US20150059342A1 - System for storing and outputting thermal energy and method for operating said system - Google Patents

System for storing and outputting thermal energy and method for operating said system Download PDF

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US20150059342A1
US20150059342A1 US14/394,141 US201314394141A US2015059342A1 US 20150059342 A1 US20150059342 A1 US 20150059342A1 US 201314394141 A US201314394141 A US 201314394141A US 2015059342 A1 US2015059342 A1 US 2015059342A1
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Prior art keywords
machine
fluid energy
thermal fluid
plant
accumulator
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Ursus Krüger
Daniel Reznik
Henrik Stiesdal
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Siemens AG
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Siemens AG
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SIEMENS WIND POWER A/S
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KRÜGER, Ursus, REZNIK, DANIEL
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/06—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein the engine being of extraction or non-condensing type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/053—Compression system with heat exchange between particular parts of the system between the storage receiver and another part of the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat

Definitions

  • the invention relates to a plant for storing thermal energy which has a circuit for a working gas.
  • the following units are interconnected in the specified sequence by means of a line for the working gas: a first thermal fluid energy machine, a heat accumulator, a second thermal fluid energy machine and a cold accumulator.
  • the first thermal fluid energy machine is operated as a working machine and the second thermal fluid energy machine is operated as a power machine, as seen in the flow direction of the working gas from the heat accumulator to the cold accumulator.
  • the invention relates to two methods for operating this plant.
  • passage through the circuit is in the direction of the heat accumulator to the cold accumulator, which corresponds to the sequence of the modular units specified above.
  • stored thermal energy from the plant can also be converted into mechanical energy, for example.
  • passage through the units is in the reverse sequence, in other words the flow direction of the working gas is reversed.
  • This working gas then passes first of all through the cold accumulator and then through the heat accumulator, wherein in this case the first thermal fluid energy machine is operated as a power machine and the second thermal fluid energy machine is operated as a working machine.
  • the terms power machine and working machine are used within the scope of this application so that a working machine absorbs mechanical work in order to fulfill its purpose.
  • a thermal fluid energy machine which is used as a working machine is therefore used as a compressor or fluid compression machine.
  • a power machine performs work, wherein a thermal fluid energy machine for performing the work converts the thermal energy which is made available in the working gas. In this case, the thermal fluid energy machine is therefore operated as a motor.
  • thermal fluid energy machine constitutes a generic term for machines which can extract thermal energy from a working fluid—a working gas within the context of this application—or can feed thermal energy to this. Both heat energy and cold energy are to be understood by thermal energy.
  • Thermal fluid energy machines can be designed as piston machines, for example.
  • Hydrodynamic thermal fluid energy machines, the impellers of which allow a continuous flow of the working gas, can preferably also be used.
  • Axially acting turbines or compressors are preferably used.
  • An object of the invention is to disclose a plant for storing thermal energy of the type specified in the introduction and methods for conversion of thermal energy (for example conversion of mechanical energy into thermal energy with subsequent storage or conversion of the stored thermal energy into mechanical energy) by means of which a utilization of the stored thermal energy which is as efficient as possible is enabled.
  • the cold accumulator being able to be connected into a circuit for a cooling medium, which differs from the aforesaid circuit, by the following units being interconnected in the specified sequence by means of a line for a cooling medium: the cold accumulator, a cooling unit and a cold consumer which is to be cooled.
  • the cooling medium is normally different from the working gas which accounts for the fact that the cooling circuit is different from the circuit.
  • the cooling circuit therefore uses the one passage system, whereas the charging circuit uses the other passage system.
  • the charging circuit can share the passage system in the cold accumulator—and possibly also other parts of the line associated with this—with a discharging circuit (more about this below). Whereas the charging circuit is responsible for storing the thermal energy, the thermal energy can be released again to the working gas via a discharging circuit.
  • the cooling unit is required in order to be able to set the necessary temperature level for the cold consumer which is to be cooled because the storage temperature of the cold accumulator is higher than the necessary temperature level.
  • precooling of the cooling medium can be carried out so that a smaller temperature difference has to be overcome in the cooling unit.
  • This also advantageously reduces the power demand for the cooling unit.
  • Process cold which accumulates anyway in the plant for storing thermal energy, can be utilized. This is admittedly no longer available during discharging for the purpose of releasing thermal energy, for which this does not have to be produced separately, however, for operation of the cold consumer which is to be cooled.
  • the overall energy balance of the plant for storing and releasing thermal energy and of the cold consumer is advantageously improved as a result.
  • the charging circuit (and discharging circuit) can be operated as an open or closed circuit (more about this below).
  • air forms the working gas which can be extracted from the atmosphere and then fed again to this.
  • a cooling unit any form of unit can be used.
  • the cold consumer is equipped according to a specific embodiment of the invention with a superconducting component.
  • a superconducting component nitrogen can be used here, especially when high-temperature superconductors, for example Bi2223 or YBCO, are being used. This has to be brought to a temperature level of approximately 50 to 60 K. A precooling via the cold accumulator to approximately 180 K simplifies the cooling process and reduces the power consumption on the cooling unit.
  • the electric machine is a generator which in particular can be installed in a wind power plant.
  • This application offers particular advantages since electric machines can be constructed with superconducting components (especially the winding of an electrically excited rotor in a synchronous generator) with a lower mass.
  • the mass of the generator constitutes the limiting factor in the design of wind power plants since the generators have to be installed at great height in the nacelle of the wind power plant.
  • the mass of the applied generators increases more quickly, however, than the output, wherein approximately a power of 1.6 lies within this ratio. Therefore, at present the economical limit for an increase of the generator output in wind power plants is approximately 6 MW.
  • the construction of wind power plants exposed to strong winds requires the installation of a larger generator capacity in the nacelle.
  • This can be achieved according to the invention by using generators with superconducting components.
  • the wind power plant is coupled to the plant according to the invention of storing and releasing thermal energy, then this has the advantage that the cold accumulator can be expediently used in order to minimize the losses which become necessary on account of the required cooling of the superconducting generator windings.
  • this plant for storing thermal energy can also be used in order to temporarily store, in a known manner per se, over-capacities in the electricity network and to convert them again into electric current, by releasing the thermal energy, in the event of consumption peaks in electric energy. It therefore involves the utilization of a synergy effect which altogether increases the efficiency during operation of the plant especially wind power plants.
  • the plant can also be operated for example with pump storage power plants or with conventional power plants, such gas-turbine power plants.
  • the electric machine is a motor which is mechanically coupled to the first thermal fluid energy machine.
  • This fluid energy machine has to be operated specifically during the charging process of the cold accumulator and of the heat accumulator (possibly also of an additional low-temperature heat accumulator) in order to bring the thermodynamic charging process into operation.
  • this motor is particularly advantageous to also construct this motor as an electric machine with a superconducting winding if the infrastructure for cooling this machine is available on account of using a superconducting generator, for example in the wind power plant. With this, a further efficiency increase for the plant is possible.
  • a further generator with superconducting components e.g. the winding
  • This is then coupled to the first fluid energy machine and used if in times of increased energy demand the heat accumulator and the cold accumulator are to be discharged.
  • the generator is connected to a third thermal fluid energy machine, wherein the third thermal fluid energy machine is connected in parallel with the first thermal fluid energy machine and a fourth thermal fluid energy machine is connected in parallel with the second thermal fluid energy machine in the charging and discharging circuit.
  • a valve mechanism is provided in each case between the first and the third thermal fluid energy machines and/or between the second and the fourth thermal fluid energy machines.
  • the one or the other fluid energy machine can now be advantageously selected in each case, depending on the flow direction of the working gas.
  • This has the advantage that the respective fluid energy machine being used can be optimized to the operating state which is to be selected. Since when using only two fluid energy machines both have to be used both as a working machine and as a power machine, depending on the flow direction, only one constructional compromise can be selected without the provision of additional fluid energy machines. Since, however, both in the thermal charging operation and in thermal discharging operation the aim is a highest possible level of efficiency, the parallel connection of fluid energy machines allows both the method for storing the thermal energy and the method for conversion of the thermal energy to be undertaken with optimum efficiency.
  • the working gas can be conducted in a closed circuit or an open circuit (this applies both to the charging circuit and to the discharging circuit, but not to the cooling circuit).
  • An open circuit always uses the ambient air as working gas. This is drawn from the environment and at the end of the process is also released into this again so that the environment closes the open circuit.
  • a closed circuit also allows the use of a working gas which is other than ambient air. This working gas is conducted in the closed circuit. Since an expansion into the environment with simultaneous adjustment of the ambient pressure and the ambient temperature does not apply, the working gas, in the case of a closed circuit, has to be conducted through a heat exchanger which allows a release or absorption of the heat of the working gas into or from the environment.
  • a low-temperature heat accumulator is additionally provided in the circuit upstream of the first fluid energy machine.
  • This heat accumulator is referred to as a low-temperature heat accumulator because the temperature level which is reached as a result of storing the heat principally lies below the temperature level of the heat accumulator.
  • Heat is defined in relation to the ambient temperature of the plant. Everything above ambient temperature is heat, whereas everything below the ambient temperature is cold. Therefore, it also becomes clear that the temperature level of the cold accumulator lies below the ambient temperature.
  • the use of the low-temperature heat accumulator has the following advantages. If the plant for storing thermal energy is used, then the low-temperature heat accumulator is passed through before passage through the first fluid energy machine which in this case works as a working machine (compressor). As a result of this, the working gas is already heated above ambient temperature. This has the advantage that the working machine has to absorb a lower level of power in order to achieve the required temperature of the working gas.
  • the heat accumulator is to be heated to above 500° C., which can advantageously also be carried out, subsequent to the preheating of the working gas, using technically available thermodynamic compressors which allow compression of the working gas to 15 bar. Therefore, recourse may advantageously be had to components for the modular units of the plant which are obtainable on the market without costly modifications.
  • the achieving of an object is additionally managed by means of the method referred to in the introduction for storing and releasing thermal energy by the cold accumulator being connected, when required, into a cooling circuit which differs from said circuit, wherein in the cooling circuit cooling medium flows through the following units in the specified sequence: the cold accumulator, a cooling unit and a cold consumer which is to be cooled.
  • the cooling circuit cooling medium flows through the following units in the specified sequence: the cold accumulator, a cooling unit and a cold consumer which is to be cooled.
  • thermosiphon for example, as the cooling unit.
  • the precooling via the cold accumulator reduces the energy expenditure in this case during operation of the cooling unit. This can also be of smaller dimensions. This make this solution particularly economical.
  • FIG. 1 shows an exemplary embodiment of the plant according to the invention as a schematic diagram
  • FIGS. 2 and 3 show exemplary embodiments of the method according to the invention (Brayton process) with reference to further schematic diagrams.
  • a plant for storing thermal energy according to FIG. 1 has a line 11 by means of which a plurality of units are interconnected in such a way that a working gas can flow through these.
  • the working gas flows through a low-temperature heat accumulator 12 and then through a first thermal fluid energy machine 13 which is designed as a hydrodynamic compressor.
  • the line then continues to a heat accumulator 14 .
  • This is connected to a second thermal fluid energy machine 15 which is designed as a hydrodynamic turbine. From the turbine, the line 11 leads to a cold accumulator 16 .
  • the cold accumulator 16 is connected to the low-temperature heat accumulator 12 by means of the line 11 , wherein in this line section provision is also made for a heat exchanger 17 via which the working gas can release heat to the environment or absorb heat from the environment (depending on the type of operation).
  • FIG. 1 a closed circuit for the working gas is provided in this respect.
  • the line section between the cold accumulator 16 and the low-temperature heat accumulator 12 together with the heat exchanger 17 are dispensed with, in a way not shown.
  • the circuit via the environment would be closed, wherein the working gas, which in this case comprises ambient air, would be drawn in at the low-temperature heat accumulator 12 and be blown out again into the environment downstream of the cold accumulator 16 .
  • FIG. 1 Also provided in FIG. 1 is a third thermal fluid energy machine 18 in the form of a hydrodynamic turbine and a fourth thermal fluid energy machine 19 in the form of a hydrodynamic compressor.
  • first hydrodynamic fluid energy machine 13 in the line 11 is connected in parallel with the third hydrodynamic machine 18 and the second fluid energy machine 15 in the line 11 is connected in parallel with the fourth fluid energy machine 19 .
  • Valve mechanisms 20 by opening and closing ensure that flow only passes through the first and second fluid energy machines or the third and fourth fluid energy machines in each case.
  • the first and second fluid energy machines 13 and 15 are mechanically intercoupled via a first shaft 21 and are driven by an electric motor M which is fed from a wind power plant 22 as long as there is no demand for the generated electric energy in the electricity network.
  • the heat accumulator 14 and the cold accumulator 16 are charged, as is explained in more detail later. If the demand for electric energy is greater in relation to the currently generated quantity of electric energy, then the electric current generated by the wind power plant 22 is fed directly into the network.
  • the plant additionally supports power generation in another operating state by the heat accumulator 14 and the cold accumulator 16 being discharged and a generator G1 being driven by the fluid energy machines 18 and 19 via a second shaft 23 .
  • the second shaft 23 is mechanically coupled to the third fluid energy machine 18 and to the fourth fluid energy machine 19 for this purpose.
  • the construction of the low-temperature heat accumulator 12 , of the heat accumulator 14 and of the cold accumulator 16 in the plant according to FIG. 1 is the same in each case and is explained in more detail by means of a detail enlargement based on the cold accumulator 16 .
  • a container the wall 24 of which is provided with an insulating material 25 which has large pores 26 .
  • the cold accumulator 16 also supplies a further line 31 with the stored cold.
  • a passage system (not shown in more detail—is provided in the cold accumulator 16 and is independent of another passage system (not shown either) which is connected to the line 11 .
  • the line 31 is part of a cooling circuit by means of which a cooling medium, such as nitrogen, can be precooled.
  • a cooling medium such as nitrogen
  • this cooling medium is circulated in the cooling circuit and also pumped through a cooling unit in the form of a thermosiphon, which is not shown in more detail.
  • bypass lines 35 which are connected to heat exchangers 36 in each case, can be connected into the cooling circuit.
  • These generators are provided with superconducting components, especially windings, comprising high-temperature superconductors.
  • the cooling medium is sufficient to hold these windings at a temperature level which the superconducting properties maintain.
  • FIG. 1 Shown in FIG. 1 is a variant of the cooling circuit in which the cooling unit is arranged outside of the wind power plant 22 .
  • the cooling unit In order to keep the paths of the line 31 to be insulated as short as possible, the cooling unit, however, is to be arranged in the direct proximity of the wind power plant 22 and of the motor M and also of the generator G1. Therefore, the cold accumulator 16 should also be arranged in the vicinity of the wind power plant 22 .
  • Such a cold accumulator 16 will advantageously be allocated in each case to only one wind power plant 22 , or to a few wind power plants 22 , of a wind park. On the other hand, the losses on account of transporting the cold in the line 31 or the cost of thermal insulation would be too high.
  • FIG. 2 Shown first of all in FIG. 2 is the charging process which functions according to the principle of a heat pump. Shown in FIGS. 2 and 3 , in contrast to FIG. 1 , is an open circuit which, however, as indicated by dash-dot lines, could be closed using the optionally provided heat exchanger 17 .
  • the states in the working gas which in the case of the exemplary embodiment of FIGS. 2 and 3 comprises air, are shown in each case in circles on the lines. At the top on the left, the pressure in bars is indicated. At the top on the right, the enthalpy in KJ/Kg is indicated. At the bottom on the left is the temperature in ° C., and at the bottom on the right the mass flow in Kg/s is indicated. The flow direction of the gas is indicated by arrows in the line 11 .
  • T 2 is the temperature at the compressor exit
  • T 1 is the temperature at the compressor inlet
  • ⁇ c is the isentropic efficiency of the compressor
  • ⁇ is the pressure ratio (in this case 15:1)
  • K is the compressibility, which in the case of air is 1.4.
  • the isentropic efficiency ⁇ c can be assumed to be 0.85 in the case of a compressor.
  • the heated working gas now passes through the heat accumulator 14 where the main part of the available thermal energy is stored. While being stored, the working gas is cooled to 20° C., whereas the pressure (apart from flow-inducted pressure losses) is maintained at 15 bar. The working gas is then expanded in two series-connected stages 15 a , 15 b of a second fluid energy machine so that it arrives at a pressure level of one bar. In the process, the working gas is cooled to 5° C. after the first stage and cooled to ⁇ 114° C. after the second stage. The basis for this calculation is also the formula specified above.
  • a water separator 29 In the part of the line 11 which connects the two stages 15 a , 15 b of the second fluid energy machine in the form of a high-pressure turbine and a low-pressure turbine, provision is additionally made for a water separator 29 . After a first expansion, this enables the air to be dried so that the air moisture which is contained in this in the second stage 15 b of the second fluid energy machine 15 does not lead to icing of the turbine blades (necessary only for the case of an open circuit).
  • the expanded and therefore cooled working gas extracts heat from the cold accumulator 16 and is heated to 0° C. as a result.
  • cold energy is stored in the cold accumulator 16 and can be utilized during a subsequent energy generation.
  • the working gas can be reheated to an ambient temperature of 20° C., as a result of which heat is extracted from the environment and made available to the process. Such a measure can naturally be dispensed with if the working gas is drawn directly from the environment since this already has ambient temperature.
  • FIG. 2 For the cooling, an embodiment which deviates from the variant in FIG. 1 is shown in FIG. 2 .
  • the motor M and the generator G1 do not have any superconducting components in this case.
  • Only the generator G2 in the wind power plant 22 which on account of its installed height in the nacelle of the wind power plant is to have a mass which is as low as possible, utilizes the advantages which are associated with superconducting windings and their smaller, necessary conductor cross sections.
  • the line 31 therefore leads without bypass lines directly to the wind power plant 22 .
  • the cooling unit 33 is also accommodated in the nacelle of the wind power plant 22 so that the paths of the cooling medium can be advantageously minimized, at least at low temperature level.
  • the discharging cycle of the heat accumulator 14 and of the cold accumulator 16 can be understood, wherein electric energy is generated at the generator G1.
  • the first fluid energy machine 13 and the second (two-stage) fluid energy machine 15 are used both in the charging cycle and in the discharging cycle. This does not impair the functioning principle of the plant but, however, is at the cost of lower efficiency. Therefore, the higher investment cost when additionally using a third and a fourth fluid energy machine is to be balanced against the gain in efficiency which is achieved when using four fluid energy machines by each being able to be optimized to the corresponding operating state.
  • dash-dot lines is the alternative of a closed circuit.
  • the water separator 29 is not shown in the representation according to FIG. 3 since this is not used.
  • the working gas is directed through the cold accumulator 16 . In the process, it is cooled from 20° C. to ⁇ 92° C. This measure serves for reducing the power consumption in order to operate the second fluid energy machine which works as a compressor.
  • the compressor compresses the working gas to 10 bar. During this, the temperature rises to 100° C. A compression of up to 15 bar would also be technically acceptable.
  • the compressed working gas passes through the heat accumulator 14 and is consequently heated to 500° C., wherein the pressure reduces slightly to 9.8 bar.
  • the working gas is then expanded by means of the first fluid energy machine which therefore works as a turbine in this operating state. An expansion to 1 bar is carried out, wherein at the outlet of the first fluid energy machine a temperature of 183° C. still prevails in the working gas.
  • the working gas is then directed through the low-temperature heat accumulator and additionally cooled to 130° C. as a result.
  • This heat has to be stored in order to serve for preheating of the working gas to 80° C. in a subsequent charging process of the heat accumulator 14 and of the cold accumulator 16 (as already described above).
  • the low-temperature heat accumulator therefore works as a temporary store and is always charged especially when the two other accumulators, i.e. the heat accumulator 14 and the cold accumulator 16 , are discharged, and vice versa.
  • the functioning principle of the plant and of the method is not limited, however, if the low-temperature heat accumulator is omitted.
US14/394,141 2012-04-17 2013-03-28 System for storing and outputting thermal energy and method for operating said system Abandoned US20150059342A1 (en)

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DE102012206296.3 2012-04-17
DE102012206296A DE102012206296A1 (de) 2012-04-17 2012-04-17 Anlage zur Speicherung und Abgabe thermischer Energie und Verfahren zu deren Betrieb
PCT/EP2013/056735 WO2013156292A1 (de) 2012-04-17 2013-03-28 Anlage zur speicherung und abgabe thermischer energie und verfahren zu deren betrieb

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CN113048010A (zh) * 2021-03-25 2021-06-29 南方电网电力科技股份有限公司 一种超导风机控制方法
CN113465226A (zh) * 2021-07-16 2021-10-01 中国科学院上海应用物理研究所 热泵式储能供电方法及装置
WO2023041132A1 (en) * 2021-09-20 2023-03-23 Stiesdal Storage A/S A method of operating a thermal energy storage system with environmental air exchange
US11637480B2 (en) 2017-11-23 2023-04-25 Siemens Energy Global GmbH & Co. KG Power plant having a cooling system, method for operating such a power plant, method for modifying a power plant

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