EP4083393A1 - Kogenerativer rankine kreislauf mit dampfentnahme aus der turbine - Google Patents

Kogenerativer rankine kreislauf mit dampfentnahme aus der turbine Download PDF

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Publication number
EP4083393A1
EP4083393A1 EP21212837.5A EP21212837A EP4083393A1 EP 4083393 A1 EP4083393 A1 EP 4083393A1 EP 21212837 A EP21212837 A EP 21212837A EP 4083393 A1 EP4083393 A1 EP 4083393A1
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EP
European Patent Office
Prior art keywords
working fluid
rankine cycle
organic
cycle plant
organic rankine
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.)
Pending
Application number
EP21212837.5A
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English (en)
French (fr)
Inventor
Mario Gaia
Roberto Bini
Andrea Duvia
Claudio Pietra
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 EP4083393A1 publication Critical patent/EP4083393A1/de
Pending legal-status Critical Current

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    • 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
    • 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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic

Definitions

  • the present invention relates to an innovative cogenerative organic Rankine cycle plant with steam extraction from the turbine.
  • thermodynamic cycle is defined as a finite succession of thermodynamic (for example isothermal, isochoric, isobaric or adiabatic) transformations at the end of which the system returns to its initial state.
  • thermodynamic for example isothermal, isochoric, isobaric or adiabatic
  • an ideal Rankine cycle is a thermodynamic cycle made of two adiabatic and two isobaric transformations, with two phase changes, from liquid to vapor and from vapor to liquid. Its purpose is to turn heat into work.
  • This cycle is generally adopted mainly in thermoelectric power plants for the production of electricity and uses water as the driving fluid, both in liquid and steam form, and the corresponding expansion takes place in the so-called steam turbine.
  • ORC organic Rankine cycles
  • ORC cycles include, by way of example, one or more pumps for feeding the organic working fluid, one or more heat exchangers for carrying out the preheating, vaporization and eventually superheating or heating phases in supercritical conditions of the same working fluid, a steam turbine for the expansion of the fluid, mechanically connected to an electric generator or an operating machine.
  • ORC cycles are also used for the production of electrical energy and for exploitation of the heat recovered from the organic working fluid in the condenser.
  • Cogeneration This is the well-known cogeneration process which provides for the simultaneous production of mechanical energy (usually transformed into electrical energy) and heat.
  • the heat produced can be used, for example, for heating or district heating of buildings and/or for production-industrial processes.
  • Cogeneration uses traditional generation systems, internal combustion engines, water steam turbines, gas turbines, combined cycles and ORC cycles.
  • a medium-high temperature cogeneration means the production of steam, water, air or any other liquid or gaseous substance, at a temperature higher than 50-60 C, i.e. higher than the temperatures at which a cooling fluid of the condenser could be maintained, should said fluid be cooled by giving heat directly to the environment (for example with an ambient temperature of 15°C, a cooling fluid could be cooled down up to 18-25°C) .
  • the solution to be adopted is to adapt the condensing temperature to the temperature requested by the heat user.
  • the condensation temperature increases (i.e. in order to satisfy heat users at temperatures equal to or higher than the minimum ones that could be obtained by transferring heat directly to the environment) the thermodynamic conversion efficiency decreases (based on the second principle of thermodynamics).
  • the aim of the present invention is therefore to define an organic Rankine cycle plant of the partially cogenerative type for delivering heat to a heat user.
  • the heat supplied to the heat user is obtained using both a partial flow of organic working fluid vapor extracted from an intermediate stage of the expansion phase in at least one turbine, and a partial flow of a primary heat source, for example a geothermal source, used as a primary heat source for the organic working fluid of the ORC plant.
  • a primary heat source for example a geothermal source
  • the two heat sources feed two separate heat exchangers (for example, an additional condenser for the vapor of the organic working fluid extracted during expansion and a high temperature heat exchanger for the partial flow of the primary heat source) placed in series and in counter-flow with respect to the heat carrier of the user.
  • two separate heat exchangers for example, an additional condenser for the vapor of the organic working fluid extracted during expansion and a high temperature heat exchanger for the partial flow of the primary heat source
  • the organic working fluid vapor extracted during expansion will have a lower temperature than the temperature of the partial flow of the primary heat source.
  • the present invention defines a partially cogenerative organic Rankine cycle with steam extraction from the turbine, according to independent claim 1.
  • a cogenerative organic Rankine cycle plant 100 according to the present invention is shown in Figure 1 and comprises, in fluid-dynamic connection between them, along a main path 5:
  • the organic cogenerative Rankine cycle plant 100 also includes:
  • the mixing point can be decided either at the design level or it can be adjusted by arranging several inlet points in the preheater 60 and by deciding where to convey the partial flow of the organic working fluid coming from the further condenser 45 by means of suitable valves.
  • the second option is preferable if the working conditions and temperatures of the cogeneration heat user change over the course of the year.
  • a second branch line 75 is provided, equipped with a regulation valve VI, in which a partial flow of the geothermal source flows which feeds a heat exchanger 80 at high temperature.
  • the partial flow withdrawal from the geothermal source that feeds the heat exchanger 80 may be either:
  • the return point of the geothermal source withdrawn after having been cooled in the heat exchanger 80 may also be either:
  • the criterion for deciding at which point to withdraw and return to the path 70 the flow rate of the geothermal source that releases heat to the heat exchanger 80 is conveniently defined in order to subtract the heat required at the minimum possible temperature (compatibly with the needs of the heat exchanger 80 and therefore of the heat user), it being evident that a withdrawal at a point of the circuit 70 where the temperature is lower and a return at a point of the circuit 70 where the temperature is higher favor the thermodynamic cycle that feeds the turbine and therefore improve the system efficiency.
  • the heat supplied to the heat user for example a district heating plant
  • a partial flow of organic working fluid vapor extracted from an intermediate stage of the expansion phase for example at the outlet of the turbine 20
  • a partial flow of the primary heat source for example a geothermal source, used as a primary heat source for the organic working fluid of the ORC plant.
  • the two heat sources feed two separate heat exchangers which transmit the heat to a heat user, for example to the working fluid of a district heating system which flows along a path 85 from a TELE IN inlet end to a TELE OUT outlet end.
  • such heat exchangers are the further condenser 45 in which the working fluid of the district heating system and the partial flow of the organic working fluid vapor extracted downstream of a first expansion and the heat exchanger 80 at a high temperature, in which the working fluid of the district heating system and the partial flow of the geothermal source are flowing in countercurrent.
  • the further condenser 45 and the heat exchanger 80 are placed in series and in countercurrent with respect to the heat carrier of the user.
  • the partial flow of the organic working fluid vapor extracted during the expansion will be at a lower temperature with respect to temperature of the partial flow of the primary heat source.
  • the partial flow control of the geothermal source which feeds the high temperature heat exchanger 80 is carried out by the first valve VI, whereas the control of the partial flow of the organic working fluid vapor extracted during the expansion and which feeds the further condenser 45 is realized by the second valve V2.
  • the two valves and the corresponding opening degree can be managed by a suitable PLC control unit which will also be electrically connected to the TC control unit of the district heating network.
  • the PLC control unit can be equipped with suitable optimization algorithms in order to make the ORC system work, as the user requests vary, always at maximum efficiency, so maximizing the supply of electrical energy and at the same time satisfying the heat user in cogeneration.
  • a typical application for such cogenerative ORC cycle plant can comprise a geothermal application (as in the example described where the primary heat source is represented by a flow of liquid water) and the heat user is a district heating network.
  • the same plant can be conveniently applied in biomass cogeneration applications.
  • a double cogeneration system can advantageously be obtained.
  • the first condenser 40 of the ORC plant (or main condenser) can supply heat to a first heat user (for example at 80-90 C), whereas the further condenser 45 and the high temperature heat exchanger 80 feed a heat user at a higher temperature (for example 100-120 C) requiring only a fraction of the thermal energy available to the main condenser.
  • the first condenser 40 instead of being an air condenser is preferably a water-cooled condenser.
  • the cogeneration ORC plant is the same as that of Figure 1 with a further variant.
  • the partial flow of the organic working fluid coming from the further condenser 45 is cooled in a further heat exchanger 90 - said exchanger being able to be installed both upstream and downstream of the second supply pump 55 - and then be mixed with the flow outgoing from the first supply pump 50, which pumps the main flow of organic working fluid out of the first condenser 40.
  • a branch line 95 equipped with a regulating valve V3, in which a partial liquid flow of organic working fluid which is preheated in the additional heat exchanger 90 before being returned to the path 5 and being mixed with the main flow of the organic working fluid at the preheater 60, as well as in the solution illustrated in Figure 1 .
  • This scheme can be convenient to have the possibility of decoupling the flow coming from the further condenser 45 from the flow sent through the further exchanger 90 and from there back to the cycle or to sub-cool the fluid before being pumped by the second supply pump 55, in order to increase the NPSH (English acronym for "net pressure suction head") upstream of the pump itself.
  • NPSH National acronym for "net pressure suction head”
  • the cogenerative ORC cycle plant illustrated in Figure 3 differs from the one illustrated in Figure 2 due to the further presence of a regenerator 105.
  • the regenerator 105 receives the main flow of the organic working fluid vapor, that is the one coming from the turbine 21 and which has processed the entire pressure drop, and in countercurrent the main flow of organic working fluid in the liquid phase, coming from the first supply pump 50.
  • the addition of a regenerator further increases the overall efficiency of the ORC cycle, in relation the characteristics of the working fluid used and the temperature of the source.
  • the turbine 22 can be a mixed flow (radial and axial) turbine with injection and/or extraction of organic working fluid in an angular stator stage, such as that described in the European patent EP3455465B1 , and the branch line 25 is located near the angular stator stage.
  • the plant illustrated in Figure 1 may also be equipped with a regenerator, as can be seen in the plant of Figure 3 .
  • the single turbine plant in Figure 4 may be equipped with a regenerator or a further heat exchanger (as in the system of Figure 2 ) or of both devices (as in the plant of Figure 3 ).
  • implementing modes are only exemplary and do not limit neither the object of the invention, nor its applications, nor its possible configurations.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP21212837.5A 2020-12-11 2021-12-07 Kogenerativer rankine kreislauf mit dampfentnahme aus der turbine Pending EP4083393A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT202000030470 2020-12-11

Publications (1)

Publication Number Publication Date
EP4083393A1 true EP4083393A1 (de) 2022-11-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP21212837.5A Pending EP4083393A1 (de) 2020-12-11 2021-12-07 Kogenerativer rankine kreislauf mit dampfentnahme aus der turbine

Country Status (1)

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EP (1) EP4083393A1 (de)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20313411U1 (de) * 2003-08-29 2003-11-06 Koehler & Ziegler Anlagentechn Kraft-Wärme-Kopplungsanlage
EP2538040A1 (de) * 2011-06-22 2012-12-26 Technische Universität München Kraft-Wärme-Kopplungs-Anlage und assoziiertes Verfahren
WO2013171685A1 (en) * 2012-05-17 2013-11-21 Exergy S.P.A. Orc system and process for generation of energy by organic rankine cycle
DE102012217339A1 (de) * 2012-09-25 2014-03-27 Duerr Cyplan Ltd. Netzwerk für das Transportieren von Wärme
WO2017199170A1 (en) * 2016-05-18 2017-11-23 Turboden S.p.A. Cogenerative organic rankine cycle system
DE102018201172A1 (de) * 2018-01-25 2019-07-25 Siemens Aktiengesellschaft Verbrennungsanlage mit Restwärmenutzung
EP3455465B1 (de) 2016-05-10 2020-08-26 Turboden S.p.A. Mischflussoptimierte turbine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20313411U1 (de) * 2003-08-29 2003-11-06 Koehler & Ziegler Anlagentechn Kraft-Wärme-Kopplungsanlage
EP2538040A1 (de) * 2011-06-22 2012-12-26 Technische Universität München Kraft-Wärme-Kopplungs-Anlage und assoziiertes Verfahren
WO2013171685A1 (en) * 2012-05-17 2013-11-21 Exergy S.P.A. Orc system and process for generation of energy by organic rankine cycle
DE102012217339A1 (de) * 2012-09-25 2014-03-27 Duerr Cyplan Ltd. Netzwerk für das Transportieren von Wärme
EP3455465B1 (de) 2016-05-10 2020-08-26 Turboden S.p.A. Mischflussoptimierte turbine
WO2017199170A1 (en) * 2016-05-18 2017-11-23 Turboden S.p.A. Cogenerative organic rankine cycle system
DE102018201172A1 (de) * 2018-01-25 2019-07-25 Siemens Aktiengesellschaft Verbrennungsanlage mit Restwärmenutzung

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