EP2825737A1 - Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation - Google Patents

Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation

Info

Publication number
EP2825737A1
EP2825737A1 EP13713841.8A EP13713841A EP2825737A1 EP 2825737 A1 EP2825737 A1 EP 2825737A1 EP 13713841 A EP13713841 A EP 13713841A EP 2825737 A1 EP2825737 A1 EP 2825737A1
Authority
EP
European Patent Office
Prior art keywords
heat
line
machine
fluid energy
heat exchanger
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Withdrawn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
EP13713841.8A
Other languages
German (de)
English (en)
Inventor
Daniel Reznik
Henrik Stiesdal
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens Gamesa Renewable Energy AS
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP13713841.8A priority Critical patent/EP2825737A1/fr
Publication of EP2825737A1 publication Critical patent/EP2825737A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • 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 given by this first line: a first thermal fluid-power machine (in particular a pump) connected as a working machine
  • Delivery point for example, a heat exchanger
  • an engine second 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 the available in the working gas thermal see converted energy.
  • the thermal fluid energy machine is thus operated as a motor.
  • thermal fluid energy machine forms a generic term for machines that can extract thermal energy from or impart thermal energy to a working fluid, in the context of this application, a working gas such as air or water vapor.
  • Thermal energy includes both thermal energy and cold energy understand thermal fluid energy machines (also shorter than
  • Fluid power machines referred to can be designed for example as piston engines. It is also possible to use hydrodynamic thermal fluid energy machines whose impellers permit a continuous flow of the working gas. Preferably, 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.
  • this object is achieved with the system specified at the outset in that the cold accumulator can deliver the stored refrigeration to a second line at a suitable delivery point, wherein 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 connected third thermal Fluidenergy- machine provided (for example, a pump), 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 sources are media which have a higher temperature level compared to the temperature level of the cold storage. If 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 can 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.
  • Delivery point for the heat accumulator 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 rather, is not directly integrated into the discharge circuit of the first line, but is connected to it 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).
  • HRSG Heat Recovery Steam Generator
  • the heat recovery 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 can 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 on 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 stated sequence via a first line and are flowed through in this order by the working medium: a first thermal fluid energy machine (in particular a pump) connected as a working machine, a heat transfer point from the heat store and a second thermal fluid energy machine connected as an engine (in particular, a steam turbine).
  • the cold storage stores the stored refrigeration to a second line
  • the second line forms a closed circuit in which the following units are passed through in the specified order on the second line: behind said discharge point for the cold stored in the cold accumulator, a working machine connected as a third thermal fluid energy machine (in particular a pump), a heat source and a fourth engine connected as an engine thermal fluid energy machine, in particular a steam turbine.
  • Figure 3 shows another embodiment of the system according to the invention in the operating states of a charging and discharging as a block diagram.
  • FIG. 1 a two-stage charging process is first shown, which operates 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 states in the working gas, which in the embodiment of Figure 1 consists of air, are each shown on the lines 30, 31 in circles. At the top left is the pressure in bar.
  • r is the isentropic efficiency of the compressor
  • K is the compressibility, which is 1.4 in air.
  • the isentropic efficiency r ⁇ c can be assumed to be 0.85 for a compressor.
  • 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.
  • Line 31 a preheating can be done by the addition of heat accumulator 12, an additional circuit is realized by an additional line 30, with the addition of heat accumulator 12 can be charged.
  • the addition 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 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 works 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.
  • the electrical energy may first drive the motor M2 to charge the additional heat storage 12. Subsequently, the heat accumulator 14 and the cold accumulator 16 can be charged by operation of the motor Ml and simultaneous discharge of the additional heat storage 12. Subsequently, by the operation of the motor M2 and the additional heat storage 12 can be recharged. When all the reservoirs are fully charged, an effective discharge cycle can be initiated to generate electrical energy (see Figure 2). However, should the excess capacity of the wind power plant 22 end without the additional heat storage 12 being able to be charged, then the energy provided in it can also be replaced by another heat source 41, or only the heat storage 14 is used (cf. Figure 2).
  • the system is now operated with a discharge circuit, which is realized by a first line 40.
  • the line 40 represents 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.
  • a heat exchanger 42 vaporizes and overheats and passes through the line 40 (valves C and D are closed) to a third thermal Fluidenergy- machine 43.
  • This is constructed in two stages, consisting of a high-pressure turbine 43a and a low-pressure turbine 43b successively to go through.
  • 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 i.
  • This pressure exists in the connecting line 40 between the high-pressure turbine 43a and the low-pressure turbine 43b or in certain operating conditions after opening the valve D also in the bypass line 46.
  • 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 which is formed by a second line 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 circuit formed by the second line 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 circuit formed by the second line 52 profits 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 cold energy from the cold storage 16 can be fed back indirectly via a third heat exchanger 57 of the second line 52 via a circuit formed by a third line 56.
  • 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 in the direction of flow.
  • ambient heat can be fed, for example, from a flow via a fourth heat exchanger 59 into the working fluid of the second conduit 52, before the first heat exchanger 51 goes through.
  • 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).
  • 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. In the extreme case, 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. In this case, in addition to the valve D, 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. In this case, the cold storage 16 is not yet charged, as this is charged together with the heat storage 14. For this operating condition, a capacitor 45 is thus switched via the valve F.
  • FIG. 3 another embodiment of the system is shown in its overall view as a block diagram. Unlike in FIGS. 1 and 2, a uniform representation has been selected.
  • the circuits formed by the second line 52 and by the third line 56 are designed essentially analogously to FIG.
  • FIG. 3 a simpler system for charging the cold accumulator 16 and the heat accumulator 14 is shown in FIG. 3 than in FIG.
  • 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. After the working medium in the conduit 63 has passed through the cold storage 16, this is via a compressor 64 from ambient conditions
  • the heat accumulator 14 is not integrated directly into the circuit 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, to the second line 52 can be discharged.
  • 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 line 67 can also be designed as an open circuit, in which the part of the line divided by the dot-dash line between the condenser 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, the heat accumulator 14 and the cold accumulator 16 and the additional heat accumulator in the system in the figures are the same in each case and is illustrated in more detail by a detail enlargement with reference to the cold accumulator 16 in FIG.
  • 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).

Abstract

L'invention concerne une installation d'accumulation et de distribution d'énergie thermique et son procédé de fonctionnement. Ladite installation comporte un accumulateur de chaleur (14) et un accumulateur de froid (16). Selon l'invention, l'accumulateur de chaleur (14) et l'accumulateur de froid (16) se déchargent dans deux circuits de décharge (40, 52) séparés, l'énergie thermique pouvant être convertie en énergie électrique par exemple par l'intermédiaire d'un générateur (G). La chaleur résiduelle produite par le processus dans le circuit (40) peut être amenée de manière avantageuse par un premier échangeur de chaleur (51) au processus dans le circuit (52), ce qui permet d'améliorer de manière avantageuse le rendement total. De manière avantageuse, la chaleur émanant de l'accumulateur de chaleur (14) peut être transmise par un générateur de vapeur à récupération de chaleur (68) au premier circuit (40). L'accumulateur de chaleur (14) et l'accumulateur de froid (16) peuvent être chargés par exemple en énergie excédentaire provenant du réseau électrique par un moteur (M). Ainsi, il est possible d'accumuler par exemple des réserves d'énergie excédentaires de sources d'énergie alternatives.
EP13713841.8A 2012-04-17 2013-03-27 Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation Withdrawn EP2825737A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13713841.8A EP2825737A1 (fr) 2012-04-17 2013-03-27 Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP12164473.6A EP2653670A1 (fr) 2012-04-17 2012-04-17 Installation de stockage et de répartition d'énergie thermique avec un accumulateur thermique et un accumulateur de froid et leur procédé de fonctionnement
PCT/EP2013/056549 WO2013156284A1 (fr) 2012-04-17 2013-03-27 Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation
EP13713841.8A EP2825737A1 (fr) 2012-04-17 2013-03-27 Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation

Publications (1)

Publication Number Publication Date
EP2825737A1 true EP2825737A1 (fr) 2015-01-21

Family

ID=48045492

Family Applications (2)

Application Number Title Priority Date Filing Date
EP12164473.6A Withdrawn EP2653670A1 (fr) 2012-04-17 2012-04-17 Installation de stockage et de répartition d'énergie thermique avec un accumulateur thermique et un accumulateur de froid et leur procédé de fonctionnement
EP13713841.8A Withdrawn EP2825737A1 (fr) 2012-04-17 2013-03-27 Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP12164473.6A Withdrawn EP2653670A1 (fr) 2012-04-17 2012-04-17 Installation de stockage et de répartition d'énergie thermique avec un accumulateur thermique et un accumulateur de froid et leur procédé de fonctionnement

Country Status (4)

Country Link
US (1) US20150136351A1 (fr)
EP (2) EP2653670A1 (fr)
CN (1) CN104302876A (fr)
WO (1) WO2013156284A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2535181A (en) * 2015-02-11 2016-08-17 Futurebay Ltd Apparatus and method for energy storage
WO2016150459A1 (fr) * 2015-03-20 2016-09-29 Siemens Aktiengesellschaft Soupapes atmosphériques de surplus pour la régulation de pression
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
DK3379040T3 (da) * 2017-03-20 2021-04-12 Lumenion Gmbh Kraftværk til generering af elektrisk energi og fremgangsmåde til drift af et kraftværk
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

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3218802A (en) * 1960-11-28 1965-11-23 Aerojet General Co Binary vapor power plant
FR2215835A6 (fr) * 1973-01-26 1974-08-23 Babcock Atlantique Sa
JPS58214606A (ja) * 1982-06-05 1983-12-13 Mitsui Eng & Shipbuild Co Ltd 二流体サイクル
US4700543A (en) * 1984-07-16 1987-10-20 Ormat Turbines (1965) Ltd. Cascaded power plant using low and medium temperature source fluid
JPS61149507A (ja) * 1984-12-24 1986-07-08 Hisaka Works Ltd 熱回収装置
JPS61171808A (ja) * 1985-01-28 1986-08-02 Toshiba Corp デユアルランキンサイクル発電プラント
JPS61237804A (ja) * 1985-04-16 1986-10-23 Kawasaki Heavy Ind Ltd 動力システム
DK23391D0 (da) 1991-02-12 1991-02-12 Soerensen Jens Richard Vindmoelle til selvforsyning og opbevaring af energi
US5813215A (en) * 1995-02-21 1998-09-29 Weisser; Arthur M. Combined cycle waste heat recovery system
US7458218B2 (en) * 2004-11-08 2008-12-02 Kalex, Llc Cascade power system
US7313926B2 (en) * 2005-01-18 2008-01-01 Rexorce Thermionics, Inc. High efficiency absorption heat pump and methods of use
US8656712B2 (en) 2007-10-03 2014-02-25 Isentropic Limited Energy storage
WO2009045196A1 (fr) * 2007-10-04 2009-04-09 Utc Power Corporation Système de cycle de rankine organique (orc) en cascade utilisant de la chaleur résiduelle d'un moteur alternatif
EP2307673A2 (fr) * 2008-08-04 2011-04-13 United Technologies Corporation Condenseur en cascade pour cycle de rankine organique géothermique à unité multiple
US8707701B2 (en) * 2008-10-20 2014-04-29 Burkhart Technologies, Llc Ultra-high-efficiency engines and corresponding thermodynamic system
US8474262B2 (en) * 2010-08-24 2013-07-02 Yakov Regelman Advanced tandem organic rankine cycle

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO2013156284A1 *

Also Published As

Publication number Publication date
CN104302876A (zh) 2015-01-21
EP2653670A1 (fr) 2013-10-23
US20150136351A1 (en) 2015-05-21
WO2013156284A1 (fr) 2013-10-24

Similar Documents

Publication Publication Date Title
EP2574739A1 (fr) Installation de stockage d'énergie thermique et son procédé de fonctionnement
EP1917428B1 (fr) Procédé d'operation d'une centrale electrique equipee d'un reservoir sous pression
EP2574740A1 (fr) Installation de stockage d'énergie thermique
EP2823156B1 (fr) Installation pour le stockage et le dépôt d'énergie thermique
EP2698505A1 (fr) Procédé de chargement et de déchargement d'un accumulateur thermique et installation pour le stockage et le dépôt d'énergie thermique appropriée à ce procédé
EP1828549B1 (fr) Centrale electrique
EP2808500A1 (fr) Pompe à chaleur dotée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluidique
WO2013156284A1 (fr) Installation d'accumulation et de distribution d'énergie thermique au moyen d'un accumulateur de chaleur et d'un accumulateur de froid et procédé de fonctionnement de ladite installation
EP2759679A1 (fr) Dispositif de stockage thermique destiné à l'utilisation de chaleur à basse température
EP2574756B1 (fr) Procédé de fonctionnement d'une centrale d'accumulation d'air comprimé adiabatique et centrale d'accumulation d'air comprimé adiabatique
EP3186506B1 (fr) Dispositif et procédé de stockage d'énergie
EP3091176B1 (fr) Procédé de réglage de la pression du gaz dans un réseau de gazoducs et station de réglage de pression de gaz
WO2016131920A1 (fr) Centrale à vapeur et procédé pour son fonctionnement
DE102012206296A1 (de) Anlage zur Speicherung und Abgabe thermischer Energie und Verfahren zu deren Betrieb
DE202005003611U1 (de) Wärmekraftwerk mit Druckluftspeichervorrichtung zum Ausgleich fluktuierender Energieeinspeisung aus regenerativen Energiequellen
EP2489840A1 (fr) Accumulateur d'énergie et son procédé de fonctionnement
EP2574738A1 (fr) Installation de stockage d'énergie thermique
DE102004028531A1 (de) Verfahren zum Betrieb einer Kraftwerksanlage, und Kraftwerksanlage
DE102012217142A1 (de) Verfahren zum Laden und Entladen eines Speichermediums in einem Wärmespeicher und Anlage zur Durchführung dieses Verfahrens
WO2018029371A1 (fr) Échangeur de chaleur destiné à être utilisé dans une partie chaude d'une centrale de stockage d'énergie par air liquide, partie chaude et procédé permettant de faire fonctionner ledit échangeur de chaleur dans ladite partie chaude
DE102009030146A1 (de) Vorrichtung und Verfahren zur Energiespeicherung und -bereitstellung
DE2304783A1 (de) Waermekraftanlage
WO2023011997A1 (fr) Moteur thermique
DE950099C (de) Verfahren zum Betriebe mehrstufiger Verpuffungsbrennkraftturbinenanlagen und Verpuffungsbrennkraftturbinenanlage zur Durchfuehrung des Verfahrens
DE102013207702A1 (de) Verfahren zum Betreiben eines Gaskompressors, sowie Kompressorstation im Verlauf einer Ferngasleitung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20141008

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS AKTIENGESELLSCHAFT

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS GAMESA RENEWABLE ENERGY A/S

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20200227

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20200709