EP2653670A1 - Anlage zur Speicherung und Abgabe von thermischer Energie mit einem Wärmespeicher und einem Kältespeicher und Verfahren zu deren Betrieb - Google Patents

Anlage zur Speicherung und Abgabe von thermischer Energie mit einem Wärmespeicher und einem Kältespeicher und Verfahren zu deren Betrieb Download PDF

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Publication number
EP2653670A1
EP2653670A1 EP12164473.6A EP12164473A EP2653670A1 EP 2653670 A1 EP2653670 A1 EP 2653670A1 EP 12164473 A EP12164473 A EP 12164473A EP 2653670 A1 EP2653670 A1 EP 2653670A1
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EP
European Patent Office
Prior art keywords
heat
line
fluid energy
cold
storage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12164473.6A
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German (de)
English (en)
French (fr)
Inventor
Daniel Reznik
Henrik Stiesdal
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Siemens AG
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP12164473.6A priority Critical patent/EP2653670A1/de
Priority to PCT/EP2013/056549 priority patent/WO2013156284A1/de
Priority to CN201380025836.0A priority patent/CN104302876A/zh
Priority to US14/394,094 priority patent/US20150136351A1/en
Priority to EP13713841.8A priority patent/EP2825737A1/de
Publication of EP2653670A1 publication Critical patent/EP2653670A1/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled

Definitions

  • the invention relates to a system for storage and release of thermal energy with a heat storage and a cold storage, wherein the heat storage can deliver the stored energy to a first line in a Endladeniklauf for a working medium at a suitable delivery point.
  • the following units are interconnected in the order indicated by this first line: a first thermal fluid energy machine (in particular a pump) connected as a working machine, a discharge point (for example a heat exchanger) for heat from the heat accumulator and a second one connected as an engine thermal fluid energy machine (for example, a steam turbine).
  • the described arrangement of the units in the discharge circuit makes it possible that the stored energy in the heat storage is delivered to the working medium and the engine connected as a second thermal fluid energy machine is used for example for driving an electric generator.
  • a charging circuit is required, which can be realized either by the first line or by another line.
  • the invention also relates to a process which is carried out with the plant described.
  • thermal fluid energy machine used as a work machine is thus operated as a compressor or as a compressor.
  • an engine performs work, wherein a thermal fluid energy machine for performing the work available in the working gas thermal Energy converts.
  • the thermal fluid energy machine is thus operated as a motor.
  • thermal fluid energy machine forms a generic term for machines that can extract a thermal energy from a working fluid, in the context of this application, a working gas such as air or water vapor, or thermal energy.
  • thermal energy is meant both thermal energy and cold energy.
  • Thermal fluid energy machines (also abbreviated to fluid energy machines in the following) can be embodied as piston machines, for example.
  • hydrodynamic thermal fluid energy machines can be used, the wheels allow a continuous flow of the working gas.
  • axially acting turbines or compressors are used.
  • the object of the invention is to provide a system for storage and release of thermal energy of the type specified (for example, conversion of mechanical energy into thermal energy with subsequent storage or conversion of the stored thermal energy into mechanical energy) and a method for their operation, with a relatively high efficiency at the same time reasonable cost of the units used is possible.
  • the cold storage can deliver the stored cold to a second line at a suitable delivery point, the second line forms a closed circuit.
  • the following units in the order specified by the second line are connected to each other: behind the said delivery point for the stored cold storage in the cold storage (ie the point at which the cold storage can deliver the stored cold to the second line) is as Work machine switched third thermal fluid energy machine (for example, a pump) provided, then a heat source is provided and then a switched as an engine thermal fluid energy machine (for example, a steam turbine) is provided.
  • Suitable heat source media are those which have a higher temperature level compared to the temperature level of the cold storage.
  • the cold storage in the charged state has a temperature level that is below the ambient conditions, as a heat source, the environment of the system can be used (for example, river water).
  • the waste heat or residual heat of another process is used, wherein the temperature level of this process is above the ambient temperature.
  • This process may be, for example, a gas turbine cycle. If the gas for this supplied in liquid form and must first be evaporated, this process can be used, for example, to charge the cold storage.
  • Other configurations are explained in more detail below. Among these is in particular the thermal energy storage to call, as this has already been explained.
  • a working medium is provided in the first line and in the second line, which undergoes a thermodynamic process for energy storage or energy recovery in the circuit.
  • This may be present in gaseous or liquid form.
  • the fluid energy machines must each be optimized for the medium. Will this be in liquid form encouraged, the choice of a pump is particularly advantageous.
  • hydrodynamic fluid energy machines (turbo-compressors) are preferably used.
  • the basic idea of the invention is that the available in the system heat storage and the available cold storage can be used independently in two Endladenik151. This makes it particularly possible to use the waste heat of operated with the heat storage Endladenikonnees operated in the cold storage Endladeniklauf. As a result, the yield of energy stored in the heat storage and in the cold storage energy is advantageously increased, whereby the overall efficiency of the system can be increased.
  • the heat source consists of a first heat exchanger, which can withdraw heat from the first line and is arranged between the third fluid energy machine and the fourth fluid energy machine.
  • This arrangement and mode of operation of the first heat exchanger makes it possible, as already indicated, that the waste heat of the discharge circuit formed in the first line can be utilized in the discharge circuit formed by the second line.
  • This temperature level is higher than that of the environment, whereby advantageously the yield of the discharge or discharge of the cold accumulator can be increased.
  • the discharge point for the heat storage is formed by a fifth heat exchanger, which can supply heat to the first line and which is connected in a circuit formed by a fourth line.
  • the following units are connected to each other in this circuit: the fifth heat exchanger, a tenth thermal fluid energy machine connected as a working machine and the heat accumulator.
  • This provides a configuration in which the heat storage is not directly integrated into the Endladeniklauf the first line, but is connected to this via a heat exchanger (fifth heat exchanger).
  • This heat exchanger is connected by the fourth line in a circuit with the heat storage 14.
  • the fluid energy machine circulates the working medium in the fourth line, so that the energy stored in the heat accumulator 14 can be supplied to the heat exchanger.
  • the fifth heat exchanger is particularly advantageously designed as a waste heat steam generator.
  • Such heat exchangers are often referred to as waste heat boiler or as HRSG (Heat Recovery Steam Generator).
  • the waste heat steam generator is advantageously operated with water, so that commercially available steam turbines for generating mechanical energy can be used in the cycle formed by the first line.
  • the heat accumulator 14 can be operated via the fourth line, for example, with air as the working medium. This has the advantage that even larger heat storage can be produced inexpensively, as any leaks in the circuit pose no threat to the environment.
  • the waste heat steam generator (ie the fifth heat exchanger) and the second thermal fluid energy machine also have a plurality of pressure stages. These pressure levels are formed by the fact that both in the heat exchanger and in the fluid energy machine corresponding pressure levels are available, which are each connected to each other with lines. As a result, the yield and thus the efficiency of the discharge process can be advantageously further increased.
  • the discharge point for the stored in the cold storage cold consists of a third heat exchanger, which can deliver heat to the second line and in through a third line formed cooling circuit is integrated.
  • the following units are connected to one another in this cooling circuit: the third heat exchanger, a fifth thermal fluid energy machine connected as a working machine, and the cold storage.
  • the fluid energy machine circulates the working medium in the third line.
  • the stored in the cold storage cold energy is discharged through the third heat exchanger to the second line, where work can be done on the fourth fluid energy machine.
  • This separation of the circuits via the second and the third line has the advantage that the cycle formed via the second line can be kept as small as possible.
  • ammonia can be used as a working medium and operated under the associated high technical safety requirements.
  • air can be used as the working medium. This is particularly advantageous if the cold storage has a large volume due to the capacity requirements.
  • Yet another embodiment of the invention provides that in the second line between the third thermal fluid energy machine and the first heat exchanger, a fourth heat exchanger is provided, which allows a heat input from the environment of the system in the second line. It must be taken into account here that the cold storage has a temperature level which is below the atmospheric ambient conditions. Therefore, heat can be supplied to the working medium in a first step from the environment before the heat is used in a second step, which is provided in the heat storage or in the residual heat of the Endladeniklaufes the heat storage. The ambient heat is thus the process additionally available, whereby the efficiency of the system can be improved.
  • the object stated at the outset is also achieved by a method for storing and emitting thermal energy achieved by a heat storage and a cold storage, in which emits the stored energy to a first line in a Endladeniklauf for a working medium during the Endladezyklusses.
  • the following units are arranged in the order indicated via a first line and are flowed through in this order by the working fluid: a working machine connected as a first thermal fluid energy machine (in particular a pump), a heat transfer point from the heat accumulator and a as an engine connected second thermal fluid energy machine (in particular a steam turbine).
  • the cold storage gives the stored refrigeration to a second line
  • the second line forms a closed circuit in which the following units are traversed in the order indicated on the second line: behind said discharge point for the Refrigeration stored in the cold accumulator is a third thermal fluid energy machine (in particular a pump) connected as a working machine, a heat source and a fourth thermal fluid energy machine connected as an engine, in particular a steam turbine.
  • FIG. 1 First, a two-stage charging process is shown, which works on the principle of a heat pump. Shown is an open charging circuit, however, as indicated by dash-dotted lines, could be closed using an optional heat exchanger 17b.
  • the conditions in the working gas, which in the embodiment FIG. 1 consists of air, are each shown on the lines 30, 31 in circles. At the top left is the pressure in bar. Top right, the enthalpy is given in KJ / Kg. Bottom left is the temperature in ° C and bottom right is the mass flow in kg / s. The flow direction of the gas is indicated by arrows in the relevant line (these arrows and circles are also used in the other figures).
  • the isentropic efficiency ⁇ c can be assumed to be a compressor with 0.85.
  • the heated working gas now passes through the heat storage 14, where the majority of the available thermal energy is stored.
  • the working gas cools to 20 ° C, while the pressure is maintained at 15 bar.
  • the working gas is expanded in two series-connected stages 35a, 35b of a seventh fluid energy machine 35, so that it arrives at a pressure level of 1 bar.
  • the working gas cools to 5 ° C after the first stage and to -100 ° C after the second stage.
  • the basis for this calculation is also the formula given above.
  • a water separator 29 is additionally provided in the part of the third line 31, which connects the two stages of the seventh fluid energy machine 35a, 35b in the form of a high-pressure turbine and a low-pressure turbine. This allows after a first relaxation, a drying of the air, so that the humidity contained in this second stage 35b of the seventh fluid energy machine 35 does not lead to icing of the turbine blades.
  • the relaxed and therefore cooled working gas withdraws heat from the cold storage 16 and is thereby heated to 0 ° C.
  • cold energy is stored in the cold storage 16, which can be used in a subsequent energy production.
  • the heat exchanger 17b must be provided.
  • the working gas can be reheated to an ambient temperature of 20 ° C, whereby the environment heat is removed, which is provided to the process.
  • such a measure can be omitted if the working gas is sucked directly from the environment, since this already has ambient temperature.
  • the additional heat storage 12 when passing through the charging circuit of the third line 31, a preheating can be done by the additional heat storage 12, an additional circuit is realized by an additional line 30, with which the additional heat storage 12 can be charged.
  • the additional heat accumulator 12 must therefore be able to be connected both to the charging circuit of the third line 31 and to the additional circuit of the additional line 30.
  • a connection to the third line 31 takes place through the valves A, while a connection to the additional line 30 is ensured by opening the valves B.
  • the air When passing through the additional line 30, the air is first passed through an eighth fluid energy machine 36, which operates as a compressor. The compressed air is passed through the additional heat storage 12, wherein the flow direction according to the indicated arrows runs exactly opposite to the charging circuit formed by the third line 31.
  • the air After the air was brought from ambient pressure (1 bar) and ambient temperature (20 ° C) through the compressor to 4 bar and a temperature of 188 ° C, the air is cooled by the additional heat storage 12 back to 20 ° C. Subsequently, the air is decompressed in two stages through the stages 37a, 37b of a ninth fluid energy machine 37, which operates as a turbine. Again, in the two stages 37 a, 37 b connecting additional line 30, a water separator 29 is provided, which works the same as that in the third line 31 located. After releasing the air via the ninth fluid energy machine 37, this has a temperature of -56 ° C at ambient pressure (1 bar).
  • a heat exchanger 17c must be provided so that the air from -56 ° C can be warmed up by heat absorption from the environment to 20 ° C.
  • the circuits of the third line 31 and the additional line 30 are set independently. Therefore, the sixth and seventh fluid energy machines are mechanically coupled via the shaft 21 to a motor M1 and the eighth and ninth fluid energy machines via the other shaft 21 to a motor M2. With overcapacities of the wind turbine 22, the electrical energy can first drive the motor M2 to charge the additional heat storage 12. Subsequently, by operation of the motor M1 and simultaneous discharge of the additional heat accumulator 12, the heat accumulator 14 and the cold accumulator 16 can be charged. Subsequently, by the operation of the motor M2 and the additional heat storage 12 can be recharged. When all accumulators are fully charged, an effective discharge cycle can be initiated to generate electrical energy (cf. FIG. 2 ). Should the excess capacity of the wind power plant 22 end, however, without the additional heat storage 12 could be charged, the energy provided in this can also be replaced by another heat source 41, or it is only the heat storage 14 is used (see. FIG. 2 ).
  • the system is now operated with a discharge circuit, which is realized by a first line 40.
  • the line 40 is a closed circuit.
  • Water is through the additional heat storage 12, the heat storage 14 and optionally by a further heat source 41, z. B. district heating, via a heat exchanger 42 and overheated and passes through the line 40 (valves C and D are closed) to a third thermal fluid energy machine 43.
  • This is constructed in two stages, consisting of a high-pressure turbine 43a and a low-pressure turbine 43b, to be run one after the other.
  • the high-pressure turbine is supplied with steam of a pressure p h .
  • the low-pressure turbine 43b satisfies steam at a lower pressure of p 1 .
  • the third fluid energy machine 43 drives a generator G via a further shaft 21. This generates power if necessary, while the thermal storage 12, 14, 16 are discharged (Rankine cycle).
  • the refrigeration energy stored in the cold storage 16 is provided to the cycle formed by the first conduit 40 not directly but via a first heat exchanger 51.
  • the first heat exchanger 51 is part of a circuit formed by a second conduit 52. This circuit itself serves to generate energy, which can be obtained via a fourth fluid energy machine 53 in the circuit of the second line 52.
  • the fourth fluid energy machine 53 is connected to a generator G via a shaft 54.
  • the fourth fluid energy machine 53 drives a fifth fluid energy machine 55, which is used as a compressor (more on this in the following).
  • the refrigeration energy from the cold storage 16 is therefore used primarily for energy production in the cycle formed by the second conduit 52 (for example, by a Rankine cycle with ammonia).
  • the cycle formed by the first line 40 benefits only indirectly from this cooling energy.
  • the cycle formed by the second conduit 52 benefits from the heat energy which is introduced into the process via the first heat exchanger. This explains the improvement in the overall efficiency of the system.
  • the cooling energy can be supplied from the cold storage 16 via a circuit formed by a third line 56 again indirectly via a third heat exchanger 57 of the second line 52.
  • the third heat exchanger 57 in provided the second line.
  • a third fluid energy machine in the form of a pump 58 then follows in the second conduit as seen in the direction of flow.
  • ambient heat can for example be fed from a flow via a fourth heat exchanger 59 into the working fluid of the second conduit 52 before it passes through the first heat exchanger 51.
  • the cooling energy is supplied from the cold storage 16 via the third line to the third heat exchanger 57.
  • the fifth fluid energy machine is provided, which causes a circulation of the working fluid in the third conduit.
  • the drive takes place directly via the shaft 54 through the fourth fluid energy machine 53.
  • this circuit formed by the third line 56 could also be omitted and, instead of the third heat exchanger 57, the cold storage 16 be provided directly in the second line 52. This is indicated by dash-dotted lines.
  • the second line 52 would be connected directly to a channel system in the cold storage 16, which causes an increase in surface area in the cold storage 16 (more on this in the following).
  • valve D By operating the valves C and D, the efficiency of the system can be improved in certain operating conditions.
  • the valve D is located in a first bypass line 46, with the opening of the valve D, the high pressure turbine 43 a can be bypassed. This operating state makes sense if the temperature in the heat accumulator 14 is no longer sufficient to overheat the steam under high pressure conditions. The latter may be due to a partial discharge or not yet complete charging of the heat accumulator 14.
  • the heat accumulator 14 is completely emptied while the additional heat accumulator 12 has already been charged.
  • This condition can arise, for example, when additional energy through the wind power plant 22 has only recently Time was made available, but now an excess demand for electrical energy to be covered.
  • the valve C of a second bypass line 47 can be switched.
  • the heat accumulator 14 is bypassed by the bypass line 47, so that the additional heat accumulator 12 can be emptied via the low-pressure turbine 43 b. Therefore, thermal energy is already available in the system, which can be converted by the generator G into electrical energy with satisfactory efficiency.
  • the cold storage 16 is not yet charged, as this is charged together with the heat storage 14.
  • a capacitor 45 is thus switched via the valve F.
  • FIG. 3 is another embodiment of the system in its overall view shown as a block diagram. Unlike in the FIGS. 1 and 2 Here, a uniform representation has been selected. The circuits formed by the second line 52 and the third line 56 are substantially analogous to FIG. 2 executed.
  • FIG. 3 a simpler system for charging the cold accumulator 16 and the heat accumulator 14 as in FIG. 1 shown.
  • the heat accumulator 14 is charged by an open circuit, which is realized by the line 60.
  • a compressor 61 ambient air is supplied via a line 60, passes through a heat exchanger 32, where the air is heated to 480 ° C and releases this heat during the passage of the heat accumulator 14 to this.
  • the heat exchanger 32 is also passed through a conduit 63 which forms the circuit with which the cold storage 16 is cooled.
  • the working fluid in the conduit 63 After the working fluid in the conduit 63 has passed through the cold storage tank 16, it is compressed by a compressor 64 from ambient conditions to 25 bar and heated to 514 ° C, passes through the heat exchanger 32 and is then expanded via a turbine 65 back to 1.1 bar , The temperature drops -121 ° C. Subsequently, the working medium in the cold storage 16 again absorbs heat and thereby cools it.
  • the compressor 64 and the turbine 65 are seated on a shaft 66 and may additionally be driven by a motor M connected to this shaft 66.
  • the heat accumulator 14 is not integrated directly into the cycle formed by the first conduit 40. Rather, another circuit is formed by a fourth conduit 67, in which the following units are passed through at a constant pressure of about 1 bar.
  • the heated to 476 ° C working fluid for example, air
  • the heat exchanger 68 releases the heat to the first line 40 and cools to 91 ° C (more on this in the following).
  • the fourth line 67 passes through the first heat exchanger 51, so that the residual heat, which was not discharged via the fifth heat exchanger 68 to the first line, can be delivered to the second line 52.
  • the working medium can be further cooled in the course of a condenser 69, wherein the capacitor 69 is also a heat exchanger, which is provided in the first conduit 40 (for more on this later).
  • the capacitor 69 is also a heat exchanger, which is provided in the first conduit 40 (for more on this later).
  • the working fluid then returns to the heat storage 14, where this is heated again.
  • the fourth conduit 67 may also be formed as an open circuit in which the dash-dotted part of the line between the capacitor 69 and the tenth fluid energy machine 70 is omitted.
  • the first line 40 forms a circuit with which current can be obtained via a shaft 71 at a generator G.
  • a circuit is operated with water, wherein the fifth heat exchanger 68 is operated as a multi-stage waste heat steam generator with a high pressure stage 68a and a low pressure stage 68b (Rankine cycle).
  • the water is fed to ambient temperature by a feed pump 44a with 5.5 bar initially in the low pressure stage 68b of the fifth heat exchanger 68.
  • One part leaves this low pressure stage 68b at 4.1 bar and 145 ° C to be fed to the low pressure stage 43b of the second thermal fluid energy machine (as steam).
  • Another part is fed by a second feed pump 44b in the liquid state, the high-pressure stage 68a of the fifth heat exchanger 68 and leaves it as steam at 80 bar and 459 ° C to the high-pressure stage 43a of the second thermal fluid energy machine 43 to be supplied.
  • Both the fourth and second thermal fluid energy machines drive a shaft 71, which is connected to a generator G. After relaxation of the vapor to 0.03 bar at 24 ° C this is fed back via the capacitor 69 of the feed pump 44a.
  • the structure of the heat accumulator 14 and the cold accumulator 16 and the additional heat storage in the system in the figures is the same and is by an enlarged detail on the basis of the cold storage 16 in FIG. 1 shown in more detail.
  • a container whose wall 24 is provided with an insulating material 25 having large pores 26.
  • Inside the container concrete 27 is provided, which acts as a heat storage or cold storage.
  • pipes 28 are laid parallel running through which the working gas flows and thereby emits heat or absorbs heat (depending on the mode and storage).
  • FIGS. 1 to 3 can also be combined with each other, so that this results in further embodiments.

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EP12164473.6A 2012-04-17 2012-04-17 Anlage zur Speicherung und Abgabe von thermischer Energie mit einem Wärmespeicher und einem Kältespeicher und Verfahren zu deren Betrieb Withdrawn EP2653670A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP12164473.6A EP2653670A1 (de) 2012-04-17 2012-04-17 Anlage zur Speicherung und Abgabe von thermischer Energie mit einem Wärmespeicher und einem Kältespeicher und Verfahren zu deren Betrieb
PCT/EP2013/056549 WO2013156284A1 (de) 2012-04-17 2013-03-27 Anlage zur speicherung und abgabe von thermischer energie mit einem wärmespeicher und einem kältespeicher und verfahren zu deren betrieb
CN201380025836.0A CN104302876A (zh) 2012-04-17 2013-03-27 具有蓄热器和蓄冷器的热能存储及释放设备及其运行方法
US14/394,094 US20150136351A1 (en) 2012-04-17 2013-03-27 System for storing and outputting thermal energy having a heat accumulator and a cold accumulator and metho for the operation thereof
EP13713841.8A EP2825737A1 (de) 2012-04-17 2013-03-27 Anlage zur speicherung und abgabe von thermischer energie mit einem wärmespeicher und einem kältespeicher und verfahren zu deren betrieb

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12164473.6A EP2653670A1 (de) 2012-04-17 2012-04-17 Anlage zur Speicherung und Abgabe von thermischer Energie mit einem Wärmespeicher und einem Kältespeicher und Verfahren zu deren Betrieb

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EP2653670A1 true EP2653670A1 (de) 2013-10-23

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EP12164473.6A Withdrawn EP2653670A1 (de) 2012-04-17 2012-04-17 Anlage zur Speicherung und Abgabe von thermischer Energie mit einem Wärmespeicher und einem Kältespeicher und Verfahren zu deren Betrieb
EP13713841.8A Withdrawn EP2825737A1 (de) 2012-04-17 2013-03-27 Anlage zur speicherung und abgabe von thermischer energie mit einem wärmespeicher und einem kältespeicher und verfahren zu deren betrieb

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EP13713841.8A Withdrawn EP2825737A1 (de) 2012-04-17 2013-03-27 Anlage zur speicherung und abgabe von thermischer energie mit einem wärmespeicher und einem kältespeicher und verfahren zu deren betrieb

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EP (2) EP2653670A1 (zh)
CN (1) CN104302876A (zh)
WO (1) WO2013156284A1 (zh)

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GB2535181A (en) * 2015-02-11 2016-08-17 Futurebay Ltd Apparatus and method for energy storage
WO2016150459A1 (en) * 2015-03-20 2016-09-29 Siemens Aktiengesellschaft Excess air valves for pressure control

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JP6708505B2 (ja) * 2016-07-14 2020-06-10 株式会社日立プラントメカニクス 高圧水素の膨張タービン式充填システム
GB2552963A (en) * 2016-08-15 2018-02-21 Futurebay Ltd Thermodynamic cycle apparatus and method
SI3379040T1 (sl) * 2017-03-20 2021-07-30 Lumenion Gmbh Elektrarna za proizvodnjo električne energije in postopek za upravljanje elektrarne
CN114592937B (zh) * 2022-04-11 2023-08-29 中国科学院工程热物理研究所 一种压缩空气和热泵储电耦合的储电系统及方法

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