EP3167166B1 - System und verfahren zur rückgewinnung von abwärmeenergie - Google Patents

System und verfahren zur rückgewinnung von abwärmeenergie Download PDF

Info

Publication number
EP3167166B1
EP3167166B1 EP14846776.4A EP14846776A EP3167166B1 EP 3167166 B1 EP3167166 B1 EP 3167166B1 EP 14846776 A EP14846776 A EP 14846776A EP 3167166 B1 EP3167166 B1 EP 3167166B1
Authority
EP
European Patent Office
Prior art keywords
working fluid
heat
heat engine
turbine
circuit
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
EP14846776.4A
Other languages
English (en)
French (fr)
Other versions
EP3167166A1 (de
Inventor
Ivan Vladimirovich Nikolin
Viacheslav Vsevolodovich Schuchkin
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
Original Assignee
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
Publication of EP3167166A1 publication Critical patent/EP3167166A1/de
Application granted granted Critical
Publication of EP3167166B1 publication Critical patent/EP3167166B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • 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
    • F01K23/04—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 condensation heat from 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/103—Carbon dioxide
    • 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/106—Ammonia
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/08—Control systems for steam boilers for steam boilers of forced-flow type of forced-circulation type
    • F22B35/083—Control systems for steam boilers for steam boilers of forced-flow type of forced-circulation type without drum, i.e. without hot water storage in the boiler
    • F22B35/086—Control systems for steam boilers for steam boilers of forced-flow type of forced-circulation type without drum, i.e. without hot water storage in the boiler operating at critical or supercritical pressure

Definitions

  • the present invention concerns a system and method for waste heat energy recovery or waste heat energy utilization.
  • waste heat is contained in the flue or exhaust gases of various industrial processes and the exhaust gases of different drives and engines and the net efficiency values in the discussion below are based on waste heat utilization from flue/exhaust gases. This is as distinct from waste heat utilization in solid bodies, such as solar collectors or some other high temperature solid structures, which may produce significantly higher values of net efficiency.
  • Waste heat can be utilized by turbine-generator systems which employ thermodynamic methods, such as the Rankine cycle, to convert heat into work.
  • this method is steam-based with the waste heat being used to raise steam in a boiler to drive a turbine.
  • a key short-coming of a steam-based Rankine cycle is its high temperature requirement; that is, it usually requires a relatively high-temperature waste heat stream (e.g. 300°C or higher) or a very large overall heat content.
  • the complexity of boiling water at multiple pressures/temperatures to capture heat energy at multiple temperature levels as the heat source stream cools is costly.
  • a steam-based Rankine cycle is not a practical option for streams of low flow rate and/or low temperature.
  • the organic Rankine cycle addresses short-comings of a steam-based Rankine cycle by replacing water with a lower-boiling-point fluid, such as a light hydrocarbon like propane or butane, or a HCFC fluid (e.g. R245fa).
  • a lower-boiling-point fluid such as a light hydrocarbon like propane or butane
  • a HCFC fluid e.g. R245fa
  • the boiling heat transfer restrictions remain, however, and new issues such as thermal instability, toxicity or flammability of the fluid arise.
  • ORC organic Rankine cycle
  • widely implementing the organic Rankine cycle (ORC) technology does not permit a utilization of all the waste heat potential due to the limited thermal stability of the organic fluid, which affects thermal efficiency of ORC systems when the waste heat source temperature exceeds 250°-300°C.
  • the total net efficiency of existing ORC units does not exceed a value of about 10%, such that up to 90% of the thermal energy is still wasted to the atmosphere.
  • Supercritical carbon-dioxide (S-CO 2 ) waste heat utilization technology has been used to address some of these issues.
  • the supercritical state of CO 2 provides improved thermal coupling with multiple heat sources and allows for development of more effective (up to 20% net efficiency) and very compact units compared with ORC systems for a variety of applications.
  • Such S-CO 2 systems often require very complex system layouts and unique heat transfer equipment, however, which lead to high capital costs and also technical difficulties. Examples of such known systems for waste heat recovery and utilization are described in the patent publications WO2011/119650A2 , WO2012/074905A2 , WO2012/074911A2 , and WO2012/074940A2 .
  • EP 2 426 435 A2 discloses a cooling installation for low energy consumption, consisting of a primary cooling circuit in which there is an object to be cooled, a compressor, a primary condenser and a primary turbine that drives an electricity generator or is directly coupled to the primary compressor, characterised in that the primary condenser is coupled to a secondary cooling circuit that follows a Rankine cycle or a TFC (Trilateral Flash Cycle system), whereby heat from the primary cooling circuit is utilised in the secondary cooling circuit that contains a secondary turbine that is coupled to an electricity generator, or is directly coupled to the primary compressor, and further contains a secondary condenser and a pressure pump.
  • a primary cooling circuit in which there is an object to be cooled, a compressor, a primary condenser and a primary turbine that drives an electricity generator or is directly coupled to the primary compressor, characterised in that the primary condenser is coupled to a secondary cooling circuit that follows a Rankine cycle or a TFC (Trilateral Flash Cycle system), whereby heat from the primary
  • WO 2013/115668 A1 discloses a heat engine and a method for utilizing waste heat.
  • an object of the present invention is to provide a new and improved system and method for utilizing and/or recovering waste heat energy from a waste heat source, such as flue gases or exhaust gases.
  • the invention provides a system for recovering and/or utilizing waste heat energy from a waste heat source, comprising:
  • the present invention may provide a new system of combined supercritical carbon-dioxide (S-CO 2 ) (first cycle) and ORC (second cycle) waste heat recovery or utilization.
  • the layout of the system may include a single waste heat exchanger and two turbines with respective coolers (heat sinks) and respective pumps/compressors for the first (S-CO 2 ) cycle and the second (ORC) cycle.
  • the invention thus provides a layout which allows high net efficiency (e.g. of about 20%) of waste heat utilization from flue gases with a single waste heat exchanger while avoiding complex known S-CO 2 system layouts that require expensive recuperators for supercritical carbon-dioxide.
  • the first heat engine typically defines a first thermodynamic circuit for circulation of the first working fluid.
  • the first heat engine includes: a first heat exchanger arranged in the first circuit and configured to transfer heat from the waste heat source to the first working fluid, and a second heat exchanger in the first circuit for cooling the first working fluid after an expansion thereof in a turbine of the first heat engine.
  • the second heat exchanger is configured and arranged to transfer residual heat from the first working fluid to the second working fluid in the second heat engine.
  • only the first heat engine obtains heat energy directly from the waste heat exchanger. Heat energy transferred to the second heat engine is non-utilized heat from the first circuit.
  • first cycle cooler/second cycle heater The transfer of heat energy transfer between the two heat engines of this combined cycle system is thus performed in a "first cycle cooler/second cycle heater” device which interfaces or joins the two circuits of the combined cycle.
  • a joint “first (S-CO 2 ) cycle cooler/second (ORC) cycle heater” contributes to heat transfer equipment costs optimization.
  • the “first (S-CO 2 ) cycle cooler/second (ORC) cycle heater” may be represented by a one-piece recuperator in the case where the second (ORC) cycle is operating at supercritical parameters or it may comprise two parts (e.g. preheater and evaporator) for a subcritical second (ORC) cycle.
  • the second heat engine includes a second turbine for expansion of the second working fluid at a position in the second circuit following or downstream of the second heat exchanger. This second turbine converts the heat energy of the second working fluid into work.
  • the second heat engine includes a by-pass conduit or path in the second circuit for by-passing the second turbine.
  • the second heat engine also includes a third heat exchanger for cooling the second working fluid after expansion thereof in the second turbine.
  • the second heat engine includes a fourth heat exchanger which is configured as a recuperator for recuperating heat energy from the second working fluid after an expansion thereof in the second turbine.
  • the fourth heat exchanger is to arranged to transfer heat to the second working fluid at a position in the second circuit adjacent to and/or upstream of the second heat exchanger.
  • the first heat engine includes a fifth heat exchanger for further cooling the first working fluid after expansion thereof in the first turbine, wherein the fifth heat exchanger is arranged or located following or downstream of the second heat exchanger.
  • the invention provides a waste heat utilization system, comprising:
  • the present invention provides a method of recovering and/or utilizing waste heat energy from a waste heat source, comprising:
  • the step of transferring heat from the first working fluid in the first heat engine to the second working fluid in the second heat engine will typically comprise both cooling the first working fluid (i.e. after thermal expansion thereof in a turbine of the first heat engine) and heating the second working fluid in the second heat engine.
  • the method may additionally comprise the step of further cooling the first working fluid after the step of transferring heat from the first working fluid to the second working fluid.
  • the second heat engine includes a second turbine for expansion of the second working fluid at a position in the second circuit following or downstream of the second heat exchanger.
  • the method of the invention preferably further includes cooling the second working fluid in the second heat engine after thermally expanding same in a second turbine.
  • the method includes directing the second working fluid to by-pass the second turbine of the second heat engine, e.g. via a by-pass conduit or path in the second circuit.
  • the secondary ORC cycle can be "turned off” using an ORC turbine bypass valve.
  • the second circuit may operate as a simple cooler of the primary S-CO 2 cycle, thereby providing flexible power management to meet consumer requirements and respond to variations in the waste heat source and environmental parameters.
  • the method further comprises recuperating heat from the second working fluid after expansion thereof in the second turbine, especially by heat transfer to the second working fluid at a position in the second circuit adjacent to and/or upstream of the second heat exchanger.
  • the heat source S may be a waste heat stream, such as gas turbine exhaust, process stream exhaust, or other combustion product exhaust stream, including furnace or boiler exhaust streams.
  • the thermodynamic system 1 may be configured to transform the waste heat into electricity for a range of different applications including but not limited to bottom cycling in gas turbines, diesel engine generator sets, industrial waste heat recovery (e.g. in manufacturing plants, refineries, compression stations), and hybrid alternatives to internal combustion engines.
  • the heat source S could derive thermal energy from renewable sources of thermal energy such as, but not limited to, solar thermal and geothermal sources.
  • the system 1 comprises a first heat engine H1 and a second heat engine H2, each of which defines a respective first and second thermodynamic cycle or circuit A, B for an associated first and second working fluid F1, F2.
  • Each of the first and second heat engines H1, H2 is used to convert thermal energy to work via thermal expansion of the respective first and second working fluid F1, F2.
  • the thermodynamic system 1 comprises a first heat engine H1 having a working fluid circuit A in thermal communication with a waste heat source S via a first heat exchanger E1. While it will be appreciated that any number of heat exchanger devices may be utilized in conjunction with one or more waste heat sources, in this exemplary embodiment the first heat exchanger E1 is a single waste heat exchanger.
  • the first heat exchanger E1 may include multiple stages of a combined waste heat exchanger. While the waste heat source S may be a fluid stream of a high temperature source itself, in other exemplary embodiments the waste heat source S may be a thermal fluid in contact with the high temperature source. The thermal fluid may thus deliver the thermal energy to the waste heat exchanger E1 to transfer the energy to the working fluid F1 in the first circuit A.
  • the first or waste heat exchanger E1 serves as a high temperature, or relatively higher temperature, heat exchanger adapted to receive a flow or stream of the waste heat source S.
  • the initial temperature of the waste heat source S entering the system 1 may range from about 200°C to greater than about 700°C.
  • the stream of the waste heat source S may have a temperature of about 500°C or higher.
  • operative temperatures and pressures and flow rates are given by way of example and are not in any way to be considered as limiting the scope of the disclosure.
  • the working fluid F1 circulated in the first circuit A of the first heat engine H1 is carbon dioxide (CO 2 ).
  • CO 2 carbon dioxide
  • Carbon dioxide as a working fluid for power generating cycles has many advantages. It is a neutral working fluid that is non-toxic, non-flammable, low cost, readily available, and has no need of recycling. Due in part to its relative high working pressure, a CO 2 system can be built that is much more compact than systems using other working fluids. The high density and volumetric heat capacity of CO 2 with respect to other working fluids makes it more "energy dense” meaning that the size of all system components can be considerably reduced without losing performance.
  • carbon dioxide as used herein is not intended to be limited to CO 2 of any particular type, purity, or grade. In an exemplary embodiment, for example, an industrial grade CO 2 may be used without departing from the scope of this disclosure.
  • the carbon dioxide (CO 2 )first working fluid F1 circulated in the first circuit A of the first heat engine H1 is delivered in a pressurized state to the waste heat exchanger E1 via a first pump or compressor P1 which is arranged in the first circuit A.
  • the CO 2 first working fluid F1 is heated in the waste heat exchanger E1 by thermal contact with the waste heat source S.
  • the compressed and heated CO 2 then undergoes an expansion in a first turbine T1 which converts a portion of the thermal energy in the working fluid F1 drawn from the waste heat source S into mechanical work.
  • a first generator G1 operably coupled to the first turbine T1 may then transform that mechanical work into electrical energy.
  • the second heat engine H2 defines a second thermodynamic cycle or circuit B, specifically an organic Rankine cycle (ORC), in which a second working fluid F2, such as a light hydrocarbon (e.g. propane or butane, or a HCFC fluid) circulates.
  • ORC organic Rankine cycle
  • the second heat exchanger E2 is effectively arranged in both the first circuit A and the second circuit B and is adapted or configured to transfer heat energy remaining in the carbon dioxide working fluid F1 after its expansion in turbine T1 to the second working fluid F2 of the second heat engine H2.
  • the CO 2 working fluid F1 may only have a temperature in the range of 70°C to 250°C, and preferably 100°C to 200°C, on entry to the second heat exchanger E2, the relatively low boiling temperature of the second working fluid F2 in the ORC heat engine H2 still enables that heat energy to be recovered very effectively.
  • the first working fluid F1 completes the first circuit A by returning to the first pump or compressor P1 to again be pressurized downstream of the waste heat exchanger E1.
  • the ORC working fluid F2 circulated in the second circuit B of the second heat engine H2 is delivered in a pressurized state to the second heat exchanger E2 via a second pump or compressor P2 arranged in the second circuit B.
  • the second working fluid F2 is heated by thermal contact with the first working fluid F1 in the second heat exchanger E2.
  • the compressed and heated ORC working fluid F2 then undergoes an expansion in a second turbine T2 which converts a portion of the thermal energy in the second working fluid F2 into work.
  • a second generator G2 which is operably coupled to the second turbine T2 may transform that work into electrical energy.
  • a third heat exchanger E3 is provided as a cooler in the second (ORC) circuit B for cooling the ORC working fluid F2.
  • the third heat exchanger E3 may be fluidly connected with a heat sink S2, optionally including a forced convection device (e.g. fan) or a cooling tower arrangement.
  • a forced convection device e.g. fan
  • the second working fluid F2 is cooled prior to returning in the ORC circuit B to be pressurized again via the second pump or compressor P2 downstream of the second heat exchanger E2.
  • the second circuit B includes a by-pass path or conduit BP with by-pass valve V arranged in parallel with the path through the second turbine T2.
  • This by-pass path BP enables the turbine T2 of the ORC heat engine H2 to be by-passed and effectively deactivated via the by-pass valve V.
  • the second circuit B may operate as a simple cooling circuit form the primary S-CO 2 circuit A, thereby allowing flexible power management to meet consumer requirements and to respond to variation in the waste heat source S and/or to environmental parameters.
  • the preferred embodiment illustrated in Fig. 1 thus provides a simple layout of a combined S-CO 2 and ORC system 1 which allows for flexible operation during waste heat recovery and utilization with high efficiency.
  • the heat engine layout in the system 1 of Fig. 1 has at least two continuously arranged non-regenerative cycles A, B with single waste heat exchanger E1 and internal heat transfer to a secondary ORC cycle in the cooler of the primary S-CO 2 cycle having high net efficiency of the combined system (e.g. up to 20%) comparable with much more complex S-CO 2 prior art systems.
  • FIG. 2 of the drawings another preferred embodiment of a waste heat recovery and utilization system 1 according to the invention is illustrated schematically.
  • the general arrangement of the first and second heat engines H1, H2 in the system 1 remains substantially unchanged, but the second heat engine H2 itself differs from the embodiment in Fig. 1 in that it includes a fourth heat exchanger E4 which is configured as a recuperator for recuperating heat energy from the second working fluid F2 after an expansion thereof in the second turbine T2.
  • the fourth heat exchanger E4 forms a thermal interface in the second circuit B between the second fluid F2 as it exits the second turbine T2 and the second fluid F2 before it enters the second heat exchanger E2.
  • the arrangement uses residual heat in the second fluid F2 after its expansion in the turbine to pre-heat the second fluid F2 at a later or downstream position in the second circuit B adjacent to the second heat exchanger E2.
  • the recuperator E4 it is possible to increase an internal thermal efficiency of the second ORC heat engine H2 by adding the recuperator E4 to the system layout.
  • the embodiment of the system 1 in drawing Fig. 2 differs from Fig. 1 in that the first heat engine H1 includes another (fifth) heat exchanger E5 fluidly connected to a heat sink S1 for further cooling the first working fluid F1 after expansion in the first turbine T1.
  • the additional heat exchanger or cooler E5 is desirable in the first (S-CO 2 ) circuit A in this case to provide the required temperature at the inlet of the first pump/compressor P1 in order to keep a reasonable value of compression work.
  • the embodiment of the system 1 in Fig. 2 is more complicated than the embodiment of Fig. 1 and requires more heat transfer equipment, it has a higher overall efficiency, offers more flexibility in control, and can be particularly suitable for some applications.
  • Fig. 3 of the drawings a flow diagram is shown that schematically illustrates the steps in a method of recovering and/or utilizing waste heat according to the preferred embodiments of the invention described above with respect to Figs. 1 and 2 .
  • the first box I of Fig. 3 represents the step of providing a supercritical CO 2 first heat engine H1 having a carbon-dioxide (CO 2 )as the first working fluid F1.
  • the second box II then represents the step of providing an organic Rankine cycle (ORC) second heat engine H2 having a light hydrocarbon as second working fluid F2.
  • the third box III represents the step of transferring heat from a waste heat source S to the first working fluid F1 (e.g.
  • the final box IV in Fig. 3 of the drawings represents the step of transferring heat from the first working fluid F1 in the first heat engine H1 to the second working fluid F2 in the second heat engine H2 to cool the CO 2 working fluid F1 after expansion in a turbine T1 of the first heat engine H1.
  • the working fluid in the first circuit A and/or the second circuit B may be a binary, ternary, or other working fluid blend.
  • the working fluid blend or combination can be selected for the unique attributes possessed by the fluid combination within the heat recovery system, as described herein.
  • one such fluid combination includes a liquid absorbent and CO 2 mixture enabling the combined fluid to be pumped in a liquid state to high pressure with less energy input than required to compress CO 2 .
  • the working fluid may be a combination of CO 2 or supercritical carbon dioxide (S-CO 2 ) and one or more other miscible fluids or chemical compounds.
  • the working fluid may be a combination of CO 2 and propane, or CO 2 and ammonia, without departing from the scope of the disclosure.
  • working fluid is not intended to limit the state or phase of matter that the working fluid is in.
  • the working fluid may be in a liquid phase, a gas phase, a supercritical phase, a subcritical state, or any other phase or state at any one or more points within the fluid cycle.
  • the working fluid may be in a supercritical state over certain portions of a circuit or cycle (the "high pressure side"), and in a subcritical state over other portions of the circuit or cycle (the "low pressure side”).
  • an entire circuit or cycle may be operated and controlled such that the working fluid is in a supercritical or subcritical state during circulation of the entire circuit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Claims (11)

  1. System (1) zur Rückgewinnung und/oder Nutzung von Abwärmeenergie aus einer Abwärmequelle (S), das Folgendes umfasst:
    eine erste Wärmekraftmaschine (H1) mit einem ersten Arbeitsfluid (F1), und einen ersten Kreislauf (A) zur Umwälzung des ersten Arbeitsfluids (F1) definierend, wobei die erste Wärmekraftmaschine (H1) für Übertragung von Wärme von der Abwärmequelle (S) zum ersten Arbeitsfluid (F1) ausgelegt und angeordnet ist, und
    eine zweite Wärmekraftmaschine (H2), speziell eine Kraftmaschine mit organischem Rankine-Kreisprozess (ORC), mit einem zweiten Arbeitsfluid (F2), und einen zweiten Kreislauf (B) zur Umwälzung des zweiten Arbeitsfluids (F2) definierend, wobei die zweite Wärmekraftmaschine (H2) für Übertragung von Wärme vom ersten Arbeitsfluid (F1) auf das zweite Arbeitsfluid (F2) ausgelegt und angeordnet ist, speziell zum Kühlen des ersten Arbeitsfluids (F1) nach Ausdehnung davon in einer Turbine (T1) der ersten Wärmekraftmaschine (H1), wobei die erste Wärmekraftmaschine (H1) eine Turbine (tl) und einen ersten Wärmetauscher (E1) im ersten Kreislauf (A) zur Übertragung von Wärme von der Abwärmequelle (S) auf das erste Arbeitsfluid (F1) und einen zweiten Wärmetauscher (E2) im ersten Kreislauf (A) zum Kühlen des ersten Arbeitsfluids (F1) nach einer Ausdehnung davon in der Turbine (T1) der ersten Wärmekraftmaschine (H1) umfasst, wobei der zweite Wärmetauscher (E2) auch im zweiten Kreislauf (B) ist zur Übertragung von Wärme vom ersten Arbeitsfluid (F1) auf das zweite Arbeitsfluid (F2) der zweiten Wärmekraftmaschine (H2), wobei die zweite Wärmekraftmaschine (H2) eine zweite Turbine (T2) zur Ausdehnung des zweiten Arbeitsfluids (F2) an einer Position im zweiten Kreislauf (B) stromabwärts des zweiten Wärmetauschers (E2) umfasst, wobei die zweite Wärmekraftmaschine (H2) einen Umgehungskreis (BP) zum Umgehen der zweiten Turbine (T2) umfasst, wobei der Umgehungskreis ein Ventil (V) zum Regeln des Betriebs davon umfasst, dadurch gekennzeichnet, dass das erste Arbeitsfluid Kohlendioxid ist.
  2. System (1) nach Anspruch 1, wobei die zweite Wärmekraftmaschine (H2) einen dritten Wärmetauscher (E3) zum Kühlen des zweiten Arbeitsfluids (F2) nach Ausdehnung davon in der zweiten Turbine (T2) umfasst.
  3. System (1) nach Anspruch 2, wobei die zweite Wärmekraftmaschine (H2) einen vierten Wärmetauscher (E4) umfasst, der einen Rekuperator im zweiten Kreislauf (B) zum Rückgewinnen von Wärme aus dem zweiten Arbeitsfluid (F2) nach Ausdehnung davon in der zweiten Turbine (T2) bildet.
  4. System (1) nach einem der Ansprüche 1 bis 3, wobei die erste Wärmekraftmaschine (H1) einen fünften Wärmetauscher (E5) zum weiteren Kühlen des ersten Arbeitsfluids (F1) nach Ausdehnung davon in der ersten Turbine (T1) aufweist, wobei der fünfte Wärmetauscher (E5) im ersten Kreislauf (A) anschließend an den oder stromabwärts des zweiten Wärmetauschers (E2) angeordnet ist.
  5. System (1), nach Anspruch 1, wobei das zweite Arbeitsfluid (F2) ein leichter Kohlenwasserstoff, vorzugsweise Propan oder Butan, oder ein CFKW-Fluid ist.
  6. Verfahren zur Rückgewinnung von Abwärme aus einer Abwärmequelle (S), das Folgendes umfasst:
    Bereitstellen einer ersten Wärmekraftmaschine (H1) mit einem ersten Arbeitsfluid (F1), wobei das erste Arbeitsfluid Kohlendioxid (CO2)ist,
    Bereitstellen einer zweiten Wärmekraftmaschine (H2), speziell einer Wärmekraftmaschine mit organischem Rankine-Kreisprozess (ORC), mit einem zweiten Arbeitsfluid (F2);
    Übertragen von Wärme von der Abwärmequelle (S) auf das erste Arbeitsfluid (F1) in der ersten Wärmekraftmaschine (H1), und Übertragen von Wärme vom ersten Arbeitsfluid (F1) in der ersten Wärmekraftmaschine (H1) auf das zweite Arbeitsfluid (F2) in der zweiten Wärmekraftmaschine (H2), speziell zum Kühlen des ersten Arbeitsfluids (F1) nach Ausdehnung in einer Turbine (T1) der ersten Wärmekraftmaschine (H1), und ferner optional Umgehen einer zweiten Turbine (T2) der zweiten Wärmekraftmaschine (H2) über einen Umgehungskreis umfassend.
  7. Verfahren nach Anspruch 6, wobei der Schritt des Übertragens von Wärme vom ersten Arbeitsfluid (F1) in der ersten Wärmekraftmaschine (H1) auf das zweite Arbeitsfluid (F2) in der zweiten Wärmekraftmaschine (H2) sowohl Kühlen des ersten Arbeitsfluids (F1) nach Ausdehnung davon in einer Turbine (T1) der ersten Wärmekraftmaschine (H1) als auch Erwärmen des zweiten Arbeitsfluids (F2) in der zweiten Wärmekraftmaschine (H2) umfasst.
  8. Verfahren nach Anspruch 6 oder Anspruch 7, wobei die zweite Wärmekraftmaschine (H2) eine zweite Turbine (T2) zur Ausdehnung des zweiten Arbeitsfluids (F2) an einer Position stromabwärts des zweiten Wärmetauschers (E2) umfasst.
  9. Verfahren nach einem der Ansprüche 6 bis 8, ferner umfassend Kühlen des zweiten Arbeitsfluids (F2) in der zweiten Wärmekraftmaschine (H2) nach Ausdehnung davon in einer zweiten Turbine (T2).
  10. Verfahren nach einem der Ansprüche 6 bis 9, ferner umfassend Rückgewinnen von Wärme vom zweiten Arbeitsfluid (F2) nach Ausdehnung davon in einer zweiten Turbine (T2), speziell durch Wärmeübertragung auf das zweite Arbeitsfluid (F2) an einer Position angrenzend an und/oder stromaufwärts des zweiten Wärmetauschers (E2).
  11. Verfahren nach einem der Ansprüche 6 bis 10, umfassend weiteres Kühlen des ersten Arbeitsfluids (F1) nach dem Schritt des Übertragens von Wärme vom ersten Arbeitsfluid (F1) auf das zweite Arbeitsfluid (F2).
EP14846776.4A 2014-09-08 2014-09-08 System und verfahren zur rückgewinnung von abwärmeenergie Active EP3167166B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/RU2014/000666 WO2016039655A1 (en) 2014-09-08 2014-09-08 System and method for recovering waste heat energy

Publications (2)

Publication Number Publication Date
EP3167166A1 EP3167166A1 (de) 2017-05-17
EP3167166B1 true EP3167166B1 (de) 2020-11-04

Family

ID=52774512

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14846776.4A Active EP3167166B1 (de) 2014-09-08 2014-09-08 System und verfahren zur rückgewinnung von abwärmeenergie

Country Status (4)

Country Link
EP (1) EP3167166B1 (de)
ES (1) ES2848307T3 (de)
RU (1) RU2673959C2 (de)
WO (1) WO2016039655A1 (de)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600078847A1 (it) * 2016-07-27 2018-01-27 Turboden Spa Ciclo a scambio diretto ottimizzato
JP6363313B1 (ja) * 2018-03-01 2018-07-25 隆逸 小林 作動媒体特性差発電システム及び該発電システムを用いた作動媒体特性差発電方法
US11047265B1 (en) 2019-12-31 2021-06-29 General Electric Company Systems and methods for operating a turbocharged gas turbine engine
US11592009B2 (en) 2021-04-02 2023-02-28 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11644015B2 (en) 2021-04-02 2023-05-09 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11293414B1 (en) 2021-04-02 2022-04-05 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power in an organic rankine cycle operation
US11493029B2 (en) 2021-04-02 2022-11-08 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11359576B1 (en) 2021-04-02 2022-06-14 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11480074B1 (en) 2021-04-02 2022-10-25 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11421663B1 (en) 2021-04-02 2022-08-23 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power in an organic Rankine cycle operation
US11255315B1 (en) 2021-04-02 2022-02-22 Ice Thermal Harvesting, Llc Controller for controlling generation of geothermal power in an organic Rankine cycle operation during hydrocarbon production
US11486370B2 (en) 2021-04-02 2022-11-01 Ice Thermal Harvesting, Llc Modular mobile heat generation unit for generation of geothermal power in organic Rankine cycle operations

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995024822A2 (en) * 1994-03-14 1995-09-21 Ramesh Chander Nayar Multi fluid, reversible regeneration heating, combined cycle
WO2011030285A1 (en) * 2009-09-09 2011-03-17 Andrew Ochse Method and apparatus for electrical power production

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4760705A (en) * 1983-05-31 1988-08-02 Ormat Turbines Ltd. Rankine cycle power plant with improved organic working fluid
RU2000449C1 (ru) * 1990-07-18 1993-09-07 Николай Яковлевич Бутаков Многоконтурна энергетическа установка
US6009711A (en) * 1997-08-14 2000-01-04 Ormat Industries Ltd. Apparatus and method for producing power using geothermal fluid
US8490397B2 (en) * 2009-11-16 2013-07-23 General Electric Company Compound closed-loop heat cycle system for recovering waste heat and method thereof
WO2011119650A2 (en) 2010-03-23 2011-09-29 Echogen Power Systems, Llc Heat engines with cascade cycles
BE1019372A3 (nl) * 2010-06-11 2012-06-05 Schutter Rotterdam B V Koelsysteem met laag energieverbruik.
US20120102996A1 (en) * 2010-10-29 2012-05-03 General Electric Company Rankine cycle integrated with absorption chiller
US8616001B2 (en) 2010-11-29 2013-12-31 Echogen Power Systems, Llc Driven starter pump and start sequence
WO2012074940A2 (en) 2010-11-29 2012-06-07 Echogen Power Systems, Inc. Heat engines with cascade cycles
US8857186B2 (en) * 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
JP5862133B2 (ja) * 2011-09-09 2016-02-16 国立大学法人佐賀大学 蒸気動力サイクルシステム
WO2013115668A1 (en) * 2012-02-02 2013-08-08 Siemens Aktiengesellschaft Heat engine and method for utilizing waste heat
US9145795B2 (en) * 2013-05-30 2015-09-29 General Electric Company System and method of waste heat recovery

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995024822A2 (en) * 1994-03-14 1995-09-21 Ramesh Chander Nayar Multi fluid, reversible regeneration heating, combined cycle
WO2011030285A1 (en) * 2009-09-09 2011-03-17 Andrew Ochse Method and apparatus for electrical power production

Also Published As

Publication number Publication date
WO2016039655A1 (en) 2016-03-17
EP3167166A1 (de) 2017-05-17
RU2017111353A3 (de) 2018-10-10
ES2848307T3 (es) 2021-08-06
RU2017111353A (ru) 2018-10-10
RU2673959C2 (ru) 2018-12-03

Similar Documents

Publication Publication Date Title
EP3167166B1 (de) System und verfahren zur rückgewinnung von abwärmeenergie
US8302399B1 (en) Organic rankine cycle systems using waste heat from charge air cooling
US9115603B2 (en) Multiple organic Rankine cycle system and method
US10934895B2 (en) Heat engine systems with high net power supercritical carbon dioxide circuits
CA2652243C (en) A method and system for generating power from a heat source
AU2010264462B2 (en) System and method for managing thermal issues in one or more industrial processes
CA2820606C (en) Parallel cycle heat engines
US8869531B2 (en) Heat engines with cascade cycles
AU2013240243B2 (en) System and method for recovery of waste heat from dual heat sources
US9341086B2 (en) Cascaded power plant using low and medium temperature source fluid
US9784248B2 (en) Cascaded power plant using low and medium temperature source fluid
US8650879B2 (en) Integration of waste heat from charge air cooling into a cascaded organic rankine cycle system
US20150075164A1 (en) Cascaded power plant using low and medium temperature source fluid
EP3835556B1 (de) Hocheffizienter organischer rankine-zyklus mit flexibler wärmeabgabe
EP3008297B1 (de) Anordnung und verfahren zur nutzung von abwärme
EP3008298B1 (de) Anordnung und verfahren zur nutzung von abwärme
US10526925B2 (en) Supercritical CO2 generation system for series recuperative type
JP2020519842A (ja) 熱源の熱利用効率を高める装置及び方法
RU140274U1 (ru) Тепловая электрическая станция

Legal Events

Date Code Title Description
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: 20170207

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 MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS AKTIENGESELLSCHAFT

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20181106

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: 20200528

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 MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1331067

Country of ref document: AT

Kind code of ref document: T

Effective date: 20201115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014072102

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: 20201104

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1331067

Country of ref document: AT

Kind code of ref document: T

Effective date: 20201104

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

Ref country code: GR

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: 20210205

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: 20210304

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: 20210204

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: 20201104

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: 20201104

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: 20201104

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: 20210204

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: 20210304

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: 20201104

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: 20201104

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: 20201104

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: 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: 20201104

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: 20201104

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: 20201104

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: 20201104

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: 20201104

Ref country code: RO

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: 20201104

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014072102

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2848307

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20210806

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

Ref country code: DK

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: 20201104

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20210805

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

Ref country code: AL

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: 20201104

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: 20201104

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

Ref country code: SI

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: 20201104

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210930

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20210908

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

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: 20210304

Ref country code: MC

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: 20201104

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

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210908

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210908

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210908

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

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

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

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

Ref country code: HU

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

Effective date: 20140908

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

Ref country code: CY

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: 20201104

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

Ref country code: IT

Payment date: 20230920

Year of fee payment: 10

Ref country code: CZ

Payment date: 20230908

Year of fee payment: 10

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

Ref country code: FR

Payment date: 20230926

Year of fee payment: 10

Ref country code: DE

Payment date: 20230928

Year of fee payment: 10

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

Ref country code: ES

Payment date: 20231018

Year of fee payment: 10

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

Ref country code: MK

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: 20201104