WO2017134177A1 - Procédé et dispositif pour capter, stocker et restituer de l'énergie thermique issue de gaz - Google Patents

Procédé et dispositif pour capter, stocker et restituer de l'énergie thermique issue de gaz Download PDF

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Publication number
WO2017134177A1
WO2017134177A1 PCT/EP2017/052282 EP2017052282W WO2017134177A1 WO 2017134177 A1 WO2017134177 A1 WO 2017134177A1 EP 2017052282 W EP2017052282 W EP 2017052282W WO 2017134177 A1 WO2017134177 A1 WO 2017134177A1
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WO
WIPO (PCT)
Prior art keywords
bulk material
bed
gas
heat
flow direction
Prior art date
Application number
PCT/EP2017/052282
Other languages
German (de)
English (en)
Inventor
Karl Brotzmann
Dragan Stevanovic
Original Assignee
Karl Brotzmann Consulting Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Karl Brotzmann Consulting Gmbh filed Critical Karl Brotzmann Consulting Gmbh
Publication of WO2017134177A1 publication Critical patent/WO2017134177A1/fr

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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
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
    • 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
    • F28D17/00—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles
    • F28D17/005—Regenerative heat-exchange apparatus in which a stationary intermediate heat-transfer medium or body is contacted successively by each heat-exchange medium, e.g. using granular particles using granular particles
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
    • 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
    • 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 present invention relates to a method for receiving, storing and releasing thermal energy of gases, in which a bed of a bulk material is traversed in a first step in a first flow direction for a first time period of a gas, thereby heat or cold to the bulk material which is stored by the bulk material, and in a second step in a second flow direction for a second period of time is traversed by a gas which absorbs heat or cold from the bulk material.
  • recuperative heat exchangers For central ventilation systems of larger design, the use of recuperative heat exchangers is known in the art. Disadvantage of these heat exchangers, however, is that the surface for the heat transfer must be large, resulting in large and therefore expensive equipment.
  • the present invention accordingly has the object to provide a method and apparatus for receiving, storing and emitting thermal energy of gases, especially for integrated heat recovery in ventilation systems that avoids the above-mentioned disadvantages of the prior art and efficient Recovery of thermal energy from gases (i.e., high efficiency recovery) while being more cost effective and compact design of the device necessary for carrying out the method makes it possible.
  • the present invention is based on the finding that such a method and such a device can be made available if
  • the present invention therefore provides a method for the uptake, storage and release of thermal energy of gases, in which a bed of bulk material is traversed by a gas in a first step in a first flow direction for a period of time ti, the heat or gives off cold to the bulk material, which is stored by the bulk material, and in a second step in a second flow direction for a time period t 2 is traversed by a gas, the heat or cold of the bulk material Jerusalemn immt, characterized in that the behaves is between bed thickness L in the flow direction of the gas and the mean particle diameter d P of the bulk material is at least 20 and the characteristic number for the heat transferred per volume and degree Kelvin, defined as ti m G ic P j / (a V s L) m is at least 0.25 kJ / m 3 K.
  • the method according to the invention offers the advantage that the recovery of thermal energy from gases can be efficiently, ie. H . with high efficiency, can be realized. Furthermore, the device for carrying out the method can be realized in a cost-effective and compact manner if the storage capacity per volume, or per mass of the memory, is significantly higher.
  • a further advantage of the method according to the invention is that the temperature of the gas at the outlet from the bulk material bed remains substantially constant both during the discharge of the thermal energy of a gas and during the absorption of the thermal energy of the gas. With the characteristics defined above, one achieves a significantly lower temperature difference between the gas and the storage material.
  • the ratio between bed thickness L in the flow direction of the gas and mean particle diameter dp of the bulk material is at least 30, more preferably at least 40, and particularly preferably at least 50.
  • the heat recovery can be more efficient, d. H. design with even higher efficiency, since the heat recovery rate increases with increasing ratio between bed thickness L in the flow direction of the gas and the mean particle diameter d P of the bulk material and also longer switching times At are possible.
  • the ratio between bed thickness L in the flow direction of the gas and the mean particle diameter dp of the bulk material is usually at most 2000.
  • the specific particle surface a (m 2 / m 3 of the bed) is so large that the ratio between the total surface a V s (as a product of the specific particle surface and the volume of the bed) and the volume flow of the gas in the normal state v G i (m 3 i N. / h) multiplies by the time period tj (h) a V s / (v Gi ti) is at least 0.05 m "1 and a maximum of 1 m 0 '1. This allows a very efficient heat transfer resulting from a very low temperature difference between solid and gaseous phases.
  • the mean particle diameter dp of the bulk material is from 0.5 mm to 50 mm. These particle diameters ensure good flowability of the bulk material bed with at the same time good absorption and storage capacity for the thermal energy of the gases flowing through.
  • the average particle diameter dp of the bulk material is preferably determined as the Sauter diameter, according to DIN N ISO 9276-2. This is defined as follows: If one were to transform the entire volume of the particles of a bed into spheres of equal size, whose entire surface is equal to the entire surface of the particles, then these spheres would have the Sauter diameter as the diameter.
  • the bulk material is preferably made of ceramic, chamotte, sil icium carbide, zirconium oxide, graph it, Eifel lava, gravel, iron ore, clay, lime, metallic particles or combinations thereof.
  • the particles of the bulk material may be spherical, gravel-shaped and / or in the form of fracture or gravel.
  • the particles used are approximately uniform.
  • the bulk material bed can be formed so that it is arranged in a column, ie in turn arranged standing or lying is, or that the bulk material is flowed through radially, as described in the patent DE4238652.
  • the first one is different from the second flow direction, i.e. Gas flows through the bed of bulk material during the time period ti in a different direction relative to the bed than the gas during the time period T 2.
  • the method according to the invention can be used in a particularly simple manner, for example for room ventilation with integrated heat recovery.
  • the bulk material is continuously flowed through by gas and it is changed between the first and the second flow direction after each time period ti or i 2 .
  • the bulk material is continuously flowed through by gas in a first or in a second flow direction, ie, once the time period ti or i 2 has elapsed, the flow direction is "switched".
  • This preferred embodiment allows a particularly effective embodiment of the method according to the invention, since the absorption of thermal energy by the gas flowing through the bulk material during a time period t 2 immediately after the release of thermal energy to the bulk material by the bulk material during a time period ti flowing gas takes place and thus the storage time and thus possibly associated storage losses of thermal energy in the bulk material are minimized.
  • the heat is delivered to the bulk material by an electric heater built into the bed.
  • the change of the flow direction is preferably carried out by means of at least one blower or a system with a plurality of valves.
  • the following relation is sufficient for the switching time ti or t 2 :
  • the thermal energy delivered by the heated gas is between 10% and 90% of the maximum possible stored thermal energy, but the difference remains almost completely in the bulk material.
  • This advantageous temperature profile is formed by a very low temperature difference between the gas phase and solid phase, which in turn is made possible by the fulfillment of the abovementioned conditions.
  • air is used as the gas during the time period ti and / or t 2 .
  • the inventive method for controlled ventilation of a room with integrated heat recovery is used. This means that the bulk material bed is flowed through during the period ti of exhaust air from the room and during the time period t 2 of fresh air from outside Shen.
  • the temperature of the room exhaust air when entering the bed of bulk material is normally 1 7 ° C to 35 ° C.
  • the temperature of the fresh air supplied from the outside when entering the bed of bulk material depends on the season and can therefore be from -30 ° C to 50 ° C.
  • the exhaust air from the room is cooled by the cold air released from the fresh air and stored in the bulk material bed and flows coolly outwards.
  • the outside air on the other hand, is warmed up so that it enters the room at about room temperature. In this case, heat is thus stored in the bulk material bed.
  • the warm season when the outside temperature is above the room air temperature, a reverse process takes place: the exhaust air from the room is warmed up by the heat stored in the storage mass and flows warm to the outside. At the same time, the outside air is cooled down so that it enters the room at room temperature. In this case, so cold, and not heat, stored in the bulk bed.
  • the room exhaust air has a high moisture content
  • a condensate can form in the colder layer of the bulk bed, the z. B. flows to the outside.
  • the energy released by the condensation is stored in the bed and, in the next phase, additionally contributes to the preheating of the outside air.
  • the outside air has a temperature of below 0 ° C and / or a humidity of less than 35%, to return a certain amount of moisture from the room air. Since the bulk material, on which condensate precipitates from the room air, has a very high specific surface area, the outside air humidifies very quickly to a relative humidity between 35% and 65%.
  • the inventive method and the device according to the invention comprising a bulk material or its use, at the same time very well suited to remove excess moisture from the room and on the other hand to moisturize dry outdoor air by an inherent recovery of moisture and a room air with a optimum humidity between 35 and 65%.
  • intermediately means that the drying takes place after a long period in comparison to the time periods ti and t 2 .
  • time periods ti and t 2 in the range of 2 minutes to 60 minutes, drying once a day, i. E. once every 24 hours.
  • t3 is preferably 3 to 5 times as large as ti or t 2 .
  • the drying can be done so that once a day for 20 minutes, the flow in the direction of the cold side, so that the bulk material is completely dried again and thus avoid possible mold growth.
  • this also regulates the humidity.
  • the procedure in each of the two beds of bulk material can be carried out independently of one another in one of the (preferred) embodiments described above.
  • the switching of the flow direction in the two bulk beds can be done in various ways:
  • the switching between the two beds of bulk material is carried out by a double design of the blower, which promote the air in different directions, with only one fan is operating at each operating phase.
  • the store consists of two or more bulk material layers each of uniform particles.
  • the bulk material bed has at least two regions with particles of different particle diameter, the region at the end of the bulk material bed, which is first flowed through in the flow direction by the heat-absorbing / cooling gas, having the larger particle diameter.
  • the bulk material can each consist of half particles with smaller and larger particle diameter.
  • the particles in each area consist of different materials.
  • the ratio between bed thickness L in the flow direction of the gas and average particle diameter d P of the bulk material is calculated as the sum of the ratios between bed thickness Lj in the flow direction of the gas and the mean particle diameter d P j of the bulk material of all subareas.
  • the ratio between bed thickness L in the flow direction of the gas and the average particle diameter dp of the bulk material in a bulk material bed having two partial areas is calculated as follows: l ⁇ / dpi + L 2 / d p2 .
  • This embodiment is particularly advantageous in applications in which a great deal of condensate formation in the bulk material is to be expected.
  • the capillary effects are less pronounced and the resulting condensate can drain easily without it accumulates in the bulk material.
  • the process according to the invention can also be used advantageously at higher temperatures, exploiting the same excellent properties:
  • the present invention provides an apparatus for carrying out the method according to the invention in any of the described embodiments, wherein the apparatus comprises a bed of a bulk material for flowing through gases and_the bulk material absorbs and stores heat or cold emitted by the gases, characterized that the device is set up to achieve the following:
  • the ratio between the bed thickness L in the flow direction of the gas and the mean particle diameter dp of the bulk material is at least 20 and at most 2000;
  • the specific particle surface a is so large that the ratio between the total surface area a V s (as product of the specific particle surface and the volume of the bed) and the Volumeflow of the gas in the standard state v G i (mi N 3 / h) is at least 0.05 m "1 and at most 1 0 m " 1 .
  • the bulk material consists of ceramic, chamotte, sil icium carbide, zirconium oxide, graph it, Eifel lava, gravel, iron ore, clay, lime, metallic particles or combinations thereof.
  • the bulk material consists of spheres, gravel-like particles, or particles in the form of fracture or gravel.
  • the device comprises a device for changing the flow direction in the bulk material bed, which preferably comprises at least one fan or a system of several valves.
  • the device comprises two, preferably independently flowed through bulk material beds of the above type.
  • the device preferably comprises two fans, each of which conveys air in different directions, with only one fan operating in each operating phase and switching of the flow direction being effected by starting the respective other fan.
  • the fans are housed between two bulk beds.
  • the bulk material bed or the bulk material beds preferably comprises two or more bulk material regions and each bulk material region has a different average particle diameter and / or another particle material.
  • a further preferred embodiment of the device according to the invention is particularly suitable for retrofitting in existing buildings.
  • the bulk material bed i.e., the heat storage mass
  • the bulk material bed is located in a container outside a building wall, which is preferably vertical to the wall.
  • the bulk material bed flows through parallel to the wall.
  • the bulk material bed is advantageously flowed through in this embodiment so that excess condensate can drain freely from the bulk material bed down.
  • This embodiment of the device according to the invention which is particularly suitable for retrofitting, has the advantage that the cross section of the wall passage / break required for the passage of air can be kept low.
  • the diameter of a cross-sectionally circular wall passage / fracture can be 60 to 100 mm, whereby an air passage of 20 to 60 m i N. 3 / h is made possible. This is very advantageous for retrofitting.
  • Fig. 5a and 5b an advantageous embodiment of the retrofit systems.
  • the arrow indicates the direction of flow of the air.
  • the inventive method using a ventilation system with heat recovery in a flow direction 1 0 cm thick bulk material bed of gravel from about the same size, spherical-like particles with a diameter of 4 mm simulated, in which thus the ratio between the bed thickness in the flow direction and the average particle diameter 25 is (c s of the particles about 1 kJ / kgK, flow rate 20 nrii.N. 3 / h, mass of the bulk material 5 kg).
  • the heat transfer coefficient defined above is 6.0 kJ / m 3 K.
  • the temperature of the outside air is 0 ° C when entering the bulk material bed and the temperature of the exhaust air is 20 ° C when entering the bulk material bed.
  • Fig. 1 the resulting temperature profile is shown in the bulk material bed.
  • the system is in a quasi-stationary state, or the temperature profiles are repeated periodically.
  • the abscissa axis shows the position within the bed and the ordinate axis the temperature.
  • the presented temperature profiles are drawn during an outdoor air phase: the first at the beginning (0th minute) and then every one more Minute later, until the profile at the end of an outside air phase (5th minute).
  • the outside air flows through the bed at 0 ° C and heats up to room temperature of 20 ° C.
  • the temperature of the preheated air remains at 20 ° C for up to two minutes. From the second minute on, the temperature of the preheated air drops, initially to a minimum, and at the end of the fifth minute to 14 ° C.
  • the mean temperature of the preheated fresh air is 18 ° C and the heat recovery 90%.
  • Fig. 2 shows the temporal temperature profile of the outlet temperatures of the same arrangement as in Fig. 1, wherein the upper curve shows the course of the temperature of the preheated outside air and the lower curve shows the course of the cooled exhaust air.
  • the upper curve shows the temperature of the preheated fresh air, as well as its mean value.
  • the lower curve shows the temperature of the cooled exhaust air.
  • the temperature change during each full 5 minute switching period is 5 to 6 ° C, while in the middle of the bed the temperature change is about 14 ° C (ie about 2.5 times as much as in the entry areas) ,
  • the switching time is 5 minutes. This short switching time is well suited for small systems, eg for the ventilation of individual rooms. For larger systems with an air flow of more than 1, 000 m 3 / h, however, a longer switching time, ie. of more than 5 minutes, beneficial.
  • the inventive method is based on a ventilation system with heat recovery in a direction of flow 25 cm thick bulk bed of gravel from about the same simulates large, spherical-like particles with a diameter of 3 mm, in which thus the ratio between the bed thickness in the flow direction and the mean particle diameter 83.
  • the switching time, and thus the time periods ti and t 2 is 20 minutes in this example.
  • the above-defined heat transfer coefficient value reaches 2.1 3 kJ / m 3 K.
  • the outside air flows through the bed at 0 ° C and heats up to 20 ° C. For about 10 minutes, the temperature of the preheated air remains constant. From the twelfth minute, it sinks and reaches a temperature of 16 ° C after 20 minutes. The mean temperature of the preheated outside air is then 19 ° C and the heat recovery level about 95%.
  • the temperature change during each full 20 minute switchover period is about 4 ° C, while in the middle of the bed the temperature change is about 14 ° C (ie 3.5 times as much as in the entry areas) , Therefore, over the embodiments of Examples 1 and 2, greater heat storage is possible. 3.
  • an advantageous embodiment of the device according to the invention for carrying out the method according to the invention will be described, which is particularly suitable for retrofitting in existing houses and apartments. This embodiment is shown in Figs. 5a and 5b.
  • a vertically arranged container (1) is a bulk material bed (2) as a heat storage mass.
  • the device is attached to a wall (3) having an opening (4) connecting the exterior and interior.
  • the opening (4) can be significantly smaller than the cross section of the Container (1), which is very advantageous for retrofitting.
  • a fan (5) which transports exhaust air or fresh air, can be mounted directly on the wall (Fig. 5a) or below the bulk material bed (2) (Fig. 5b).
  • the fan position can thus, depending on the installation location (outside or inside), be selected so that the noise emissions are minimized in the interior.
  • the ventilation systems are shown, which operate at ambient temperatures.
  • this method is also very well suited for significantly higher temperature ranges and significantly longer switching times.
  • the method according to the invention is simulated on the basis of a high-temperature installation for storing and emitting thermal energy in the temperature range between 550 ° C. and 1100 ° C.
  • the bulk material bed made of 12 mm aluminum ball is 1 2 m high.
  • the switching time is 10 hours and the air flow 25,000 m i N. 3 / h.
  • the above-described heat transfer coefficient is 0.68 kJ / m 3 K.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Solid-Sorbent Or Filter-Aiding Compositions (AREA)
  • Ventilation (AREA)

Abstract

La présente invention concerne un procédé pour capter, stocker et restituer de l'énergie thermique issue de gaz, le procédé comprenant les étapes suivantes : une première étape au cours de laquelle un lit de matière en vrac est parcouru par un gaz dans une première direction de circulation au cours d'un premier intervalle de temps t1, ledit gaz fournissant à la matière en vrac du chaud ou du froid qui est stocké dans la matière en vrac ; et une deuxième étape au cours de laquelle la matière en vrac est parcourue par un gaz dans une deuxième direction de circulation pendant un intervalle de temps t2, ledit gaz emmagasinant alors le chaud ou le froid de la matière en vrac, l'indice de chaleur transmise par unité de volume et degré Kelvin, défini en tant que ti mGi cpi / (a Vs Δ), valant au moins 0,25 kJ/m3K et au maximum 25 kJ/m3K, où i=1,2 désigne l'intervalle de temps t1 ou t2 , mGi représente le débit de gaz, cpi représente la capacité thermique spécifique du gaz , a représente la surface particulaire spécifique, Vs représente le volume de la matière en vrac et L est l'épaisseur du lit dans la direction de circulation du gaz. L'invention concerne par ailleurs un dispositif pour mettre en œuvre le procédé.
PCT/EP2017/052282 2016-02-03 2017-02-02 Procédé et dispositif pour capter, stocker et restituer de l'énergie thermique issue de gaz WO2017134177A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016001163.7 2016-02-03
DE102016001163.7A DE102016001163A1 (de) 2016-02-03 2016-02-03 Verfahren und Vorrichtung zur Aufnahme, Speicherung und Abgabe thermischer Energie von Gasen

Publications (1)

Publication Number Publication Date
WO2017134177A1 true WO2017134177A1 (fr) 2017-08-10

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WO (1) WO2017134177A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE545571C2 (en) * 2020-06-11 2023-10-24 Vattenfall Ab A method for storing thermal energy, a thermal storage system and a use of such a thermal storage system

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2419778A1 (de) * 1974-02-25 1975-09-04 Boehler & Co Ag Geb Regenerativwaermetauscher fuer gase
EP0908692A2 (fr) * 1997-10-08 1999-04-14 ATZ-EVUS Applikations- und Technikzentrum für Energieverfahrens-, Umwelt- und Strömungstechnik Procédé de fonctionnement d'un régénérateur et régénérateur
WO2009103795A2 (fr) * 2008-02-20 2009-08-27 I-Sol Ventures Gmbh Matériau composite pour accumulateur thermique
WO2012020233A2 (fr) * 2010-08-12 2012-02-16 Highview Enterprises Limited Procédé et appareil pour stocker l'énergie thermique
WO2013005192A1 (fr) * 2011-07-07 2013-01-10 Saint-Gobain Centre De Recherches Et D'etudes Europeen Centrale thermique dotée d'un régénérateur et son procédé de production
GB2493951A (en) * 2011-08-24 2013-02-27 Isentropic Ltd Apparatus for storing energy
DE102012019791A1 (de) * 2012-10-04 2014-04-10 Technische Universität Ilmenau Kugelumlauf-Wärmespeicher
WO2014082716A1 (fr) * 2012-11-30 2014-06-05 Saarstahl Ag Procédé pour faire fonctionner un régénérateur (réchauffeur à galets) ainsi que le régénérateur lui-même

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4238652C1 (de) 1992-11-16 1994-05-11 Air Liquide Regenerator zum Aufheizen von Gasen

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2419778A1 (de) * 1974-02-25 1975-09-04 Boehler & Co Ag Geb Regenerativwaermetauscher fuer gase
EP0908692A2 (fr) * 1997-10-08 1999-04-14 ATZ-EVUS Applikations- und Technikzentrum für Energieverfahrens-, Umwelt- und Strömungstechnik Procédé de fonctionnement d'un régénérateur et régénérateur
WO2009103795A2 (fr) * 2008-02-20 2009-08-27 I-Sol Ventures Gmbh Matériau composite pour accumulateur thermique
WO2012020233A2 (fr) * 2010-08-12 2012-02-16 Highview Enterprises Limited Procédé et appareil pour stocker l'énergie thermique
WO2013005192A1 (fr) * 2011-07-07 2013-01-10 Saint-Gobain Centre De Recherches Et D'etudes Europeen Centrale thermique dotée d'un régénérateur et son procédé de production
GB2493951A (en) * 2011-08-24 2013-02-27 Isentropic Ltd Apparatus for storing energy
DE102012019791A1 (de) * 2012-10-04 2014-04-10 Technische Universität Ilmenau Kugelumlauf-Wärmespeicher
WO2014082716A1 (fr) * 2012-11-30 2014-06-05 Saarstahl Ag Procédé pour faire fonctionner un régénérateur (réchauffeur à galets) ainsi que le régénérateur lui-même

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