heat transfer within a fluid between thermal conduction (low Rayleigh) and natural convection (high Rayleigh).

[0149] The "D / L" ratio allows us to take into account a ratio of the geometric quantities of the flow.

[0150] The dimensionless Reynolds number (Re) expresses the flow regime: the flow is laminar at low Re, turbulent at high Re, and transient between the two (hatched area on [Fig.4]).

[0151] Thus, depending on these parameters, the flow can be qualified as follows: - LFC: flow called "Laminar Forced Convection", i.e. laminar with forced convection; - TFC: flow called "Turbulent Forced Convection", i.e. turbulent with forced convection; - LMC: flow called "Laminar Mixed Convection", i.e. laminar with mixed convection; - TMC: flow called "Turbulent Mixed Convection", i.e. turbulent with mixed convection; - LNC: flow described as "Laminar Natural Convection", i.e., laminar flow with natural convection; or - TNC: flow called "Turbulent Natural Convection", i.e. turbulent with natural convection.

[0152] This figure shows that the operating conditions of thermal storage (flow rate and temperatures of the heat transfer fluid) generally encountered on networks of heat, lead to unfavorable conditions for heat transfer between the heat transfer fluid and the phase change material, particularly due to the convection mode of the heat transfer fluid.

[0153] In the illustrated example [Fig. 4], the thermo-hydraulic conditions of the heat transfer fluid flowing in a thermal storage system whose tubes lack inserts induce a mixed convection heat exchange mode for the heat transfer fluid (moreover, in a transient flow regime). Mixed convection heat exchange is constrained by its inherent instability, leading to variations in the overall heat transfer coefficient and consequently in the heat output.

[0154] The graph in [Fig.4] further illustrates that the installation of inserts inside the tubes to reduce the hydraulic section has the positive consequence of exiting the mixed convection zone (as well as the transient flow regime).

[0155] Several technical problems are therefore encountered in a latent heat storage system using a phase change material.

[0156] Figures 5 to 7 illustrate a thermal storage system (TSS) 1 implementing a phase change material (PCM) 2 according to a first embodiment of the present invention.

[0157] As illustrated in [Fig.5], the thermal storage system 1 here comprises a calender 12.

[0158] The calender 12 here designates an enclosure forming an envelope of the thermal storage system 1.

[0159] Thus, for example, either the PCM is contained in the shell and the heat transfer fluid flows through conduits, or the PCM is contained in capsules (as illustrated [Fig.1 1]) and the heat transfer fluid flows around the capsules and is contained in the shell.

[0160] The grille 12 is here considered to be cylindrical.

[0161] The calender 12 has two fluid inlets / outlets through each of which fluid enters or leaves the system, also referred to herein as "terminals": an upper terminal 141, herein comprising an upper main hydraulic tube, and a lower terminal 142, herein comprising a lower main hydraulic tube.

[0162] As described below, the upper terminal 141 is thus configured to form an inlet of the heat transfer fluid 3 during a downward flow, as illustrated [Fig.6], while the lower terminal 142 is thus configured to form an inlet of the heat transfer fluid 3 into the shell during a flow considered to be upward, as illustrated [Fig.7].

[0163] Terminals 141, 142 are here arranged along a longitudinal axis X of the system, which is here a longitudinal axis of the grille.

[0164] The thermal storage system 1 also includes a heat exchanger 11.

[0165] The heat exchanger 11 is arranged in the shell 12.

[0166] The heat exchanger 11 mainly comprises a bundle 111 of conduits 14.

[0167] The bundle 111 of conduits 14 here designates a set of conduits 14, comprising at least three conduits 14a, 14b, 14c.

[0168] In the embodiment example of figures 5 to 7, the conduits 14 are tubes 114, and therefore comprise at least three tubes 114a, 114b, 114c.

[0169] The conduits 14 are here straight and parallel to each other.

[0170] Tubes 114 are for example finned tubes; however, they could be standard tubes, without fins.

[0171] The heat exchanger 11 further comprises here an upper collecting plate 112, and a lower collecting plate 113, shown for example in top view in [Fig.8].

[0172] The conduits 14 extend between the upper collecting plate 112 and the lower collecting plate 113.

[0173] Each conduit 14 is fixed, for example welded, at a first end of the conduit, to the upper collector plate 112 and, at a second end of the conduit, to the lower collector plate 113.

[0174] The upper collector plate 112 and the lower collector plate 113 are here parallel to each other.

[0175] The upper collector plate 112 and the lower collector plate 113 are arranged in the grille along a cross-section of the grille, for example orthogonal to the longitudinal axis X.

[0176] Each of the upper collector plate 112 and the lower collector plate 113 closes the section of the grille that it occupies.

[0177] Thus, the heat transfer fluid can only flow from one terminal 141, 142 to the other of the thermal storage system 1 through the conduits 14.

[0178] The heat exchanger 11 arranged in the grille 12 thus divides the grille 12 into three compartments:

[0179] - an upper compartment 130, also referred to as the "upper dispenser" 130 or " upper fluid collector » 130, between the upper terminal 141 and the duct bundle 111 14, or the upper collector plate 112 if such a plate is present,

[0180] - a central compartment formed by the bundle 111 of conduits 14, between the plate upper collector 112 and lower collector plate 113 where applicable, and

[0181] - a lower compartment 135, also referred to as the "lower dispenser" 135 or " lower fluid collector » 135, between the duct bundle 111 of conduit 14, or the lower collector plate 113 if such a plate is present, and the lower terminal 142.

[0182] In the central compartment, the thermal storage system includes the phase change material (PCM) 2.

[0183] The phase change material 2 therefore occupies a defined volume in the shell 12 and thus surrounds at least part of the conduits 14.

[0184] The phase change material (PCM) 2, as described above, is a material configured to take a first state when it is at a temperature below a phase change temperature, and a second state when it is at a temperature above a phase change temperature.

[0185] For example, the phase change material 2 has a melting temperature, and it is in the solid state when it is at a temperature below its melting temperature, and in the liquid state when it is at a temperature above its melting temperature.

[0186] Consequently, the phase change material 2 can have a first density when it is in its first state, and a second density, possibly different from the first density, when it is in its second state.

[0187] The phase change material 2 can therefore occupy a first volume when it is in its first state, and a second volume, possibly different from the first volume, when it is in its second state.

[0188] Therefore, it may be preferable for the phase change material 2 to occupy only a part of the available volume in the central compartment when it is in a state so as to allow for possible expansion when it passes from one state to another.

[0189] Thus, on [Fig.5], the phase-change material 2 leaves an available space 121 between its surface and one end (preferably an upper end, but which can be a lower end) of the conduits 14, and for example here with respect to the upper collecting plate 112.

[0190] The upper distributor 130 includes an upper fluid distribution box 133.

[0191] The upper distributor 130 also includes an upper partial distribution box 131.

[0192] The upper partial distribution box 131 is separate from the upper fluid distribution box 133.

[0193] The upper distributor 130 includes, for example, a wall which is adjacent to the upper partial distribution box 131 and the upper fluid distribution box 133. The adjoining wall divides, for example, a volume of the upper distributor 130 into two sub-volumes 131a, 133a.

[0194] The upper partial distribution box 131 thus delimits a first of the two sub-volumes 131a and the upper fluid distribution box 133 thus delimits a second of the two sub-volumes 133a.

[0195] The wall of the upper fluid distribution box 133 here has a bell shape covering a first part of the bundle 111 of conduits 14, here over the upper collecting plate 112.

[0196] The upper fluid distribution box 133 is here centered with respect to the bundle 111 of conduits 14, and more particularly here with respect to the upper collector plate 112, and / or in the upper distributor 130.

[0197] The upper distributor 130 thus comprises the second sub-volume 133a delimited by at least the party wall and the first part of the bundle 111 of conduits 14, and the first sub-volume 131a delimited between at least the party wall, a second part of the bundle 111 of conduits 14, and a part of the wall of the grille 12 defining the upper distributor 130.

[0198] In the present embodiment, the first sub-volume 131a surrounds, or rather encompasses, the second sub-volume 133a.

[0199] The second part of the upper collecting plate 112 therefore extends between the first part of the upper collecting plate 112, capped by the wall of the upper fluid distribution box 133, and the part of the wall of the grille 12.

[0200] Here, the first part of the upper collector plate 112 and the second part of the upper collector plate 112 form the whole of the upper collector plate 112.

[0201] An upper end of each of the conduits of the conduit bundle therefore opens either into the upper fluid distribution box 133 (i.e. into the second sub-volume 133a), or into the upper partial distribution box 131 outside of the upper fluid distribution box 133 (i.e. into the first sub-volume 131a).

[0202] Thus, on the side of the upper partial distribution box 131, a first conduit 14a of the at least three conduits 14 opens into the first sub-volume 131a, while at least a second conduit 14b and a third conduit 14c of the at least three conduits 14 open into the second sub-volume 133a.

[0203] In addition, the upper fluid distribution box 133 includes an upper hydraulic valve device 31, for example disposed in the wall of the upper fluid distribution box 133.

[0204] The upper hydraulic valve device 31 is configured here to allow passage of heat transfer fluid 3 from the first sub-volume 131a to the second sub-volume 133a.

[0205] Thus, the upper hydraulic valve device 31 is configured to allow a flow of heat transfer fluid 3 from the upper terminal 141 to all the conduits 14, promoting the most homogeneous distribution possible of the heat transfer fluid 3 in all the conduits 14.

[0206] The upper hydraulic valve device 31 is further centered here with respect to the wall of the upper fluid distribution box 133.

[0207] In other words, it is here centered with respect to the longitudinal axis X so as to be directly above the upper terminal 141.

[0208] Thus, a fluid flow from the upper terminal 141 arrives at the upper hydraulic valve device 31, promoting its opening, and therefore facilitating a distribution of the fluid flow between the first sub-volume 131a and the second sub-volume 133a.

[0209] The upper hydraulic valve device 31 includes, for example, a non-return valve.

[0210] In the present embodiment, the upper hydraulic valve device 31 comprises a single valve, which includes a flap and at least one spring system to promote a return of the flap to the closed position and close the wall in which the upper hydraulic valve device 31 is disposed.

[0211] The at least one spring comprises, for example, a helical spring, and / or a flat spring, and / or a leaf spring.

[0212] In the closed position, the upper hydraulic valve device 31 closes, in a manner that is as airtight as possible to the heat transfer fluid 3 circulating in the thermal storage system 1, the upper fluid distribution box 133.

[0213] To promote sealing, the upper fluid distribution box 133 can be provided with a seat on which the flap rests when it is in the closed position.

[0214] As illustrated [Fig.7], in upward flow, i.e. entering through the lower terminal, the upper hydraulic valve device 31 remains closed because the pressure difference on either side of the flap creates a force which has the effect of pressing the flap onto its seat.

[0215] As illustrated [Fig.6], in downward flow, i.e. entering through the upper terminal, the jet effect arriving on the upper hydraulic valve device 31 induces its opening.

[0216] In the lower distributor 135, between the bundle 111 of conduits 14 and the lower terminal 142, in this case between the lower collector plate 113 and the lower terminal 142, the thermal storage system 1 includes a lower fluid distribution box 132, and a lower partial fluid distribution box 134.

[0217] A lower distributor volume 135 is here divided into three sub-volumes 135a, 132a, 134a.

[0218] A first sub-volume 134a of the three sub-volumes is thus globally delimited between a first part of the bundle 111 of conduits 14 (of the lower collecting plate 113) and a wall of the lower partial fluid distribution box 134.

[0219] A second sub-volume 132a of the three sub-volumes is thus globally delimited between a second part of the bundle 111 of conduits 14 (of the plate lower collector 113), and a wall of the lower fluid distribution box 132.

[0220] A third sub-volume 135a of the three sub-volumes is thus globally delimited between the wall of the lower fluid distribution box 132 and the lower boundary 142.

[0221] The wall of the lower partial fluid distribution box 134 here has a bell shape capping the first part of the lower collecting plate 113.

[0222] The lower partial fluid distribution box 134 is here centered with respect to the bundle 111 of conduits 14 (at the lower collector plate 113), and / or in the lower distributor 135.

[0223] In addition, at least the third conduit 14c opens, on the side of the lower distributor 135, into the lower partial fluid distribution box 134, i.e. into the first sub-volume 134a, while at least the first conduit 14a and the second conduit 14b open outside the lower partial fluid distribution box 134, i.e. out of the first sub-volume 134a.

[0224] In particular, the first conduit 14a and the second conduit 14b open into the lower fluid distribution box 132, i.e. into the second sub-volume 132a.

[0225] The lower distributor 135 includes a lower partial hydraulic tube 143 which communicates on the one hand in the first sub-volume 134a and on the other hand in the third sub-volume 135a.

[0226] The lower partial hydraulic tubing 143 thus allows a flow of the heat transfer fluid 3 between at least the third conduit 14c and the lower terminal 142.

[0227] The wall of the lower fluid distribution box 132 also has a bell shape, here covering the bundle 111 of conduits 14, in this case the entire lower collector plate 113. In addition, it here encompasses the lower partial fluid distribution box 134.

[0228] The lower fluid distribution box 132 is here centered with respect to the bundle 111 of conduits 14 (with respect to the lower collector plate 113), and / or in the lower distributor 135.

[0229] The second part of the bundle 111 of conduits 14 (of the lower collecting plate 113) therefore extends between the first part of the bundle 111 of conduits 14 (of the lower collecting plate 113) capped by the wall of the lower partial fluid distribution box 134 and the wall of the lower fluid distribution box 132.

[0230] Here, the first part of the bundle 111 of conduits 14 (of the lower collecting plate 113) and the second part of the bundle 111 of conduits 14 (of the lower collecting plate 113) form the whole bundle 111 of conduits 14 (of the lower collecting plate 113).

[0231] In the present embodiment, the second sub-volume 132a surrounds, or rather encompasses, the first sub-volume 134a.

[0232] In the present embodiment, part of the wall of the lower fluid distribution box 132 forms part of the wall of the lower distributor 135, i.e. here part of the wall of the grille 12.

[0233] In addition, the lower fluid distribution box 132 includes a lower hydraulic valve device 32, for example disposed in the wall of the lower fluid distribution box 132.

[0234] The lower hydraulic valve device 32 is configured here to allow passage of heat transfer fluid 3 from the second sub-volume 132a to the third sub-volume 135a.

[0235] Thus, the lower hydraulic valve device 32 is configured to allow a flow of heat transfer fluid 3 from at least the first conduit 14a and the second conduit 14b, towards the lower terminal 142.

[0236] The lower hydraulic valve device 32 is further centered here with respect to the wall of the lower fluid distribution box 132.

[0237] In other words, it is here centered with respect to the longitudinal axis X and is located directly above the lower terminal 142.

[0238] Thus, a fluid flow from the second sub-volume 132a converges towards the lower bound 142.

[0239] The lower hydraulic valve device 32 includes, for example, an annular valve.

[0240] In the present embodiment, the lower hydraulic valve device 32 comprises a single annular valve which surrounds the lower partial hydraulic tubing 143.

[0241] For example, the annular valve includes an annular flap and at least one spring system to promote a return of the annular flap to the closed position.

[0242] At least one spring comprises, for example, a helical spring, and / or a flat spring, and / or a leaf spring.

[0243] In the absence of flow, the lower hydraulic valve device 32 is preferably closed.

[0244] In the closed position, the lower hydraulic valve device 32 closes the lower fluid distribution box 132, in a manner that is as airtight as possible to the heat transfer fluid 3 circulating in the thermal storage system 1.

[0245] To promote sealing, the lower fluid distribution box 132 can be provided with a seat on which the annular flap rests when it is in the closed position.

[0246] As illustrated [Fig.7], in upward flow, i.e. entering from the lower terminal, the lower hydraulic valve device 32 remains closed because the pressure difference on either side of the flap creates a force which has the effect of pressing the flap shut.

[0247] According to an interesting option not shown, the thermal storage system 1 may include a deflector to direct the jet arriving from the lower terminal 142 and generate a jet effect that keeps the lower hydraulic valve device 32 closed by pressing on it, for example, on its flap. Once the lower hydraulic valve device 32 is closed, the force due to the pressure difference is exerted in the correct direction to keep it closed.

[0248] As illustrated [Fig.6], in downward flow, i.e. entering through the upper terminal, the jet effect arriving from the upper terminal 141 on the lower hydraulic valve device 32 induces its opening.

[0249] In addition, the lower fluid distribution box 132 includes, for example, a central opening forming the lower partial hydraulic tubing 143 so as to allow free flow between the first sub-volume 134a and the third sub-volume 135a.

[0250] In operation, a variation in the density of the phase change material 2 between the two states it can take, for example between its solid state and its liquid state, may require certain precautions to be taken when charging and discharging the thermal storage system 1.

[0251] In the case of a phase-change material having a higher density in the solid state than in the liquid state, and of heat storage based on the liquid-solid phase change, it is therefore preferable to carry out a charge starting from the top of the system (downward flow) so as to establish a negative temperature gradient in the downward vertical direction.

[0252] This operating method avoids the formation of pockets / volumes of phase change material in the liquid state inside a volume of phase change material in the solid and compact state, which would cause significant thermomechanical stresses on the structure of the thermal storage system 1, likely to cause plastic deformations (degradation) or even damage to it (mechanical rupture of the heat exchanger and / or the calender).

[0253] Under load, an important constraint is therefore generally to establish a negative temperature gradient in the downward vertical direction, so that the expansion of the phase-change material during melting can be compensated by a gas head.

[0254] Under these assumptions, the direction of flow of the heat transfer fluid is therefore generally forced from the top to the bottom of the heat exchanger.

[0255] In this configuration, all the hydraulic valve devices 31, 32 of the heat exchanger are open to allow a partial flow of heat transfer fluid 3 to pass through.

[0256] The opening of the hydraulic valve devices 31, 32 is carried out passively, actuated by the pressure difference of the heat transfer fluid 3 on either side of the hydraulic valve devices 31, 32, as described above.

[0257] As illustrated in [Fig.6], the hydraulic flow of the heat transfer fluid 3 then takes place in a single pass through all the conduits 14 of the thermal storage system 1 during a downward flow.

[0258] The arrangement of the upper hydraulic valve device 31 and the upper hydraulic valve device 32 is such that they are then opened by the downward flow of fluid 3.

[0259] Given the distribution and division of the supply flow of the heat transfer fluid 3 at the inlet of the thermal storage system 1 (i.e. at the upper terminal 141 in this case), the low partial flow through each conduit 14 results in a low flow velocity and consequently a low convective heat transfer coefficient of the heat transfer fluid 3, compared to the hydraulic configuration obtained with this thermal storage system 1 during an upward flow, as described below.

[0260] As illustrated in [Fig.7], the direction of fluid flow is forced from bottom to top (upward flow) and the velocity of the heat transfer fluid 3 in the conduits 14 is increased to obtain more power.

[0261] In this upward flow configuration, the upper hydraulic valve devices 31 and lower 32 are closed by the flow, conditioning the hydraulic path taken by the heat transfer fluid 3 through passes of the heat exchanger.

[0262] Indeed, due to pressure losses in the flow, the pressure at point B above the hydraulic valve device 31 is lower than the pressure at point A below the hydraulic valve device 31 (similarly, the pressure at point D above the hydraulic valve device 32 is lower than the pressure at point C below the hydraulic valve device 32).

[0263] In the closed position, the hydraulic valve devices 31, 32 therefore do not allow the passage of a flow of heat transfer fluid 3 through an orifice which they obstruct (valve seat for example), i.e. through the corresponding upper fluid distribution box 133 and lower fluid distribution box 132.

[0264] The closing of the hydraulic valve devices 31, 32 is carried out passively, by the force exerted by the pressure difference of the heat transfer fluid 3 on either side of the hydraulic valve devices 31, 32, and possibly by the action of an optional return spring which can advantageously equip each hydraulic valve device 31, 32.

[0265] The hydraulic flow of the heat transfer fluid 3 then takes place in multi-pass (3 passes on the [Fig.7]) through the heat exchanger of the thermal storage system 1.

[0266] In this configuration, the heat transfer fluid 3 entering the thermal storage system 1 through the lower terminal 142 flows into the third conduit 14c by upward flow, then into the second conduit 14b by downward flow, then into the first conduit 14a by upward flow, and can then exit the thermal storage system 1 through the upper terminal 141 after having traveled through the first sub-volume 131a.

[0267] The hydraulic flow of the heat transfer fluid 3 takes place vertically both in the upward direction (first and third pass) and in the downward direction (second pass) according to the orientation of the pass of conduits (in parallel) through which the heat transfer fluid 3 passes.

[0268] Given the reduced number of conduits 14 traversed during each pass by the heat transfer fluid 3, the partial flow rate of the fluid per conduit is higher than if all the conduits 14 were traversed together in parallel.

[0269] A high partial flow rate through each conduit can then cause a higher flow velocity and consequently a higher convective heat transfer coefficient of the heat transfer fluid, compared to the hydraulic configuration of the thermal storage system 1 in downward flow.

[0270] Fig. 8 illustrates the bundle 111 of conduit 14 seen from above according to an example embodiment, for example according to the example embodiment of Fig. 7, in which the conduits would be represented according to the section AA indicated in Fig. 8.

[0271] In this embodiment example, the conduit bundle comprises thirty-seven conduits 14.

[0272] Here, the conduits 14 are arranged in concentric rings.

[0273] A first ring comprising the first conduit 14a is an outer ring comprising eighteen conduits.

[0274] A second ring, comprising the second conduit 14b, is inscribed in the first ring and comprises twelve conduits 14.

[0275] A third ring, comprising the third conduit 14c, is inscribed in the second ring and comprises six conduits 14.

[0276] Finally, the bundle of conduits here comprises a central conduit, surrounded by the third ring.

[0277] In upward flow, the heat transfer fluid 3 entering the thermal storage system 1 through the lower terminal 142 flows into the third ring and the central conduit by upward flow, for example at a normalized speed of 1 m / s. Then, it flows into the second ring by downward flow at a normalized speed of approximately 0.3 m / s to 0.9 m / s, for example, and then into the first ring by upward flow, at a normalized speed of approximately 0.2 m / s to 0.6 m / s, for example.

[0278] A simulation of the heat exchange in upward flow (here discharge) was carried out using a 1D simulation with the following assumptions: - Initial temperature of MCP storage: 65 °C - Circulation of the heat transfer fluid in thirty-seven vertical tubes of 1.3 m - Temperature of the heat transfer fluid at the storage inlet: 2°C - Expected discharge power: 23 kW - Flow rate of the heat transfer fluid changing over time in order to achieve a constant power discharge

[0279] In single-pass configuration, the duration for which it is possible to supply the expected power is 29 min.

[0280] In a configuration with three passes going from 7 tubes to 12 tubes and then to 18 tubes, the duration during which it is possible to supply the expected power is 34 min, i.e. an extended duration of approximately 15%.

[0281] Of course, as mentioned previously, considering a PCM with a lower density in the solid state than in the liquid state, it is preferable for the feed and discharge flows to be reversed, i.e., for example, upward flow during discharge. Therefore, the arrangement of the manifolds / distributors and valves described here would be reversed, so that the upward flow (entering through the lower terminal) is single-pass, and the downward flow (entering through the upper terminal) is multi-pass.

[0282] Fig. 9 represents a second example of an embodiment of a thermal storage system 1, in which devices of the thermal storage system 1 are accessible and removable from outside the thermal storage system 1.

[0283] This embodiment differs from that of figures 5 to 7 in particular by the upper fluid distribution box 133.

[0284] In this embodiment, the upper fluid distribution box 133 has a tube at one end of which the upper hydraulic valve device 31 is offset.

[0285] The upper hydraulic valve device 31 is thus accessible via the upper terminal 141.

[0286] If necessary, the upper terminal 141 and / or the lower terminal 142 can also be removed to facilitate access to the thermal storage system 1 in order to facilitate maintenance or repair.

[0287] Fig. 10 represents a third example of the realization of a thermal storage system 1, in which the conduits 14 are formed by parallel plates.

[0288] This embodiment also differs from that of Figures 5 to 9 in the shape of the grille. Indeed, the arrangement of plates to form the ducts implies an easier fabrication of the grille 12 in a generally parallelepiped shape rather than a cylindrical one.

[0289] In addition, the upper fluid distribution box 133 is here delimited in the upper distributor 130 by at least one vertical wall, the "party" wall.

[0290] Thus, the first sub-volume 131a is located on one side of the vertical wall and the second sub-volume 133a is located on the other side of the vertical wall.

[0291] The upper fluid distribution box 133 is here arranged on one side in the grille without necessarily being centered.

[0292] The same applies to the lower fluid distribution box 132.

[0293] In the present embodiment example, the first sub-volume 134a is juxtaposed with the second sub-volume 132a.

[0294] The lower fluid distribution box 132 is here arranged on one side of the grille without necessarily being centered.

[0295] Fig. 11 represents a fourth example of an embodiment of a thermal storage system 1, in which the PCM 2 is encapsulated, conduits 14 being delimited by at least one capsule 20, or even formed between two capsules 20 of PCM.

[0296] This embodiment also differs from that of Figures 5 to 8 in that the thermal storage system 1 further comprises at least one partition 116, 116' delimiting at least a part of one of the conduits 14.

[0297] In this case, a partition 116, 116' is here arranged between two capsules 20.

[0298] Thus, the partition 116, 116' and a first capsule 20 define a conduit of a first side of partition 116, 116', and the same partition 116, 116' and a second capsule 20, adjacent to the first capsule 20, define another conduit on a second side of said partition 116,116'.

[0299] The thermal storage system 1 is thus configured so that the flow of fluid 3 bypasses the partition 116, 116' during a flow of heat transfer fluid 3 entering through the lower terminal 142.

[0300] The partition 116, 116' thus defines a hydraulic baffle.

[0301] In the present embodiment, a first partition 116 extends a wall of the lower partial fluid distribution box 134 between two capsules 20, and a second partition 116' extends a wall of the upper fluid distribution box 133 between two other capsules 20.

[0302] During an incoming flow through the upper terminal illustrated in [Fig. 11] B), the presence of partitions 116, 116' has little or no effect on the flow, and the fluid 3 flows into all the conduits 14, as in the other embodiments described previously.

[0303] During an incoming flow through the lower terminal illustrated in [Fig. 11] C), the heat transfer fluid 3 flows into the third conduit 14c by upward flow, then into the second conduit 14b by downward flow, then into the first conduit 14a by upward flow, and then can exit the thermal storage system 1 through the upper terminal 141 after having traveled through the first sub-volume 131a, as in the embodiments previously described.

[0304] Now, it should be noted here that the third conduit 14c can be a conduit defined on a first side of the first partition 116, while the second conduit 14b can be a conduit defined on a second side of the first partition 116, and / or a conduit defined on a first side of the second partition 116', while the first conduit 14a can be a conduit defined on a second side of the second partition 116'.

[0305] Such a partition 116, 116' can nevertheless be added in at least one of the embodiments described above.

[0306] Fig. 12 illustrates another option applicable to any of the embodiments described above or in connection with Figures 13 to 15.

[0307] According to this option, the thermal storage system 1 may include flow restriction / reduction elements 117, configured to increase pressure losses, and thus reduce the flow rate.

[0308] In the embodiment example of [Fig. 12], the thermal storage system 1 includes a constriction element 117 disposed in the upper hydraulic tube of the terminal 141.

[0309] The constriction element 117 is, for example, here an added element, but it could also be formed by a section deformation of the tubing, for example.

[0310] In an example of an embodiment not shown, such a constriction element 117 could also be disposed in the lower hydraulic tube of the lower terminal 142, whether or not such a constriction element 117 is present in the upper hydraulic tube of the upper terminal 141. This is particularly interesting when, as mentioned previously, the PCM used has a lower density in the solid state than in the liquid state, so that it is then preferable that the pressurized and discharged flows be reversed with respect to those detailed here.

[0311] The invention thus makes it possible to define two differentiated flow configurations of the heat transfer fluid in the duct bundle, depending on the inlet of the heat transfer fluid 3.

[0312] In the discharge configuration of the thermal storage system (i.e., in heat release), the flow of fluid 3 through the conduit bundle This is achieved through a multi-pass process, which increases the fluid velocity within the ducts, and therefore the convective heat transfer coefficient of the heat transfer fluid 3 at the duct wall. Consequently, the thermal power exchanged between the heat transfer fluid 3 and the phase-change material 2 is relatively higher.

[0313] In the load configuration of the thermal storage system (i.e., in heat accumulation), the flow of fluid 3 through the conduit bundle is single-pass. This allows (if necessary) for a temperature gradient to be maintained in the vertical direction throughout the conduits, and thus limits the risk of the formation of pockets of liquid phase-change material within a solid volume (which could lead to degradation or even destruction of the thermal storage system 1).

[0314] In this configuration also, the fluid velocity in the tubes is lower than in the multi-pass configuration, which induces a reduced heat exchange coefficient, and therefore a lower power exchanged.

[0315] Finally, [Fig. 13] presents yet another example of an embodiment of the invention, in which the hydraulic distribution and collection are ensured by "manifolds".

[0316] Indeed, in this example, the upper distributor 130 includes distribution manifolds formed from a plurality of pipes.

[0317] For example, the upper distributor 130 includes a main pipeline.

[0318] The main pipeline has a free end forming the upper terminal 141 and the upper hydraulic valve 31 disposed at a non-zero distance from the upper terminal, and the main pipeline also has a part such that the upper hydraulic valve 31 is disposed between the upper terminal 141 and this part of the main pipeline.

[0319] The upper fluid distribution box 133 is here formed by this part of the main pipe, as well as by at least two secondary pipes (there could be more than two although only two are illustrated) which extend from this part of the main pipe.

[0320] In this embodiment example, the secondary pipes are parallel to each other.

[0321] Each of the at least two secondary pipes communicates with at least one conduit 14.

[0322] In this case, a first of the at least two secondary pipes of the upper fluid distribution box 133 communicates with at least the third conduit 14c and a second of the at least two secondary pipes of the upper fluid distribution box 133 communicates with at least the second conduit 14b.

[0323] The upper partial distribution box 131 is here formed by another secondary pipe which extends from another part of the main pipe of the upper distributor 130, which is that defined between the upper terminal 141 and the upper hydraulic valve 31. This other secondary pipe communicates here with the first conduit 14a.

[0324] The upper distributor 130 here forms an upper main collection which can be disassembled in parts to access the upper hydraulic valve device 31.

[0325] Similarly, the lower distributor 135 includes distribution manifolds formed by a plurality of pipes. For example, the lower distributor 135 includes a main pipe. The main pipe has a free end forming the lower terminal 142 and the lower hydraulic valve 32 disposed at a non-zero distance from the lower terminal 142, and the main pipe of the lower distributor 135 also includes a portion such that the lower hydraulic valve 32 is disposed between the lower terminal 142 and this portion of the main pipe. The lower fluid distribution box 132 is formed here by this portion of the main pipe of the lower distributor 135, as well as by at least two secondary pipes (there could be more than two, although only two are illustrated) extending from this portion of the main pipe of the lower distributor 135.

[0326] In this embodiment example, the secondary pipes are parallel to each other.

[0327] Each of the at least two secondary pipes of the lower fluid distribution box 132 communicates with at least one conduit 14. In this case, a first of the at least two secondary pipes of the lower fluid distribution box 132 communicates with at least the first conduit 14a and a second of the at least two secondary pipes of the lower fluid distribution box 132 communicates with at least the second conduit 14b.

[0328] The lower partial distribution box 134 is here formed by another secondary pipe which extends from another part of the main pipe of the lower distributor 135, which is that defined between the lower terminal 142 and the lower hydraulic valve 32. This other secondary pipe communicates here with the third conduit 14c.

[0329] Similarly, the lower distributor 135 here forms a lower main collection which can be disassembled in parts to access the lower hydraulic valve device 32.

[0330] Fig. 14 illustrates a downward flow; the fluid entering the system through the upper terminal 141.

[0331] In the configuration of [Fig. 14], the upper hydraulic valve device 31 and the lower hydraulic valve device 32 are in the open position, allowing the heat transfer fluid to flow through them. The heat transfer fluid enters through the upper distributor 130 (i.e., the upper main manifold) and is distributed into the various secondary lines (upper secondary manifolds). The heat transfer fluid flows through all the conduits 14 and exits via the secondary lines of the lower distributor 135, and is then collected by the main line of the lower distributor 135 before exiting the thermal storage system 1 through the lower terminal 142.

[0332] Fig. 15 illustrates an upward flow; the fluid entering the system through the lower terminal 142.

[0333] In the configuration of [Fig. 15], the upper hydraulic valve 31 and the lower hydraulic valve 32 are blocked (closed), preventing the heat transfer fluid from passing through them. The heat transfer fluid enters through the main line of the lower distributor 135 and is distributed only in the line of the lower partial distribution box 134, given the closed position of the lower hydraulic valve 32 in this flow configuration. After passing up the third line 14c, blocked by the upper hydraulic valve 31 in the closed position, the heat transfer fluid collected by the first of the at least two secondary lines of the upper fluid distribution box 133 is then distributed by the second of the at least two secondary lines of the upper fluid distribution box 133.The heat transfer fluid descends through the second conduit 14b and is then collected by the second of at least two secondary conduits of the lower fluid distribution box 132, passes behind the lower hydraulic valve device 32 which is in the closed position, then feeds the first of at least two secondary conduits of the lower fluid distribution box 132 and ascends through the first conduit 14a. Arriving in the conduit of the upper partial distribution box 131, beyond the upper hydraulic valve device 31 in the closed position, the fluid exits the thermal storage system 1 through the upper terminal 141.

[0334] Of course, as before, considering a PCM with a lower density in the solid state than in the liquid state, the pressurized and discharged flows can be reversed compared to those described here. Consequently, the arrangement of the manifolds / distributors and valves described here would also be reversed, so that an upward flow (entering through the lower terminal) would be single-pass, and a downward flow (entering through the upper terminal) would be multi-pass.

Claims

1. Demands Thermal storage system (1) implementing a phase-change material (2), the thermal storage system (1) comprising the phase-change material (2), and a heat exchanger (11) having an upper terminal (141) and a lower terminal (142) configured to form an inlet or outlet of a heat transfer fluid (3) in the thermal storage system (1), the heat exchanger (11) having a bundle (111) of conduits (14) extending between the upper terminal (141) and the lower terminal (142), the bundle (111) of conduits (14) having at least three conduits including a first conduit (14a), a second conduit (14b) and a third conduit (14c), each of the conduits (14) being configured to receive a flow of the heat transfer fluid (3), at least a portion of each of the conduits (14) being in contact with the phase-change material (2),the thermal storage system (1) comprising an upper distributor (130) extending between the upper terminal (141) and the bundle (111) of conduits (14), and a lower distributor (135) extending between the bundle (111) of conduits (14) and the lower terminal (142), and the upper distributor (130) comprising an upper partial distribution box (131) and an upper fluid distribution box (133), and the lower distributor (135) comprising a lower partial fluid distribution box (134) and a lower fluid distribution box (132), at least the first conduit (14a) opening on the one hand into the upper partial distribution box (131) outside the upper fluid distribution box (133) and on the other hand into the lower fluid distribution box (132) outside the lower partial fluid distribution box (134),at least the second conduit (14b) opening on one side into the upper fluid distribution box (133) and on the other side into the lower fluid distribution box (132) outside the lower partial fluid distribution box (134), and at least the third conduit (14c) opening on the one hand into the upper distribution box of, fluid (133) and on the other hand in the lower partial fluid distribution box (134), the lower distributor (135) further comprising a lower partial hydraulic tube (143) configured to permit a flow of the heat transfer fluid (3) between the lower partial fluid distribution box (134) and the lower terminal (142), the upper fluid distribution box (133) comprising an upper hydraulic valve device (31), and the lower fluid distribution box (132) comprising a lower hydraulic valve device (32), the upper hydraulic valve device (31) and the lower hydraulic valve device (32) being configured to be open when a flow of heat transfer fluid (3) enters through the upper terminal (141) and closed when a flow of heat transfer fluid (3) enters through the lower terminal (142).

2. Thermal storage system (1) according to claim 1, characterized in that it is configured to include a single pass of heat transfer fluid (3) during a flow from the upper terminal (141) to the lower terminal (142).

3. Thermal storage system (1) according to any one of claims 1 or 2, characterized in that it is configured to include an odd number of passes of heat transfer fluid (3) during a flow from the lower terminal (142) to the upper terminal (141), and comprising at least three passes.

4. Thermal storage system (1) according to any one of claims 1 to 3, characterized in that it is configured to distribute a flow of heat transfer fluid (3), flowing from the upper terminal (141) to the lower terminal (142), in all the conduits (14) of the bundle (111) of conduits.

5. Thermal storage system (1) according to any one of claims 1 to 4, characterized in that it is configured to carry a flow of heat transfer fluid (3), flowing from the lower terminal (142) to the upper terminal (141), through the third conduit (14c), then the second conduit (14b) and then the first conduit (14a).

6. Thermal storage system (1) according to any one of claims 1 to 5, wherein the upper hydraulic valve device (31) comprises a passive system configured to be open by a pressure difference of the heat transfer fluid (3) on either side of the upper hydraulic valve device (31).

7. Thermal storage system (1) according to any one of claims 1 to 6, wherein the lower hydraulic valve device (32) comprises a passive system configured to be opened by a pressure difference of the heat transfer fluid (3) on either side of the lower hydraulic valve device (32).

8. Thermal storage system (1) according to any one of claims 1 to 7, wherein at least one of the upper hydraulic valve device (31) and the lower hydraulic valve device (32) comprises at least one spring-loaded valve.

9. Thermal storage system (1) according to any one of claims 1 to 8, wherein the heat exchanger (11) comprises an upper collecting plate (112) and a lower collecting plate (113), and the conduits of the bundle (111) of conduits (14) extend from the upper collecting plate (112) to the lower collecting plate (113).

10. Thermal storage system (1) according to any one of claims 1 to 9, wherein at least one of the conduits (14) of the bundle (111) of conduits comprises at least one tube (114).

11. Thermal storage system (1) according to claim 10, wherein at least one tube (114) has an outer surface carrying heat exchange fins (115).

12. Thermal storage system (1) according to any one of claims 1 to 11, wherein at least one of the conduits (14) of the bundle (111) of conduits comprises at least one plate delimiting a passage of the fluid (3) in a conduit.

13. Thermal storage system (1) according to any one of claims 1 to 12, comprising at least one partition (116) delimiting at least one conduit (14), the thermal storage system (1) being configured so that the fluid flow (3) bypasses the partition (116) when a heat transfer fluid (3) flows in through the lower terminal (142).

14. Thermal storage system (1) according to any one of claims 1 to 13, wherein the heat exchanger (11) comprises at least one capsule (20) containing the phase change material (2).

15. Thermal storage system (1) according to any one of claims 1 to 14, comprising a shell (12) containing the phase change material (2), the heat exchanger (11) being disposed in the shell (12).

16. Thermal storage system (1) according to any one of claims 1 to 15, comprising at least one constriction element, the at least one constriction element being disposed in a part of at least one hydraulic tube, in particular a hydraulic tube of the upper terminal (141).

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