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    • 专利摘要:
    Is concerned a heat exchanger comprising: at least one first free space (7, 9) for a fluid (3), at least one thermally conductive wall (11) which at least locally limits said at least one first free space, such that heat exchange can take place between said first fluid and said at least one thermally conductive wall. To have a thermal energy storage function, said at least one thermally conductive wall is hollow and contains a material (13) for storing heat energy by latent heat accumulation, in heat exchange with said fluid (3). .
    公开号:FR3052549A1
    申请号:FR1655394
    申请日:2016-06-10
    公开日:2017-12-15
    发明作者:Fabrice Chopard；Boris Chauvet
    申请人:Hutchinson SA；
    IPC主号:
    专利说明:

    HEAT ENERGY STORER EXCHANGER
    The present invention relates to the field of thermal management.
    Are particularly concerned: - a heat exchanger for implementing an exchange of thermal energy with at least a first fluid or between a first fluid and a second fluid, - a generally polygonal plate-shaped member for the realization of a hollow wall of this heat exchanger, in particular in two more particular cases, - a first assembly comprising a plurality of such assembled elements, - a second assembly comprising the aforementioned heat exchanger, with all or part of its characteristics, and a thermally insulating casing which contains, - and a thermal management facility provided with said exchanger.
    In the art there are of course heat exchangers.
    Thus, the publications of patent applications EP165179 and WO1989000664 respectively provide a plate heat exchanger and a tubular heat exchanger.
    A problem remains however in connection with the capacity, on circuits where at least one fluid circulates, at different temperatures depending on the moment, to take advantage of this situation for effective thermal management inviting to avoid unnecessary loss of thermal energy. this fluid (s) have, if only because of this difference in temperature.
    It may be typical that at a given moment a first fluid is in a position to release, or in need of having to release a thermal energy which subsequently a second fluid may need, or any fluid, or even itself, and / or that certain fluids are at a time to be heated and at another time to cool. In addition, the thermal management of an installation, and seek to avoid unnecessary loss of thermal energy, are now considerations to take into account. It is in this context that a heat exchanger is proposed comprising: at least one first free space for a (first) fluid, at least one thermally conductive wall which at least locally limits said at least one first free space , so that a heat exchange can take place between said first fluid and said at least one thermally conductive wall, characterized in that, to have a thermal energy storage function, said at least one thermally conductive wall is hollow and encloses a heat energy storage material by latent heat accumulation, in heat exchange with at least said first fluid.
    To implement a heat exchange between a first and a second fluid: the exchanger will also comprise at least a second free space for the second fluid, such that said first and second fluids flow into the first fluid; ) and second (s) free spaces, respectively, - and said at least one thermally conductive wall will separate said first and second free spaces between them, so that heat exchange between said first and second fluids takes place through said at least one thermally conductive wall.
    Thus, there will be a heat exchanger with storage capacity and delayed recovery of a thermal energy and capable of treating the thermal management of two fluids.
    It may also be that a fluid has in the exchanger more to wait in terms of temperature change of the thermal energy storage material than an exchange with another fluid.
    In this case, it is proposed that said first free space, in the heat exchanger, be divided into at least two (sub) pipes where the two flows (a priori generally parallel) of the first fluid can flow at the same time, the wall thermally conductive which contains the thermal energy storage material is then interposed between said two (sub) conduits.
    If indeed we want to implement a heat exchange between a first and a second fluid, in the context above, it is then proposed that the exchanger further comprises: - at least a second free space for the second fluid, such that said first and second fluids flow into the first (s) and second (s) free spaces, respectively, - and an additional thermally conductive wall separating said first and second free spaces between them, so that the heat exchange between the two fluids takes place through said additional thermally conductive wall. A priori, this additional thermally conductive wall will be devoid of thermal energy storage material.
    The quality of heat exchange will be favorably considered to achieve a high-performance solution while providing a mass production capacity for possible application on vehicles. This can have a direct consequence on the weight and / or the bulk, therefore the relevance, of the solution.
    It is therefore proposed that the, or each said wall may internally present a succession of recesses where are arranged portions of the thermal energy storage material.
    Combining multiple hollows and / or nesting shapes (bumps and hollows) will optimize the weight and bulk, for a given efficiency, or even create pockets / cells serving as possibly individualized receptacles for the accumulation product of latent heat.
    And to optimize also heat exchange, manufacture and use, it is recommended that the wall (s) comprise plates having individually an outer face to be placed in contact with the first or second fluid and an opposite inner face, the inner face. at least one of said plates having recesses where portions of the thermal energy storage material are disposed.
    In addition, it is proposed that the inner faces of the plates may present each of the recesses that face each other, so that the individual portions of the thermal energy storage material disposed in the recesses are engaged in two said recesses which are made face.
    Thus, it will facilitate the establishment and then secure the maintenance in place of these parts of the thermal energy storage material to be disposed in the troughs
    And to manufacture the plates provided with these hollows, we can then quite simply, from flat metal plates, stamp them to form the hollows, fill with the thermal energy storage material the hollows of one of the plates , and comb the whole with the other plate, then fix a priori by welding (in the present description, welding, and other similar techniques such as welding-diffusion, or brazing are equivalents).
    No need for a container for the storage material (which may be based on MCP) or other hollow closing parts, or receiving volumes of this material.
    When Γοη mentions that the exchanger includes plates with inner faces having depressions, it could be only a single plate folded on itself.
    In addition, to facilitate the manufacture, storage and use of the thermal energy storage material, including its installation, it is proposed that, in a said hollow wall, this material has a solid state in the form of 'a single block with hollows and bumps. No need for a waterproof container to be filled with this material.
    In this way, there may also be self-setting of the material in the wall, which is significant in handling and manufacturing series.
    To promote the rigidity of the plates while taking advantage of the bumps and hollows zones then formed, it is also proposed that said plates comprise corrugated plates defining elongated channels forming the recesses where said portions of the thermal energy storage material are disposed. .
    This will again be an ergonomic realization, quite simple, can be obtained by stamping metal plates. A maximum of two plates, without MCP container, will suffice.
    Such a solution will guide the fluid in its free circulation space, for example two transverse general directions to one another, two different stages of the exchanger, typically in said first and second free spaces of circulation of fluids.
    As a material (s) for storing thermal energy, the use of (at least) a PCM material will therefore be favorably provided. Alternatively, it is possible, although not considered preferable here, to use a device operating on the basis of reversible thermochemical reactions as provided in the TCS technology: (CaO / Ca (OH) 2; metal oxides -restructuration-; sulphides see http://energy.gov/sites/prod/files/2014/01/f6/tces_workshop_2013_sa ttler.pdf). For all purposes, it is confirmed that a phase change material - or MCP; PCM English - means a material capable of changing physical state, for example between liquid and solid, in a temperature range for example between -50 ° C and 180 ° C. The transfer of heat (or heat transfer) is done by using its Latent Heat (CL): the material can then store or transfer energy by simple change of state, while maintaining a substantially constant temperature, that of change of state.
    As for the expression "transversely" or "transverse (e)", it has the direction oriented (e) transversely, not necessarily strictly perpendicular to an axis or a reference direction.
    The thermally insulating material (s) hereafter mentioned may be a "simple" insulator such as glass wool, but a foam, for example polyurethane or polyisocyanurate, will certainly be preferred, or even more favorably a porous or even nano-porous thermally insulating material (which therefore includes foams but also fibrous materials, such as glass wool or rock wool) arranged in a vacuum envelope, to define at least one panel insulation, PIV.
    "PIV" or PIV structure means a structure under "controlled atmosphere", that is to say either filled with a gas having a thermal conductivity lower than that of ambient air (26 mW / mK), or "Depression", therefore under a pressure lower than the ambient pressure (thus <10 Pa). A pressure between 10 Pa and 10 Pa in the chamber may in particular be suitable. The enclosure may contain at least one heat insulating material a priori porous (pore sizes less than 1 micron). In this case, the performance of the thermal management to be assured will be further improved, or the overall weight decreased compared to another insulator. Typically, PIV panels (vacuum insulating panel; VIP) are thermal insulators in which at least one porous material, for example silica gel or silicic acid powder (SiO 2), is pressed into a plate and surrounded, under partial air vacuum, a gas-tight wrapping foil, for example plastic and / or laminated aluminum. The resulting vacuum typically lowers the thermal conductivity to less than about 0.01 / 0.020 W / m 2 K under the conditions of use. An insulation efficiency 3 to 10 times higher than that of more conventional insulating materials is thus obtained. The aforementioned heat exchanger may in particular be a plate exchanger, with rigid plates and free space (s) extending through the exchanger, so that the fluid (s) ( s) flowing therethrough, transversely or parallel to one another, through the exchanger, if two fluids are involved.
    Such an exchanger may be ergonomic, compact and of limited weight.
    Alternatively, the hollow wall enclosing the thermal energy storage material, and more preferably the exchanger itself, will be made of flexible, preferably rubbery material, so as to adapt to the shapes and locations of the applications to which the exchanger / storer will be intended.
    Especially in this case, said hollow wall, and preferably again the exchanger itself, may (have) be tubular.
    Applications to hoses and other pipes in vehicles are planned, including in confined areas and where weight can be a major criterion.
    As an element for producing a hollow wall of the aforementioned heat exchanger, with all or part of its characteristics, a first solution provides a generally polygonal plate-shaped element comprising: a first plate having recesses inner face and bumps on the outer face and, peripherally, folded edges at least for some in the same direction, on two opposite sides, - a second generally planar plate, fixed with the first plate, engaged between two opposite folded edges of the first plate, and having bumps on the outer face and hollow on the inner side disposed opposite the hollows of the first plate, - and a thermal energy storage material, by latent heat accumulation, of which at least parts are arranged in the opposite hollows of the plates.
    Two possibilities are then offered, in particular: a) said folded edges are folded alternately in one direction and inversely on two adjacent sides, or - b) said folded edges are folded in the same direction only on said two opposite sides.
    It should be preferred to bend the first plate outward on said two opposite sides.
    A second aforementioned element solution consists in proposing one which comprises: a first plate having depressions on the inner side and bumps on the outer face and, peripherally, on two opposite sides, edges bent in the same direction, towards the outside, - a second plate fixed with the first plate and having the same inner bumps and inner depressions, arranged opposite the recesses of the first plate and, peripherally, on two opposite sides, again folded edges in the same direction, outwardly - as well as said storage material, at least parts of which are arranged in the face-to-face recesses of the plates.
    For an application with two fluids that do not mix, and at least for the second solution, the first and second plates will preferably be rotated relative to each other by 90 ° about an axis passing through the faces inner and outer plates.
    For the first solution, we can superimpose the elements by rotating them relative to each other by 180 ° around an axis passing through the overall plane of the second plate.
    And, for an application with two fluids not mixing, once two elements of the first solution b) superimposed and fixed together to create a said fluid free space, they will preferably be rotated relative to each other 90 ° around an axis passing through the inner and outer faces of the plates.
    With the aforementioned elements, it will also be possible to produce an assembly where these elements, stacked, will thus be fixed together in pairs along the folded edges, to define between two outer faces of two elements arranged face to face, at least one free space fluidics.
    Thus, it will be possible to produce a modular exchanger, with elementary modules that are easy to manufacture, in series, typically by stamping thin thin metal plates.
    A further set comprising: - the heat exchanger in question, and - a thermally insulating casing, containing this heat exchanger and provided with walls containing at least one thermal insulator, the collector volumes of said at least first fluid being interposed between end openings of each free space and at least some of the housing walls traversed by inlet or outlet connections of said at least first fluid.
    The walls containing the thermal insulation will be PIV structure if we aim for a good compromise thermal performance / weight / bulk.
    Is also concerned a thermal management facility comprising: the aforementioned heat exchanger, with all or part of its characteristics, this exchanger being arranged at a cross between a first circuit for the first fluid and a second circuit for the second fluid, so that: - outside the heat exchanger, the first and second fluids flow independently in functional units (on a heat engine, for example cylinders, an air / water radiator, a cylinder head, etc.) on which the one and / or the other fluids act or with which they interact, - and that in the heat exchanger, the first fluid can circulate in the first (s) free space (s) and the second fluid can circulate in the second (s) space (s) free (s), - means (such as one or more pumps) circulation of the first and second fluids, in the first and second circuits respectively, and - at least one valve placed at least on the second circuit of the second fluid, for: - at a first moment (T1) of operation of the installation, let the first fluid circulate alone in the heat exchanger, without the second fluid, and - at a second moment (T2) of operation of the installation, let the first and second fluids flow together in the heat exchanger.
    If necessary, the invention will be better understood and other characteristics, details and advantages thereof will become apparent upon reading the following description, given by way of non-limiting example and with reference to the accompanying drawings, in which: which: - Figure 1 is a diagram of a heat exchanger according to the invention, in cutaway view, Figure 8 is an exploded view, - Figure 2 is a view of a generally plate-shaped member polygonal which can define in elevation half of a stage of exchanger, - Figure 2 is a section along the line III-III, - Figure 4 is an exploded view of an alternative to the previous solution, before assembly, - the FIG. 5 is a section along the line VV of the element of FIG. 4, assembled; FIGS. 6, 7 show in perspective two other element alternatives for the stages of the exchanger, FIG. with tearing off a variant of a tubular exchanger which may be of flexible structure, for example, for an establishment around (or instead of) a hose, - Figures 11,12,13,14 show in perspective two other alternatives of elements for the stages of the exchanger, with exploded views Figures 12,14 and assembled sections, according to XI-XI and XIII-XIII, Figures 11 and 13 respectively, and - Figures 15,16 schematize two applications where can be used the aforementioned exchangers.
    In the first figures, there are examples of heat exchanger 1 for an exchange of thermal energy between a first fluid 3 and a second fluid 5, which can be liquid and / or gaseous respectively. The exchanger 1 comprises: at least one first free space 7 for the first fluid and at least one second free space 9 for the second fluid, such that these first and second fluids flow into the first and second (s) free spaces, respectively, - and at least one thermally conductive wall 11 which separates between them two adjacent free spaces 7,9, so that the heat exchange between the fluids 3,5 takes place through the (each) wall 11 concerned. The expression "at least one free space" indicates this space can be in the form of one or more volumes. In the example of Figures 6-7, it is a single volume with a kind of spacers defining the height of the free space considered, and in the example of Figures 1-5 and 8, a series of adjacent volumes two by two each channeling the fluid considered.
    The or each wall 11 is hollow and contains a material 13 for storing heat energy by latent heat accumulation. This material will thus be, in heat exchange with at least one, and preferably the two first and second fluids 3,5. In this way, we will have in the heat exchanger a thermal energy storage function.
    Using one or more material (s) MCP will allow to combine efficiency, limited weight, flexibility in the choice of shapes or flexibility.
    As a choice of this type of material, it will be possible to provide a rubber composition as described in EP2690137 or EP2690141. Paraffin-based material, eutectic fatty acid (myristic-capric) or eutectic hydrated salt (calcium + potassium chloride) could also be used. Alternatively, the material could be based on fatty acid, paraffin, or eutectic or hydrated salt. Other possibilities exist, such as a PCM impregnated in a porous network.
    Returning to the structure of the exchanger 1, the example of FIGS. 1-7 shows that the or each wall 11 internally has a succession of recesses 15 in which parts 13a, 13b of the material 13 are arranged.
    Preferably, this will be coupled with, on the outer side, ie on the side directed towards the first (or second) free space (s) 7, a succession of bumps 17 on this wall (at the level of said inner recesses 15 where then will extend, between said two bumps, said free space (s) considered (s), so as to nest or inter-engage these forms together to maximize heat exchange surfaces and compactness, thus to promote a reduced weight, for a given efficiency.
    In order to make it possible to house the most important volumes of this material 13, the embodiments illustrated for example in FIGS. 2-3,5-7 show hollows 15 which advantageously face each other.
    The presence of the inner depressions 15 on the walls 11 must facilitate the establishment and maintenance of the storage material 13, especially since it is proposed that, in the case of a PCM, it is presented, in a solid state having depressions 130 and bumps 131, the latter being housed in the recesses 15. The material is directly in the recesses 15 of the wall, without the need for an intermediate container to fill and close.
    Thus, in a hollow wall 11, the bumps 131 of the storage material will become lodged in the recesses 15.
    And to promote the self-setting of the material in the wall 11, the embodiment illustrated for example in FIGS. 4-5 shows a material 13 in the form of a single block, in other words a sheet, interposed between two first and second free spaces 7,9.
    To promote easy manufacture and series, an embodiment of the walls 11 with plates 21, as shown, may be very appropriate.
    These plates 21, of which individually the outer face 210a is in contact with the fluid 3 or 5 considered, will present favorably, on the opposite inner face 213 and as illustrated, said recesses 15 where in this case will be disposed the relevant parts of the storage material 13 of thermal energy.
    To increase the useful volume of the thermal energy storage material 13 while stabilizing it in the exchanger 1, it is furthermore possible to recommend that two such plates 21 face-to-face, as in the embodiment illustrated in FIG. 5, are used as a wall with, disposed between and in their inner recesses 15, the material 13, these plates being separated by (at least) a spacer or shim 23.
    In the embodiment shown schematically in these figures 4-5, the spacer 23 is in the form of a peripheral frame 233 in the middle of which extends the block of material 13 and spacers 230 provided with passages 231 which are traversed by the block of material ( its liquid state having allowed this), which was molded there in the liquid state (MCP in liquid phase for example). The spacer 23 may be metallic, with a continuous and solid peripheral frame, 233.
    The two plates 21 are then separated by the block of material 13 and the spacer 23. The whole is attached peripherally sealingly vis-à-vis the material 13 in its liquid state.
    If, alternatively, it is desired to favor the aforementioned nests while keeping two adjacent plates directly together by their internal faces 213, for example by direct welding of metal plates between the recesses 15, face to face, it may be preferable, as in the embodiment illustrated in FIGS. 1-3, that, in a hollow wall 11, the material 13 is presented as a series of several elements 134 which are belly or bulging outwardly, each adapted to be housed in at least one said recess 15, so that between two side-by-side hollow, such as 15a1,15a2, of the same plate there is no material 13 for storing thermal energy.
    The recesses 15 may individually define a closed contour socket 25 (FIGS. 1-3).
    This may make it possible to produce the walls 11 by molding, or, if they are metallic, by stamping a series of such cells 25 on a single plate which can then be folded on its lateral edges (see below), or even folded on it. same, to create the closed volume 25 which can each contain a portion of said material 13.
    To promote the rigidity of the plates while taking advantage of the bumps 17 and hollow zones 15 then formed, it is also proposed, alternatively, as in the embodiment illustrated in FIGS. 2, 3, that said plates 21 are corrugated, defining elongated channels 151 forming the recesses 15 where are disposed of said parts of the material 13.
    Such a solution will guide the fluid 3 or 5 considered in its free circulation space 7 or 9, for example two general directions 7a, 9a transverse to each other two stages 27a, 27b different from the exchanger 1, typically in said first and second free spaces for fluid circulation (Figure 1 in particular).
    From the foregoing it should be understood that it will be easy with a plate base to construct a multi-stage heat exchanger 1 from a series of elementary modules 10 constructed with a single type of plate 10a, as in the embodiments illustrated in Figure 7 for example, or two types of plates 10b1,10b2 as in the embodiment of Figures 2,3,6 for example. The heat exchanger 1 may in particular be a plate heat exchanger, with rigid plates 21 and first and second free spaces 7, 9 extending through the exchanger, so that the first and second fluids they flow transversely or parallel to one another.
    The stages of the exchanger-storer 1 will then rise in a direction A perpendicular to the general plane 100a of the plates then parallel to each other.
    Alternatively, the hollow wall 11 enclosing the material 13, and preferably, more generally the storage exchanger 1 itself will be (a) flexible material, preferably rubber, as in the embodiment shown in Figure 9.
    In this case, in particular, said hollow wall 11, and preferably again the storage exchanger 1 itself, may (have) be tubular (s), for example an application to hoses and other pipes in a vehicle (automobile, aircraft, ship ...), typically where weight or accessibility is a major criterion.
    Thus, FIG. 9 shows that the tubular heat exchanger 110 also comprises the first and second free spaces 7, 9 for two exchange fluids 3.5, with a thermally conductive wall 11 hollow between them with a material 13 (MCP typically). The wall 11 has externally and internally a succession of bumps and depressions 15,17.
    The realization could be made from a flexible flat plate form rolled on itself substantially in cylinder and fixed to itself at its ends wound to obtain a laterally closed tube.
    Couplings 101, 103, differentiated for each fluid, allow the inputs and outputs of fluids 3,5. In the center can still circulate a third fluid 105 which can also be in heat exchange with the peripheral fluid which circulates radially closest to it, here the fluid 5. To create a heat exchange between the fluid 105 and the peripheral fluid which circulates radially the closest to him, here the fluid 5, the wall 111 of the heat exchanger 110 which separates them is thermally conductive. The circulation paths of the fluids in the heat exchanger 110 may be various: circulations for some in opposite directions (see Figure 9), in helices for all or part of the peripheral fluids 3.5 ... etc.
    As regards the modular character that the storage exchanger 1 may have, the exemplary embodiments of FIGS. 1-5,8 show a possible embodiment from an element 100 in the general form of a polygonal plate (here rectangular) comprising a first plate 10BI peripherally presenting, on all its edges, flanges (or folded edges) 29a, 29b alternately in one direction and in reverse on two adjacent sides 31a, 31b and 31c, 31d, and depressions 15 on the inside. 213 and bumps 17 on the outer face, - a second plate 10b2 fixed with the first plate 10bI, engaged between two opposite flanges, 29b, of the first plate and also having bumps 17 on the outside and hollow 15 on the inside. these recesses being disposed opposite the recesses 15 of the first plate 10bI (see Figure 3 for example). and thus the material 13 of which at least parts 13a are individually arranged in the recesses 15 of the plates.
    To fix the plates together, each will advantageously have a continuous planar frame 31, two planar frames 31 (applied one against the other) of two plates 10b1, 10b2 coming from an inner face to an inner face (first solution, FIGS. 2-3) or inner face against flat face of the frame forming the spacer or shim 23 (second solution, Figures 4-5), to be fixed together tightly, as above.
    The exemplary embodiments of FIGS. 6, 7 show alternative embodiments from element 101 or 103 respectively.
    In a first variant, as in FIG. 6, an element 101 always in the general shape of a polygonal plate (here rectangular) comprises: a first plate 10c1 having depressions 15 on the inside face and bumps 17 on the outer face and, peripherally, on two opposite sides, flanges, or folded edges 29a1,29a2, in a same direction, towards the outer face 212a, - a second plate 10c2 fixed with the first plate and having bumps 17 on the outer face and depressions 15 on the inner side arranged opposite the recesses of the first plaquelOcl, and, peripherally, on two opposite sides, edges 29a3,29a4 also folded in the same direction, to the outer face 212b, the first and second plates can be rotated relative to the other 90 ° around an axis passing through the inner and outer faces of the plates (axis A), if one wants unmixed and transverse fluid flows 3.5, - and t or always the intermediate material 13.
    Figures 6-7, the blocks of MCP are isolated / distinct from each other. The recesses where the bulging portions 134 of the material 13 are arranged individually define a cell 25 with a closed contour.
    In a second variant, as in FIG. 7, the generally polygonal plate element (here rectangular) 103 comprises: a first plate 10b having bumps 17 on the outside and indentations 15 on the inside, and - a second plate 10b2 generally flat having the same bumps 17 and recesses 15 disposed opposite the recesses of the first plate 10bI, and always the intermediate material 13.
    The face-to-face depressions define individual material cells.
    The second plate 10b2 is engaged between two opposite folded edges of the first plate.
    The plates 10b1, 10b2 will be secured together by their respective surfaces and planar areas which extend between the inner depressions 15.
    On the outer face and peripherally on all sides, the first plate 10bI has (like that of Figures 2,3) edges 29a1,29a, 29a3,29a4 folded in opposite pairs, on one side to the adjacent side.
    To form one of the free spaces (7,9), the ends 290 of the folded edges will then be fixed with (typically welded / brazed) with the ends 290 of the folded edges of another element 101 or 103.
    We can proceed in a comparable manner with the solutions of Figures 1-5 to create the free space or spaces (9 and / or 10); identified ends 291 of the folded edges, Figures 1-3.
    In other words, it will be possible to produce a set 160 of elements (FIG. 1) of the type presented above comprising several said elements 100, 101, 103 for example, fixed together in pairs along the folded edges, such as 29a1, 29a2,29a3,29a4, to define between two outer faces of two elements arranged face to face at least one free space 7 or 9.
    If two fluids are then in circulation, like those 3.5 of FIGS. 1.8, they will be able to circulate in parallel or transversely to one another, according to the relative orientations of the superposed adjacent plates used.
    Figures 1,8, it will be noted that with a stack in a direction A of a stepped succession for example of elements 100: - each issued from the assembly of first plate 10bI, with alternating flanges 29a or 29b on all sides (31a, 31b, 31c, 31d), with a second plate 10b2, and arranged, from one stage 27a to the next 27b, with a relative rotation of 90 ° about the axis A (here axis of symmetry), will be able to create, as illustrated, a succession of free spaces 7 and 9, floor after floor, with, between two successive stages, such 161,162, a hollow wall 11, with cells 25 in the example, containing material 13.
    Fluid 3.5 pass, every other floor, in the free spaces 7,9, in two transverse directions, each perpendicular to the axis A.
    And around this stack, which in the example offers six stages of free space to the fluid 3 and five stages of free space to the fluid 5, stands a collector volume 163 per side face; see in particular figure 8.
    Each collecting volume 163, located opposite an opening 70 or 90 end of each free space here 7,9, receives the fluid considered, here 3 or 5, to pass through the free spaces 7 or 9 of heat exchange , or just passing in this (these) free space (s).
    Thus, each series of free space stages 7 (respectively 9) communicates upstream (with respect to the direction of circulation of the fluid considered) with a first collector volume 163 and, downstream, with a second collector volume 163 located opposite opposite side.
    Externally, each collecting volume 163 is bounded by a side wall 165.
    Each side wall 165 will preferably be traversed at 167 by a passage communicating with a collector volume 163, for connection to a conduit 169 for supplying or discharging fluid 3 or 5.
    Each side wall 165 will also preferably contain a thermal insulating material 171.
    Between two adjacent lateral faces, such as 165a, 165b, the collector volumes 163 are fluidically isolated from each other.
    For this, each assembly of first and second plates 10b1, 10b2 has an overhanging tab 175 in each lateral angle (FIGS. 2, 8, 8 in particular).
    To facilitate this, the plates may be favorably made from all stampable and weldable metals.
    The tabs 175 usefully form, in each corner, an edge parallel to the stacking direction A, here the vertical. To obtain a complete block, therefore a multi-stage heat exchanger / store, it will suffice, as is apparent from FIGS. 1.8, to superimpose elements 100 (or 101 or 103 in particular) with plates welded together along the turned edges and vertical edges. This will result in an alternation of channels or free spaces 7,9, crossed with respect to each other and closed on two opposite sides.
    The final embodiment of the block will then pass through an interface with the side walls 165, for the peripheral sealing, and thus the insulation between the collector volumes 163.
    Rather than a direct engagement with these walls, it is proposed here that the axial lines (in this case vertical lines) of tabs 175 fixed together engage between two vertical wedges 179, for example chamfered, of intermediate frames 177.
    The intermediate frames 177 will then be interposed, laterally, between the stack of elements 100 and the side wall 165 opposite.
    In the lateral angles, pillars 179 are raised axially between two adjacent side walls 165, or, as in the illustrated example, between two adjacent lateral frames 177, the whole being then covered by side walls 165.
    Fastening means, such as screws 173, will be able to join together, all here engaged in the side walls 165 and the corner pillars 179.
    Transversally to the axis A, here above and below, plates 181 of lid, full, participate in the closure, preferably sealed and thermally insulated, the collector volumes 163. Like the walls 165, the plates 181 preferably each contain a thermal insulating material 171.
    In fact, it is recommended that (preferably all) these walls 165 and plates 181 are PIV structure, therefore airtight. Thus, their interior volumes containing the thermal insulation (s) 171 will be under the controlled atmosphere created for example because of a peripheral welding of a plastic or metal envelope containing this (s) insulation (s) ) heat (s) 171. The passages for the ducts 169 and screws 173 will then be sealed.
    The pillars or uprights 179 may not be of PIV structure.
    All assembled and fixed, we obtain the housing 183 operational as heat exchanger / storage thermally efficient with an internal circulation of fluids. One advantage of the PIV solution is to limit the thickness of insulator 171, especially if a porous insulator, such as an airgel, is used, and therefore either to increase the internal volume of the housing available for the exchanger or the overall volume of the case. Better insulation and / or weight limitation can also be expected.
    With regard to the tabs 175, one embodiment provides, as shown in FIG. 2, to form them all, per element 100, in a first plate 10bI, taking advantage of the bias extensions (at 45 ° a priori, as shown) created by two adjacent edges. alternately folded, such as 29a, 29b.
    Each plate 10BI may be thus stamped as illustrated in FIGS. 4,6,7, after which it was sufficient to put in place the storage material 13, and to close the whole by the second plate 10b2 engaged between the edges of the first plate 10BI and fixed with it, preferably in a sealed manner with the (x) MCP material (s) contained (s).
    Thus, each finite element such as 100, 101 or 103 will thus have peripherally sealed walls that are fastened peripherally, for example welded at the location of the continuous planar frames 31 of two said plates arranged face to face.
    In Figure 10, we see an alternative to the solution of Figure 1.
    This is a situation where the heat exchanger 210, which is not seen here the external packaging casing (with the collector volumes 163, the side walls 165 through which the ducts 169 feed and covers 181 of the FIG. 8) is adapted so that the first free space 7 (stage 270a) is, in the exchanger, split into at least two sub-ducts 7a, 7b where the (first) fluid 3 can flow at the same time.
    Between the two sub-ducts 7a, 7b extends, in the heat exchanger, a said thermally conductive wall 11 which encloses the thermal energy storage material 13 which is therefore interposed between the two sub-ducts 7a, 7b.
    Thus, the fluid 3 will split in the exchanger in several streams, here two parallel (sub) flows (see arrows Figure 10), the intermediate material 13 (typically containing MCP) charging or releasing energy thermal, depending on the fluid temperature 3.
    All the stages of the exchanger 210 could be like the stage 270a above.
    However, it will be possible to find that a second fluid 5 also circulates in the exchanger 210, in heat exchange with the (first) 3-stage fluid 270b - without mixing these flows.
    It is for this reason that the exchanger 210 further comprises: at least one second free space 9 for the second fluid 5, so that said first and second fluids 3.5 flow in the first and second (s) free spaces, respectively, - and that an additional thermally conductive wall 211 separates between them first and second adjacent free spaces 7, so that the heat exchange between the first and second fluids 3, 5 with two adjacent successive stages, 27a, 27b takes place through this additional thermally conductive wall 211.
    Thus, between two sub-ducts 7a, 7b, where the first fluid 3 circulates, will be interposed a material 13 for storing thermal energy, whereas this will not be the case between the first and second ducts 7, 9 where thus circulating respectively the first and second fluids 3,5, without mixing, substantially transversely to each other. The double wall 211 is thus devoid of material 13.
    The walls 11,211 may be metallic.
    With reference to FIGS. 11-14, a manner of manufacturing the walls 11, 211 of FIG. 10 will now be presented.
    The wall 11 of Figure 11 is made as shown in Figure 12, from two identical parallelepiped plates 10b3 whose two opposite edges 29b are folded (at right angles) in the same direction.
    The two plates are parallel. In the general plane of each plate, the frame 31 surrounds the central portion provided with depressions 15 and bumps 17, here again in the manner of a corrugated sheet.
    Between the two plates 10b3 is interposed the material 13.
    For assembly, one of the two plates is rotated 180 ° with respect to the other, around the X axis passing through the two opposite unfolded edges, with the edges 29b back to back. They are then assembled in an airtight manner (typically soldered), by their frames 31 applied against each other, after interposition of the material 13, so as to obtain the double wall 11 of FIG. 11.
    The wall 211 of Figure 13 is made as shown in Figure 14, from the two plates 10b3 identically folded opposite edges 29b.
    Nothing is interposed between the two parallel plates 10b3.
    For assembly, one of the two plates is rotated 180 ° with respect to the other, around the axis X passing through the two opposite unfolded edges, with the edges 29b facing each other. They are then assembled airtight (typically welding), by the ends 290 of their folded edges so as to create between the two plates the duct 9.
    If the corrugated sheet form is provided, the corrugations then cross from one plate to another, which favorably increases the exchange surfaces.
    A stage 270b is then created. To create an adjacent stage 270a, it suffices to place a double plate 11 and a double plate 211 in coaxial manner, superimposing them together and then sealing the two end lengths in an airtight manner (typically welding). 290 of the first on the two opposite edges of the frame 31 facing it.
    Thus, we obtain two crossed superimposed ducts, isolated from one another and separated by a "simple" wall (without material 13).
    If above the double plate 11 is placed another double plate 211 oriented like the previous one and still fixed by the ends 290, then the two above-mentioned superimposed sub-ducts 7a, 7b separated by the double wall 11 of material are created. 13.
    As previously, in order to avoid the mixing of the fluids 3,5 of the tongues 175, usefully form, at each angle, an edge parallel to the stacking direction A which makes it possible to obtain a multi-stage heat exchanger / store (see FIG. 10), having an alternation of channels or free spaces 7,9, crossed with respect to each other closed on two sides.
    This exchanger 210 can then be placed in the housing 183 as shown in FIG. 8, to collect the fluid (s) at the outlet of the exchange plates and for peripheral thermal insulation.
    An operational application of the exchangers with thermal storage capacity 1,210 may be the following, as shown schematically in FIG. 15 or 16 on a thermal management installation comprising: the heat exchanger (1 or 210) at a cross between a first circuit 6 for the first fluid 3 and a second circuit 16 for the second fluid 5, so that: - outside the heat exchanger, the first and second fluids independently circulate in functional members (14, 140, 23) on which they act or with which they interact and in said exchanger, the first fluid 3 can circulate in the first free space (s) 7 and the second fluid can circulate in the second space (s) (s) free 9, - means (12,143,217) for circulation of the first and second fluids, in the first and second circuits respectively (and in the exchanger), and at least one valve 251 placed at least on the second c circuit 16, for: - at a first moment (Tl) of operation of the installation, let the first fluid 3 circulate alone in the heat exchanger, without the second fluid 5, and - at a second moment (T2) of operation of the installation, let the first and second fluids flow together in the heat exchanger.
    Typically, this thermal management facility is expected to be mounted on a heat engine 8, in particular an internal combustion engine.
    Consider, in a first case, as Figure 15, a first circuit 6 of engine oil (for example an automatic gearbox oil 213) and a second circuit 16 of water. It is then preferably the exchanger / storage 210 (Figure 10) which will be mounted at the intersection of the circuits, as illustrated. From the launch of the engine 8, for example after the vehicle has been parked 5-7 hours outside, under 5 ° C, and while the material 13 of thermal energy storage of each of the walls 11 of the floors 270a is assumed in liquid phase, for example to 80-100 ° C, the oil flows in the circuit 6 via the oil pump 217. At this time, says T1: the oil enters (as a first fluid 3) by an inlet 169 (Figure 8) in the stages 270a of the heat exchanger 210 (Figure 10), for example to 6-8 ° C. It is heated therein by the MCP 13, while access to the heat exchanger for the water of the circuit 16 (as a second fluid 5) is then prohibited, the inlet valve 251 being closed.
    The displacement motor 8 operating, the water then circulates in certain ducts and parts of the vehicle (cylinders 14, cylinder head 141 for example) via the water pump 143 of the circuit 16. At this moment, the water 5 is still too cold to heat the oil. The motor thermostat 145 and the valve 251, then closed, force it to circulate only in the engine, without any circulation in the exchanger / storage 210. However, the water rises faster in temperature than the oil. Once it reaches a temperature higher than that of the oil, the inlet valve 251 opens (and, when the time comes, the thermostat 145 passes the water in the radiator 18, if it is useful to cool it so that it does not exceed about 90 ° C, preferably). Said second moment T2 has arrived, it being specified that another valve 252 can block a return of water to the exchanger 210 (FIG. 15).
    While the oil continues to circulate in the stages 270a of the exchanger / storage 210, the circulating water 5 now reaches, via an arrival 169 independent of the previous, in the stages 270b (Figure 10). The oil is then heated by the water, and possibly by the material 13 on both sides of which it flows and which gives energy to it through the walls 211, as long as the MCP is not passed below its temperature of change of states (of the order therefore of 60-70 ° C in the example).
    The temperature rise of the engine continues. The water now reaches exchanger 210 at 80 ° C. The oil continues to heat by exchange with the water 5, through the walls 211. The oil now reaches the exchanger / storage 210 at over 70 ° C. It begins to bring heat to the material 13 which then charges thermal energy, which will be available for the next operation of the engine, after a new stop.
    Continuing to heat in the engine, the temperature (t1) of the oil 3 now exceeds 90 or 100 ° C, so that (t2) of the water 5.
    To avoid overheating, the oil then transfers heat energy to the water 5 (walls 11) and the material 13 (as far as possible) into the exchanger / storage tank 210.
    In another case, as FIG. 16 where, at the intersection of the circuits, the exchanger / storer 1 will be mounted (FIG. 1), the second water circuit 16 in connection with the engine 8 will now be used on the engine 8. vehicle air circuit, as the first circuit 6 on which is mounted a turbocharger 12. The engine 8 is turbocharged in this example.
    Let us first consider that, as in the previous case, the vehicle concerned was parked, even in the cold (negative temperature in winter), engine 8 stopped, for 5-6 hours. If, during its operation prior to this stop, the engine 8 has worked for example 10-15 mns with its turbo 12 launched, the MCP 13 has exceeded its temperature of change of state and is therefore, in the example, beyond beyond its liquefaction temperature. All the more with the thermal insulation (preferably with side walls 165 PIV) of the housing 183 and the multiple stages of the exchanger / storage 1, it is near for a certain time (5-6 hours in the example ), to heat the fluid 3 (here air) at the next engine start.
    This engine start then occurs. The turbocharger 12 is still stopped. At this moment, outside air 3 arriving, still relatively cold, from the first air circuit 6 to the combustion chamber (s) 14/140 of the engine 8, then circulates in passing through the stages 27a of the exchanger / storage 1.
    It is then said first moment Tl: the valve 251 is closed and forces the water of the circuit 16 to circulate only in the engine, off the exchanger / storage 1. Thus, the water being itself itself cold, one prevents the air then losing calories in a heat exchange between them, while it has heated in exchange with the material 13 hotter than him.
    Thus passed for example from 5-10 ° C to for example respectively between 40-50 ° C, this air will be able to feed at a favorable temperature the (the) chamber (s) of combustion 14/140.
    A few minutes (3 to 4 for example) after this first phase following the engine start, the turbocharger 12 starts. This causes an immediate increase in pressure and temperature (at more than 150 ° C., typically around 180 ° C.) of the air (of the oxidizer) of the first circuit 6.
    However, supplying the combustion chambers 14 of the cylinders 140 at such temperatures is inappropriate: too high thermal stress, yield drop ... Do it to 100-130 ° C and preferably to 110 ° C is sought.
    Moreover, the motor 8 is then already in operation; since a few minutes, so with its circuit 16 of course active, the water (as a coolant of the relevant parts of the engine) is already relatively hot in the circuit 16, even if it is cold around. Indeed, for example a well-known motor thermostat 145, then closed, could have forced the water to circulate only in the engine, without therefore temporarily circulating in the radiator 18. This water will be quickly warmed by circulating around the cylinders 140 and in the cylinder head 141 of the engine 8 before returning to the water pump 143 (see Figure 16).
    Thus, it is reasonable to consider a rise in water temperature up to 40-60 ° C at this time.
    The cycle of said moment T2 in the exchanger / storage 1 can intervene, especially since this second fluid 5 is at time T2 at a favorable temperature (50 ° C for example) to lower that of the air from the turbo 12 which, when passing through the stages 27a, could supply thermal energy to the material 13.
    With these two heat exchanges, here simultaneous, it can be considered that at this moment T2, while at the outlet of turbo 12 the compressed air (for example towards 2-2.5 105 Pa in absolute pressure) is at a temperature of 170.degree. 190 ° C, it can go down to 110-120 ° C after exchange, in the exchanger / storage 1, with the material 13 and water 5.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    A heat exchanger comprising: at least one first free space (7) for at least one first fluid (3); at least one thermally conductive wall (11) which at least locally limits said at least one first free space (9); ), so that a heat exchange can take place between said first fluid and said at least one thermally conductive wall (11), characterized in that, to have a thermal energy storage function, said at least one thermally conductive wall (11) a thermally conductive wall (11) is hollow and contains a heat storage material (13, 13a) by latent heat accumulation, in heat exchange with at least said first fluid.
    [2" id="c-fr-0002]
    2. Heat exchanger according to claim 1, for implementing a heat exchange between said first fluid (3) and a second fluid (5), wherein: the exchanger further comprises at least a second free space (9) for the second fluid (5), such that said first and second fluids flow into the first (s) and second (s) free spaces, respectively - said at least one thermally conductive wall separates said first and second free spaces (7, 9) so that heat exchange between said first and second fluids takes place through said at least one thermally conductive wall (11).
    [3" id="c-fr-0003]
    3. Heat exchanger according to claim 1, wherein said first free space (7) is, in the exchanger, split into at least two ducts (7a, 7b) where two flows of the first fluid (3) can flow at the same time, the thermally conductive wall (11) which encloses the thermal energy storage material (13, 13a) being interposed between the two ducts (7a, 7b).
    [4" id="c-fr-0004]
    4. Heat exchanger according to claim 3, for implementing a heat exchange between said first fluid (3) and a second fluid (5), wherein the exchanger further comprises: - at least a second free space (9) for the second fluid (5), such that said first and second fluids flow into the first (s) and second (s) free spaces, respectively; - an additional thermally conductive wall (211) separates them from said first and second second free space (7,9), such that heat exchange between said first and second fluids takes place through said additional heat-conducting wall (211).
    [5" id="c-fr-0005]
    5. Heat exchanger according to claim 1 or 2, wherein the, or each said wall (11) has internally a succession of recesses where are disposed portions of the thermal energy storage material.
    [6" id="c-fr-0006]
    6. Heat exchanger according to any one of claims 2,4, wherein the wall (s) (11,211) comprise plates (10bI, 10b2; 10c1,10c2) individually having an outer face to be placed in contact with the first or the second fluid (3,5) and an opposite inner face, the inner face of at least one of said plates having recesses (15) where portions of the thermal energy storage material are disposed.
    [7" id="c-fr-0007]
    7. Heat exchanger according to any one of the preceding claims, wherein the one or more thermal energy storage materials (13) comprise a MCP material.
    [8" id="c-fr-0008]
    8. plate heat exchanger according to claim 6 or claims 6 and 7, wherein the plates (11) are rigid and said at least first and second free spaces (7,9) extend through the heat exchanger. heat so that said first and second fluids flow into the first (s) and second (s) free spaces, respectively, transversely or parallel to each other, through said heat exchanger with plates.
    [9" id="c-fr-0009]
    9. A generally polygonal plate-shaped element for producing a hollow wall of the heat exchanger according to any one of the preceding claims, which comprises: a first plate (10b1) having depressions on the inside and bumps on the outer face and, peripherally, edges (29a, 29b) folded at least for some in the same direction, on two opposite sides, - a second plate (10b2) generally flat, fixed with the first plate, engaged between two opposite edges folded of the first plate, and having bumps on the outer face and recesses (15) on the inner face disposed opposite the recesses of the first plate, - and a material (13) for storing thermal energy, by heat accumulation. latent, at least parts of which are arranged in the face-to-face depressions of the plates.
    [10" id="c-fr-0010]
    The element of claim 9, wherein the folded edges (29a, 29b) are bent alternately in one direction and reverse on two adjacent sides.
    [11" id="c-fr-0011]
    11. Element in the general form of a polygonal plate for producing a hollow wall of the heat exchanger according to any one of the preceding claims, which comprises: a first plate (10c1) having recesses (15) on the inside face; and bumps (17) on the outside and, peripherally, on two opposite sides, edges (29a1, 29a2) folded in the same direction, towards the outer face, - a second plate (10c2) fixed with the first plate and having bumps on the outer face and depressions on the inner face disposed opposite the recesses of the first plate, and, peripherally, on two opposite sides, edges (29a3, 29a4) bent in the same direction, towards the outer face, - and a heat energy storage material (13), latent heat accumulation, of which at least portions are disposed in the face-to-face recesses of the plates.
    [12" id="c-fr-0012]
    An assembly of individual elements according to any one of claims 9 to 11, which comprises a plurality of said elements secured together in pairs along the folded edges (29a1, 29a2 ... 29a, 29b) to define between two outer faces of two elements arranged face to face, at least one free space for a circulation of a fluid (3, 5).
    [13" id="c-fr-0013]
    13. An assembly comprising: - the heat exchanger according to any one of claims 1 to 8, and - a thermally insulating casing (183) containing the heat exchanger and provided with walls (165, 181) containing at least one thermal insulator ( 171), volumes (163) collector of said at least first fluid (3) being interposed between end openings of each free space (7,9) and at least some of the walls (165) of the housing through which there are connections ( 169) input or output of said at least first fluid (3).
    [14" id="c-fr-0014]
    14. The assembly of claim 13 wherein the walls (165,181) containing the thermal insulation (171) are PIV structure.
    [15" id="c-fr-0015]
    15. A thermal management system comprising: - the heat exchanger (1,210) according to claim 2 or 4, alone or in combination with any one of claims 3 to 8, or the assembly according to claim 13 or 14, heat exchanger being arranged at a cross between a first circuit (6) for the first fluid (3) and a second circuit (16) for the second fluid (5), so that: - out of the heat exchanger, the first and second fluids (3,5) circulate independently in functional members (14,140 ...) on which they act or with which they interact, - in the heat exchanger, the first fluid (3) can circulate in the ( s) first free space (s) (7) and the second fluid (5) can circulate in the second (s) free space (s) (9), - means (12,143,217) for circulating the first and second fluids (3,5) in the first and second circuits (6,16) respectively, - at least one anne (251) placed at least on the second circuit (16) of the second fluid (5), for: ~ at a first moment (Tl) of operation of the installation, let the first fluid (3) circulate alone in the heat exchanger (1, 210), without the second fluid (5), and - at a second moment (T2) of operation of the installation, let the first and second fluids (3.5) flow together in the heat exchanger .
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    同族专利:
    公开号 | 公开日
    WO2017212198A4|2018-02-15|
    CN109477694A|2019-03-15|
    US20190310026A1|2019-10-10|
    EP3469286A1|2019-04-17|
    WO2017212198A1|2017-12-14|
    FR3052549B1|2019-10-11|
    引用文献:
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    法律状态:
    2017-05-05| PLFP| Fee payment|Year of fee payment: 2 |
    2017-12-15| PLSC| Search report ready|Effective date: 20171215 |
    2018-05-23| PLFP| Fee payment|Year of fee payment: 3 |
    2019-05-22| PLFP| Fee payment|Year of fee payment: 4 |
    2020-05-26| PLFP| Fee payment|Year of fee payment: 5 |
    2021-05-20| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1655394|2016-06-10|
    FR1655394A|FR3052549B1|2016-06-10|2016-06-10|HEAT ENERGY STORER EXCHANGER|FR1655394A| FR3052549B1|2016-06-10|2016-06-10|HEAT ENERGY STORER EXCHANGER|
    CN201780044099.7A| CN109477694A|2016-06-10|2017-06-09|Heat exchanger-storage heater|
    EP17735200.2A| EP3469286A1|2016-06-10|2017-06-09|Heat exchanger-accumulator|
    US16/307,899| US20190310026A1|2016-06-10|2017-06-09|Heat exchanger - accumulator|
    PCT/FR2017/051482| WO2017212198A1|2016-06-10|2017-06-09|Heat exchanger-accumulator|
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