WO2016050367A1

WO2016050367A1 - Discharging system with a high temperature thermal energy exchange system and method

Info

Publication number: WO2016050367A1
Application number: PCT/EP2015/055956
Authority: WO
Inventors: Henrik Stiesdal; Till Andreas Barmeier; Volker Seidel
Original assignee: Siemens Aktiengesellschaft
Priority date: 2014-09-30
Filing date: 2015-03-20
Publication date: 2016-04-07

Abstract

A discharging system with a least one high temperature thermal energy exchange system is provided. The high temperature thermal energy exchange system comprises at least one heat exchange chamber with chamber boundaries which surround at least one heat exchange chamber interior of the heat exchange chamber, wherein the chamber boundaries comprise at least one inlet opening for guiding in an inflow of at least one heat transfer fluid into the heat exchange chamber interior and at least one outlet opening for guiding out an outflow of the heat transfer fluid out of the heat exchange chamber interior, at least one heat storage material is arranged in the heat exchange chamber interior such that a heat exchange flow of the heat transfer fluid through the heat exchange chamber interior causes a heat exchange between the heat storage material and the heat transfer fluid. The discharging system is equipped with at least one discharging unit for discharging the heat transfer fluid of the outlet flow from heat for production of electricity.

Description

DISCHARGING SYSTEM WITH A HIGH TEMPERATURE THERMAL ENERGY EXCHANGE SYSTEM AND METHOD

BACKGROUND OF THE INVENTION

1. FIELD OF THE INVENTION

The present invention refers to a discharging system with a high temperature thermal energy exchange system and a method for discharging heat storage material of the high temperature thermal energy exchange system from thermal energy

2. DESCRIPTION OF THE RELATED ART

Despite the integration of renewable energy into the public electric energy system (power grid) a large share of elec^¬ tricity is nowadays still generated by fossil energy sources But the global climate change requires the further develop^¬ ment of renewable energies.

The energy output of renewable energy sources like wind and solar is not constant throughout a day or throughout a year. Consequently, electricity which is generated by utilizing en^¬ ergy from renewable energy sources fluctuates.

In order to handle this fluctuating electricity energy storage units are developed. Such energy storage units are a) me^¬ chanical storage units e.g. pumped hydro storage, compressed air storage or flywheels, (b) chemical energy storage units e.g. storage of hydrogen, batteries and organic molecular storage, (c) magnetic energy storage units, and (d) thermal energy storage units with water or molten salts. However, only pumped hydro storage is already today well- established and matured as a large scale energy storage tech^¬ nology. All other storage technologies are lacking capability to store electric energy at low cost, whereas pumped hydro storage is geographically limited to certain regions (suffi^¬ cient geodetic heights) .

SUMMARY OF THE INVENTION It is an objective of the invention to provide an efficient solution for releasing stored energy.

This objective is achieved by the invention specified in the claims .

A discharging system with at least one heat exchange chamber with chamber boundaries is provided. The chamber boundaries surround at least one heat exchange chamber interior of the heat exchange chamber. The chamber boundaries comprise at least one inlet opening for guiding in an inflow of at least one heat transfer fluid into the heat exchange chamber inte^¬ rior and at least one outlet opening for guiding an outflow of the heat transfer fluid out of the heat exchange chamber interior. At least one heat storage material is arranged in the heat exchange chamber interior such that a heat exchange flow of the heat transfer fluid through the heat exchange chamber interior causes a heat exchange between the heat storage material and the heat transfer fluid. The inflow of the heat transfer fluid into the heat exchange chamber and the outflow of the heat transfer fluid out of the heat ex^¬ change chamber result in the heat exchange flow of the heat transfer fluid through the heat exchange chamber interior. The discharging system is equipped with at least one dis^¬ charging unit for discharging the heat transfer fluid of the outflow from heat for production of electricity. With the aid of the discharging unit thermal energy is removed from the heat transfer fluid and consequently from the heat storage material. This removed heat is used for the production of electricity .

In addition to the discharging system with the high tempera- ture thermal energy exchange system, a method for discharging heat storage material of the charging system from thermal en^¬ ergy is provided. Thereby, in a discharging mode of the high temperature thermal energy exchange system, a heat transfer fluid is guided through the heat exchange chamber interior. By that, a discharging of the heat transfer material from thermal energy is caused. During the discharging mode a heat transfer from the heat storage material to the heat transfer fluid takes place. Thermal energy is absorbed by the heat transfer fluid.

In a preferred embodiment, the discharging unit comprises at least one heat exchanger for discharging the heat transfer fluid of the outflow. The heat exchanger is thermally coupled with the outflow of the heat transfer fluid. By that, thermal energy is removed from the heat transfer fluid. The removed thermal energy can be used in a power cycle for the produc^¬ tion of electricity.

This power cycle can be an ORC (Organic Rankine Cycle) . In a preferred embodiment, the discharging unit comprises at least one steam power plant. The power cycle is a steam cycle. For instance, the thermal energy from the high temperature ther^¬ mal energy exchange system can be used for the heating of feeding water of the steam cycle or alternatively for the generation of steam of the generation of subcritical or supercritical steam.

The heat exchange chamber is a space, cavity, excavation or a housing in which the heat storage material is located. Within the heat exchange chamber the heat exchange takes place. In order to provide an efficient heat exchange, the heat ex^¬ change chamber is preferably thermally insulated against the surroundings. The loss of thermal energy is reduced by the thermal insulation.

The heat transfer fluid is guided (led) into the heat ex- change chamber interior via the inlet opening and is guided out of the heat exchange chamber interior via the outlet opening. There is an inlet area of the chamber boundary with the inlet opening and there is an outlet area of the chamber boundary with the outlet opening.

For the guiding of the heat transfer fluid into the heat ex^¬ change chamber and for the guiding of the heat transfer fluid out of the heat exchange chamber a pipe system (or channel system, ducting system) is used. This pipe system can be closed (with a closed loop) or can be open (with an open loop) . For instance the heat transfer fluid is ambient (air of the environment) . The loop is an open loop. Air from the environment is introduced into the high temperature thermal energy exchange system and air of the high temperature ther- mal energy exchange system is released to the surroundings. There is an air exchange during the operation of the high temperature thermal energy exchange system. In contrast to that, there is no air exchange or a selectively adjustable air exchange during the operation in a closed loop. This has following specific advantage: In a situation with an almost completely charged heat storage material, heat transfer fluid with remaining heat is released to the environment in an open loop. The remaining heat is lost. In contrast to that, in a closed loop this heat transfer fluid with remaining heat stays in the high temperature thermal energy exchange system. The remaining heat is not lost. Therefore, in a preferred em^¬ bodiment, a closed loop is implemented and wherein the inflow comprises the outflow. The outflow is guided back to the in^¬ let opening. Therefore, in a preferred embodiment, a closed loop is implemented and wherein the inflow comprises the out^¬ flow. The outflow is guided back to the inlet opening. The discharging system is operated in the discharging mode. The discharged high temperature thermal energy exchange sys^¬ tem can be charged again. For charging the high temperature thermal energy exchange system, it is operated in a charging mode .

In order to increase the flexibility the steam cycle of fos^¬ sil fired power plants (or nuclear power plants, etc.) can be combined with the high temperature thermal energy exchange system proposed here. Either the installed equipment is sole^¬ ly used to generate electrical energy with the stored thermal energy in a heat recovery process like in CCPP (combined cy^¬ cle power plant) or the high temperature thermal energy ex^¬ change system is used to increase the flexibility of a ther- mal power plant. In the latter case the boiler is operated with fuel when fuel costs are lower than electricity costs and the storage is charged if electricity prices are low. Charging can take place during a period of excess production of energy.

The discharging mode can be realized when electricity prices and demand are high or when the production of renewable ener^¬ gies is low. Well suited are CCPP since their heat recovery steam generator (HRSG) is similar to the application proposed here. Nevertheless hard coal, oil, gas, waste incineration, wood or lignite fired power plants can be used since the heater device can be designed for high temperature to match the temperatures used in the steam generator. In a hybrid mode the fuel can be used to increase the temperature from the temperature level of the storage to the operating temper^¬ ature of the original furnace or boiler design.

Depending on the operating mode, a specific opening can have the function of an inlet opening or the function of an outlet opening. The flow direction of the heat exchange flow depends on the operating mode. Preferably, during the charging mode the heat exchange flow is directed in a charging mode direc^¬ tion, during the discharging mode the heat exchange flow is directed in a discharging mode direction and the charging mode direction and the discharging mode direction are opposite to each other (countercurrent ) . But, a change of the di^¬ rections of the heat exchange flow is not necessary. Charging mode direction and discharging mode direction comprise the same direction (co-current) . In a different operational use the main flow direction of the heat transfer fluid is the same for the charging mode and the discharging mode. In countercurrent operation, switching from the charging mode to the discharging mode the direction of the exchange flow through the heat exchange chamber interior is reversed and consequently, the function of the openings (inlet opening, outlet opening) is reversed, too. With such a solution it is especially advantageous to use the same heat transfer fluid for the charging mode and for the discharging mode. But of course, different heat transfer fluids for the charging mode and the discharging mode can be used, too. The high temperature thermal energy exchange system is espe^¬ cially adapted for operation at high temperatures. Therefore, in a preferred embodiment, an operating temperature of the operating mode is selected from the range between 300 °C and 1000 °C, preferably selected from the range between 500 °C and 1000 °C, more preferably selected from the range between 600 °C and 1000 °C, 650 °C to 1000 °C and most preferably be^¬ tween 700 °C and 1000 °C. A deviation of the temperature ranges is possible. In this context, very advantageous is an upper limit of the temperature range of 900 °C and most pref- erably an upper limit of the temperature range of 800 °C.

The heat storage material can be liquid and/or solid. For in^¬ stance, a core of the heat storage material is solid and a coating of this solid core is liquid. Such a liquid coating can comprise ionic liquid.

The solid material comprises preferably bulk material. Mix^¬ tures of different liquid materials and different solid mate- rials are possible as well as mixtures of liquid and solid materials .

It is possible that the heat storage material is a thermo- chemical energy storage material: Energy can be stored via an endothermic reaction whereas energy can be released via an exothermic reaction. Such a thermo chemical storage is for instance the calcium oxide/calcium hydroxide system. These heat storage materials can be arranged in specific containers out of non-reactive container material. Non-reactive means that no chemical reaction between the heat storage material and the container material takes place during the heat ex^¬ change process. Moreover, a complex high temperature thermal exchange system with different heat exchange units with different heat stor^¬ age materials and/or different heat transfer fluids is possi^¬ ble, too. For Instance, a thermal exchange unit with stones as heat storage material and a thermal exchange unit with a phase change material as a heat storage material are combined together .

In a preferred embodiment, the heat storage material compris^¬ es at least one chemically and/or physically stable material. In the range of the operational temperature the heat storage material does not change its physical and/or chemical proper^¬ ties. A physically stable material does not change its physi^¬ cal properties during the heat exchange. For instance, the heat storage material remains in a solid state in the operat- ing temperature range. A chemically stable material does not change its chemical composition during the heat exchange. For instance, such a chemically stable material is a phase change material (PCM) . In a preferred embodiment, the heat storage material compris^¬ es sand and/or stones. The stones can be natural stones or artificial stones. Mixtures thereof are possible, too. Arti^¬ ficial stones can consist of containers which are filled with heat storage material. This heat storage material is for in^¬ stance a phase-change material or a thermo-chemical storage material (see above) . Preferably, the stones comprise gravels (pebbles) , rubbles and/or grit (splits). The artificial material comprises pref^¬ erably clinkers or ceramics. Again, mixtures of the mentioned materials are possible, too. In order to provide a cheap energy storage material it is ad^¬ vantageous to use waste material. Therefore, in a preferred embodiment, the artificial material comprises at least on by^¬ product of an industrial process. For instance, the by^¬ product is iron silicate. Iron silicate origins from a slag of copper production.

In a preferred embodiment, heat exchange channels are embed^¬ ded in the heat storage material for guiding of the heat ex^¬ change flow through the heat exchange chamber interior. The heat storage material forms a heat exchange bed. The heat ex^¬ change bed comprises the heat exchange channels. The heat ex^¬ change channels are embedded into the heat storage bed such that the heat exchange flow of the heat transfer fluid through the heat exchange channels causes the heat exchange between the heat storage material and the heat transfer flu^¬ id. The heat exchange channels can be formed by interspaces (gaps) of the heat storage material. For instance, the heat storage material comprises stones. The stones form the heat exchange bed with the heat exchange channels. In addition or alternatively, the heat storage material is porous. Open pores of the heat storage material form the heat exchange channels .

In a preferred embodiment, the high temperature thermal ener- gy exchange system is equipped with at least one flow adjust^¬ ing element for adjusting the heat exchange flow of the heat transfer fluid through the heat exchange chamber interior, the inflow of the heat transfer fluid into the heat exchange chamber interior and/or the outflow of the heat transfer fluid out of the heat exchange chamber interior. With the aid of the flow adjusting element it is possible to adjust a temper^¬ ature distribution in the heat exchange chamber interior and within the heat storage material respectively. The use of a number of flow adjusting elements is advantageous for a fine tuning of the heat exchange flow and consequently for a fine tuning of the temperature distribution in the heat storage material .

Preferably, the flow adjusting element comprises at least one active fluid motion device (with a corresponding software system) which is selected from the group consisting of blower, fan and pump and/or the flow adjusting element comprises at least one passive fluid control device which is selected from the group consisting of activatable bypass pipe, nozzle, flap and valve. A multitude of these devices are possible as well as a combination of these devices. With the aid of such devices the heat exchange flow can be modified such that the heat exchange occurs efficiently. In addition, flow adjusting elements can be arranged serially or in parallel. For in^¬ stance, two flaps are arranged at two inlet openings in order to adjust the inflows of the heat transfer fluid into the heat exchange chamber and consequently in order to adjust the temperature distribution in the heat exchange chamber.

The flow adjusting element is arranged in the heat exchange chamber, downstream of the heat exchange chamber and/or upstream of the heat exchange chamber.

In the context of the active fluid motion devices it is ad^¬ vantageous that driving units of the active fluid motion de^¬ vices like electric motors and electrical equipment are lo^¬ cated outside of the (possibly very hot) heat exchange flow.

The special advantage of passive control devices is that they are cheap. In addition, passive control devices are very re^¬ liable . The heat exchange chamber is a vertical heat exchange chamber and/or a horizontal heat exchange chamber. The term "horizontal heat exchange chamber" implies a hori^¬ zontal main (average) flow of the heat transfer fluid through the heat exchange chamber interior. The flow direction of the horizontal main flow is essentially parallel to the average surface of the earth. The horizontal direction is essentially a perpendicular direction to the direction of the gravity force which affects the heat transfer fluid. Perpendicular means in this context that deviations from the perpendicular^¬ ity of up to 20° and preferably deviations of up to 10° are possible .

A horizontally oriented direction of the heat exchange flow can be achieved by lateral inlet openings and/or lateral out^¬ let openings. The horizontal heat exchange chamber comprises these openings in its side chamber boundaries. In addition, with the aid of an active fluid motion control device like a blower or a pump the heat exchange flow in the heat exchange chamber interior is caused. The heat transfer fluid is blown or pumped into the heat exchange chamber interior or is pumped or sucked out of the heat exchange chamber interior.

In contrast to the term "horizontal heat exchange chamber", the term "vertical heat exchange chamber" implies a vertical main flow of the heat transfer fluid through the heat ex^¬ change chamber interior. For instance, the operating mode is the charging mode. In a vertical heat exchange chamber the heat exchange flow is preferably directed downwards (top down) during the charging mode. The vertical main flow (essentially parallel but in the opposite direction to the di^¬ rection of gravity force) can be caused by an active fluid motion device (blower or pump) . The inlet opening is located at a top of the heat exchange chamber and the outlet opening is located at a bottom of the heat exchange chamber. Based on natural convection, in a vertical heat exchange chamber the temperature of the heat storage material along a cross section perpendicular to the flow direction of the heat transfer fluid is approximately the same (horizontal isother- mal lines) .

In contrast to that, in a horizontal heat exchange chamber due to natural convection the temperature of the heat storage material along the cross section perpendicular to the flow direction of the heat transfer fluid (see below) can differ (inclined isothermal lines) .

It has to be noted that the terms "horizontal" and "vertical" are independent from the dimensions of the heat exchange chamber and its orientation. Decisive is the direction of the flow of the heat transfer fluid through the heat exchange chamber interior. For instance, a "horizontal heat exchange chamber" can have a chamber length which is less than the chamber height of the heat exchange chamber.

Besides pure vertical and horizontal heat exchange chambers, a mixture of "vertical heat exchange chamber" and "horizontal heat exchange chamber" is possible, too. In such a heat ex^¬ change chamber, the main flow of the heat transfer fluid is the result of horizontal and vertical movement of the heat transfer fluid through the heat exchange chamber interior.

In a preferred embodiment, at least two inlet openings are arranged vertically to each other and/or at least two outlet openings are arranged vertically to each other. Openings are arranged above each other. By this measure it is possible to influence a vertical distribution of heat exchange flows in order to improve a temperature distribution (temperature front) in the heat storage material and heat exchange chamber interior respectively. Isothermal lines perpendicular to the flow direction are influenced. The temperature front is defined by neighboring cold and hot areas of the heat storage material in the heat exchange cham^¬ ber interior caused by the flow of the heat transfer fluid through the heat exchange chamber interior. The temperature front is aligned perpendicular to the respective flow direc^¬ tion of the heat exchange flow through the heat exchange chamber. During the charging mode the heat exchange flow is directed in a charging mode direction wherein the temperature front moves along this charging mode direction. In contrast to that, during the discharging mode the heat exchange flow is directed in the discharging mode direction (opposite to the charging mode direction) wherein the temperature front moves along the discharging mode direction. In both cases, the temperature front of the heat exchange chamber is migrat- ing through the heat exchange chamber to the respective hot/cold ends of the heat exchange chamber. It is to be noted that in case of countercurrent operation, the hot (hot open^¬ ing) end remains the hot end (hot opening) , independently from the mode (charging or discharging mode) .

The temperature front is a zone of strong temperature gradi^¬ ent in the heat storage material, i.e. high temperature dif^¬ ference between hot and cold areas. In this application it separates the hot (charged with thermal energy) and the cold (not charged) zone in the heat exchange chamber within the heat storage material. The temperature front develops due to the transfer of thermal energy from the heat transfer fluid to the heat storage material during charging and from the heat storage material to the heat transfer fluid during dis- charging. Isothermal zones/lines develop ideally (e.g. with^¬ out the influence of gravitation) perpendicular to the main flow direction, i.e. zones/lines of constant temperature.

In order to optimize the efficiency of the high temperature thermal energy exchange system it is advantageous to ensure a uniform temperature front. There are just small variations concerning the temperature gradients perpendicular to the flow direction. In a vertical heat exchange chamber with a flow direction top down, the temperature front is nearly uniform due to natural convection. So, in this case additional measures are not necessary. In contrast to that, natural con^¬ vection leads to a non-uniform temperature front in a hori- zontal heat exchange chamber. So, in this case additional measures could be meaningful (like usage of more openings or usage of more flow adjusting elements) .

Preferably, the chamber boundary with one of the openings comprises a transition area with a tapering profile such that an opening diameter of the opening aligns to a first tapering profile diameter of the tapering profile and a chamber diameter of the heat exchange chamber aligns to a second ta^¬ pering profile diameter of the tapering profile. The transi- tion area comprises an increasing cross section from the respective opening towards the heat exchange chamber. This is especially advantageous for the inlet opening. The diameter of the transition area expands from the opening diameter of the inlet opening to the diameter of the chamber opening. With the aid of the tapering profile the inflow of the heat transfer fluid is guided into the heat exchange chamber inte^¬ rior. The guided inflow is distributed to a wide area of heat storage material. By this measure a capacity of the heat ex^¬ change unit (heat storage material which is located in the heat exchange chamber) can be highly exploited. In addition, the efficiency of the heat exchange can be improved by adapt^¬ ing the heat exchange flow. Remark: For additionally adapting the heat exchange flow, a diffuser can be located at the in^¬ let opening, especially in the transition area. By means of the diffuser an incident flow of the heat transfer fluid into the heat exchange chamber can be adjusted. For instance, such a diffuser is formed by stones which are located in the tran^¬ sition area with the tapering profile. For the case that the heat exchange chamber comprises a num^¬ ber of inlet openings it is very advantageous to arrange a described transition area in at least one of the inlet open- ings . Preferably, a number of inlet openings or every inlet opening comprises its individual transition area.

The transition area with the outlet opening can be tapered, too: A tapering of the chamber opening to the outlet opening is implemented. By this measure the guiding of heat flow out of the interior of the heat exchange chamber is simplified.

In a configuration where the flow direction of charging and discharging are opposite the tapering of the transition area at the inlet opening and the tapering of the transition area at the outlet opening ensure a desired flow distribution of the heat transfer fluid in both operating modes. In this context the use of a short transition area is very advantageous. For instance, the short transition area com^¬ prises a dimension which is less than 50% of a heat exchange chamber length. For instance, the dimension is about 20% of the heat exchange chamber length. The length is the heat ex- change chamber dimension that is parallel to the main flow direction of the heat transfer fluid through the heat ex^¬ change chamber. But of course, the dimension of the transi^¬ tion area is dependent on a number of features of the com^¬ plete system, e.g. temperature of the heat transfer fluid, mass flow of the heat exchange flow, speed of the heat ex^¬ change flow at the relevant opening, etc.

In order to save space and in order to reduce the surface- volume ratio for a reduced heat loss, it is advantageous to implement a transition area as short as possible. The result is a short transition channel for guiding the inflow into the heat exchange chamber interior. Besides an efficient usage of the capacity of the heat exchange unit a low space require^¬ ment is connected to this solution.

Preferably, the heat exchange chamber comprises a cylindri- cally shaped chamber boundary. For instance, the chamber boundary which comprises the inlet opening is formed as a circular cylinder and/or the chamber boundary with the outlet opening is formed as a circular cylinder. Such shapes lead to best surface-volume ratios. The heat transfer fluid is selected from the group consisting of a liquid and a gas. The gas is selected from the group consisting of inorganic gas and/or organic gas. The inorganic gas is preferably air. Mixtures of different liquids are pos^¬ sible as well as mixtures of different gases.

Preferably, the heat transfer fluid comprises a gas at ambi^¬ ent gas pressure. Preferably, the gas at the ambient pressure is air. The ambient pressure (900 hPa to 1.100 hPa) varies such that the heat exchange flow through the heat exchange chamber interior is caused.

In a preferred embodiment, the high temperature thermal ener^¬ gy exchange system is equipped with at least one measuring device for determining a charge status of the high tempera- ture thermal energy exchange system. Preferably, the men^¬ tioned measuring device for determining a charge status of the high temperature thermal energy exchange system is a thermocouple. The thermocouple is a temperature measuring de^¬ vice which is based on the Seebeck effect. Alternatively, the temperature measuring device is based on electrical re^¬ sistance .

For instance, the charge status of the high temperature ther^¬ mal energy exchange system comprises the degree of the charg- ing of the heat storage material with heat. With the aid of the measured charge status the operating mode (charging mode or discharging mode) can be monitored. Information about the charge status can be used for the process control of the op^¬ erating modes. The charge status or state of charge refers to the energy content of the high temperature thermal exchange system which is related to the temperature of the heat stor^¬ age material. If a large share of the heat storage material comprises a high temperature the state of charge or charge status is higher than if a small share of the heat storage materials at a high temperature.

In this context it is advantageous to use a number of such measuring devices. Preferably, these measuring devices are distributed over the heat exchange chamber.

The heat exchange chamber can comprise large dimensions.

Preferably, a length of the heat exchange chamber is selected from the range between 20 m - 250 m, a width of the heat ex^¬ change chamber is selected from the range between 20 m - 250 m and a height of heat exchange chamber is selected from the range of 10 m - 60 m. For the charging cycle and/or for the discharging cycle the high temperature thermal energy exchange system comprises preferably a particle filter or other means to remove parti^¬ cles from the heat transfer fluid, for instance a cyclone particle remove system. The removing of particles servers the purpose of efficient heat transfer, avoid deposition of the particles, avoid cloaking and avoid possible fires. It is possible to use this filter device just for commissioning purposes. In this case, after the initial operation the fil^¬ ter device is removed.

With the invention following specific advantages are

achieved :

- With the aid of the discharging system with the high tem- perature thermal energy exchange system stored thermal energy can be released efficiently.

- Excess electricity is used for the charging mode. Excess electricity is transformed into thermal energy which is stored. During the discharging mode thermal energy is trans^¬ formed into electricity, e.g. with the aid of a water steam cycle. This transformation is very efficient due to high tem^¬ peratures provided by the high temperature exchange system. Electricity from the discharge mode is available during peri^¬ ods of high electricity consumption and high demand (of con^¬ sumers or of the energy market) . - Usually, the location of production of electricity with the aid from renewable energy sources such as onshore and off^¬ shore wind does not coincide with the region of high power consumption. Weak grid node points can cause a grid overload since they were designed for a constant base load and not for fluctuating renewable energy. The excess energy that exceeds the capacity of the grid can reach up to 20%. In this case the renewable energy sources have to be curtailed or even shutdown. With the invention an efficient storage of the ex^¬ cess electricity is possible.

- Thermal energy on a high temperature level can be stored over a long period of time. The thermal heat storages could deliver heat for more than 10 hours up to 10 days. The high temperature level in this kind of storages can be more than 600 °C and it can be directly used for reconversion in a wa^¬ ter steam cycle. The electrification of the stored thermal energy via the water steam cycle does not depend on fuel like gas or coal and hence it is CO₂ emission free. - The high temperature thermal energy exchange system offers a higher energy density compared to other storage technolo^¬ gies. This means that more energy can be stored in a smaller volume. In addition, bulk heat storage materials are much cheaper and cost effective than molten salts or phase change materials which are currently developed.

- Due to high temperatures an additional heating up for sub^¬ sequent electrification processes, e.g. additional heating up of steam of a water/steam cycle is not necessary.

- The used heat storage materials are simple and regionally available natural products like basalt stones. By-products and waste materials from industrial processes e.g. iron sili- cate slag from copper production are possible storage materials as well. This reduces the costs and causes short

transport distances. - The high temperature thermal energy exchange system can be operated under ambient pressure (heat transfer fluid at ambi^¬ ent pressure) . So, there is no need for installing pressure units in view of the heat transfer fluid. It is easier to reach a necessary reliability of the high temperature thermal energy exchange system. In addition, high pressure units would be expensive.

- The stored thermal energy could be used for ORC (Organic Rankine Cycle) power plants. These power plants operate at relatively low operating temperatures. But preferably, the stored thermal energy is used for steam power plants. Due to the high load capacity and the high possible operating tem^¬ peratures of the high temperature thermal energy exchange system the working fluid (steam) of the steam power plant can be operated at high temperatures (steam parameter) . This re^¬ sults in a high efficiency of the steam cycle of the steam power plant.

- Preferably, the high temperature thermal energy exchange system comprises a pipe system with compensation units (e.g. expansion joints) for balancing different thermal induced di^¬ mension changes (thermal dynamic loads) . Thermal mismatch does not result in a damage of the pipe system. This leads to a high reliability. Alternatively or in addition, the pipe system comprises thermally insulated components, like chan^¬ nels which are insulated from the inside.

- The discharging system can be combined with conventional power plants, e.g. a coal power plant. The shutdown of such a power plant and the subsequent start of the power plant are expensive. With the aid of the discharging system it is pos^¬ sible to avoid the shutdown and start of the power plant. The electricity is transformed into thermal energy which is stored by the high temperature thermal energy exchange system via the charging mode. Via the discharging mode this charged thermal energy is used for the production of electricity. - Generally, there is a wide use of the high temperature thermal energy exchange system for this high quality heat. It is useable not only for water steam cycles, it can also be used for industrial or power plant processes or for district heating or for industrial steam.

BRIEF DESCRIPTION OF THE DRAWINGS

Further features and advantages of the invention are produced from the description of exemplary embodiments with reference to the drawings. The drawings are schematic.

Figures 1 to 4 show different high temperature thermal energy exchange systems. Figure 2A show a vertical heat exchange chamber in a dis^¬ charging mode.

Figure 2B show the vertical heat exchange chamber of figure 2A in a charging mode.

Figure 3 and 4 show horizontal heat exchange chambers.

Figures 5A and 5B show vertical heat exchange chambers. Figures 6A, Fig 6B and Fig 6C show high temperature thermal energy exchange systems with different thermal insulations of the heat exchange chamber.

Figure 7 shows a complete discharging system with a high tem- perature thermal energy exchange system.

Figure 8 shows a combined cycle power plant. Figures 9 to 12 show different discharging systems.

Given is a discharging system 1000 with a least one high tem- perature thermal energy exchange system 1 with a heat ex^¬ change chamber 11 on a high temperature level.

The high temperature thermal energy exchange system 1 com^¬ prises a heat exchange chamber 11 on a high temperature lev- el, which will be charged and discharged with thermal energy via a heat transfer fluid 13 and stored in the heat storage material 121.

The temperature level of the stored heat is significantly higher compared to methods applied so far to increase the ef^¬ ficiency of the discharging system. The temperature level lies between 300 °C and 800 °C, preferably between 550 °C and 650 °C. The thermal capacity of the high temperature thermal energy exchange system lies in the range between 0.3 GWh and 100 GWh, which causes a thermal power of 50 MW.

The high temperature thermal energy exchange system 1 com^¬ prises at least one heat exchange chamber 11 with chamber boundaries 111 which surround at least one heat exchange chamber interior 112 of the heat exchange chamber 11. The heat exchange chamber is a horizontal heat exchange chamber 114.

The chamber boundaries 111 comprise at least one inlet open- ing 1111 for guiding in an inflow 132 of at least one heat transfer fluid 131 into the heat exchange chamber interior 112 and at least one outlet opening 1112 for guiding an outflow 133 of the heat transfer fluid out of the heat exchange chamber interior 112. At least one heat storage material 121 is arranged in the heat exchange chamber interior 112 such that a heat exchange flow 13 of the heat transfer fluid 131 through the heat exchange chamber interior 112 causes a heat exchange between the heat storage material 121 and the heat transfer fluid 131.

The heat exchange chamber is at least partly integrated in the earth. An alternative embodiment of the high temperature thermal energy exchange system comprises a completely inte^¬ grated heat exchange chamber.

The discharging system is equipped with at least one dis- charging unit 400 for discharging the heat transfer fluid of the outflow 133 from heat for production of electricity.

The high temperature thermal energy exchange system 1 is equipped with a number of measuring devices 1500 for deter- mining a charge status of the high temperature thermal energy exchange system 1. These measuring devices are distributed mainly in the heat exchange chamber 11.

The heat exchange chamber 11 is thermally insulated against the surrounding. There is a thermal insulation unit 300.

Different thermal insulation possibilities (thermal insula^¬ tion stacks) are shown in figures 6A, 6B and 6C. Concerning figure 6A the insulation unit 300 comprises a first insula- tion cover sheet 301. This first insulation cover sheet comprises gas concrete, for instance Ytong®. Alternatively this first insulation cover sheet comprises bricks, clay, ceram^¬ ics, clinker, concrete, plaster, fiber reinforced plaster, and/or metal.

The next insulation layer 302 comprises mineral wool and/or rock wool. Alternatively this insulation layer 302 comprises foamed clay or glass concrete. Mixtures of these materials are possible, too.

A third insulation layer 303 completes the insulation unit: This third insulation layer 303 has the function of a sup^¬ porting structure and comprises gas concrete (for instance Ytong® or clay) , clinker, concrete, plaster, fiber reinforced plaster and/or metal.

Alternatively, the first insulation layer 301 is omitted (figure 6B) .

In a further alternative solution the thermal insulation unit 300 comprises an additional intermediate insulation cover layer 304 (figure 6C) . This additional cover layer comprises gas concrete, clay or ceramics and has the function of an ad^¬ ditional supporting structure.

Exemplarily, the length 118 of the horizontal heat exchange chamber 11 is about 200 m, the height 119 of the heat ex- change chamber 11 is about 10 m and the width of the heat ex^¬ change chamber 11 is about 50 m.

Alternatively, a vertical heat exchange chamber 113 is used (figures 2A and 2B) . For instance, the height 120 of this vertical heat exchange chamber 113 is about 40 m, a width 119 about 20 m and a length of about 40 m.

Alternatively, cylindrically shaped heat exchange chambers 113 are used.

The proposed high temperature thermal energy exchange system will store energy on a high temperature level, which can be used during discharging to produce steam in a water steam cycle for reconversion into electrical energy. Therefore, one or several heat exchange chambers filled with solid heat storage material are used. The solid heat storage material could be bulk storages material with sand, stones or gravels, rubbles, splits, clinkers, ceramics, slag and other bulk ma^¬ terials, for example basalt or iron silicate slag.

The solid materials can be used alone or can be mixed with other heat storage materials (e.g. due to limited availabil^¬ ity of materials, in order to improve the flow behavior of the heat exchange flow of the heat transfer fluid through the heat exchange chamber interior or in order to improve the heat exchange between the heat storage material and the heat transfer fluid) for the use in the high temperature thermal energy exchange system. Different particle sizes or mixture of different particle sizes (improving flow behavior and en^¬ ergy density) can be used, too. As a result, the filling of the heat exchange chamber with heat storage material can be homogenous or inhomogeneous .

This solid bulk material is heated up and stores the thermal energy over a long time period. The shape and the arrangement of one or several heat exchange chambers with the heat stor^¬ age material are according to the usage and the integration in a certain system. The shape of the base area of the heat exchange chamber depends on whether the heat exchange cham^¬ ber (s) will be built vertically (no negative effect of natu^¬ ral convection) or horizontally (simple construction and incident flow, adaption to local conditions) as shown in fig- ures 1 and 2A and 2B. The cross section of the heat exchange chamber will be a trapezoid, if the heat exchange chamber is horizontal) .

In both cases (horizontal heat exchange chamber and vertical heat exchange chamber), there is a transition area 116 of the heat exchange chamber 11 with a tapering profile 1161. There^¬ by an opening diameter 1113 of the opening 1111 or 1112 aligns to a first tapering profile diameter 1162 of the ta^¬ pering profile and a chamber diameter 117 of the heat ex- change chamber 11 aligns to a second tapering profile diame^¬ ter 1163 of the tapering profile (see figures 1, 2A, 2B, 5A or 5b) . The inflow 132 of the heat transfer fluid 13 is guid^¬ ed into the heat exchange chamber interior 112. The guided inflow is distributed to a wide area of heat storage material 121. By this measure a capacity of the heat exchange unit

(heat storage material 121 which is located in the heat ex^¬ change chamber 11) can be utilized in an advantageous manner. The transition area 116 is short. The transition area 116 comprises dimension 1162 which is less than 50% of a heat ex^¬ change chamber length 118 of the heat exchange chamber 11. The short transition area 116 projects into the heat exchange chamber 11. The result is a short transition channel for the guiding of the inflow 132 into the heat exchange chamber interior 112 of the heat exchange chamber 11.

In order to adapt the heat exchange flow 13 the high tempera- ture thermal energy exchange system comprises a flow adjust^¬ ing element 134. This flow adjusting element 134 is a blower.

Furthermore the heat exchange chamber 11 can comprise one or several inlet openings 1111 and outlet openings 1112 as shown in figure 3.

The high temperature thermal energy exchange system 1 is ad^¬ ditionally equipped with at least one flow adjusting element 134. The flow adjusting element is an active fluid motion de- vice (1341) like a blower or a pump. Such a device enables a transportation of the heat transfer fluid 131 through the heat exchange chamber interior 111 of the heat exchange cham^¬ ber 11. The blower or the pump can be installed upstream or downstream of to the heat exchange chamber 11.

In addition, at least one passive fluid control 1342 device like a valve is located upstream or downstream of the heat exchange chamber 11. For the charging mode the downstream installation (installation of the adjusting device at the cold end of the high tem^¬ perature thermal energy exchange system) is advantageous: Relatively cold heat transfer fluid passes the flow adjusting device after releasing of heat to the heat storage material. In contrast to that, in a discharging mode the upstream installation of the flow adjusting device is advantageous: Rel^¬ atively cold heat transfer fluid passes the flow adjusting element before absorbing heat from the heat storage material. For both modes, the flow adjusting element is located at the same position.

In case of vertical heat exchange chambers the inlet openings and outlet openings can be installed at the top and bottom

(decreasing and avoiding natural convection) . Horizontal heat exchange chambers can have inlet openings and outlet openings on top and bottom (decreasing natural convection) or sideways (simple and inexpensive construction and simple incident flow) .

The heat transfer fluid 131 enters the heat exchange chamber 11 through a diffuser 1164. The diffuser 1164 comprises stones 1165 and is arranged at the transition area 116 of the heat exchange chamber 11.

Furthermore the heat transfer fluid 131 can be liquid or gas^¬ eous, which also can be organic or inorganic. In order to guide the heat transfer fluid 131 shutters and/or valves (passive fluid control devices) are used.

Figure 2A shows a vertical heat exchange chamber 113 in a discharging mode. The discharging mode direction 136 is ori- ented upwards.

Figure 2B shows the vertical heat exchange chamber 113 of Figure 2A in a charging mode. The charging mode direction 135 is directed downwards.

Figure 3 shows a horizontal heat exchange chamber 114. There^¬ by two inlet openings 1111 are arranged above each other as well as two outlet openings 1112. These openings 1111 and 1112 are arranged at individual transition areas 1166 of the heat exchange chamber 11. At least every individual transi^¬ tion area 1166 of the inlet openings comprises a tapering profile. By means of the individual transition areas 1166, diffusers 1164 with stones 1165 are formed. For that, the transition areas are filled with stones up to a third. Again: Measuring devices 1500 for determining a charge status of the high temperature thermal energy exchange system are distrib^¬ uted in the heat exchange chamber 11.

Depending on the usage and the demands, the capacity of the high temperature thermal energy exchange system can easily be adapted (heat storage material, dimensions of the heat ex^¬ change chamber, etc.) . For instance, to increase the capacity of high temperature thermal energy exchange system the high temperature thermal energy exchange system is equipped with several heat exchange chambers as shown in figure 4.

Thereby the heat exchange chambers can be arranged in paral- lei, serially, in line, on top of each other and/or as single one. Figure 4 show such an embodiment with a parallel ar^¬ rangement: Three heat exchange chambers 11 form together a common storage unit of the high temperature thermal energy exchange system.

Referring to figure 7, the complete charging and discharging system 1000 for a high temperature thermal energy exchange system 1 comprises one or several electrical heating devices 201, one or several machines to circulate the working fluid such as blowers 211 or pumps 1341 and one or several heat ex^¬ change chambers 11. The electrical heating devices 200 can be resistance heater 201, inductive heater or others. These de^¬ vices are connected by a pipe or ducting system 1001. The high temperature thermal energy exchange system shown in fig- ure 7 comprises a closed loop 1005.

For the charging mode, the heat transfer fluid 131 is heated up from ambient conditions by the electrical heater 201. Alternatively, the heating (partial heating or complete heat^¬ ing) of the heat transfer fluid is carried out with the aid of waste heat e.g. from industrial or power plant processes or from geothermal sources with or without an electrical heating device.

This charged heat transfer fluid is guided into the heat ex- change chamber interior 112 of the heat exchange chamber 11 for charging the heat storage material. Thereby the heat ex^¬ change between the heat transfer fluid and the heat storage material takes place. With reference 2000 the temperature front at a certain time of this charging process is shown.

The machine to circulate the heat transfer fluid 131 is pref^¬ erably installed upstream or alternatively downstream of the electrical heating device or downstream of heat exchange chamber. Several heat exchange chambers 11 are combined for varying charge and discharge duration (not shown) . Alterna^¬ tively, just one heat exchange chamber 11 is used in order to cover the required storage capacity.

For the discharging mode the high temperature thermal energy exchange system comprises one or several heat exchange cham^¬ bers 11 mentioned above, an active fluid motion control de^¬ vice 1341 to circulate the heat transfer fluid 131 and a thermal machine for re-electrification, which can be a water/steam cycle 1003. The working fluid of this cycle is wa- ter and steam. The water/steam cycle 1003 has the function of a discharging unit 400. With the aid of the heat exchange system (heat exchanger) 1002 thermal energy of the heat transfer fluid is transferred to the working fluid of the steam cycle 1002.

The different components of the high temperature thermal en^¬ ergy exchange system 1 are connected with a pipe or ducting system 1001. The flow adjusting element guides the heat transfer fluid through the heat exchange chamber of the high temperature thermal energy exchange system, thermal energy is transferred from the heat storage material 121 to the heat transfer fluid 131 and is transported to the thermal machines or further applications e.g. district heating, preheating of the discharge cycle, heating of different components of the high temperature thermal energy exchange system etc. If the thermal machine is a water steam cycle, a steam generator, a heat exchanger or an evaporator, which consist of one or sev- eral units, the thermal energy is transferred to water to generate steam which is fed to a thermal engine to produce electrical power as shown in figure 7. If the working fluid downstream of this thermal machine still contains thermal en^¬ ergy at a temperature level higher than ambient, this energy can be stored in the same heat exchange chamber or in another heat exchange chamber.

The complete system with all components in charge and dis^¬ charge cycle for the high temperature thermal energy exchange system is shown in figure 7.

In an energy system with high penetration of renewable energy the profitability of fossil fueled thermal power plants suf^¬ fers from low operation hours. This can lead to a complete shutdown of such plants for economic reasons.

The components are connected with a pipe or ducting system. The fluid machine guides the heat transfer fluid through the heat exchange chamber interior, thermal energy is transferred from the heat storage material to the heat transfer fluid and transported to the thermal machine. Via the heat exchanger 2300 thermal energy is transferred to the steam cycle 2200 of the discharging unit 400. If the thermal machine is a water steam cycle, a steam gener^¬ ator, a heat exchanger or an evaporator, which consist of one or several units, transfers the thermal energy to water to generate steam which is fed into a thermal engine to produce electrical power. If the working fluid downstream of this thermal machine still contains thermal energy at a tempera^¬ ture level higher than ambient, this energy can be stored in another thermal storage, which can comprise one or several heat exchange chambers. This thermal energy can alternatively be used else wise for heating etc.

In a closed discharge cycle (discharging system) , the ex- hausted gas which leaves the thermal machine is preferably guided into the first thermal storage exchange chamber again as shown in figure 12.

The discharging (and charging) system of a high temperature thermal exchange system comprises one or several heat ex^¬ change chambers (storage units) , one or several charging units (heating devices like resistance heater or inductive heater) and one or several machines to circulate the heat ex^¬ change fluid such as blowers or pumps. These units are con- nected by a pipe or ducting system. The heat transfer fluid is heated up from ambient conditions, is pre- or complete heated up with waste heat from industrial or power plant pro^¬ cesses with or without a charging unit (heating device) . Several heat exchange chambers are combined for varying charge and discharge duration. Alternatively one heat ex^¬ change chamber is solely used to cover the required storage capacity . One or several thermal high temperature thermal exchange sys^¬ tems can comprise solid heat storage material with stones, sand, gravels, rubbles, splits, clinkers etc., which could also be basalt or iron silicate slag for example. This solid bulk material is heated up and stores the thermal energy over a long time period.

Furthermore the described discharging system for the high temperature thermal energy exchange system can also be used in a closed charging cycle. The heat transfer fluid that leaves the heat exchange chamber is guided to a cold side of the charging unit. The heat transfer fluid is heated up in every cycle and does not need to be heated up from ambient conditions as shown in fig. 12. Either the installed equipment is solely used to generate electrical energy with the stored thermal energy in a heat recovery process like in CCPP or the high temperature thermal exchange system is used to increase the flexibility of a thermal power plant. In the latter case the boiler is fired with fuel when fuel costs are lower than electricity costs and the high temperature exchange system is charged if elec^¬ tricity prices are low.

The discharging of the charged system can be realized when electricity prices and demand are high or when the production of renewable energies is low. Well suited are CCPP since their heat recovery steam generator (HRSG) is similar to the application proposed here. Nevertheless, hard coal, oil, gas, waste incineration, wood or lignite fired power plants can be used since the charging unit can be designed for high temper^¬ ature to match the temperatures used in the steam generator. In a hybrid mode the fuel can be used to increase the temper^¬ ature from the temperature level of the high temperature thermal exchange system to the operating temperature of the original furnace or boiler design. Figure 8 shows a conventional combined cycle power plant

(CCPP) with a gas cycle 2100 including a gas turbine 2110, a generator 2120. Exhaust gas of the gas turbine is guided to the heat exchanger 2300. By the heat exchanger 2300 thermal energy is transferred to the steam cycle 2200. Thereby steam is produced for driving the steam turbine 2210 which is connected to the generator 2220 of the steam cycle 2200. Recovered water is pumped back to the heat exchanger by the pump 2230.

Figures 9 to 12 show different discharging systems which are derived from the conventional combined cycle power plant shown in figure 8. Example 1 :

The gas cycle 2100 is replaced by the high temperature ther- mal energy exchange system 1 (figure 9) . The heat exchanger 2300 is fed by the heat transfer fluid 131 of the outflow 133. Thereby a blower 2130 is used. The blower is located downstream of the heat exchange chamber 11 of the high temperature thermal energy exchange system 1. The blower 2130 has the additional function of the flow adjusting element 134 for guiding the heat transfer fluid through the heat exchange chamber interior 112 of the heat exchange chamber 11.

This example is an open loop. The heat transfer fluid (air) is released to the environment after the discharging is car^¬ ried out. This is denoted by the reference 2140 (like in fig^¬ ure 8 which refers to the conventional CCPP) .

Example 2 :

Here, an open loop is described, too. In contrast to example 1 the blower 2130 is located upstream of the heat exchange chamber 11 (figure 10) . Example 3:

In contrast to the open loop examples 1 and 2, the blower 2130 of this example with an open loop is located downstream to the heat exchanger 2300 (figure 11) .

Example 4 :

In contrast to the examples 1 to 3, this example refers to a closed loop solution. With the blower 2130 the heat transfer fluid 131 is guided back to the heat exchange chamber 11 af^¬ ter passing the heat exchanger 2300 (figure 12) .

Claims

Patent claims

1. Discharging system (1000) with a least one high tempera^¬ ture thermal energy exchange system (1), with

- at least one heat exchange chamber (11) with chamber bound^¬ aries (111) which surround at least one heat exchange chamber interior (112) of the heat exchange chamber (11), wherein

- the chamber boundaries ( 111 ) comprise at least one inlet opening (1111) for guiding in an inflow (132) of at least one heat transfer fluid (131) into the heat exchange chamber in^¬ terior (112) and at least one outlet opening (1112) for guiding an outflow (133) of the heat transfer fluid out of the heat exchange chamber interior (112);

- at least one heat storage material (121) is arranged in the heat exchange chamber interior (112) such that a heat ex^¬ change flow (13) of the heat transfer fluid (131) through the heat exchange chamber interior (112) causes a heat exchange between the heat storage material (121) and the heat transfer fluid ( 131 ) ; and

- the discharging system is equipped with at least one dis^¬ charging unit (400) for discharging the heat transfer fluid of the outflow (133) from heat for production of electricity.

2. Discharging system according to claim 1, wherein the dis- charging unit (400) comprises at least one heat exchanger

(2300) for discharging the heat transfer fluid of the outflow (133) .

3. Discharging system according to claim 1 or 2, wherein the discharging unit (400) comprises at least one steam power plant (2200) .

4. Discharging system according to one of the claims 1 to 3, wherein heat exchange channels (122) are embedded in the heat storage material (121) for guiding of the heat exchange flow (13) through the heat exchange chamber interior (112) .

5. Discharging system according to one of the claims 1 to 4, wherein the thermal energy exchange system (1) is equipped with at least one flow adjusting element (134) for adjusting the heat exchange flow (13) of the heat transfer fluid (131) through the heat exchange chamber interior (112), the inflow (132) of the heat transfer fluid (13) into the heat exchange chamber interior ( 112 ) and/or the outflow (133) of the heat transfer fluid out of the heat exchange chamber interior (112) .

6. Discharging system according to claim 5, wherein the flow adjusting element (134) comprises at least one active fluid motion device (1341) which is selected from the group consisting of blower and pump (1341) and/or the flow adjusting element (134) comprises at least one passive fluid control device (1342) which is selected from the group consisting of activatable bypass pipe, nozzle and valve.

7. Discharging system according to one of the claims 1 to 6, wherein the heat exchange chamber (11) is a vertical heat ex^¬ change chamber (113) and/or a horizontal heat exchange cham^¬ ber (114) .

8. Discharging system according to one of the claims 1 to 7, wherein the chamber boundary (111) with one of the openings

(1111, 1112) comprises a transition area (116) with a tapering profile (1161) such that an opening diameter (1113) of the opening (1111, 1112) adapts to a chamber diameter (117) of the heat exchange chamber (11) .

9. Discharging system according to one of the claims 1 to 8, wherein at least two inlet openings (1111) are arranged ver^¬ tically to each other and/or at least two outlet openings (1112) are arranged vertically to each other.

10. Discharging system according to one of the claims 1 to 9, wherein the heat storage material (21) comprises at least one chemically and/or physically stable material.

11. Discharging system according to one of the claims 1 to

10, wherein the heat storage material comprises sand and/or stones .

12. Discharging system according to one of the claims 1 to

11, wherein the heat transfer fluid (13) comprises a gas at ambient gas pressure. 13. Discharging system according to claim 12, wherein the gas at the ambient pressure is air.

14. Discharging system according to one of the claims 1 to

13. wherein a closed loop is implemented and wherein the in- flow comprises the outflow.

15. Method for discharging heat storage material of the dis^¬ charging system according to one of the claims 1 to 14 from thermal energy, wherein in an operating mode of the high thermal energy exchange system (1) a heat exchange flow (13) of heat transfer fluid (131) is guided through the heat ex^¬ change chamber interior (112), whereby a discharging of the heat storage material (121) is caused. 16. Method according to claim 14, wherein an operating temperature of the operating mode is selected from the range be^¬ tween 300 °C and 1000 °C, preferably selected from the range between 500 °C and 1000 °C, more preferably selected from the range between 600 °C and 1000 °C and 650 °C to 1000 °C and most preferably between 700 °C and 1000 °C.