EP3155226B1 - Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur - Google Patents

Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur Download PDF

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Publication number
EP3155226B1
EP3155226B1 EP15750771.6A EP15750771A EP3155226B1 EP 3155226 B1 EP3155226 B1 EP 3155226B1 EP 15750771 A EP15750771 A EP 15750771A EP 3155226 B1 EP3155226 B1 EP 3155226B1
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EP
European Patent Office
Prior art keywords
pressure
thrust
steam turbine
partition wall
steam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP15750771.6A
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German (de)
English (en)
Other versions
EP3155226A1 (fr
Inventor
Jan Walkenhorst
Uwe Zander
Armin De Lazzer
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 AG
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Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL15750771T priority Critical patent/PL3155226T3/pl
Publication of EP3155226A1 publication Critical patent/EP3155226A1/fr
Application granted granted Critical
Publication of EP3155226B1 publication Critical patent/EP3155226B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status 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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
    • 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
    • F01D25/12—Cooling
    • 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
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
    • 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
    • F05D2240/00—Components
    • F05D2240/55—Seals
    • F05D2240/56—Brush seals
    • 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
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
    • F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam

Definitions

  • the invention relates to a steam turbine comprising an inner housing and an outer housing and a rotor which is rotatably mounted within the inner housing, wherein the outer housing is arranged around the inner housing, wherein the rotor arranged along a first flow direction high-pressure region and along a second flow direction having arranged medium-pressure region.
  • the invention further relates to a method for cooling a steam turbine, wherein the steam turbine has a high-pressure region and a medium-pressure region, wherein a rotor is arranged between the high-pressure region and the medium-pressure region and has a thrust balance intermediate bottom.
  • a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
  • gas turbines are traversed with gas and / or air as the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
  • gas turbines has steam turbines z.
  • An open cooling system which is open to the flow channel, can also be implemented in the case of gas turbines without partial turbine-external supply of cooling medium.
  • an external supply for cooling medium should be provided. The prior art relating to gas turbines can not therefore be used for the assessment of the present application subject.
  • a steam turbine typically comprises a rotor-mounted rotatably mounted rotor disposed within a housing.
  • the rotor When flowing through the interior of the flow channel formed by the housing jacket with heated and pressurized steam, the rotor is rotated by the steam through the blade.
  • the blades of the rotor are also referred to as blades.
  • usually stationary guide vanes are suspended on the inner housing, which engage along an axial extent of the body in the interspaces of the rotor blades.
  • a vane is typically held at a first location along an interior of the steam turbine casing. In this case, it is usually part of a stator blade row, which comprises a number of guide vanes which are arranged along an inner circumference on an inner side of the steam turbine housing.
  • Each vane has its blade radially inward.
  • a row of vanes at said first location along the axial extent is also referred to as a vane grille or ring.
  • a number of vane rows are connected in series. Accordingly, at a second location along the axial extent behind the first location, a further second blade is held along the inside of the steam turbine housing.
  • a pair of a vane row and a blade row is also referred to as a vane stage.
  • the housing jacket of such a steam turbine can be formed from a number of housing segments.
  • the housing shell of the steam turbine is to be understood as meaning, in particular, the stationary housing component of a steam turbine or a partial turbine which has an interior in the form of a flow channel along the longitudinal direction of the steam turbine, which is provided for flowing through with the working medium in the form of steam.
  • this can be an inner casing and / or a guide vane carrier.
  • Embodiments are known in which the first flow channel is designed for high-pressure blading and the second flow channel is designed for medium-pressure blading.
  • the directions of flow of the first flow channel and the second flow channel in this case show in the opposite direction to thereby minimize the thrust balance.
  • such designs include a rotor formed with a high-pressure region and a medium-pressure region, which is mounted rotatably within an inner housing, wherein an outer housing is arranged around the inner housing.
  • the high pressure area is designed for live steam temperatures. After flowing through the live steam through the high-pressure area, the steam flows to a reheater and is there brought to a higher temperature and then flows through the medium-pressure region of the steam turbine.
  • the invention begins, whose object is to provide a steam turbine and a method for their production, in which the steam turbine is cooled particularly effectively even in the high temperature range.
  • the object is achieved by a steam turbine according to claim 1 and by a method according to claim 9.
  • An essential idea of the invention is to form a passive cooling.
  • the invention is geared to a steam turbine in the aforementioned compact design.
  • This means that the steam turbine within a common outer housing has a high-pressure area and a medium-pressure area.
  • the high pressure area is designed for live steam temperatures.
  • the live steam temperatures are between 530 ° C and 720 ° C at a pressure of 80-350 bar.
  • the medium pressure range is designed for temperatures in the input range of 530-750 ° C at a pressure of 30-120 bar.
  • a live steam initially flows through a partial turbine designed for live steam. After flowing through the live steam through the high-pressure area, this flows to a reheater and is heated there to the medium-pressure inlet temperatures and then flows through the medium-pressure range. After flowing through the medium-pressure region of the steam flows to a low pressure region and there has lower steam parameters.
  • An essential idea of the invention is now to design the steam turbine in such a way that a thrust balance intermediate floor can be passively cooled.
  • a thrust balance intermediate floor can be passively cooled.
  • a branched off from the high-pressure flow channel at a suitable location from the flow channel which is guided to a point for thrust balance intermediate floor.
  • This steam can then in the area between thrust balance intermediate floor and the Inner case spread out.
  • Another essential idea of the invention is that the aforementioned steam can mix with a part of the live steam, which can then be guided back to the first flow channel via a cross-return channel.
  • the first high-pressure blade stage is arranged in front of the second high-pressure blade stage as seen along the first flow direction.
  • the steam taken from the first high-pressure blade stage has higher steam parameters than the steam taken from the second high-pressure blade stage.
  • a target-oriented suitable steam can be taken from the high pressure blading area.
  • the first thrust balance piston intermediate floor space along the first flow direction is arranged in front of the second thrust balance intermediate floor space. Since the thermal load of the thrust balance intermediate floor is different, the invention provides that a better cooling possibility is possible if the first thrust balance intermediate floor space along the first flow direction is arranged in front of the second thrust balance intermediate floor space.
  • a first brush seal is arranged between the inner housing and the thrust balance intermediate bottom along the second flow direction before the second thrust compensation intermediate floor space and a second brush seal along the second flow direction behind the first thrust compensation intermediate floor space.
  • the thermal compensation can be optimized.
  • connection is formed with connecting tubes, this also leads to an advantageous temperature compensation.
  • the steam turbine is formed with a second cross-return channel, which is arranged as a communicating tube between a third thrust balance intermediate bottom space formed between the thrust balance intermediate bottom and the inner housing and after a third high-pressure blade stage.
  • the third high-pressure blade stage is arranged behind the second high-pressure blade stage.
  • the thrust balance intermediate floor can be optimally cooled.
  • FIG. 1 shows a steam turbine 1 comprising an inner housing 2 and an outer housing 3 and a rotor 4.
  • the rotor 4 is rotatably mounted within the inner housing 2.
  • the storage is not shown in detail.
  • the outer housing 3 is arranged around the inner housing 2.
  • the rotor 4 is formed substantially rotationally symmetrical about the axis of rotation 5.
  • the rotor 4 has a high-pressure region 7.
  • the rotor 4 has a medium-pressure region 9 which is arranged along the second flow direction 8.
  • the inner housing 2 has in the high-pressure region 7 a plurality of high pressure guide vanes (not shown), which are arranged on the circumference about the axis of rotation 5.
  • the high-pressure guide vanes are arranged such that along the first flow direction 6, a high pressure flow passage 10 is formed with a plurality of high pressure blade stages (not shown) each having a row of high pressure blades and a series of high pressure vanes.
  • Fresh steam flows into the steam turbine 1 via a first high-pressure inflow region 11 and then flows through the high-pressure flow channel 10.
  • the steam expands, the temperature decreasing.
  • the thermal energy of the steam is converted into rotational energy of the rotor 4.
  • the steam flows from a high pressure discharge area 12 from the steam turbine 1 to a reheater (not shown).
  • the reheater the cooled steam is brought back to a high temperature which is comparable to the live steam temperature in the high-pressure inflow region.
  • the pressure in the inflow region 11 is significantly lower.
  • the inner housing 2 has in the central pressure region 9 a plurality of medium-pressure guide vanes (not shown), which are arranged such that along the second flow direction 8, a medium-pressure flow channel 13 with a plurality of medium-pressure blade stages (not shown), each having a series medium-pressure blades and a number of medium-pressure vanes is formed.
  • the steam after the reheater flows through the medium-pressure inflow region 14 through the medium-pressure flow channel 13.
  • the thermal energy of the steam is converted into rotational energy of the rotor 4.
  • the steam flows out of the steam turbine 1 via an outlet 15.
  • the steam is then forwarded to a low pressure turbine part (not shown) or a process steam process.
  • the rotor 4 has between the high-pressure flow channel 10 and the medium-pressure flow channel 13 to a thrust balance intermediate bottom 16. This thrust balance intermediate bottom 16 has a larger diameter than the rotor 4th
  • the live steam temperature is 530 ° C - 720 ° C at a pressure of 80bar - 350bar.
  • the mean pressure temperature is 530 ° C - 750 ° C at a pressure of 30bar - 120bar.
  • FIG. 2 shows a section of the steam turbine 1 from FIG. 1 , wherein further features of the invention in FIG. 2 are shown.
  • the inner housing 2 has a connection 17 which is arranged as a communicating tube between the high-pressure flow channel 10 after a first high pressure vane stage 18 and a first thrust balance intermediate bottom space 19, wherein the thrust balance intermediate bottom space 19 between the thrust balance intermediate bottom 16 and the inner housing 2 is arranged.
  • the inner housing 2 has a plurality of segments 20 in the region of the thrust balance intermediate floor 16. The segments 20 each have a labyrinth seal (not shown).
  • the inner housing 2 further includes a first cross recirculation passage 21 disposed as a communicating tube between a second thrust balance intermediate floor space 19 (located between the thrust balance intermediate floor 16 and the inner housing 2) and after a second high pressure paddle stage 22.
  • the first high-pressure vane stage 18 is arranged in front of the second high-pressure vane stage 23 along the first flow direction 6.
  • the first thrust balance intermediate floor space 19 is arranged in front of the second thrust balance intermediate floor space 22 as seen along the first flow direction 6.
  • first brush seal 24 along the second flow direction 8 before the second thrust balance intermediate floor space 22 arranged.
  • a second brush seal 25 is arranged along the second flow direction 8 behind the first thrust balance intermediate floor space 16.
  • the first cross recirculation passage 21 may be formed with tubes (not shown) in alternative embodiments. In the in the FIG. 2 illustrated embodiment, the cross return passage 21 is disposed in the inner housing 2.
  • the compound 17 is in the in FIG. 2 selected embodiment in the inner housing 2 is formed and in alternative embodiments, the connection 17 may be formed with connecting tubes.
  • the steam turbine 1 has a second cross recirculation passage 26 which is formed as a communicating tube between a third thrust balance intermediate bottom space 27, which is arranged between the thrust balance intermediate bottom 16 and the inner housing 2 and arranged after a third high-pressure blade stage 28 high-pressure inflow space in the high-pressure flow channel 10 ,
  • the third high-pressure blade stage 28 is arranged behind the second high-pressure blade stage 23 as seen in the first flow direction 6.
  • the cross-return passage 26 may be formed in the inner housing 20. In alternative embodiments, the third cross return passage 26 may be formed as a tube.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)

Claims (10)

  1. Turbine (1) à vapeur comprenant
    une carcasse (2) intérieure et une carcasse (3) extérieure ainsi qu'un rotor (4), monté tournant dans la carcasse (2) intérieure,
    la carcasse (3) extérieure étant disposée autour de la carcasse (2) intérieure,
    dans laquelle le rotor (4) a une partie (7) de haute pression, disposée suivant un premier sens (6) d'écoulement et une deuxième partie (9) de moyenne pression, disposée suivant un deuxième sens (8) d'écoulement,
    dans laquelle la carcasse (2) intérieure a plusieurs aubes directrices de haute pression, dans la partie (7) de haute pression,
    qui sont disposées
    de manière à former, dans le premier sens (6) d'écoulement, un canal (10) d'écoulement de haute pression ayant plusieurs étages d'aubes de haute pression, qui ont chacune une série d'aubes mobiles de haute pression et une série d'aubes directrices de haute pression,
    dans laquelle la carcasse (2) intérieure a, dans la partie (9) de moyenne pression, plusieurs aubes directrices de moyenne pression,
    qui sont disposées
    de manière à former, suivant le deuxième sens (8) d'écoulement, un conduit d'écoulement de moyenne pression ayant plusieurs étages d'aubes de moyenne pression, qui ont chacune une série d'aubes directrices de moyenne pression et une série d'aubes directrices de moyenne pression,
    dans laquelle le rotor (4) a un fond (16) intermédiaire de compensation de poussée, entre la partie (7) de haute pression et la partie (9) de moyenne pression,
    caractérisée en ce que
    la carcasse (2) intérieure a une liaison (17), qui est constituée sous la forme d'un tuyau communiquant, entre le canal (10) d'écoulement de haute pression, après un premier étage (18) d'aubes de haute pression, et un premier espace (19) de fond intermédiaire de compensation de poussée,
    dans laquelle la carcasse (2) intérieure a un premier canal (21) de retour en croix, qui est formée sous la forme d'un tuyau communiquant, entre un deuxième espace (22) intermédiaire de compensation de poussée, qui est disposé entre le fond (16) intermédiaire de compensation de poussée et la carcasse (2) intérieure, et un canal (10) d'entrée de haute pression, disposé après un deuxième étage (23) d'aubes de haute pression du canal (10) d'écoulement de haute pression.
  2. Turbine (1) à vapeur suivant la revendication 1,
    dans laquelle le premier étage (18) d'aubes de haute pression est disposé, considéré suivant le premier sens (6) d'écoulement, avant le deuxième étage (23) d'aubes de haute pression.
  3. Turbine (1) à vapeur suivant la revendication 1 ou 2,
    dans laquelle le premier espace (19) de fond intermédiaire de compensation de poussée est disposé, considéré suivant le premier sens (6) d'écoulement, avant le deuxième espace (22) de fond intermédiaire de compensation de poussée.
  4. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    dans laquelle, entre la première carcasse (22) intérieure et le fond (16) intermédiaire de compensation de poussée, est disposée une première étanchéité (24) à brosse, suivant le deuxième sens (8) d'écoulement, avant le deuxième espace (22) de fond intermédiaire de compensation de poussée et une deuxième étanchéité (25) à brosse, derrière, suivant le deuxième sens (8) d'écoulement, le premier espace (19) de fond intermédiaire de compensation de poussée.
  5. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    dans laquelle le premier canal (21) de retour en croix est constitué de tuyaux.
  6. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    dans laquelle la liaison (17) est constituée de tuyaux de liaison.
  7. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    comprenant un deuxième canal (26) de retour en croix, qui est sous la forme d'un tuyau communiquant entre un troisième espace (27) de fond intermédiaire de compensation de poussée, disposé entre le fond (16) intermédiaire de compensation de poussée et la carcasse (2) intérieure,
    et un espace d'entrée de haute pression, disposé après un troisième étage (28) d'aubes de haute pression, du canal (10) d'écoulement de haute pression.
  8. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    dans laquelle le troisième étage (28) d'aubes de haute pression est disposé, considéré dans le premier sens (6) d'écoulement, derrière, le deuxième étage (23) d'aubes de haute pression.
  9. Procédé de refroidissement d'une turbine (1) à vapeur,
    dans lequel la turbine (1) à vapeur a une partie (7) de haute pression, une partie (9) de moyenne pression, un rotor (2) ayant un fond (16) intermédiaire de compensation de poussée, entre la partie (7) de haute pression et la partie (9) de moyenne pression, dans lequel on prélève de la vapeur de la partie (7) de haute pression et on l'envoie à un espace compris entre le fond (16) intermédiaire de compensation de poussée et une carcasse (2) intérieure, caractérisé
    en ce que l'on envoie de la vapeur de l'espace compris entre le fond (16) intermédiaire de compensation de poussée et la carcasse (2) intérieure à la partie (7) de haute pression par l'intermédiaire d'un canal (21) de retour en croix.
  10. Procédé suivant la revendication 9,
    dans lequel on envoie de la vapeur supplémentaire entre le fond (16) intermédiaire de compensation de poussée et la carcasse (2) intérieure, par l'intermédiaire d'un deuxième canal (26) de retour en croix, dans la partie (7) de haute pression.
EP15750771.6A 2014-08-20 2015-08-19 Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur Not-in-force EP3155226B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15750771T PL3155226T3 (pl) 2014-08-20 2015-08-19 Turbina parowa i sposób eksploatacji turbiny parowej

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14181559.7A EP2987952A1 (fr) 2014-08-20 2014-08-20 Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur
PCT/EP2015/068991 WO2016026880A1 (fr) 2014-08-20 2015-08-19 Turbine à vapeur et procédé pour faire fonctionner une turbine à vapeur

Publications (2)

Publication Number Publication Date
EP3155226A1 EP3155226A1 (fr) 2017-04-19
EP3155226B1 true EP3155226B1 (fr) 2018-08-15

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EP14181559.7A Withdrawn EP2987952A1 (fr) 2014-08-20 2014-08-20 Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur
EP15750771.6A Not-in-force EP3155226B1 (fr) 2014-08-20 2015-08-19 Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur

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EP14181559.7A Withdrawn EP2987952A1 (fr) 2014-08-20 2014-08-20 Turbine à vapeur et procédé de fonctionnement d'une turbine à vapeur

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US (1) US10436030B2 (fr)
EP (2) EP2987952A1 (fr)
JP (1) JP6416382B2 (fr)
KR (1) KR101949058B1 (fr)
CN (1) CN106574502B (fr)
BR (1) BR112017002944A2 (fr)
PL (1) PL3155226T3 (fr)
RU (1) RU2655068C1 (fr)
WO (1) WO2016026880A1 (fr)

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EP3453848A1 (fr) * 2017-09-08 2019-03-13 Siemens Aktiengesellschaft Turbine à vapeur dotée d'une chambre de piquage
CN109826675A (zh) * 2019-03-21 2019-05-31 上海电气电站设备有限公司 汽轮机冷却系统及方法
CN113047911B (zh) * 2021-03-10 2022-01-14 东方电气集团东方汽轮机有限公司 一种推力平衡结构

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JP2017525887A (ja) 2017-09-07
RU2655068C1 (ru) 2018-05-23
KR101949058B1 (ko) 2019-02-15
KR20170043590A (ko) 2017-04-21
US20170234131A1 (en) 2017-08-17
CN106574502A (zh) 2017-04-19
EP2987952A1 (fr) 2016-02-24
CN106574502B (zh) 2018-04-13
US10436030B2 (en) 2019-10-08
WO2016026880A1 (fr) 2016-02-25
PL3155226T3 (pl) 2019-01-31
JP6416382B2 (ja) 2018-10-31
BR112017002944A2 (pt) 2017-12-05
EP3155226A1 (fr) 2017-04-19

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