EP3850194B1 - Dampfturbine und verfahren zum betreiben derselben - Google Patents

Dampfturbine und verfahren zum betreiben derselben Download PDF

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Publication number
EP3850194B1
EP3850194B1 EP19795107.2A EP19795107A EP3850194B1 EP 3850194 B1 EP3850194 B1 EP 3850194B1 EP 19795107 A EP19795107 A EP 19795107A EP 3850194 B1 EP3850194 B1 EP 3850194B1
Authority
EP
European Patent Office
Prior art keywords
pressure
inner housing
steam
low
process steam
Prior art date
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Active
Application number
EP19795107.2A
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German (de)
English (en)
French (fr)
Other versions
EP3850194A1 (de
Inventor
Stefan PREIBISCH
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 Energy Global GmbH and Co KG
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Publication date
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Publication of EP3850194A1 publication Critical patent/EP3850194A1/de
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/005—Sealing means between non relatively rotating elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/14—Casings modified therefor
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
    • F01K7/025—Consecutive expansion in a turbine or a positive displacement engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/94—Functionality given by mechanical stress related aspects such as low cycle fatigue [LCF] of high cycle fatigue [HCF]
    • F05D2260/941—Functionality given by mechanical stress related aspects such as low cycle fatigue [LCF] of high cycle fatigue [HCF] particularly aimed at mechanical or thermal stress reduction

Definitions

  • the present invention relates to a steam turbine according to the preamble of independent claim 1 and a method for operating a steam turbine according to the preamble of independent claim 7.
  • steam is used as the working medium to operate steam turbines.
  • the steam is heated in a steam boiler and flows into the steam turbine as process steam via pipes.
  • the previously absorbed thermal energy of the working medium is converted into kinetic energy.
  • the kinetic energy is usually used to operate a generator, which converts the mechanical power generated into electrical power. Alternatively, the kinetic energy can also be used to drive machines such as pumps.
  • the relaxed and cooled process steam flows into a condenser, where it is condensed by heat transfer in a heat exchanger and fed back to the steam boiler as water for heating.
  • Usual steam turbines have at least one high-pressure part and at least one low-pressure part, which are also referred to as high-pressure or low-pressure stages.
  • the low-pressure part the temperature of the process steam drops sharply, which can lead to partial condensation of the process steam.
  • the low-pressure part is very sensitive to the moisture content of the process steam. If the process steam reaches the low-pressure part of the steam turbine with a moisture content of approx. 8 to 10%, measures must be taken to reduce the moisture content of the process steam to a permissible level before entering the low-pressure part.
  • the process steam is heated before entering the low-pressure section so-called intermediate superheating.
  • reheating the process steam is heated again so that the moisture content drops.
  • the entire steam mass flow is removed from the steam turbine after the high-pressure part, fed to the reheating and raised approximately to the temperature of the live steam.
  • the process steam is then fed to the low-pressure part. Without such reheating, the steam turbine would have to be stopped because condensed water droplets could hit the rotating turbine blades and cause damage to the turbine blades due to droplet erosion.
  • At least one medium-pressure stage is used in addition to a high-pressure and a low-pressure stage.
  • This type of reheating of the process steam is carried out between the individual turbine stages. This leads to higher efficiency, as mechanical energy can be generated more efficiently in the turbine stages using the superheated steam.
  • the material on the outer wall is subjected to high stress.
  • the colder steam is removed from the first turbine stage, fed to the reheater and the heated process steam is fed to the second turbine stage.
  • High temperature differences occur in the outer wall in the transition area between the first turbine stage and the second turbine stage. Since the end of the first turbine stage, from which the cold process steam is removed, and the beginning of the second turbine stage, into which the hot process steam is supplied from the reheater, are close together, high thermal stresses occur in the outer wall. This can lead to leaks or cracks in the external wall.
  • the steam turbine has a steam turbine outer casing. Furthermore, the steam turbine has a high-pressure inner housing with a first process steam inlet section and a first process steam outlet section for guiding process steam through the high-pressure inner housing from the first process steam inlet section to the first process steam outlet section in a first process steam expansion device. Furthermore, the steam turbine has a low-pressure inner housing with a second process steam inlet section and a second process steam outlet section for guiding process steam through the low-pressure inner housing from the second process steam inlet section to the second process steam outlet section in a second process steam expansion direction. In addition, the steam turbine has a reheater located downstream of the high-pressure inner casing and downstream of the low-pressure inner housing is arranged, wherein the high-pressure inner housing and the low-pressure inner housing are arranged within the steam turbine outer housing.
  • the high-pressure inner housing and the low-pressure inner housing are arranged such that the first steam inlet section of the high-pressure inner housing faces the second steam inlet section of the low-pressure inner housing.
  • the fact that the first steam inlet section of the high-pressure inner housing faces the second steam inlet section of the low-pressure inner housing means that the first steam inlet section of the high-pressure inner housing points or is aligned in the opposite direction or substantially in the opposite direction as the second steam inlet section of the low-pressure inner housing. Accordingly, the first process steam expansion direction runs opposite or substantially opposite to the second process steam expansion direction.
  • the high-pressure inner housing and the low-pressure inner housing are thus arranged such that a process steam flooding direction through the high-pressure inner housing runs in the opposite direction, in particular 180° opposite, to a process steam flooding direction through the low-pressure inner housing.
  • superheated process steam in the form of live steam, can be fed into the high-pressure inner housing, which is rotated in the opposite direction to the steam, and can be expanded to the pressure and temperature level of a so-called cold intermediate superheat.
  • the process steam can be led to the reheater.
  • Reheated process steam from the reheater can then slide into the low-pressure inner housing facing a main flow direction and relax there down to condensation pressure in the steam turbine.
  • the low-pressure inner housing is to be understood as meaning an inner housing in which, at least on average, a lower pressure prevails or arises than in the high-pressure inner housing. That is, the low-pressure inner housing can also be understood to mean, in particular, a medium-pressure inner housing.
  • Process steam is understood to mean steam, in particular water vapor, which flows through components of the steam turbine during operation of the steam turbine.
  • An expansion direction is to be understood as meaning a direction in which the process steam essentially moves or is directed. This means that if the process steam moves into a steam turbine section, for example from left to right, this is to be understood, in simplified terms, as a linear expansion direction to the right. Furthermore, in the present case, a relaxation direction is to be understood as meaning a pressure direction from a high-pressure area into a low-pressure area or into a pressure area with a lower pressure than in the high-pressure area. Accordingly, an upstream steam turbine section is to be understood as a section that is arranged opposite to the expansion direction.
  • the task is solved by the features of independent patent claim 1.
  • the task is solved by the features of independent patent claim 7.
  • a steam turbine is provided.
  • the steam engine has a steam turbine outer casing.
  • the steam turbine has a high-pressure inner housing with a first process steam inlet section and a first process steam outlet section for guiding process steam through the high-pressure inner housing from the first process steam inlet section to the first process steam outlet section in a first process expansion device.
  • the steam turbine has a low-pressure inner housing with a second process steam inlet section and a second process steam outlet section for guiding process steam through the low-pressure inner housing from the second process steam inlet section to the second process steam outlet section in a second process steam expansion device.
  • the steam turbine has a reheater for reheating process steam, which can be removed downstream of the high-pressure inner housing and upstream of the low-pressure inner housing.
  • the high-pressure inner housing and the low-pressure inner housing are arranged within the steam turbine outer housing and the high-pressure inner housing and the low-pressure inner housing are arranged such that the first steam inlet section of the high-pressure inner housing faces the second steam inlet section of the low-pressure inner housing and further downstream of the high-pressure inner housing a process steam deflection section for diverting process steam from the first steam outlet section in a direction opposite to the first steam expansion device into a gap which is between an inner wall of the steam turbine outer housing and an outer wall of the high-pressure inner housing and at least in sections between the inner wall of the steam turbine outer housing and an outer wall of the low-pressure inner housing extends.
  • a high-pressure sealing shell for at least partially sealing the upstream end section of the high-pressure inner housing and at an upstream end section of the low-pressure inner housing, on which the second process steam end section is designed, a low-pressure sealing shell for at least partially sealing of the upstream end portion of the low-pressure inner housing are arranged, and wherein the high-pressure sealing shell and the low-pressure sealing shell are arranged adjacent to one another.
  • the high-pressure inner housing is designed in such a way that process steam can be removed from the high-pressure inner housing and can be conducted in an area between the high-pressure sealing shell and the low-pressure sealing shell.
  • the process steam which can be taken from the high-pressure inner housing, is throttled directly to the reheating parameters without doing any work. As a result, the steam is significantly warmer than the process steam that was expanded within the first steam expansion device.
  • the removed process steam can thereby be used to direct it into an area of the high-pressure sealing shell and the low-pressure sealing shell in order to locally heat the area and in particular the second inner housing. This means that so-called cold spots cannot occur on the rotor and in the area of the second steam inlet section of the low-pressure inner housing. This results in a positive temperature distribution both in terms of rotor mechanics and rotor dynamics. Due to the lower thermally driven deformation on the low pressure inner housing The clearances between the rotor of the steam turbine and the inner housing can be set smaller.
  • the high-pressure sealing shell is designed such that a predeterminable leakage mass flow can be conducted via the high-pressure sealing shell in an area between the high-pressure sealing shell and the low-pressure sealing shell. Because the high-pressure sealing shell is designed in such a way that a sufficiently large vapor mass flow (leakage flow) can be conducted through the high-pressure sealing shell into the area between the high-pressure sealing shell and the low-pressure sealing shell, the space between the two sealing shells can be heated accordingly, so that the rotor mechanical and Rotor dynamic properties in terms of temperature are positively influenced, so that no cold spots arise on the rotor and the area of the second process steam inlet section is preheated accordingly.
  • the additional formation of lines and openings within the first expansion device can therefore be dispensed with, which significantly reduces the design effort.
  • the existing leakage flow from the high-pressure sealing shell is used for heating, whereby the high-pressure sealing shell must be designed so that the leakage mass flow is higher than would be technically necessary.
  • the leakage mass flow can be easily determined or adjusted by appropriately increasing the gap between the sealing shells and the rotor.
  • a further embodiment of the invention provides that the high-pressure sealing shell and the low-pressure sealing shell are designed and coordinated with one another in such a way that the leakage mass flow through the high-pressure sealing shell is greater than the leakage mass flow through the low-pressure sealing shell.
  • the leakage mass flow via the high-pressure sealing shell is at least 30%, preferably at least 50% larger than the leakage mass flow via the low-pressure sealing shell.
  • the difference in the mass flows results in a blocking mass flow which prevents the cold reheating steam from penetrating into the low-pressure sealing shell and thus into the second expansion device.
  • the hot leakage mass flow from the first expansion device ensures preheating of the rotor between the first sealing shell and the second sealing shell and preheating, in particular of the second process steam inlet section at the second expansion device.
  • a further embodiment of the invention provides that a sealing web is designed on a downstream end section of the low-pressure inner housing for sealing a steam turbine area between the downstream end section of the low-pressure inner housing and the steam turbine outer housing.
  • process steam flows around the low-pressure inner housing during operation.
  • the sealing web which is preferably designed as an integrated sealing web on the downstream end section of the low-pressure inner housing.
  • a further embodiment of the invention provides that the reheater is arranged outside the steam turbine outer casing. This is particularly advantageous with regard to assembly, disassembly, maintenance and repair.
  • the process results in a rotor-mechanical and rotor-dynamic positive temperature distribution.
  • the imposed temperature field allows higher absolute temperature differences in the reheating to be achieved and thus the overall efficiency can be increased.
  • One embodiment of the method provides that the extracted process steam (leakage steam) flows via the high-pressure sealing shell into the area between the high-pressure sealing shell and the low pressure sealing shell.
  • the method according to the invention can be implemented with little design effort and therefore cost-effectively.
  • the conversion of existing steam turbines to the process described can be accomplished using simple means.
  • FIG. 1 shows the basic structure of a steam turbine 1 according to the invention.
  • the steam turbine 1 has a steam turbine outer housing 20, in which there is a high-pressure inner housing 30, a low-pressure inner housing 40 in the form of a medium-pressure inner housing and a further low-pressure inner housing 90.
  • a live steam or process steam source 10 for supplying process steam to the high-pressure inner housing 30 is arranged upstream of the high-pressure inner housing 30.
  • the high-pressure inner housing 30 has a first process steam inlet section 31 and a first process steam outlet section 32 for guiding process steam through the high-pressure inner housing 30 from the first process steam inlet section 31 to the first process steam outlet section 32 in a first process steam expansion device 33.
  • the low-pressure inner housing 40 has a second process steam inlet section 41 and a second process steam outlet section 42 for guiding process steam through the low-pressure inner housing 40 from the second process steam inlet section 41 to the second process steam outlet section 42 in a second process steam expansion device 43.
  • the steam turbine 1 further has a reheater 50, which is arranged downstream of the high-pressure inner housing 30 and upstream of the low-pressure inner housing 40. The arrangement does not refer to a spatial arrangement, but rather to a fluid arrangement.
  • the high-pressure inner housing 30 and the low-pressure inner housing 40 are arranged such that the first steam inlet section 31 of the high-pressure inner housing 30 faces the second steam inlet section 41 of the low-pressure inner housing 40.
  • the steam turbine 1 Downstream of the high-pressure inner housing 30, the steam turbine 1 has a process steam deflection section 60 for diverting process steam from the first steam outlet section 32 in a direction opposite to the first steam expansion device 33 into a gap 70 of the steam turbine 1.
  • the gap 70 extends between the steam turbine outer housing 20 and the high-pressure inner housing 30 and at least in sections between the steam turbine housing 20 and the low-pressure inner housing 40.
  • At a downstream end section of the low-pressure inner housing 40 there is a sealing web 80 for sealing a steam turbine area between the downstream end section of the low-pressure inner housing 40 and the steam turbine outer housing 20 designed.
  • the reheater 50 is arranged outside the steam turbine outer casing 20.
  • the high-pressure inner casing 30 and the low-pressure inner casing 40 are provided as separate components in a common steam turbine outer casing 20.
  • a high-pressure sealing shell 34 is arranged for partially sealing the downstream end section of the high-pressure inner housing 30.
  • a low-pressure sealing shell 44 for partially sealing the upstream end section of the low-pressure inner housing 40 is arranged.
  • the high-pressure sealing shell 34 and the low-pressure sealing shell 44 are arranged adjacent to one another.
  • a further high-pressure sealing shell 35 is arranged for at least partially sealing the downstream end section of the high-pressure inner housing 30.
  • the high-pressure sealing shell 34 is designed and designed in such a way that a predeterminable leakage mass flow emerges through it and can be conducted into the area 110 between the high-pressure sealing shell 34 and the low-pressure sealing shell 44.
  • the sealing shell or the sealing gap can be designed so that a predeterminable leakage mass flow passes through the sealing shell.
  • the high-pressure sealing shell 34 and the low-pressure sealing shell 44 are coordinated with one another in such a way that the leakage mass flow via the high-pressure sealing shell 34 is greater than the leakage mass flow via the low-pressure sealing shell 44.
  • the leakage mass flow via the high-pressure sealing shell 34 is at least 30%, preferably at least 50 % greater than the leakage mass flow through the low-pressure sealing shell 44.
  • Figure 2 shows a detailed view Z Figure 1 . Based on Figure 2 and with reference to Figure 1 and the descriptions made for this purpose, a method according to the invention for operating a steam turbine according to the invention is explained below.
  • a high-pressure sealing shell 34 is arranged at the end portion of the high-pressure inner housing 30.
  • a low-pressure sealing shell 44 is arranged to seal the gap between the upstream end portion of the low pressure inner housing 40 and the shaft 100.
  • the high-pressure sealing shell 34 and the low-pressure sealing shell 44 are arranged adjacent to one another.
  • the process steam is then passed from the first process steam inlet section 31 to the first process steam outlet section 32 and then passed through the first process steam outlet section 32 from the high-pressure inner housing 30 via the process steam deflection section 60 into the gap 70 to the reheater 50.
  • the process steam is passed through the gap 70 for cooling the steam turbine outer housing 20 or the steam turbine 1 along the high-pressure inner housing 30 and along the low-pressure inner housing 40.
  • the heated or superheated process steam is passed from the reheater 50 through the second process steam inlet section 41 into the low-pressure or medium-pressure inner housing. From there, the process steam slides into the further low-pressure inner housing 90 with the expansion direction remaining the same.
  • the low-pressure inner housing 40 and the area 110 of the shaft 100 which lies between the high-pressure sealing shell 34 and the low-pressure sealing shell 44, can be heated locally.
  • an opening in the high-pressure inner housing 30 and a corresponding pipeline can be provided.
  • the steam can be removed from the inner housing via the high-pressure sealing shell 34 particularly easily and without any additional design effort.
  • the gap in the high-pressure sealing shell 34 must be designed accordingly. The hot steam can then pass from the high-pressure inner housing 30 directly into the space between the first high-pressure sealing shell 34 and the second low-pressure sealing shell 44.
  • the steam that flows out via the high-pressure sealing shell 34 has almost live steam parameters, it can be used to heat the area 110 between the high-pressure sealing shell 34 and the low-pressure sealing shell 44. This results in a positive temperature distribution in terms of rotor dynamics and rotor mechanics.
  • the pressure on the outside of the low-pressure inner housing 40 is higher than on the inside, the reason for this is the pressure loss in the gap, which leads to intermediate superheating 50.
  • the process steam, which is taken from the high-pressure inner housing 30 and is conducted in the area 110 between the high-pressure sealing shell 34 and the low-pressure sealing shell 44, is thus sucked into the low-pressure inner housing 40 and thereby ensures that the low-pressure inner housing 40 is heated.
  • the high-pressure sealing shell 34 and the low-pressure sealing shell 44 are coordinated so that the process steam which flows out via the high-pressure sealing shell 34 is at least 30%, preferably at least 50% larger than the leakage mass flow via the low-pressure sealing shell 44.
  • the difference in the mass flows results in a blocking mass flow being created, which prevents the penetration of cold steam flowing to the reheater 50 is prevented from entering the high-pressure sealing shell 34.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP19795107.2A 2018-11-13 2019-10-15 Dampfturbine und verfahren zum betreiben derselben Active EP3850194B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018219374.6A DE102018219374A1 (de) 2018-11-13 2018-11-13 Dampfturbine und Verfahren zum Betreiben derselben
PCT/EP2019/077895 WO2020099054A1 (de) 2018-11-13 2019-10-15 Dampfturbine und verfahren zum betreiben derselben

Publications (2)

Publication Number Publication Date
EP3850194A1 EP3850194A1 (de) 2021-07-21
EP3850194B1 true EP3850194B1 (de) 2023-09-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19795107.2A Active EP3850194B1 (de) 2018-11-13 2019-10-15 Dampfturbine und verfahren zum betreiben derselben

Country Status (8)

Country Link
US (1) US11560812B2 (ja)
EP (1) EP3850194B1 (ja)
JP (1) JP7263514B2 (ja)
CN (1) CN113015845B (ja)
BR (1) BR112021008477A2 (ja)
DE (1) DE102018219374A1 (ja)
PL (1) PL3850194T3 (ja)
WO (1) WO2020099054A1 (ja)

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Publication number Publication date
CN113015845A (zh) 2021-06-22
JP2022509766A (ja) 2022-01-24
BR112021008477A2 (pt) 2021-08-03
US11560812B2 (en) 2023-01-24
JP7263514B2 (ja) 2023-04-24
CN113015845B (zh) 2023-08-04
DE102018219374A1 (de) 2020-05-14
WO2020099054A1 (de) 2020-05-22
EP3850194A1 (de) 2021-07-21
US20210396154A1 (en) 2021-12-23
PL3850194T3 (pl) 2024-02-26

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