EP3379040A1 - Centrale de production d'électricité et son procédé de fonctionnement - Google Patents

Centrale de production d'électricité et son procédé de fonctionnement Download PDF

Info

Publication number: EP3379040A1
Authority: EP; European Patent Office
Prior art keywords: heat storage; fluid; heat; heat exchanger; working fluid
Prior art date: 2017-03-20
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.): Granted

Application number

EP17161768.1A

Other languages

German (de)

English (en)

Other versions

EP3379040B1 (fr

Inventor

Andrew Zwinkels

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.)

Lumenion GmbH

Original Assignee

Lumenion GmbH

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

2017-03-20

Filing date

2017-03-20

Publication date

2018-09-26

2017-03-20 Priority to PT171617681T priority Critical patent/PT3379040T/pt

2017-03-20 Application filed by Lumenion GmbH filed Critical Lumenion GmbH

2017-03-20 Priority to EP17161768.1A priority patent/EP3379040B1/fr

2017-03-20 Priority to PL17161768T priority patent/PL3379040T3/pl

2017-03-20 Priority to ES17161768T priority patent/ES2861551T3/es

2017-03-20 Priority to SI201730702T priority patent/SI3379040T1/sl

2017-03-20 Priority to DK17161768.1T priority patent/DK3379040T3/da

2018-03-11 Priority to CN201880028319.1A priority patent/CN110573699B/zh

2018-03-11 Priority to US16/494,560 priority patent/US10858960B2/en

2018-03-11 Priority to AU2018236959A priority patent/AU2018236959B2/en

2018-03-11 Priority to CA3057239A priority patent/CA3057239A1/fr

2018-03-11 Priority to PCT/EP2018/055990 priority patent/WO2018172107A1/fr

2018-03-11 Priority to JP2019550149A priority patent/JP7126090B2/ja

2018-09-26 Publication of EP3379040A1 publication Critical patent/EP3379040A1/fr

2019-10-14 Priority to ZA2019/06756A priority patent/ZA201906756B/en

2021-01-13 Application granted granted Critical

2021-01-13 Publication of EP3379040B1 publication Critical patent/EP3379040B1/fr

2021-04-07 Priority to HRP20210553TT priority patent/HRP20210553T8/hr

Status Active legal-status Critical Current

2037-03-20 Anticipated expiration legal-status Critical

Images

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
- F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
- F01K3/186—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters using electric heat
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H7/00—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release
- F24H7/02—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid
- F24H7/0208—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid using electrical energy supply
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H2240/00—Fluid heaters having electrical generators
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H7/00—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release
- F24H7/02—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid
- F24H7/04—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid with forced circulation of the transfer fluid
- F24H7/0408—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid with forced circulation of the transfer fluid using electrical energy supply
- F24H7/0433—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid with forced circulation of the transfer fluid using electrical energy supply the transfer medium being water
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
- F28D2020/0047—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material using molten salts or liquid metals
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
- F28D2020/0078—Heat exchanger arrangements

Definitions

the disclosure relates according to claim 1, a power plant for generating electrical energy. Moreover, the disclosure according to claim 12 relates to a method for operating a power plant.
the power plant may be a facility that burns an energy source to generate electrical power through the heat energy released.
This includes, for example, gas-fired power stations and coal-fired power plants, which burn natural gas or coal as energy sources.
a reformer a synthesis gas or hydrogen gas can be generated and burned.
the amount of electrical energy generated which is fed by numerous producers in an electric grid, varies greatly in time.
the total amount of electrical energy generated varies greatly over time. This allows the available electrical energy to significantly exceed current demand.
Energy storage devices that store energy in electrical or chemical form can store only relatively small amounts of energy at a reasonable cost. In order to store larger amounts of energy pumped storage plants are also used. However, these require a large difference in height, which is usually feasible only in mountainous areas.
the power plant also includes at least a first turbine and a generator coupled to the first turbine for generating electrical energy from a rotational movement provided by the turbine.
the electric heater may include, for example, resistive elements that generate heat when traversed by an electric current.
the heat energy is then stored in the heat storage body.
This may for example comprise a metal plate.
the tubes of the heat exchanger may either directly contact the heat storage body or be connected to the heat storage body via a thermal interface material (eg, a metal body) that is part of the heat exchanger.
the heat exchanger can be designed in the length and the cross section of its tubes so that the heat storage fluid evaporates when flowing through the heat exchanger, so for example, liquid water is converted into water vapor.
electrical energy is taken from an external power grid and stored with the heat storage device in the form of heat energy.
the stored heat energy can be converted back into electrical energy and output to the external power grid.
a control unit can be set whether currently more electrical energy is taken from the mains or discharged to the mains. As a result, fluctuations in an amount of energy in the power grid can be at least partially compensated.
the heat storage bodies are in this case operated between a minimum temperature and a maximum temperature.
the temperature difference therebetween determines what amount of energy the heat storage body can store during operation and release to the heat storage fluid.
a variable temperature of the heat storage body has the consequence that the temperature of the heat storage fluid after flowing through a heat exchanger is also dependent on the instantaneous temperature of the associated heat storage body. The temperature of the heat storage fluid can therefore vary considerably during operation.
a heat storage fluid circuit is connected to the heat exchanger or the heat exchangers.
a working fluid circuit other than the heat storage fluid circuit is connected to the first turbine (and more particularly to any other turbines that may be present).
At least one first fluid circulation heat exchanger is present and connected to the heat storage fluid circuit and the working fluid circuit for transferring heat from the heat storage fluid to a working fluid in the working fluid circuit.
the heat storage fluid is not passed through the turbine (s). Rather, only the working fluid is passed through the turbine (s). As a result, a temperature fluctuation of the heat storage fluid has little effect on the temperature of the working fluid.
the turbine can be driven with steam at a substantially constant temperature.
a relatively high pressure of, for example, 100 bar is needed only at the turbine (s). Due to the two separate circuits, the pressure of the fluid at the heat storage units need not be as high as the fluid pressure at the turbines.
a working fluid pump may be operated to increase the pressure of the working fluid in the working fluid circuit
a heat storage fluid pump may be operated to increase the pressure of the working fluid in the heat storage fluid circuit.
the working fluid pump and the heat storage fluid pump are operated so that the pressure of the working fluid is greater than the pressure of the heat storage fluid.
the power of the working fluid pump may be greater than that of the heat storage fluid pump.
the higher pressure can be defined, for example in a pressure comparison in each case behind the respective pump.
the working fluid circuit and the heat storage fluid circuit may each comprise a pipe system, these two pipe systems are separated from each other.
the fluid circulation heat exchanger may be a heat exchanger having separate heat storage fluid and working fluid conduits. Thermal energy is transferred from the heat storage fluid to the working fluid via a thermal bridge, for example a metal connection between the separate lines.
the heat storage fluid and the working fluid may each be a basically any liquid or any gas.
the heat storage fluid may in particular be an oil, in particular a thermal oil.
the oil may comprise salts and may thus melt at about 200 ° C and be usable from this temperature to about 600 ° C.
saline thermal oils are particularly well suited to heat energy of to record the heat storage units.
the heat storage fluid may accordingly be a liquid which is in liquid form both before and after passing through the heat exchangers.
the working fluid may be different from the heat storage fluid and, in particular, may be water or an aqueous solution. In this case, the working fluid when flowing through the fluid or the heat exchanger (s) can be evaporated.
the boiling temperature of the working fluid at the pressure generated by the working fluid pump may be lower than 200 ° C, so that it is ensured that the working fluid is always evaporated in the fluid circuit heat exchanger, regardless of whether the heat storage fluid is currently a high temperature (approx 600 ° C) or a low temperature (about 250 ° C).
a second turbine and a second fluid circuit heat exchanger may be present.
the second turbine may also be coupled to the generator or to a second generator to drive it.
the first turbine may be located downstream of the first fluidic circuit heat exchanger.
the second fluidic circuit heat exchanger may be disposed downstream of the first turbine.
the second turbine may be located downstream of the second fluidic circuit heat exchanger.
the first and second fluid circulation heat exchangers can be separated from each other and in particular formed the same.
the first and second fluid circulation heat exchangers can also be formed by a unit which comprises separate lines for the heat storage fluid, for the working fluid before flowing through the first turbine and for the working fluid after flowing through the first turbine.
the first and the second fluid circuit heat exchangers can be arranged in the heat storage fluid circuit in two mutually parallel lines.
the heat storage fluid circuit therefore has a branching on two lines, which are both flowed through by heat storage fluid.
the first fluid circulation heat exchanger is arranged and in the other of these lines, the second fluid circulation heat exchanger is arranged.
the two lines open into each other downstream of the two fluid circulation heat exchangers.
the "parallel" arrangement is therefore not to be regarded as geometrically parallel, but as a contrast to a series arrangement in succession, in which the two fluid circuit heat exchangers would flow through one after the other.
this ensures a sufficiently high heat transfer in both heat exchangers.
a controller may be provided in the heat storage fluid circuit and configured to variably set a split of heat storage fluid to the first fluidic circuit heat exchanger and the second fluidic circuit heat exchanger.
a heat transfer from the heat storage fluid to the working fluid for the two fluid circuit heat exchangers can be set different from each other.
the working fluid may have cooled down after flowing through the first turbine, but may still be warmer than before it flows through the first fluid circuit heat exchanger.
the working fluid in the second fluidic circuit heat exchanger would have to absorb less heat energy than in the first fluidic circuit heat exchanger.
the control device can, for example, conduct more heat storage fluid to the first fluid circulation heat exchanger than to the second fluid circulation heat exchanger.
a first bypass may be provided around the first fluidic circuit heat exchanger to direct working fluid bypassing the first fluidic circuit heat exchanger to the first turbine.
a bypass can therefore be understood as a bypass.
a first bypass controller may be provided and configured to variably set a split of working fluid to the first fluidic circuit heat exchanger and the first bypass. In this way, a heat transfer in the first fluidic circuit heat exchanger can be varied to the working fluid. As a result, for example, temperature fluctuations of the heat storage fluid can be partially or completely compensated, so that a heat transfer to the working fluid is only slightly influenced by a temperature fluctuation of the heat storage fluid.
the first bypass and the controller may form a first quench cooler.
This is a mixer in which a fluid is cooled by mixing it with a cooler fluid.
the cooler fluid is the fraction of the working fluid which has bypassed the first fluidic circuit heat exchanger.
a second bypass may be provided with respect to the second fluidic circuit heat exchanger.
a second bypass may be present around the second fluid circuit heat exchanger in order to guide working fluid to the second turbine while bypassing the second fluid circuit heat exchanger.
a second bypass controller may be provided and configured to variably set a split of working fluid to the second fluidic circuit heat exchanger and the second bypass. In this way, in turn, the two fluid circuit heat exchangers can be operated differently and it can be set in each case a desired temperature of the working fluid after flowing through the respective fluid circuit heat exchanger.
bypasses it is also possible, alternatively or in addition to the bypasses described above, to provide one or two corresponding bypasses for heat storage fluid in the heat storage fluid circuit.
a variable portion of the heat storage fluid is directed through the associated fluid circulation heat exchanger to vary a heat transfer to the working fluid.
the heat storage fluid is always present in liquid form and is not evaporated. Upon evaporation, the heat storage fluid would suddenly withdraw large amounts of energy from the heat storage as soon as it reaches its edge or beginning. Disadvantageously, this would discharge the heat storage spatially uneven. In addition, the sudden evaporation would lead to material stresses. These problems are avoided if the heat storage fluid is not evaporated.
the working fluid for driving the turbine (s) should be in the form of vapor or gas. This is made possible by the two separate fluid circuits and different fluids:
the working fluid may have a lower boiling point / boiling temperature than the heat storage fluid so that the working fluid in the first fluid circulation heat exchanger evaporates.
An optional second fluid circulation heat exchanger As a rule, the working fluid enters in vapor form and continues to be heated / superheated.
An electrical energy consumption by the electric heater is useful at a low electricity price, that is, in an oversupply of electrical energy in a power grid, which is referred to here as an external power grid.
the turbine and the generator can be operated relatively stable in terms of time, that is to say they have no time-varying fluctuations.
An electrical control unit may be provided and configured to variably adjust whether more electric power is currently being picked up from an external power supply by the electric heater (s) or output to the external power supply by the generator.
Preferred variants of the method according to the invention result from the intended use of the power plant according to the invention.
the method variants described are also to be regarded as variants of the power plant according to the invention.
FIG Fig. 3 An embodiment of a power plant 110 according to the invention is shown schematically in FIG Fig. 3 shown.
the power plant 110 includes a first turbine 120 and may include a second turbine 121 or even other turbines (not shown).
the turbines 120, 121 are driven by a flowing working fluid.
the working fluid can a vapor, for example water vapor.
Coupled to the turbines 120, 121 is a generator 123 which converts the rotational energy provided by the turbines 120, 121 into electrical energy. The electrical energy is then output to an external power grid.
the power plant 110 is used to compensate for fluctuations in the amount of electrical energy in the external power grid. For this purpose, the power plant 110 to receive electrical energy from the external power grid, if there is an oversupply in particular. In the event of oversupply, an electricity price can become very small or even negative in the meantime, which means that the consumption of electrical energy is almost free or in some cases even money-raising.
the absorbed electrical energy is to be stored in the power plant 110 and again output as electrical energy at another time.
the power plant 110 comprises at least one heat storage device 100.
the power plant 110 comprises at least one heat storage device 100.
a heat storage device 100 is closer in FIG FIG. 1 as a perspective view and in FIG. 2 shown as a sectional view.
Each heat storage device 100 comprises at least one, preferably a plurality of heat storage units 1, which are stacked one above the other.
Each heat storage unit 1 comprises an electric heater 10. This converts electrical energy into heat energy, preferably substantially completely, that is, more than 90% of the energy absorbed by the electric heater 10 is converted into heat energy. The electrical energy is absorbed from the external power grid.
Each heat storage unit 1 furthermore comprises at least one, in particular exactly two, heat storage bodies 30, 31. These can be metal bodies or plates which serve to store heat energy.
each heat storage unit also includes a heat exchanger 50 which has a plurality of heat storage tubes 51.
Each heat exchanger 50 is adjacent to at least one of the heat storage bodies 30.
thermal energy is transferred from the heat storage body 30 to the heat exchanger tubes and a heat storage fluid carried therein.
Heat transfer fluid is transferred to the various heat exchangers via a distributor tube 45 50 split. After flowing through the heat exchanger 50, the heat storage fluid is combined in a manifold 55.
the heat energy of the heat storage fluid can now be used to generate electrical energy again.
the heat storage fluid is not passed through the turbines 120, 121. Rather, the heat is transferred from the heat storage fluid to a different working fluid, which is passed in a separate circuit, the working fluid circuit 140.
the heat storage fluid circulates in a separate circuit, the heat storage fluid circuit 130th
a heat storage fluid pump 125 is arranged, which circulates the heat storage fluid in the circuit 130.
a working fluid pump 145 is arranged in the working fluid circuit 140, which circulates the working fluid in the circuit 140.
the working fluid pump 145 is a significant higher pressure than provided by the heat storage fluid pump 125, for example, at least 10 times as high pressure.
the heat storage fluid may have a higher boiling point than the working fluid, so that the heat storage fluid is present as a liquid and is not vaporized by heat from the heat storage units.
the working fluid is vaporized by the heat energy from the heat storage fluid and liquefied after flowing through the turbine 120, 121 in a condenser 124.
the condenser 124 may, as shown, comprise a heat exchanger through which heat is removed from the working fluid, for example to a liquid which may then be further used, for example for heating purposes.
heat storage fluid is not evaporated, the above-described disadvantage is avoided that by evaporation suddenly large amounts of energy is removed from a portion of the heat storage body 30.
the heat storage fluid may be, for example, an oil while the working fluid is water or an aqueous solution.
At least a first fluid circulation heat exchanger 131 is present.
a second fluid circulation heat exchanger 132 is also provided. Through each of these heat exchangers 131, 132, working fluid and separately therefrom heat storage fluid is passed, wherein the respective tubes are thermally coupled to each other for a high heat transfer.
the first fluid circulation heat exchanger 131 is disposed upstream of the turbine 120 with respect to the working fluid circuit 140.
the second fluid circuit heat exchanger 132 is, however, arranged with respect to the working fluid circuit 140 between the two turbines 120, 121.
the two fluid circuit heat exchangers 131, 132 can be arranged parallel to one another with regard to the heat storage fluid circuit 130.
a line of the heat storage fluid upstream of the two fluid circuit heat exchangers 131, 132 can be divided into two lines 135, 136 which extend through in each case one of the two fluid circuit heat exchangers 131, 132. Thereafter, the two lines 135, 136 are brought together again.
the heat storage devices 100 may be disposed on mutually parallel lines. This has the advantage that the thermal storage devices 100 arranged parallel to one another are discharged substantially equally, that is to say, in particular essentially the same amount of energy is transferred to the heat storage fluid flowing through. Thus, it is avoided that a heat storage device 100 has reached a maximum temperature and therefore can not receive and store any further energy from the external power grid while another of the heat storage devices 100 is far from the maximum temperature. If as many of the heat storage devices 100 can simultaneously receive electrical energy, a maximum possible consumption of electrical energy is advantageously higher.
some of the heat storage devices 100 may be arranged one behind the other in the heat storage fluid circuit 130, that is, through which the heat storage fluid flows successively.
the discharge ie the heat transfer to the heat storage medium
the heat storage fluid should not fall below a minimum temperature, resulting in a minimum temperature for a heat storage device 100.
it is desirable that a minimum temperature of the heat storage device 100 is low, because it makes a possible temperature difference of the heat storage device 100, and thus its storage capacity, high. If two or more heat storage devices 100 are arranged one behind the other, they can be operated with different minimum temperatures.
a front one of these heat storage devices 100 may have a lower minimum temperature than a rear one of these heat storage devices 100.
the rear heat storage device 100 guarantees a desired minimum temperature of the heat storage fluid.
the front thermal storage device 100 can be operated over a very wide temperature range (that is, over a wider temperature range than the rear thermal storage device 100), and thus has a particularly large storage capacity.
the respective maximum temperatures of successively arranged heat storage devices 100 may be different.
a control device may be provided and operated to operate, from the heat storage devices 100 arranged one behind the other, a front heat storage device 100 over a larger temperature range than a rear heat storage device 100.
the entire mass of its heat storage bodies 30 is also relevant. If a rear heat storage device 100 made up of a plurality of heat storage devices arranged one behind the other is anyway used over a smaller temperature range, the mass of their heat storage bodies may be smaller than the mass of the heat storage bodies of the front heat storage device 100. This can be realized, for example, by using the front heat storage device more heat storage units than the rear heat storage device; Incidentally, the heat storage units of the front and rear heat storage devices 100 may be the same.
the power plant 110 may also have a burner for a (fossil) energy carrier, for example for burning coal, natural gas or synthesis gas.
a burner for a (fossil) energy carrier for example for burning coal, natural gas or synthesis gas.
the resulting heat released can also be transferred to the working fluid or the heat storage fluid. It can be provided to control a power of the burner depending on a current consumption of the electric heater 10.
a current consumption takes place in particular (or exclusively) when an oversupply of electrical energy is present. At this time, therefore, it is desirable that less electric power is generated and thus the performance of the burner is reduced.
the performance of the burner can be reduced to a reduced level when the heat storage devices 100 are being charged, especially when their electrical power consumption exceeds a predetermined threshold.
the output of the burner is not lowered to the reduced value but kept at a higher level when the power consumption of the electric heaters does not exceed the threshold value.
the power plant according to the invention can be stored in a simple and cost-effective manner large amounts of electrical energy as heat energy and then be converted back into electrical energy.

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Engineering & Computer Science (AREA)
Mechanical Engineering (AREA)
General Engineering & Computer Science (AREA)
Chemical & Material Sciences (AREA)
Combustion & Propulsion (AREA)
Physics & Mathematics (AREA)
Thermal Sciences (AREA)
Engine Equipment That Uses Special Cycles (AREA)
Control Of Eletrric Generators (AREA)

EP17161768.1A 2017-03-20 2017-03-20 Centrale de production d'électricité et son procédé de fonctionnement Active EP3379040B1 (fr)

Priority Applications (14)

Application Number	Priority Date	Filing Date	Title
EP17161768.1A EP3379040B1 (fr)	2017-03-20	2017-03-20	Centrale de production d'électricité et son procédé de fonctionnement
PL17161768T PL3379040T3 (pl)	2017-03-20	2017-03-20	Elektrownia do wytwarzania energii elektrycznej i sposób eksploatacji elektrowni
ES17161768T ES2861551T3 (es)	2017-03-20	2017-03-20	Central eléctrica para generar energía eléctrica y procedimiento para operar una central eléctrica
SI201730702T SI3379040T1 (sl)	2017-03-20	2017-03-20	Elektrarna za proizvodnjo električne energije in postopek za upravljanje elektrarne
DK17161768.1T DK3379040T3 (da)	2017-03-20	2017-03-20	Kraftværk til generering af elektrisk energi og fremgangsmåde til drift af et kraftværk
PT171617681T PT3379040T (pt)	2017-03-20	2017-03-20	Central de produção de energia elétrica e método de funcionamento de uma central de produção de energia elétrica
US16/494,560 US10858960B2 (en)	2017-03-20	2018-03-11	Power plant for generating electrical energy and method for operating a power plant
AU2018236959A AU2018236959B2 (en)	2017-03-20	2018-03-11	Power plant for generating electrical energy and method for operating a power plant
CN201880028319.1A CN110573699B (zh)	2017-03-20	2018-03-11	生成电能的发电所和运行发电所的方法
CA3057239A CA3057239A1 (fr)	2017-03-20	2018-03-11	Centrale electrique servant a produire une energie electrique et procede servant a faire fonctionner une centrale electrique
PCT/EP2018/055990 WO2018172107A1 (fr)	2017-03-20	2018-03-11	Centrale électrique servant à produire une énergie électrique et procédé servant à faire fonctionner une centrale électrique
JP2019550149A JP7126090B2 (ja)	2017-03-20	2018-03-11	電気エネルギーを発生させるための発電所および発電所を稼働させる方法
ZA2019/06756A ZA201906756B (en)	2017-03-20	2019-10-14	Power plant for generating electrical energy and method for operating a power plant
HRP20210553TT HRP20210553T8 (hr)	2017-03-20	2021-04-07	Elektrana namijenjena stvaranju električne energije i postupak rada s elektranom

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
EP17161768.1A EP3379040B1 (fr)	2017-03-20	2017-03-20	Centrale de production d'électricité et son procédé de fonctionnement

Publications (2)

Publication Number	Publication Date
EP3379040A1 true EP3379040A1 (fr)	2018-09-26
EP3379040B1 EP3379040B1 (fr)	2021-01-13

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Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP17161768.1A Active EP3379040B1 (fr)	2017-03-20	2017-03-20	Centrale de production d'électricité et son procédé de fonctionnement

Country Status (14)

Country	Link
US (1)	US10858960B2 (fr)
EP (1)	EP3379040B1 (fr)
JP (1)	JP7126090B2 (fr)
CN (1)	CN110573699B (fr)
AU (1)	AU2018236959B2 (fr)
CA (1)	CA3057239A1 (fr)
DK (1)	DK3379040T3 (fr)
ES (1)	ES2861551T3 (fr)
HR (1)	HRP20210553T8 (fr)
PL (1)	PL3379040T3 (fr)
PT (1)	PT3379040T (fr)
SI (1)	SI3379040T1 (fr)
WO (1)	WO2018172107A1 (fr)
ZA (1)	ZA201906756B (fr)

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US11053847B2 (en)	2016-12-28	2021-07-06	Malta Inc.	Baffled thermoclines in thermodynamic cycle systems
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AU2018236959A1 (en)	2019-10-03
HRP20210553T1 (hr)	2021-09-03
JP2020513081A (ja)	2020-04-30
US20200011207A1 (en)	2020-01-09
PT3379040T (pt)	2021-04-15
CN110573699A (zh)	2019-12-13
HRP20210553T8 (hr)	2022-01-21
AU2018236959B2 (en)	2023-01-05
CN110573699B (zh)	2021-10-22
CA3057239A1 (fr)	2018-09-27
ZA201906756B (en)	2021-02-24
JP7126090B2 (ja)	2022-08-26
US10858960B2 (en)	2020-12-08
DK3379040T3 (da)	2021-04-12
ES2861551T3 (es)	2021-10-06
SI3379040T1 (sl)	2021-07-30
WO2018172107A1 (fr)	2018-09-27
EP3379040B1 (fr)	2021-01-13
PL3379040T3 (pl)	2021-07-05

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WO2013034139A1 (fr)	2013-03-14	Procédé et dispositif de stockage et de récupération d'une énergie thermique
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DE102013222677B4 (de)	2016-01-07	Wärmeübertragervorrichtung, Wärmespeichervorrichtung und Verfahren zum Übertragen und/oder Speichern von Wärme
EP2600058A1 (fr)	2013-06-05	Dispositif de transfert d'un liquide de travail dans un état gazeux ou vaporeux, notamment pour la production de vapeur d'eau
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DE102019217998A1 (de)	2021-05-27	Vorrichtung und Verfahren zur Ausspeicherung eines thermischen Energiespeichers, insbesondere eines Flüssigsalzspeichers

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