EP4473196B1 - Turbomaschine mit integriertem drehzahlminderer/vervielfacher - Google Patents

Turbomaschine mit integriertem drehzahlminderer/vervielfacher

Info

Publication number
EP4473196B1
EP4473196B1 EP23705655.1A EP23705655A EP4473196B1 EP 4473196 B1 EP4473196 B1 EP 4473196B1 EP 23705655 A EP23705655 A EP 23705655A EP 4473196 B1 EP4473196 B1 EP 4473196B1
Authority
EP
European Patent Office
Prior art keywords
turbomachine
speed reducer
multiplier
shaft
pressure
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.)
Active
Application number
EP23705655.1A
Other languages
English (en)
French (fr)
Other versions
EP4473196A1 (de
Inventor
Roberto Bini
Mario Gaia
Davide Colombo
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.)
Turboden SpA
Original Assignee
Turboden SpA
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 Turboden SpA filed Critical Turboden SpA
Publication of EP4473196A1 publication Critical patent/EP4473196A1/de
Application granted granted Critical
Publication of EP4473196B1 publication Critical patent/EP4473196B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/04—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially axially
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • 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
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • 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
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • 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
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • 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
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • 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
    • F01D25/18—Lubricating arrangements
    • F01D25/20—Lubricating arrangements using lubrication pumps
    • 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/005—Steam engine plants not otherwise provided for using mixtures of liquid and steam or evaporation of a liquid by expansion

Definitions

  • the present invention relates to a turbomachine, for example a turbine or a compressor, provided with an integrated speed reducer/multiplier.
  • the turbine is suitable for thermodynamic steam cycles and is particularly suitable for an organic Rankine cycle (hereinafter also ORC cycle).
  • the compressor may belong to a heat pump system.
  • the speed reducer/multiplier is used to reduce the turbine output speed or to increase the compressor input speed so that the solution is suitable for coupling with a generator or with an industrial electric motor, preferably with 4 poles.
  • thermodynamic cycle is defined as a finite succession of thermodynamic transformations (for example isotherms, isochores, isobars or adiabatic) at the end of which the system returns to its initial state.
  • This cycle can be direct, for example a direct Rankine cycle, in which a thermal source is used for the production of mechanical/electrical energy and heat at a lower temperature than that of the thermal source.
  • the thermodynamic cycle can also be of the inverse type, for example a heat pump cycle, in which a mechanical/electrical energy source is used together with a thermal source to produce heat at a higher temperature than that of the thermal source.
  • an ideal Rankine cycle in its simplest version is a thermodynamic cycle composed of two adiabatic transformations and two isobaric transformations, characterized by the fact that the working fluid undergoes changes of state, from liquid to gaseous and vice versa.
  • a direct cycle its purpose is to transform heat into work.
  • This cycle is generally adopted above all in thermoelectric plants for the production of electricity and uses water as the driving fluid, both in liquid form and in the form of steam, with the so-called steam turbine.
  • ORC organic Rankine cycles
  • the plant for an ORC cycle includes one or more pumps to feed the organic working fluid, one or more heat exchangers to carry out the preheating, vaporization and possible superheating or heating phases in supercritical conditions of the same working fluid, a vapor turbine for the expansion of the fluid, mechanically connected to an electric generator, a condenser which returns the organic working fluid to the liquid state and a possible regenerator to recover the heat downstream of the turbine and upstream of the condenser.
  • a speed reducer is normally placed between the turbine and the electric generator in order to reduce the speed of the turbine shaft to values suitable for operating the electric generator.
  • a heat pump cycle envisages a compressor which, by absorbing energy from an electric motor, raises the pressure of the working fluid; a condenser in which the working fluid condenses and transfers heat to the user, a throttling valve (or in any case an expander) in which the working fluid in the liquid phase expands to a lower pressure and an evaporator in which the working fluid vaporizes by absorbing heat from the low-temperature heat source.
  • a speed multiplier is normally placed between the electric generator and the compressor in order to increase the speed of the electric motor to values suitable for operating the compressor.
  • the critical component in the turbomachine-reducer/multiplier coupling is the rotary seal on the turbomachine shaft which must prevent the working fluid from escaping from inside the turbomachine itself. Furthermore, high rotation speeds of the turbomachine and high process temperatures make the proper functioning of this seal particularly critical.
  • Document CN 107 355 271 A discloses an organic Rankine cycle kilowatt-class power generation device, comprising a turbine, a gearbox, a coupling and a generator; the high-speed shaft of the gear box is directly connected with the center of the turbine; the low-speed shaft of the gear box is connected with the generator. Anyhow, this document does not disclose how to avoid contamination between working fluid and lubrication oil.
  • Document WO 2015/091434 A1 relates to an apparatus for sealing an internal environment of a turbomachine.
  • the apparatus according to the invention relates to a seal on a rotating shaft of a turbomachine.
  • the purpose of the seal is to prevent the escape of a working fluid from the turbomachine into the external environment.
  • Document EP 2 161417 A1 relates generally to the field of a Rankine cycle system and, more particularly, to a system and method for lubricating a screw expander in a Rankine cycle system.
  • the proposed solution (which will preferably be applicable to turbomachine with a power higher than 100 kW) allows to overcome the limits and defects of what is currently available, providing for the use of a rotating seal towards the external environment of the traditional type, such as a so-called mechanical, installed on the slow shaft of a turbomachine. Therefore, this seal will operate under absolutely quiet speed and temperature conditions. Furthermore, the seal is easily replaceable because it is in fact external to the turbomachine itself.
  • a turbomachine is described provided with an integrated speed reducer/ multiplier and a seal downstream of the speed reducer/ multiplier, having the characteristics stated in the independent product claim annexed to the present description.
  • figure 1 illustrates a non-limiting embodiment of a turbine equipped with a speed reducer.
  • the reducer will be replaced by a speed multiplier which in fact performs the same function as the reducer but with an inverted power flow mechanics that pass through it.
  • the integrated turbine/reducer system 20 comprises an expansion turbine 1 connected to a speed reducer 2.
  • the speed reducer 2 reduces the rotation speed of the shaft 3 of the turbine to a value suitable for driving a preferably synchronous 4-pole electric generator 18 (of known type) connected to the electric net.
  • a 4-pole generator will rotate at 1500rpm (1800rpm on a 60Hz net) whereas the turbine typically requires a much higher rotational speed, such as 6000rpm (a compressor even higher speeds).
  • the turbine 1 operates in an organic Rankine cycle (ORC) plant.
  • ORC organic Rankine cycle
  • the turbine 1 is an axial turbine and even more preferably it is a multistage axial turbine with the rotor discs mounted cantilevered on the shaft 3 of the turbine 1.
  • the speed reducer 2 is preferably an epicyclic speed reducer in order to keep the input and output shafts of the gear reducer also co-axial.
  • the shaft 3 of the turbine 1 is physically separated from an input shaft 2' of the reducer 2 and is supported by oil-lubricated rolling bearings 4 installed inside the casing 5 of the turbine shaft.
  • the rolling bearings 4 of the shaft 3 of the turbine 1 provide both radial and axial support to the shaft itself.
  • a sealing device 6 is provided, such as for example a labyrinth seal, or in any case a device which does not have a perfect seal, preferably non-contacting seals.
  • This type of seal does not provide a completely hermetic separation of the shaft 3 from the process zone but is suitable for operating at much higher speeds and temperatures than a rotary contact seal. Since inside the turbine there is a slightly higher pressure than that present in the casing 5 (or rather the pressure in the casing 5 is maintained at a slightly lower level than that of the turbine), the environment inside of the casing 5 of the shaft 3 receives a small flow rate of working fluid which mixes with the lubricating oil.
  • the speed reducer 2 is designed to be pressure-tight and is connected to the casing 5 of the shaft 3 via a sealed connection pipe 7', preferably a bellows pipe, so that the pressure inside the speed reducer is equal to the pressure acting on the shaft 3 and there is no communication with the external environment.
  • the speed reducer 2 is also connected to the discharge side of the turbine (or to the suction side in the case of the compressor) via a pressure balancing line 8 in which a compressor 14 is installed, so that it is ensured that the pressure in the inside of the speed reducer 2 is slightly lower than that of the turbine discharge to achieve what was previously said, in order to avoid the entry of lubricating oil into the process area of the turbine 1. In this way lubricating oil infiltrations are avoided inside the process area, while, as already mentioned, there will be small infiltrations of organic working fluid inside the casing 5 of the shaft 3 and the speed reducer 2.
  • the balancing line 8 As an alternative to connecting the balancing line 8 to the discharge side of the turbine, it may be convenient to connect this line to a suitable point in the system (ORC cycle or heat pump) where the pressure is in any case lower than the turbine discharge pressure, to avoid the need for the compressor 14. It is also possible to maintain the pressure value inside the turbine 1 slightly higher than in the reducer 2 through suitable design measures in the turbine, for example with a suitable arrangement of the labyrinths inside the turbine 1 itself.
  • the output shaft 2" of the speed reducer 2 is provided with a double mechanical seal 9, which thus guarantees complete sealing against the external environment.
  • This double mechanical seal 9 works with rotation speeds and with temperatures which are much lower than those inside the turbomachine, thus resulting in a reliable and frequently used component in the industry, for example of rotary pumps, and will preferably be of the type with barrier fluid (typically the same lubricating oil as for bearings and gearbox). Furthermore, this double mechanical seal 9 is in such a position that it is not necessary to disassemble the shaft 3 of the turbine 1 in cases where the seal itself has to be repaired or replaced.
  • the lubricating oil by means of a suitable pump 16, is pumped into a cooler 13 and then into the lubrication circuit, having the function of both lubrication and cooling for the components of the speed reducer (gears, rolling bearings) and for the shaft 3 (and related rolling bearings 4) of the turbine 1.
  • the lubricating oil will be contaminated by the organic working fluid which emerges from the sealing device 6 of the turbine 1 on the basis of the mixing properties of the two fluids. Therefore, a separator 15 can advantageously be installed to separate the organic working fluid from the lubricating oil, thus allowing the lubricating properties of the oil to be kept under control.
  • the separator 15 can be heated to a controlled temperature by means of the coil 21 to improve the separation process.
  • the separated working fluid will be conveniently returned to the ORC (or heat pump) cycle circuit, for example by connecting it to balancing line 8 as in Fig. 1 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (12)

  1. Integriertes System (20) bestehend aus einer Turbomaschine (1) und einem Drehzahlminder-oder Vervielfach-Getriebe (2), wobei:
    - eine Welle (3) der Turbomaschine (1) von einer Eingangswelle (2') des Drehzahlminder-oder Vervielfach-Getriebe (2) getrennt und über eine Kupplung (7) mit dieser verbunden ist,
    - zwischen einem Prozessbereich eines Arbeitsfluides der Turbomaschine (1) und einem Gehäuse (5) der Welle (3) der Turbomaschine (1) ist eine Labyrinthdichtung (6) angeordnet, die das Arbeitsfluid vom Schmieröl des Gehäuses (5) und des Drehzahlminder-oder Vervielfach-Getriebe (2) trennt,
    wobei der Druck im Gehäuse (5) der Welle (3) der Turbomaschine (1) und des Drehzahlminder-oder Vervielfach-Getriebe (2) niedriger ist als der Druck des organischen Arbeitsfluides im Prozessbereich der Turbomaschine, wobei das System (20) ist dadurch gekennzeichnet, dass
    - eine Ausgangswelle (2") des Drehzahlminder-oder Vervielfach-Getriebe (2) ist mit einer mechanischen Dichtung (9) ausgestattet; und
    - dass das System (20) einen Abscheider (15) zur Trennung des Schmieröls vom Arbeitsfluid umfasst.
  2. System (20) nach Anspruch 1, wobei die Turbomaschine eine Expansionsturbine (1) für eine Organic Rankine Cycle (ORC)-Anlage ist.
  3. System (20) nach Anspruch 2, wobei die Expansionsturbine (1) eine mehrstufige Axialturbine ist.
  4. System (20) nach Anspruch 3, wobei die mehrstufige Axialturbine mit freitragend auf der Welle (3) montierten Rotorscheiben ausgestattet ist.
  5. System (20) nach Anspruch 1, wobei die Turbomaschine (1) ein Kompressor für ein Wärmepumpensystem ist.
  6. System (20) nach Anspruch 1, wobei das Drehzahlminder-oder Vervielfach-Getriebe (2) ein Planetengetriebe ist.
  7. System (20) nach einem der vorhergehenden Ansprüche, wobei die Welle (3) der Turbomaschine (1) durch ölgeschmierte Wälzlager (4) im Gehäuse (5) gelagert ist.
  8. System (20) nach einem der vorhergehenden Ansprüche, wobei das Drehzahlminder-oder Vervielfach-Getriebe (2) über eine Druckausgleichsleitung (8) mit der Niederdruckseite der Turbomaschine (1) verbunden ist.
  9. System (20) nach Anspruch 8, wobei an der Ausgleichsleitung (8) eine Vorrichtung (14) vorgesehen ist, die den Druck im Untersetzungs- oder Übersetzungsgetriebe (2) niedriger hält als den Druck in der Turbomaschine (1).
  10. System (20) nach einem der Ansprüche 1 bis 7, wobei das Untersetzungs- oder Übersetzungsgetriebe (2) über eine Druckausgleichsleitung (8) mit einem Punkt der Organic Rankine Cycle-Anlage oder der Wärmepumpenanlage verbunden ist, an dem der Druck niedriger ist als der Auslassdruck der Turbomaschine (1).
  11. System (20) nach einem der vorhergehenden Ansprüche, wobei die Komponenten des Untersetzungs- oder Übersetzungsgetriebe (2) durch Zwangsumlauf von Schmieröl geschmiert und gekühlt werden und ein Schmier- und Kühlkreislauf (17) für das Schmieröl einen Tank (12), eine Pumpe (16) und einen Kühler (13) umfasst.
  12. System (20) nach einem der vorhergehenden Ansprüche, wobei im Schmierkreislauf ein weiterer Abscheider (15) vorhanden ist, wobei solcher Abscheider durch eine Spule (21) auf eine vorgegebene Temperatur erwärmt wird, um die Trennung und Rückgewinnung des Arbeitsfluides vom Schmieröl durch Verdampfung zu erleichtern.
EP23705655.1A 2022-02-02 2023-01-30 Turbomaschine mit integriertem drehzahlminderer/vervielfacher Active EP4473196B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT202200001793 2022-02-02
PCT/IB2023/050793 WO2023148602A1 (en) 2022-02-02 2023-01-30 Turbo machine with integrated speed reducer / multiplier

Publications (2)

Publication Number Publication Date
EP4473196A1 EP4473196A1 (de) 2024-12-11
EP4473196B1 true EP4473196B1 (de) 2025-12-03

Family

ID=81393001

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23705655.1A Active EP4473196B1 (de) 2022-02-02 2023-01-30 Turbomaschine mit integriertem drehzahlminderer/vervielfacher

Country Status (2)

Country Link
EP (1) EP4473196B1 (de)
WO (1) WO2023148602A1 (de)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100034684A1 (en) * 2008-08-07 2010-02-11 General Electric Company Method for lubricating screw expanders and system for controlling lubrication
ITCO20130070A1 (it) * 2013-12-18 2015-06-19 Nuovo Pignone Srl Apparato per realizzare una tenuta di fluido in un ambiente interno di una turbomacchina
CN107355271B (zh) * 2017-07-25 2023-06-09 航天推进技术研究院 一种有机朗肯循环千瓦级发电装置

Also Published As

Publication number Publication date
EP4473196A1 (de) 2024-12-11
WO2023148602A1 (en) 2023-08-10

Similar Documents

Publication Publication Date Title
EP3947922B1 (de) Energieerzeugungssystem und verfahren zur leistungserzeugung durch betrieb eines solchen energieerzeugungssystems
US11293309B2 (en) Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
US8739538B2 (en) Generating energy from fluid expansion
US10267184B2 (en) Valve network and method for controlling pressure within a supercritical working fluid circuit in a heat engine system with a turbopump
KR930008676B1 (ko) 열을 동력으로 변환시키는 동력장치
US8400005B2 (en) Generating energy from fluid expansion
US20230417151A1 (en) Intercooled Cascade Cycle Waste Heat Recovery System
US10677255B2 (en) Dry gas seal cooling arrangement and method
CN111594283B (zh) 一种两级透平气悬浮orc发电系统及控制方法
WO2011058832A1 (ja) エンジン廃熱回収発電ターボシステムおよびこれを備えた往復動エンジンシステム
EP4127435B1 (de) Integrierter hermetisch abgedichteter turboexpander-generator mit fliegendem turbotriebwerk
RU2453731C2 (ru) Винтовая машина, система преобразования энергии и способ преобразования энергии
KR101501852B1 (ko) 회전기 구동 시스템
US20150107249A1 (en) Extracting Heat From A Compressor System
EP4473196A1 (de) Turbomaschine mit integriertem drehzahlminderer/vervielfacher
CN113661307B (zh) 发电系统和通过操作这种发电系统来发电的方法
JPH02252901A (ja) スクリュー膨張機の給油装置
JP7177835B2 (ja) 統合冷却を含む、特にランキンサイクルタイプの閉回路用の電気式ターボポンプアセンブリ

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

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

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

Free format text: ORIGINAL CODE: 0009012

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20240808

AK Designated contracting states

Kind code of ref document: A1

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

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20250707

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

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

REG Reference to a national code

Ref country code: CH

Ref legal event code: F10

Free format text: ST27 STATUS EVENT CODE: U-0-0-F10-F00 (AS PROVIDED BY THE NATIONAL OFFICE)

Effective date: 20251203

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602023009303

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20260303

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20260122

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20260301

Year of fee payment: 4

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20260131

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20260303

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20260121

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1863807

Country of ref document: AT

Kind code of ref document: T

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20260406

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20260403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20251203