EP3469190B1 - Kraftwerk mit wärmespeicher - Google Patents

Kraftwerk mit wärmespeicher Download PDF

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Publication number
EP3469190B1
EP3469190B1 EP17735045.1A EP17735045A EP3469190B1 EP 3469190 B1 EP3469190 B1 EP 3469190B1 EP 17735045 A EP17735045 A EP 17735045A EP 3469190 B1 EP3469190 B1 EP 3469190B1
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EP
European Patent Office
Prior art keywords
pressure part
power plant
steam
medium
plant according
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Active
Application number
EP17735045.1A
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German (de)
English (en)
French (fr)
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EP3469190A1 (de
Inventor
Stefan Becker
Erich Schmid
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 Energy Global GmbH and Co KG
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Siemens AG
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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
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • 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
    • F01K3/004—Accumulation in the liquid branch of the circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/06—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein the engine being of extraction or non-condensing type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/003—Arrangements for measuring or testing
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F01K3/14—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having both steam accumulator and heater, e.g. superheating accumulator

Definitions

  • the present invention relates to a power plant with a steam circuit, which can be supplied with thermal energy for steam preparation in the area of a waste heat steam generator, and to a method for operating such a power plant.
  • power plants which can quickly deliver power to the supply networks, or can quickly draw power from them, are very advantageous.
  • the power plants should also cover a high output range so that they can be used in both peak and low-load operations.
  • the WO 2014/026784 A1 discloses for example a power plant arrangement with a high temperature storage unit which requires operating temperatures of over 600 ° C.
  • the DE 10 2012 108 733 A1 also describes a system for generating hot water or steam by a high temperature storage for use in a gas turbine power plant, in which a storage material is located in the high temperature storage.
  • a gas turbine power plant with improved flexibility is known, wherein a heat store and a container are provided, so that hot water can be supplied from the container to the gas turbine during operation to increase the output.
  • the US 2014/0165572 A1 also discloses a preheater for fuel gas for a gas turbine through stored thermal energy.
  • the US 2015/027122 A1 discloses an energy storage power plant with a water vapor circuit which can be supplied with thermal energy for steam preparation in the area of a heat recovery steam generator, the water vapor circuit comprising a high pressure part and a medium pressure part in the area of the heat recovery steam generator, and further comprising a heat accumulator having a phase change material.
  • auxiliary steam from an auxiliary steam generator or a neighboring system is often used to keep the functional components warm in the steam circuit.
  • the auxiliary steam pressures are relatively low, which in turn severely limits the temperatures for keeping warm.
  • the auxiliary steam generator generally requires relatively expensive natural gas or electrical energy to provide the required amounts of energy, which means that this method has economic disadvantages.
  • a power plant with a water vapor circuit which can be supplied with thermal energy for steam preparation in the area of a heat recovery steam generator, the water vapor circuit comprising a high pressure part, a medium pressure part and a low pressure part in the area of the heat recovery steam generator, and furthermore a one Phase change material (PCM) having heat accumulator is included, which is not arranged in the area of the heat recovery steam generator, whereby to supply the heat accumulator with thermally treated water, a supply line starting from the high-pressure part or the medium-pressure part is included and a discharge line for dispensing thermally treated water from the heat accumulator, which opens into the medium pressure part, the low pressure part or a steam turbine.
  • PCM Phase change material
  • an energetic heat storage concept is therefore proposed which is integrated in the power plant.
  • the heat store has a carrier medium which only carries out relatively small changes in volume when the thermal energy is stored or removed.
  • These materials phase change materials (PCM), are integrated in the heat storage and enable the storage of relatively large amounts of thermal energy in a relatively small space.
  • the phase change material is supplied in the heat accumulator by steam from the high pressure part or the medium pressure part, whereby both the phase change material located in the heat accumulator is thermally charged and the heat accumulator itself can be filled with steam, for example.
  • phase change material ensures a largely constant temperature level, provided that the temperature-related phase change in the phase change material has not yet been completed.
  • the thermal properties of phase change materials are well known to those skilled in the art.
  • the phase change material can be present in the heat storage approximately in an encapsulated form, e.g. B. spherical, egg-shaped, pellet-shaped, in the form of short or long rods, etc., and is from the water vapor from the high pressure part or the Medium pressure part surrounds or is flowed around by this. So there can be direct contact between the water vapor and the possibly encapsulated phase change material.
  • an encapsulated form e.g. B. spherical, egg-shaped, pellet-shaped, in the form of short or long rods, etc.
  • the high-pressure part, the medium-pressure part and the low-pressure part of the water vapor circuit differ from one another on account of the prevailing temperatures or the pressure level in the water vapor circuit.
  • the low-pressure section, medium-pressure section and high-pressure section can all have their own pressure vessel, their own economizer, their own heat exchanger and their own superheater or reheater.
  • the terms high-pressure part, medium-pressure part and also low-pressure part are general technical terms and are used sufficiently in power plant technology. In particular, it should be pointed out that these terms cannot be used interchangeably.
  • Steam for example, can also be removed from the heat accumulator or processed in it, if the functional components of the water vapor circuit are to be kept warm, but without the heat recovery steam generator being fired regularly or at all.
  • the power plant can be in standby mode or be switched off, however, thermal energy from the Heat storage for keeping the thermal functional components of the steam cycle available.
  • phase change material Due to the high storable thermal energy density in the heat store, which is made possible by the use of the phase change material, keeping warm can be achieved particularly advantageously in terms of energy. An electric or a fuel-operated auxiliary steam generator is therefore no longer necessary. Since the phase change material, after being charged, can also provide a largely constant temperature level over relatively long periods of time, the water vapor in the heat store, which is in thermal interaction with the phase change material, can also be kept at a largely identical temperature level. This in turn ensures that the thermal functional components of the water vapor circuit are supplied with thermally conditioned water from the heat store for a long time.
  • the heat store is designed as a pressure vessel in which the phase change material is arranged.
  • the phase change material can be present in isolated pieces, so that it is in direct contact with thermally treated water or water vapor when the heat accumulator is loaded.
  • the phase change material can also be arranged around the pressure vessel, so that the heat transfer between the phase change material and water or water vapor takes place via the side walls of the heat accumulator.
  • the phase change material ensures an increase in the heat capacity of the heat accumulator and thus a relatively smaller design.
  • phase change material is of course suitably adapted to the desired or prevailing temperatures in the heat accumulator.
  • temperature range of the phase change of the phase change material is close to or at the required or desired storage temperature in the Heat storage.
  • this also applies to all embodiments of the power plant according to the invention.
  • the heat store has a sparger, via which the thermally treated water can be distributed from the feed line into the heat store.
  • a sparger is essentially a network of pipes that has numerous small openings through which the thermally treated water can be distributed into the heat store. When the thermally treated water is introduced into the heat storage device, the sparger ensures that all areas of the heat storage device are exposed to thermal energy as evenly as possible, which in particular increases the storage rates.
  • the heat accumulator has at least one pressure measuring device and / or one temperature measuring device.
  • the loading and unloading of the heat accumulator can thus take place depending on the temperature or pressure.
  • the power plant can also include a control valve in the supply line as well as in the discharge line, which allow the required flows or pressures to be set.
  • the heat accumulator can be loaded and unloaded depending on the pressure or temperature. Such a regulation can be integrated into the control technology of the power plant.
  • a flash tank is connected in the discharge line, which enables a separation of vaporous and liquid water.
  • the flash tank can be used to separate off vaporized portions of the water that has been drained off and possibly feed it back into the steam cycle for further use.
  • a vaporous portion can in the low-pressure part of the steam cycle be initiated in order to be available for further use.
  • the feed line comes from an economizer or from a steam drum of the medium-pressure part. Accordingly, the heat accumulator can be supplied with relatively inexpensive thermally treated water, which means that the heat accumulator can be charged at a relatively low cost.
  • the supply line can come from an economizer or a superheater of the high-pressure part. Since the high-pressure part provides water at a significantly higher pressure or higher temperature, this embodiment is economically less advantageous compared to the previous ones, but allows the heat accumulator to be charged to a higher pressure or a higher temperature level. Likewise, the thermally conditioned water which is possibly stored in the heat store can still be kept available for use over a longer period of time.
  • a return line is provided which is fluidly connected to the heat accumulator on the one hand and on the other hand opens into the medium pressure part at a location where liquid water is conducted.
  • This location is preferably the steam drum or the feed water line.
  • thermally enriched water can thus be discharged from the heat store and reintroduced into the water vapor cycle.
  • the heat accumulator is charged for the first time, in which steam condensation takes place, it is desirable to return the condensed portions back into the water vapor cycle, in particular to a place where liquid water is also conducted. This is possible in particular in the medium pressure section in the area of the steam drum or feed water line.
  • a return line is further provided which is fluidly connected to the heat accumulator on the one hand and on the other hand opens into a flash tank from which a steam line leads into the low pressure part.
  • a liquid line can also open into the low-pressure part at a point at which liquid water is conducted. Due to the separation of vaporous and liquid parts in the flash tank, the low-pressure part can be supplied with both vaporous and liquid parts of the thermally conditioned water. The use of the flash tank therefore does not require a phase-specific return of thermally conditioned water in the return line, since the vapor phase can be separated from the liquid phase in the flash tank. As a result, wet steam, for example, can be returned from the heat store to the low-pressure part via the return line.
  • the power plant also has a steam superheater which is connected in the discharge line downstream of the heat store and also has a phase change material.
  • the steam superheater for example, can also be designed, like the heat accumulator, as a combination of steam accumulator and integrated phase change material.
  • An exemplary embodiment has, for example, the form of a storage box which is integrated in a standard container and has suitable connection points for a feed line or discharge line. The supply of thermally processed water vapor from the heat store can take place in different ways. Depending on the operational requirements, the feed can be designed so that, for. B.
  • the stored water is drained off after a request for secondary frequency support and the stored water is drained off at the medium pressure part between the steam drum and the superheater of the medium pressure part.
  • the derived, thermally treated water from the heat accumulator is consequently thermally conditioned again in the superheater of the medium-pressure part to such an extent that steam of a sufficiently high temperature level can be provided in order to increase the power operation of the steam turbine.
  • thermal energy from the overheating process is sometimes used to increase performance, a significant amount of thermal energy is nevertheless dissipated from the heat store for increasing performance.
  • the stored water is drained off when the steam turbine starts and the stored water is drained off directly to the steam turbine without first being fed to the medium-pressure part or the low-pressure part of the power plant.
  • the discharged water is preferably further processed thermally, for example by providing a further, second heat store or steam superheater, which is connected to the discharge and again releases thermal energy to the discharged water.
  • a second heat store can also be designed, for example, as a heat store with phase change material.
  • the drained water is preferably again with a second heat storage thermally processed again and supplied to reheating.
  • the steam turbine is in standby mode or may be completely removed from the grid.
  • the stored water is drained off under normal load of the steam turbine and the stored water is drained off to the medium-pressure part for a further increase in output.
  • the drained water is used to cover peak loads.
  • FIG. 1 shows a schematic circuit view of an embodiment of the power plant 1 according to the invention, in which water is thermally expanded into a steam circuit 2 via a heat recovery steam generator 3 in order to subsequently convert its thermal energy into rotary mechanical energy by means of a steam turbine 4.
  • the waste heat steam generator 3 is supplied with thermal energy in particular via the exhaust gas of a gas turbine 8, the regions of the water vapor circuit 2 which are arranged closer to the gas turbine in terms of flow technology have a higher temperature.
  • the individual heat exchangers 3 can be assigned to different areas within the heat recovery steam generator 3. The area which has the highest temperatures and pressures is the high-pressure part 11, the part which has the subsequently higher pressures and temperatures is the medium-pressure part 12 and the third part, the low-pressure part 13, has the lowest pressures or temperatures.
  • Both the high-pressure part 11 and the medium-pressure part 12, as well as the low-pressure part 13, can have an economizer, a heat exchanger with a steam drum, and an intermediate superheater or superheater.
  • the individual pressure parts 11, 12, 13 are connected to individual turbines of the multi-part steam turbine 4 in accordance with the pressure or temperature level. So is the high pressure part 11 with a high pressure steam turbine 5 connected, the medium-pressure part 12 with a medium-pressure steam turbine 6 and the low-pressure part 13 with a low-pressure steam turbine 7.
  • the individual steam turbines 5, 6, 7 are each connected to one another by a shaft, the gas turbine 8 also having a coupling 9, for example the steam turbine 4 can be connected via this shaft.
  • a generator 10 is mechanically connected to the shaft, so that electrical power can be provided when the rotary movement is carried out.
  • a heat accumulator 20 which has a phase change material 21 which is integrated in the heat accumulator 20.
  • the phase change material 21 is present in the form of individual pieces that are encapsulated in the heat store 20, for example as a bed.
  • thermally treated water for example in the form of steam, can first be removed from the economizer 14 of the medium-pressure part 12 and fed to the heat accumulator 20.
  • the heat accumulator 20 is connected to the economizer 14 of the medium pressure part 12 via a feed line 25, the flow quantity of thermally treated water removed from the medium pressure part 12 being able to be adjusted by means of a feed valve 28.
  • the steam can be removed from the heat accumulator 20, for example to increase the output when the power plant 1 is operating.
  • the steam is supplied to the medium pressure part 12 in the area between the steam drum 15 and the superheater 16 of the medium pressure part 12, for example via a discharge line 26.
  • the amount of steam supplied can in turn be adjusted via a discharge valve 27 in the discharge line 26.
  • the additional amount of steam supplied to the medium-pressure part 12 can enable increased power operation of the steam turbine 4, as a result of which electrical power can be output by the generator 10 to an increased extent.
  • FIG 2 shows a further embodiment of the power plant 1 according to the invention in a schematic circuit view.
  • the basic structure of the water vapor circuit 2 of the power plant 1 is the same as in the embodiment Figure 1 , Only the connection of the heat accumulator 20 is different in that the supply line 25 is connected to the high pressure part 11 rather than the medium pressure part 12. The connection is in this case directly upstream of the superheater 17 of the high-pressure part 11.
  • the heat accumulator 20 can be charged with steam at a significantly higher temperature level as well as pressure level. This in turn results in a higher energy content in the heat accumulator 20, so that when discharging via the discharge line 26 into the medium-pressure part 12, comparatively more energy can be dissipated to increase the performance of the steam turbine 4.
  • FIG 3 shows a further embodiment of the power plant 1 according to the invention, the basic structure of the water vapor circuit 2 in turn essentially the same as the previous embodiments.
  • the heat accumulator 20, is designed as a vapor pressure accumulator, in which a sparger 32 is arranged, via which the steam supplied via the feed line 25 from the high-pressure part 11 can be distributed relatively evenly.
  • the steam required to charge the heat accumulator 20 is removed from the superheater 17 of the high-pressure part 11.
  • the power plant 1 After removal of high-pressure steam from the water vapor circuit 2 and supplying it to the heat store 20, some portions of the steam typically condense, which can be fed to the low-pressure part 13 via the return line 24.
  • the power plant 1 also has a flash tank 30, which is also connected to the return line 24.
  • a steam line 31 leads out of the flash tank 30 and is connected to the steam drum of the low-pressure part 13.
  • the liquid condensate in the flash tank 30 can also be fed to the steam drum of the low-pressure part 13, but in an area in which the liquid phases of the water are accumulated.
  • a water supply line 33 is also provided, which can discharge thermally treated water from the economizer of the medium pressure part 12. The amount of water carried here is adjusted via a water supply valve 34 in the water supply line 33.
  • the vapor accumulated in the heat accumulator 20 is fed to a steam superheater 40 via a flash valve, which is not provided with reference numerals, which is designed approximately as a storage box.
  • the water vapor emerging from this steam superheater 40 is then fed to the medium-pressure steam turbine 6 of the steam turbine 4.
  • the water vapor circuit has a bypass line 35 which connects the steam from the steam superheater 40 removed steam mixes with steam from the superheater 17 of the high-pressure part 11.
  • the steam superheater 40 is preferably also designed as a heat accumulator with phase change material, the thermal loading of this steam superheater 40 being essentially comparable to the charging of the heat accumulator 20.
  • the required line sections or method steps are not described further in the present application, but are understandable to the person skilled in the art.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP17735045.1A 2016-08-04 2017-06-26 Kraftwerk mit wärmespeicher Active EP3469190B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016214447.2A DE102016214447B4 (de) 2016-08-04 2016-08-04 Kraftwerk mit Phasenwechselmaterial-Wärmespeicher und Verfahren zum Betreiben eines Kraftwerks mit Phasenwechselmaterial-Wärmespeicher
PCT/EP2017/065645 WO2018024409A1 (de) 2016-08-04 2017-06-26 Kraftwerk mit wärmespeicher

Publications (2)

Publication Number Publication Date
EP3469190A1 EP3469190A1 (de) 2019-04-17
EP3469190B1 true EP3469190B1 (de) 2020-02-26

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Application Number Title Priority Date Filing Date
EP17735045.1A Active EP3469190B1 (de) 2016-08-04 2017-06-26 Kraftwerk mit wärmespeicher

Country Status (8)

Country Link
US (1) US10794226B2 (ja)
EP (1) EP3469190B1 (ja)
JP (1) JP6803966B2 (ja)
KR (1) KR102165184B1 (ja)
CN (1) CN109563746B (ja)
DE (1) DE102016214447B4 (ja)
ES (1) ES2787031T3 (ja)
WO (1) WO2018024409A1 (ja)

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WO2024020634A1 (en) * 2022-07-29 2024-02-01 Graphite Energy (Assets) Pty Limited Energy storage and utilisation system

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US20190301306A1 (en) 2019-10-03
DE102016214447A1 (de) 2018-02-08
US10794226B2 (en) 2020-10-06
KR102165184B1 (ko) 2020-10-13
CN109563746B (zh) 2022-04-26
JP2019527791A (ja) 2019-10-03
KR20190034602A (ko) 2019-04-02
CN109563746A (zh) 2019-04-02
WO2018024409A1 (de) 2018-02-08
ES2787031T3 (es) 2020-10-14
JP6803966B2 (ja) 2020-12-23
DE102016214447B4 (de) 2020-12-24
EP3469190A1 (de) 2019-04-17

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