US20120241120A1 - Latent heat store - Google Patents

Latent heat store Download PDF

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Publication number
US20120241120A1
US20120241120A1 US13/385,429 US201213385429A US2012241120A1 US 20120241120 A1 US20120241120 A1 US 20120241120A1 US 201213385429 A US201213385429 A US 201213385429A US 2012241120 A1 US2012241120 A1 US 2012241120A1
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United States
Prior art keywords
heat exchanger
heat
unit
fluid
units
Prior art date
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Abandoned
Application number
US13/385,429
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English (en)
Inventor
Hubert Hagel
Juergen Licht
Sebastian Franz
Roland Froemel
Stefan Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Handtmann Systemtechnik GmbH and Co KG
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Handtmann Systemtechnik GmbH and Co KG
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Assigned to HANDTMANN SYSTEMTECHNIK GMBH & CO. KG reassignment HANDTMANN SYSTEMTECHNIK GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAGEL, HUBERT, LICHT, JUERGEN, Franz, Sebastian, FROEMEL, ROLAND, SCHNEIDER, STEFAN
Publication of US20120241120A1 publication Critical patent/US20120241120A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/021—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material and the heat-exchanging means being enclosed in one container
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00492—Heating, cooling or ventilating [HVAC] devices comprising regenerative heating or cooling means, e.g. heat accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/001—Heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/14—Indicating devices; Other safety devices
    • F01P2011/205—Indicating devices; Other safety devices using heat-accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0004—Particular heat storage apparatus
    • F28D2020/0008—Particular heat storage apparatus the heat storage material being enclosed in plate-like or laminated elements, e.g. in plates having internal compartments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0004—Particular heat storage apparatus
    • F28D2020/0021—Particular heat storage apparatus the heat storage material being enclosed in loose or stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0069—Distributing arrangements; Fluid deflecting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the invention relates to a latent heat store comprising a plurality of heat exchanger units which are arranged alongside one another and each comprise at least one phase change store according to the preamble of Claim 1 .
  • Latent heat stores are used for the temporary intermediate storage of heat, with a phase change of the widest variety of substances in the event of a change in temperature being utilized.
  • a preferred field for the application of such latent heat stores has primarily also become vehicles with internal combustion engines or fuel cells with or without reformation.
  • the waste heat which arises during operation is preferably intermediately stored in an appropriate latent heat store, in order to provide heat energy for the start-up phase, primarily after a pause in operation where the engine is switched off, for preheating or heating up the widest variety of components, such as catalytic converters, engine components or the like.
  • the start-up phase specifically forms a relatively large number of undesired or harmful exhaust gas components, which form because vehicle components are not yet at operating temperature.
  • the catalytic converters which to some extent are used diversely, but also components of the combustion chambers of the engine and moving parts of the engine.
  • a good heat exchange between the heat store masses, or the phase change material, and the heat exchanger fluid, in particular the heat exchanger liquid, is decisive for discharging and charging the heat stores.
  • DE 41 33 360 C2 and DE 38 21 358 A1 have already disclosed latent heat stores with phase change material, wherein the heat exchanger fluid does not flow rectilinearly between the entrance and the exit of the latent heat store on the shortest path, but instead by detours, and therefore by an extended flow path through the store.
  • the heat exchanger fluid does not flow rectilinearly between the entrance and the exit of the latent heat store on the shortest path, but instead by detours, and therefore by an extended flow path through the store.
  • DE 90 05 049 has already disclosed a cylindrical latent heat store, in which the heat medium is supplied to the individual segments on one side of the cylinder and then the heat medium flows through the heat segments from this point transversely to the opposite side, and the heat medium is collectively discharged in an appropriate manner in a lateral collection channel.
  • DE 4 322 813 has already described the use of vacuum insulations and of getter elements
  • DE 10 2004 023 347 A1 has already described the use of thin-layer electric heaters between two flat sides of two adjacent heat segments.
  • a latent heat store is distinguished, by way of example, by the fact that at least one common intake for supplying the heat exchanger fluid to the heat exchanger units and for dividing said fluid into a plurality of separate partial flow sections and also at least one common drain for discharging the heat exchanger fluid from the heat exchanger units and for bringing all partial flow sections together are provided, such that the heat exchanger units arranged between the intake and the drain form a stack collectively exposed to the flow, and such that the heat exchanger units of the stack collectively exposed to the flow are connected in parallel to one another, wherein the inflow point of the heat exchanger unit is arranged in the central region of the heat exchanger unit and the outflow point of the heat exchanger unit is arranged in the radially outwardly arranged casing region of the heat exchanger unit, or wherein the inflow point of the heat exchanger unit is arranged in the radially outwardly arranged casing region of the heat exchanger unit and the outflow point of the heat exchanger unit is arranged in the
  • the sums of all lengths of the individual flow paths between the entrance and the exit of the latent heat store are approximately the same in the case of parallel flow through the stack.
  • the fluid flows through the regions outside the direct, rectilinear connection line of the two inflow and outflow points each arranged on the outside at the edge of the cylinder and on opposing sides to a significantly smaller degree compared to the direct intermediate region along the straight, central connection line.
  • the heat fluid therefore preferably flows from the centrally or axially arranged inflow point from inside in the radial direction and primarily advantageously over the full extent or over the entire cross section or over the entire circumference of the heat exchanger units uniformly outward to the preferably substantially annular outflow point or to the lateral surface of the housing or of the heat store, where it is collected and collectively discharged.
  • the heat fluid is guided from outside via the substantially annular inflow point or from the lateral surface of the housing/heat store in the radial direction and substantially over the full extent over the entire cross section or circular surface inward to the central or axially arranged outflow point.
  • dead regions are formed for the heat fluid laterally alongside said connection line, in which dead regions said fluid has regions of return flow/vortices and/or only a very low flow or possibly even no flow at all. Therefore, existing latent heat stores cannot realize optimum charging and therefore also discharging of heat, since regions of differing warmth or fewer warm regions arise. Accordingly, the storage size of the latent heat store or the power density, i.e. the amount of power per unit volume, of existing latent heat stores is also considerably poorer than in the case of the invention.
  • the heat exchanger units according to the invention have a short intake flow path in the region of the intake, but a correspondingly long drain flow path to the drain of the latent heat store.
  • the situation is accordingly the opposite, i.e. a long intake flow path but a correspondingly short drain flow path.
  • the sum of the intake flow path to the heat exchanger unit and the path along the heat exchanger unit plus the drain flow path of said heat exchanger unit is virtually the same for all heat exchanger units of the stack and over the entire circumference of the heat exchanger units.
  • the flow resistances of all partial flow sections of the heat exchanger fluid from the intake to the drain are substantially of the same magnitude.
  • the cross-sectional ratios and the length ratios of the individual partial flow sections are matched to one another in such a manner, e.g. by means of throttle and/or regulating elements, that the approximately identical flow resistances are established.
  • a latent heat store it is possible to provide more heat energy, e.g. to exhaust gas catalytic converters and/or components of the engine, etc., than is achieved with latent heat stores according to the prior art given the same structural volume after a preceding stoppage phase.
  • the latent heat stores disclosed in DE 41 33 360 C2 and DE 38 21 358 A1 have a serial connection of appropriate heat exchanger units, such that a higher temperature level and therefore greater amounts of heat energy are stored at the intake of the latent heat store than is possible in the drain region of the latent heat store in the case of cooled heat exchanger fluid. Accordingly, primarily the existing heat exchanger units cannot store an optimum or high amount of energy in the outflow region of the latent heat store, which leads to a relatively low energy efficiency for the entire stack or latent heat store.
  • all heat exchanger units have a substantially identical form. It is thereby possible for a stack to be formed from identical heat exchanger units, such that the production of the individual heat exchanger units is improved on account of the production of a relatively large number of identical heat exchanger units.
  • the housing has a substantially cylindrical form.
  • a cylindrical housing has improved stability and pressure properties and also flow properties.
  • this is a central difference in relation to the stack and to the passage of flow through the latent heat store according to DE 41 33 360 C2, wherein the stacks are not stacked transversely to the mid-axis, but rather in the direction of the mid-axis, such that they have to have the widest variety of cross-sectional areas in the case of the cylindrical housing disclosed. Accordingly, in this case it is not possible to produce and stack any identical heat exchanger units, as is advantageously effected however according to the present invention.
  • the heat exchanger units are produced substantially from high-grade steel, with the provision of a high-grade steel with relatively good thermal conductivity being advantageous. Accordingly, a high chemical resistance and also an advantageous thermal conductivity function of the heat exchanger units are achieved.
  • the object of the invention can also be achieved in that the heat exchanger units have at least one spacer for fixing a spacing for the heat exchanger fluid to flow through between the heat exchanger units. It is thereby possible for separately producible and/or mountable spacers and/or fixings for producing a spacing between the heat exchanger units to be dispensed with. This leads to a particularly advantageous production of the latent heat store according to the invention.
  • the spacers according to the invention for the heat exchanger units have the effect that a defined through-flow of the heat exchanger fluid in the intermediate region between two heat exchanger units is ensured. This leads to advantageous flow conditions and pressure losses within the latent heat store or the stack according to the invention, which in turn ensures advantageous heat management in terms of the charging and discharging of the latent heat store.
  • the phase change stores comprise at least the spacers and that the phase change stores are in the form of spacers.
  • the phase change stores are dimensioned in such a way that they realize a predefined or defined spacing between two heat exchanger units, and at the same time form open flow cross sections for the heat exchanger fluid between the heat exchanger units.
  • the phase change stores are also ensured in this respect that identical flow conditions and therefore pressure losses are ensured between the individual heat exchanger units, which leads to an advantageous flow through the entire stack or latent heat store.
  • the spacers are in the form of a bend of a heat exchanger unit.
  • the heat exchanger units can be produced from deformed/reformed metal sheets, in which case by way of example two advantageously shaped metal sheets are connected to one another in such a way that a storage volume for the phase change material is generated.
  • the advantageous bends which at the same time are in the form of spacers according to the invention. This leads to a particularly cost-effective method for producing the individual heat exchanger units and therefore the entire latent heat store.
  • the bends may fulfill not only spacing functions, but also further functions, e.g. centering, i.e. alignment in relation to the central mid-axis and/or to the housing, and/or also a fixing function in terms of twisting, adjustment of the heat exchanger units both in the transverse direction and in the longitudinal direction and/or in the radial direction of the latent heat store according to the invention.
  • centering i.e. alignment in relation to the central mid-axis and/or to the housing
  • a fixing function in terms of twisting adjustment of the heat exchanger units both in the transverse direction and in the longitudinal direction and/or in the radial direction of the latent heat store according to the invention.
  • the latent heat store according to the invention is realized with an advantageous design and such that it can be manufactured cost-effectively.
  • adjacent heat exchanger units it is also possible for example for adjacent heat exchanger units to be welded or spot-welded to one another or fixed cohesively to one another and/or spaced apart, in order inter alia to suppress a relative movement therebetween, such that as far as possible there is no change concerning the flow paths or pressure losses between the heat exchanger units and/or between heat exchanger units and the housing even in the long term.
  • the heat exchanger units which preferably consist essentially of sheet metal, or the phase change stores can therefore have inter alia depressions or recesses such as grooves, etc., and/or protrusions or elevations or the like, in order to ensure an advantageous fluid flow and/or spacing and/or fixing/holding between two adjacent heat exchanger units and/or in relation to the housing of the latent heat store.
  • a latent heat store according to the preamble of Claim 1 and/or according to one of the above-mentioned embodiments can advantageously be distinguished by the fact that the heat exchanger units have at least one anti-twist device for preventing radial twisting of heat exchanger units. It has been found that this is advantageous specifically when radially symmetrical housing forms or heat exchanger units are used. In this case, anti-twist means primarily make advantageous, stable flow conditions possible between the heat exchanger units or in the latent heat store according to the invention.
  • the spacers of the heat exchanger units are in the form of an anti-twist device.
  • a corresponding multiple function reduces the outlay on design and therefore production.
  • the housing advantageously has at least one thermal insulation unit as a sheathing. It has been found that primarily a vacuum insulation unit is particularly advantageous, since a distinctly high or advantageous thermal insulation action is achieved with a relatively small insulation volume. This is particularly advantageous primarily for vehicle applications, since in this case there is generally relatively little space available.
  • a particularly advantageous embodiment, which achieves the object according to the invention, of a latent heat store according to the preamble of Claim 1 having a vacuum insulation unit as a thermal insulation unit and/or according to one of the above-mentioned variant embodiments is distinguished by the fact that the vacuum insulation unit comprises at least one getter unit with a getter material.
  • An advantageous getter material ensures a particularly advantageous vacuum in the vacuum insulation unit.
  • the gas molecules enter into a direct chemical bond with the atoms of the getter material at the surface of the getter material, or the gas molecules in the vacuum are detained by sorption.
  • gases or molecules which remain are appropriately bound in the vacuum, such that the vacuum of the vacuum insulation unit can be improved or can be retained even over a relatively long time.
  • getter material use is made for example of barium, aluminum, titanium, zirconium and/or magnesium and/or the alloys thereof.
  • the getter material is preferably in the form of disks, pellets, rings or the like, and a plurality of such getter units are secured together, for example, by means of a securing element, for example by means of a metal sheet or the like which is to be formed appropriately.
  • the getter material is arranged on the side lying opposite an evacuation opening of the housing or of the insulation unit. Since the getter material acts like a pump, the vacuum can thereby be generated in an advantageous manner, in which case narrow points or the like which may be present between the two housings or the opposing sides of the latent heat store are not disadvantageous for the evacuation.
  • the getter material By heating the getter material, the latter can be regenerated or reactivated, such that substantially the original binding capacity or sorption capacity of the getter material is available again. This regeneration or reactivation can be effected very frequently.
  • the getter material is advantageously arranged in the region of the intake of the latent heat store within the vacuum insulation unit.
  • the heat exchanger fluid can thereby be advantageously provided for heating or regenerating the getter material.
  • This regeneration of the getter material can be initiated or carried out, for example, after predefined time intervals and/or if required by means of advantageous sensors or the like.
  • a vacuum which is advantageous also in the long term in the vacuum insulation unit is of great advantage primarily for ensuring the high thermal insulation action. Accordingly, the amount of heat stored by the phase change material can also be advantageously provided after relatively long periods of time for appropriate applications, such as the heating of vehicle components or the like.
  • waste heat from the cooling water and/or from the exhaust system and/or from the brake system and/or from other vehicle components which produce waste heat can be used in vehicle applications for heat storage according to the invention.
  • vehicle applications for heat storage according to the invention for heat storage according to the invention.
  • the latent heat store it is generally advantageous to provide a heat transfer oil or the like as the heat exchanger fluid, which is pumped through the latent heat store or pumped along the heat exchanger units, for example by means of an advantageous pump.
  • phase change material a salt or the like which has a phase change at about 200° C., for example.
  • This phase change material is stored in the phase change store or in appropriate chambers of the heat exchanger units, which, for example, are evacuated.
  • the latent heat store advantageously has an inner housing, in which the stack with the heat exchanger units is arranged, and an outer housing, with thermal insulation or a vacuum being provided between the inner housing and the outer housing.
  • components of the latent heat store according to the invention which come into contact with the vacuum are formed from high-grade steel, e.g. 1.4301 or the like. Compared to many other metals, high-grade steel has, for example, a lower outgassing rate.
  • the vacuum insulation unit at least in parts has a surface layer or a coating for reducing the emissions into the vacuum.
  • a relatively favorable material is provided for the vacuum insulation unit or the housing. Losses resulting from heat radiation can be reduced by up to about 50% for example by an advantageous low-emission coating or surface layer with an advantageous material, such as preferably copper and/or e.g. silver, aluminum, zinc, etc. In principle, it is advantageous to use low-emission materials for the vacuum insulation unit.
  • the surface of the vacuum insulation unit or of (if possible all) components which come into contact with the vacuum is at least partially advantageously electropolished and/or blasted with glass beads or the like, for example.
  • an emittance of less than 3% can be achieved by the measures according to the invention.
  • all surfaces which emit heat or come into contact with the vacuum should have the smallest possible emittance, in order to keep radiation losses as small as possible.
  • such surfaces are preferably likewise electropolished and/or advantageously coated.
  • Advantageous, for example flexible, holding and/or fixing devices can be provided for fixing or arranging the inner housing or the stack within the outer housing.
  • (metal) strips or the like and/or spiral springs or spring elements can be used for holding both in the longitudinal and/or in the radial direction.
  • Holding components having a relatively poor thermal conductivity e.g. ⁇ 10 W/mK are particularly advantageous, such that thermal conduction between the stack or the inner housing and the outer housing is minimized as far as possible. This also applies in relation to advantageous intake lines and/or drain lines between the outer housing and the inner housing or the stack of the latent heat store.
  • the holding and/or fixing device can be in the form of a so-called supported vacuum insulation system.
  • a supported vacuum insulation system advantageously comprises numerous insulating/supporting elements such as insulating fibers, e.g. made of glass fibers or the like, wherein the space in which these are arranged is evacuated and, in particular applications, may be sealed off by means of a sleeve or cladding layer, e.g. made of foil or the like.
  • the inner housing and the outer housing of the latent heat store according to the invention substantially advantageously form the cladding layer, such that a separate or additional foil or the like can be dispensed with.
  • the vacuum insulation system is in the form of a supported vacuum insulation system, it is advantageously possible to dispense with an additional holding and/or fixing device between the two housings.
  • the insulating/supporting elements can perform the holding and/or fixing function. If corresponding (metallic) holding and/or fixing devices are dispensed with, it is possible to achieve a particularly advantageous insulation action.
  • the intake and/or the drain lines have a bent form and/or have advantageous regions in order to be able to compensate for changes in length of the lines as far as possible with low stresses.
  • flow advantageously passes through the latent heat store according to the invention, such that essentially no dead regions or regions through which flow passes poorly are generated within the store, as was readily the case to a considerable extent to date in the prior art.
  • the latent heat store according to the invention is used for electric vehicles or else hybrid vehicles with an electric drive motor, it may be particularly advantageous for achieving the object of the invention to arrange at least one electric heating element for heating the phase change stores and/or heat exchanger units in particular within the heat exchanger housing.
  • At least two separate latent heat stores according to the invention are provided in a vehicle.
  • a first latent heat store which is supplied or charged with heat energy, e.g. waste heat from the brake system and/or from the electric drive motor, etc.
  • a second latent heat store which is supplied or charged with electric energy, e.g. from the electric traction battery/accumulator, a photovoltaic unit arranged on the sleeve or outer skin of the vehicle and/or from a vehicle-external or stationary energy supply, e.g. from the “electric socket” or from an electric “filling station”.
  • the vehicle-external charging variant of the invention in particular makes it possible for the latent heat store according to the invention to be supplied or charged with energy at the same time or additionally during the electric charging of the traction battery/accumulator, for example.
  • Latent heat stores according to the invention can advantageously provide the stored energy/heat inter alia for the air conditioning or heating of a passenger cabin or the like and/or for preheating vehicle components such as the battery/storage battery, catalytic converters, etc.
  • the heat exchanger fluid is in the form of gas, preferably air.
  • a fan or the like is advantageously provided for gas/air to flow through the latent heat store according to the invention.
  • the heating element is arranged between two adjacent heat exchanger units. This achieves a particularly effective and efficient transfer of energy from the electric heating element to the heat exchanger units or to the phase change material.
  • the electric heating can be realized in the manner of an immersion heater or the like.
  • the heating element is in the form of a heating foil.
  • This heating foil is relatively thin and can advantageously be brought into direct contact with the heat exchanger units and thus be arranged very close to the phase change material. This additionally improves the heat absorption.
  • the use of a heating foil is particularly advantageous.
  • said heating foil can be arranged or inserted between two planar sides/surfaces of the adjacent heat exchanger units. This is of major advantage when numerous heat exchanger units are used or stacked, particularly during production and also in relation to the utilization of space within the latent heat store according to the invention and also in relation to the most homogeneous possible heating and therefore storage of the energy/heat introduced.
  • FIG. 1 shows a schematic cross section in the longitudinal direction through a latent heat store according to the invention
  • FIG. 2 shows a schematic cross section in the longitudinal direction through an inner part of the latent heat store according to the invention as shown in FIG. 1 , with a heat exchanger stack and inner housing,
  • FIG. 3 shows a schematic plan view perpendicular to the longitudinal direction onto the inner part of the latent heat store according to the invention as shown in FIG. 1 ,
  • FIG. 4 shows a schematic, perspective view of a first heat exchanger unit of the stack shown in FIG. 2 ,
  • FIG. 5 shows a schematic plan view of a second, alternative heat exchanger unit for the stack shown in FIG. 2 ,
  • FIG. 6 shows a schematic, enlarged sectional side view of two stacked heat exchanger units according to FIG. 2 .
  • FIG. 7 shows a schematic, perspective view of a getter pellet unit.
  • FIG. 1 schematically shows a latent heat store 1 , i.e. a so-called PCM (Phase Change Material) store 1 , according to the invention.
  • heat exchanger units i.e. so-called sheets 2
  • the latent heat store 1 comprises, as the outer sleeve, an outer housing 3 with a cylindrical casing 4 and a base element 5 .
  • a vacuum connection 7 is visible on the outside, this being used for generating a vacuum 9 between the outer housing 3 and an inner housing 8 and then being closed, in particular crimped.
  • the inner housing additionally has a cover 27 and a base 19 .
  • both an intake 10 and a drain 11 for a heat exchanger fluid such as a liquid or a gas, in particular a heat transfer oil, air or the like, are provided on the outside on the side of the outer or inner cover 6 , 27 .
  • a heat exchanger fluid such as a liquid or a gas, in particular a heat transfer oil, air or the like
  • These are preferably used for the input and/or the output of the heat energy, which is intermediately stored in the latent heat store 1 , in particular by means of the PCM material stored or incorporated in chambers 14 of the sheets 2 .
  • the chambers 14 or pockets are preferably evacuated and/or permanently closed.
  • each sheet 2 comprises a plurality of chambers 14 , which are arranged annularly or concentrically around the mid-axis, for example.
  • the sheets 2 are preferably produced from sheet metal, provision being made for example of a planar metal sheet and a metal sheet which has numerous protrusions intended for the formation of the chambers 14 and which is cohesively bonded, in particular (laser) welded, to the planar metal sheet in an advantageous manner.
  • FIG. 4 An alternative anti-twist means for two sheets 2 which lie against one another with the planar side is realized with the variant according to FIG. 4 .
  • the individual sheets 2 have a plurality of lugs or wings 16 which are arranged on the outside or circumference and are partially bent in the direction of the mid-axis 12 (not shown), such that they interlock with corresponding wings 16 of an adjacent sheet 2 and/or pair of sheets and thus effectively prevent relative twisting in the radial direction.
  • further (partially bent) wings 31 or lugs 31 are provided in the central region of the sheets 2 and radially align or center the sheets 2 and generate one or more open flow cross-sectional openings with respect to the pipe 18 .
  • the chambers 14 have advantageous surface structures or so-called combs 17 , which are in the form of spacers in relation to the spacing between two adjacent sheets 2 preferably in the direction of the longitudinal axis or mid-axis 12 (cf. FIG. 6 ). These combs 17 are shown inter alia in FIGS. 4 to 6 , in which case one or by way of example more grooves oriented in the radial direction are in the form of combs 17 .
  • the sheets 2 have an inflow point 34 in the region of a centric or axial mid-point or in the region of the longitudinal axis 12 .
  • An outflow point 35 is provided according to the invention directed circumferentially or outward with respect to the casing or housing 8 . In this exemplary embodiment, the outflow point 35 has a substantially annular form or is in the form of a ring.
  • said ring or the outer circumference could also be in the form of an inflow point and the center hole or the center could be in the form of an outflow point according to the invention, wherein an advantageous radially oriented flow of the heat exchanger fluid is likewise realized over substantially the full extent of the cross section or over the circular surface of the sheets 2 .
  • the preferably radially oriented combs 17 produce a gap 33 through which the heat exchanger fluid flows preferably in the radial direction approximately perpendicular to the longitudinal direction 12 , such that the fluid can flow around the chambers 14 virtually over the entire area thereof and in the radial direction. This makes advantageous heat exchange possible between the fluid and the PCM material.
  • a PCM material having a phase change approximately in the region of about 200° C. is particularly advantageous.
  • a suitable heat exchanger fluid in particular a heat transfer oil, which is suitable for this temperature range.
  • the fluid is supplied to the sheets 2 or the inflow points 34 thereof or to the stack 13 using a pipe 18 , which is arranged approximately centrally in the longitudinal direction 12 and is spaced apart from a base 19 of the inner housing 8 .
  • An open end 20 of the pipe 18 advantageously has a so-called crown design, in order inter alia to compensate for possible assembly/component tolerances, i.e. to prevent a sufficient opening cross section for the fluid flowing out from being disadvantageously undershot even in the case of a slightly variable spacing between the end and the base 19 (even in the case of contact).
  • an inner spring element 21 is provided.
  • this spring 21 not only compensates for thermally induced changes in length of the stack 13 , but also presses the sheets 2 against one another, such that for example the transfer of heat to contact surfaces, in particular the planar side (cf. above), is also improved.
  • the gaps 33 between the chambers 14 have a thickness of about 0.5 mm or a few millimeters.
  • a sleeve 28 is arranged on the pipe 18 , in order inter alia to prevent an upper pressure plate 29 from becoming caught during adjustment and also a disadvantageous flow of the heat exchanger fluid along the pipe 18 .
  • the pressure plate 29 advantageously distributes the locally introduced spring force of the spring 21 over the entire radius. So that this is effected as homogeneously as possible, the pressure plate 29 has a slightly conical profile of about 1° toward the center.
  • the intake 10 and the drain 11 have regions for compensating for thermally induced changes in length, e.g. in particular metal bellows 30 or the like provided in the bend region.
  • the inner container/housing 8 is thermally insulated with respect to the outer housing 3 by means of a vacuum 9 .
  • a getter material or getter pellets 25 is or are advantageously arranged on the inner and/or outer housing 3 , 8 and/or on fixing/holding devices such as clamping or spring elements 22 , 23 , 24 and/or on the intakes/drains 10 , 11 .
  • the getter pellets 25 are preferably arranged on the outer housing 3 , in particular on the base 5 , and/or on the intake 10 by means of a holder 26 .
  • the getter material or the getter pellets 25 can advantageously be regenerated by heating.
  • the regeneration heat can be conveyed from outside through the wall or through the base 5 to the getter pellets 25 by means of a separate heat source and/or by means of the heat exchanger fluid.
  • the holder 26 should conceal the surface of the getter pellets 25 as little as possible, in order to make the advantageous accumulation of remaining atoms or molecules of the vacuum 9 possible.
  • the fixing/holding devices such as clamping or spring elements 22 , 23 , 24 hold and fix the inner container or housing 8 at a spacing from the outer housing 3 .
  • These elements should as far as possible be formed in such a manner that relatively poor thermal conduction by the latter is obtained.
  • these can be produced inter alia in a relatively long and thin form or with a small cross section and also from appropriate material.
  • a high-grade steel having relatively poor thermal conduction properties can be used for this purpose.
  • FIG. 3 shows the preferred installation position.
  • the holders or springs 23 and 24 have webs 32 , which are oriented in the direction of the greatest expected acceleration, in this case primarily in the vertical direction.
  • the drain 11 runs in the vertical direction, in order to minimize convection losses by the heat exchanger liquid.
  • the fluid flows through the intake 10 to the pipe 18 and enters into the inner space of the latent heat store 1 at the open end 20 .
  • an annular contact surface of the lowermost sheet 2 together with the base 19 prevents unintentional “underwashing” of the lowermost sheet 2 .
  • the fluid flows inter alia to the first/lowermost inflow point 34 between the lowermost and the second lowest sheet 2 in the radial direction past the chambers 14 thereof or the lowermost/first gap 33 to the outflow point 35 or to the circumference or outer edge of the sheets 2 .
  • the fluid flows along further outflow points 35 of the other sheets 2 and along the casing of the housing 8 to the cover 27 and through the drain 11 out of the latent heat store 1 .
  • a second flow path branches off at the open end 20 in such a manner that this partial flow flows back/up along the pipe 18 and then, at the next inflow point(s) 34 , through the next or second gap 33 between two adjacent sheets 2 or chambers 14 and in the radial direction to the outer circumference or to the next outflow point(s) 35 of the next sheets 2 and then in turn along further outflow points 35 of the other sheets 2 and along the casing of the housing 8 to the cover 27 or drain 11 .
  • the slide bushing or sleeve 28 is intended to prevent tilting of the pressure plate upon thermal expansion and “slide” on the oil guiding pipe 18 .
  • the bushing material is preferably brass. Brass and high-grade steel have good sliding properties.
  • the tolerances between the slide bushing 28 and the oil guiding pipe 18 are selected to be as small as possible, in order to have the smallest possible gap between the components, which permits no or only a very small bypass leakage.
  • the height or the gap length should be maximized for the installation, in order for it to be possible to provide the narrowest and longest possible gap.
  • the spring 21 inside should apply a defined contact pressure of the pressure plate 29 to the PCM stack 13 .
  • this contact pressure should be at least as great as the maximum lateral acceleration which occurs.
  • a spring force of about 220-250 N is selected. This should be ensured for all thermal states. This means that, for example at about ⁇ 40° C., the PCM stack height is reduced by about 5 mm as compared with about 20° C. At an operating temperature of about 250° C., the height increases by about 5 mm, for example, as compared with 20° C.
  • the material of the spring 21 should be suitable for temperatures of >about 350° C., since the spring preload has to be retained after the heat-treatment process for evacuation.
  • the oil guiding pipe 18 has a “crown design”.
  • the design is chosen such that the “tips” of the crown cannot act as a cutting edge in the case of direct contact with the base 19 .
  • the crown is intended to prevent blockage of the oil flow, should the pipe 18 be incorrectly installed until contact or should the pipe 18 be present on the base 19 on account of thermal distortion. Furthermore, it serves for additional centering of the PCM stack 13 and conveys the fluid or heat transfer oil to the base 19 of the store 1 .
  • the pressure plate 29 serves as an “end cover” of the PCM stack 13 .
  • This end cover 29 together with the slide bushing 28 , is intended to prevent a bypass leakage, in that the plate 29 conducts the oil flow in any case through the uppermost level of the PCM sheet.
  • the pressure plate 29 has the task of distributing the spring force, which is introduced locally at the spring seat, as homogeneously as possible over the entire radius. Therefore, the pressure plate 29 tapers conically toward the center at about 1°. If appropriate, the material thickness of the pressure plate 29 may be reduced by introducing beads and/or ribs etc. for stiffening and distributing forces. Lugs of the plate 29 which are bent upward additionally serve as centering for the spring 21 .
  • Casing of the housing 8 the special feature here is that the outer surface of the inner casing should be electropolished, for example. This reduces impurities, which would be very harmful during evacuation, and reduces the emittance of the surface and improves the outgassing rate. A reduction in the emittance leads to a reduction in the radiation losses.
  • the outer surface should be completely free of dirt and grease.
  • the PCM sheets 2 are preferably welded together from two high-grade steel sheet halves. One side of the metal sheet has deep-drawn pockets or chambers 14 into which the liquid PCM is filled. A metal sheet which likewise has deep-drawn pockets or chambers 14 or preferably finally a flat, punched metal sheet is welded thereto.
  • An electrically heatable heating foil or the like (not shown inter alia in FIG. 2 or 6 merely for reasons of clarity) can advantageously be arranged between two flat, adjacent sides of two PCM sheets 2 (e.g. above and/or below the two PCM sheets 2 in FIG. 6 ).
  • the electrical contact is made between the electric heating elements/foils arranged between two PCM sheets 2 by stacking the PCM sheets 2 one on top of another.
  • the electrical connection of PCM sheets 2 to PCM sheets 2 can advantageously be “looped through” or passed on.
  • the latent heat store according to the invention preferably has a common electrical connection on the outside or on the outer housing 3 , e.g. two electric conductors (conductor ends), with which the heating element/foil or the numerous heating elements/foils within the housing 8 or between the PCM sheets 2 are supplied with electric energy.
  • each pocket 14 In order for it to be possible to set the oil gap in each level, so-called “spacer combs” 17 are integrally formed in each pocket 14 .
  • the individual pockets 14 are welded in a holding-down device, for example by means of a laser.
  • each pocket 14 is preferably provided with two circumferential weld seams.
  • wings 16 which serve as spacers are fitted on the outside. This spacing is needed since the oil rises on the casing.
  • the wings 16 also serve as spring elements, since instances of radial thermal expansion can occur as a result of differences in temperature in the sheet 2 itself. This thermal expansion is compensated for by the resilient wings 16 in an advantageous manner.
  • the wings 16 serve as a torsional barrier, since the wings 16 engage into one another in the mounted operating state. Alternatively, a torsional barrier can also be ensured by spot-welding the individual sheets 2 .
  • the wings 31 on the inside like the outer wings 16 likewise serve for the support, thermal compensation and/or centering of the oil guiding pipe 18 . Furthermore, the three inner wings 31 form so-called “oil riser pockets”. In these pockets, the oil can flow back/rise coaxially along the oil guiding pipe 18 and flow into the respective level.
  • the special feature here is that the outer surface should likewise be electropolished, for example. This reduces impurities, which would be very harmful during evacuation, and reduces the emittance of the surface and improves the outgassing rate. A reduction in the emittance leads to a reduction in the radiation losses.
  • the polished surface has to be completely free of grease and clean.
  • the outer surface should be electropolished. This reduces impurities, which would be very harmful during evacuation, and reduces the emittance of the surface and improves the outgassing rate. A reduction in the emittance leads to a reduction in the radiation losses.
  • the inner base 19 should be designed in such a way that the lowermost PCM sheet 2 has a circumferential linear seating. This prevents a bypass leakage of the oil.
  • the polished surface should be completely free of grease and clean, which inter alia improves the outgassing rate.
  • the geometry is advantageously such that the base has a sufficient rigidity, in order to withstand the vacuum 9 and other influences.
  • the inner surface of the casing or housing 3 should likewise be electropolished, for example. This reduces impurities, which would be very harmful during evacuation, and reduces the emittance of the surface. A reduction in the emittance leads to a reduction in the radiation losses.
  • the polished surface should be completely free of grease and clean, which inter alia improves the outgassing rate. Beads in the casing on the outside stabilize the casing under negative pressure inside. It is therefore possible to use a thinner starting material.
  • the metal bellows 30 of the intake 10 and/or drain 11 has the task of compensating for the thermal expansion of the inner container 8 . To this end, about ten billows which can compensate for thermal stresses are integrated in each bend. Furthermore, the metal bellows 30 should have the smallest possible wall thickness together with the longest possible overall length. Heat losses as a result of heat conduction are therefore reduced.
  • the holders 23 , 24 have the function of fixing the vacuum gap of the inner container 8 in relation to the outer container 3 .
  • the holders 23 , 24 are preferably optimized in terms of their thermal conductivity, i.e. they are as long as possible with the smallest possible cross section.
  • the holders 23 , 24 are to be arranged in such a way that the legs 31 of the holder 23 , 24 are oriented parallel to the direction of greatest acceleration.
  • the axis of greatest acceleration is the Z axis of the vehicle (pitch holes).
  • the legs 31 of the holders 23 , 24 are to be placed under tensile load; this tensile loading is spring-loaded inter alia by the spring 22 on the outside.
  • the holders 23 , 24 as well as all (metallic) elements which come into contact with the vacuum are preferably to be treated appropriately, i.e. electropolished, clean, free of grease, etc.
  • the spring 22 on the outside should place the lower holder 24 under tensile preload in order to minimize oscillation of the inner container 8 .
  • the spring 22 is preferably in the form of a spiral spring, since spiral springs have the advantage of an extremely long wire length and thus have small heat losses as a result of thermal conductivity.
  • the material of the spring should be designed for common applications for temperatures >about 350° C., since the spring preload has to be retained after the heat-treatment process for evacuation.
  • the spring 22 as well as all (metallic) elements which come into contact with the vacuum is preferably to be treated appropriately, i.e. electropolished, clean, free of grease, etc.
  • Getter pellets 25 Getters “capture” free molecules which have not been pumped out or have passed into the vacuum space 9 as a result of microleakages and/or as a result of so-called “virtual leakages”, and bind them to the surface thereof. Following activation or regeneration (heating to >about 200° C.), the molecules bound to the surface diffuse into the interior of the getter, where they are chemically bonded. The surface then has “free” points again in order to be able to bind foreign molecules anew. Getters therefore make a large contribution to lengthening the life of the vacuum. Furthermore, they can shorten the evacuation time, since they likewise have a pump effect.
  • the getter holder 26 is to be designed preferably in such a way that it can accommodate the getter pellets 25 in an advantageous manner. At the same time, however, very little of the surface of the getter pellets 25 should be concealed by the holder 26 . Furthermore, the getter holder 26 should conduct the externally applied activation temperature as well as possible to and around the getter 25 , such that the getter is activated over the entire surface.
  • the getter holder 26 as well as all (metallic) elements which come into contact with the vacuum is preferably to be treated appropriately, i.e. electropolished, clean, free of grease, etc.
  • the pinch pipe 7 or the connection 7 serves as a connection for a vacuum pump.
  • the store is evacuated via the latter.
  • the pinch pipe 7 is preferably soldered or welded onto the cover 6 .
  • the pipe 7 is made of copper, for example, since copper can be deformed and pinched off in an advantageous manner. Once the vacuum pressure has been reached, the pipe 7 is pinched, for example by means of pliers or the like, cut off and at the same time tightly welded.
  • the pinch pipe 7 is to be designed to be as large as possible (e.g. >about 20 mm), since this represents the bottleneck upon evacuation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US13/385,429 2011-02-22 2012-02-21 Latent heat store Abandoned US20120241120A1 (en)

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US20120279679A1 (en) * 2010-01-29 2012-11-08 Soukhojak Andrey N Thermal energy storage
US20120312279A1 (en) * 2011-06-13 2012-12-13 Denso International America, Inc. Hot Oil Thermal Battery
US20150114590A1 (en) * 2012-04-10 2015-04-30 Siemens Aktiengesellschaft Heat accumulator for power plant capacities
US20150176913A1 (en) * 2013-12-19 2015-06-25 Dana Canada Corporation Conical Heat Exchanger
CN106536884A (zh) * 2014-07-18 2017-03-22 翰昂汽车零部件有限公司 汽车的排气热量蓄热装置
US20170248375A1 (en) * 2014-09-05 2017-08-31 Borgwarner Inc. Heat exchanger and storage device for cold vehicle startup with regenerative capability
US20180023453A1 (en) * 2016-07-20 2018-01-25 Denso Corporation Engine warm-up apparatus for vehicle
CN108139169A (zh) * 2015-09-30 2018-06-08 西门子股份公司 具有热储存材料的尺寸改变的补偿的热交换***和通过使用热交换***用于交换热的方法
US20180175420A1 (en) * 2016-12-15 2018-06-21 Hyundai Motor Company Heat exchange device for cooling water of fuel cell and fuel cell system comprising the same
US20190193511A1 (en) * 2017-11-14 2019-06-27 Konvekta Aktiengesellschaft (Ag) Heating system with heat accumulator arrangement for hybrid or electric vehicles, and method thereto
US11027589B2 (en) * 2018-04-10 2021-06-08 Ford Global Technologies, Llc Electric motor with cooling system and corresponding method
CN113483589A (zh) * 2021-07-12 2021-10-08 中国工程物理研究院激光聚变研究中心 一种基于分形树状肋片的储热换热器
US11245142B2 (en) * 2018-10-25 2022-02-08 Sunlight Aerospace Inc. Methods and apparatus for thermal energy management in electric vehicles
US20220221230A1 (en) * 2019-07-09 2022-07-14 Siemens Gamesa Renewable Energy Gmbh & Co. Kg Thermal energy storage
US11476474B2 (en) 2016-12-14 2022-10-18 Hyundai Motor Company Heat exchange apparatus for cooling water of fuel cell and fuel cell system including the same

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DE202012011625U1 (de) 2012-12-05 2013-03-05 Heinrich Beutler Warmwasserspeicher für Brauchwasser mit Solarmodul
DE102013003357B4 (de) * 2013-02-27 2021-07-01 Jobst Kerspe Kombinierte Speicher- und Heizvorrichtung
DE102013213317A1 (de) 2013-07-08 2015-01-08 Volkswagen Aktiengesellschaft Verfahren und System zur Wärmeübertragung für ein Fahrzeug
DE102014016214A1 (de) * 2014-10-31 2016-05-04 Webasto SE Wärmetauscher und Heizgerät mit einem derartigen Wärmetauscher
DE102014225620A1 (de) * 2014-12-11 2016-06-16 Siemens Aktiengesellschaft Latentwärmespeicher
FR3040208B1 (fr) * 2015-08-20 2020-10-23 Hutchinson Dispositif thermique pour un fluide, avec chicanes, et circuits associes
ES2870918T3 (es) * 2016-05-27 2021-10-28 Axiotherm GmbH Elemento acumulador de calor latente, encapsulación para un material acumulador de calor latente y acumulador de calor latente
CN108507176B (zh) * 2017-02-28 2022-10-14 美的集团股份有限公司 电热水器内胆及热水器

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US20120279679A1 (en) * 2010-01-29 2012-11-08 Soukhojak Andrey N Thermal energy storage
US20120312279A1 (en) * 2011-06-13 2012-12-13 Denso International America, Inc. Hot Oil Thermal Battery
US9175647B2 (en) * 2011-06-13 2015-11-03 Denso International America, Inc. Hot oil thermal battery
US10082341B2 (en) * 2012-04-10 2018-09-25 Siemens Aktiengesellschaft Heat accumulator for power plant capacities
US20150114590A1 (en) * 2012-04-10 2015-04-30 Siemens Aktiengesellschaft Heat accumulator for power plant capacities
US20150176913A1 (en) * 2013-12-19 2015-06-25 Dana Canada Corporation Conical Heat Exchanger
US10107556B2 (en) * 2013-12-19 2018-10-23 Dana Canada Corporation Conical heat exchanger
CN106536884A (zh) * 2014-07-18 2017-03-22 翰昂汽车零部件有限公司 汽车的排气热量蓄热装置
US10309364B2 (en) 2014-07-18 2019-06-04 Hanon Systems Exhaust heat regenerator for vehicle
US20170248375A1 (en) * 2014-09-05 2017-08-31 Borgwarner Inc. Heat exchanger and storage device for cold vehicle startup with regenerative capability
US10982909B2 (en) * 2015-09-30 2021-04-20 Siemens Gamesa Renewable Energy A/S Heat exchange system with compensation of dimension change of heat storage material and method for exchanging heat by using the heat exchange system
CN108139169A (zh) * 2015-09-30 2018-06-08 西门子股份公司 具有热储存材料的尺寸改变的补偿的热交换***和通过使用热交换***用于交换热的方法
US20180245860A1 (en) * 2015-09-30 2018-08-30 Siemens Aktiengesellschaft Heat exchange system with compensation of dimension change of heat storage material and method for exchanging heat by using the heat exchange system
US20180023453A1 (en) * 2016-07-20 2018-01-25 Denso Corporation Engine warm-up apparatus for vehicle
US10494985B2 (en) * 2016-07-20 2019-12-03 Denso Corporation Engine warm-up apparatus for vehicle
US11777112B2 (en) 2016-12-14 2023-10-03 Hyundai Motor Company Heat exchange apparatus for cooling water of fuel cell and fuel cell system including the same
US11476474B2 (en) 2016-12-14 2022-10-18 Hyundai Motor Company Heat exchange apparatus for cooling water of fuel cell and fuel cell system including the same
US10818944B2 (en) * 2016-12-15 2020-10-27 Hyundai Motor Company Heat exchange device for cooling water of fuel cell and fuel cell system comprising the same
US20180175420A1 (en) * 2016-12-15 2018-06-21 Hyundai Motor Company Heat exchange device for cooling water of fuel cell and fuel cell system comprising the same
US20190193511A1 (en) * 2017-11-14 2019-06-27 Konvekta Aktiengesellschaft (Ag) Heating system with heat accumulator arrangement for hybrid or electric vehicles, and method thereto
US11027589B2 (en) * 2018-04-10 2021-06-08 Ford Global Technologies, Llc Electric motor with cooling system and corresponding method
US11245142B2 (en) * 2018-10-25 2022-02-08 Sunlight Aerospace Inc. Methods and apparatus for thermal energy management in electric vehicles
US20220221230A1 (en) * 2019-07-09 2022-07-14 Siemens Gamesa Renewable Energy Gmbh & Co. Kg Thermal energy storage
CN113483589A (zh) * 2021-07-12 2021-10-08 中国工程物理研究院激光聚变研究中心 一种基于分形树状肋片的储热换热器

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DE102012002952A1 (de) 2012-08-23
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