EP2217793B1 - Vorrichtung zur energieerzeugung - Google Patents

Vorrichtung zur energieerzeugung Download PDF

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Publication number
EP2217793B1
EP2217793B1 EP08844382.5A EP08844382A EP2217793B1 EP 2217793 B1 EP2217793 B1 EP 2217793B1 EP 08844382 A EP08844382 A EP 08844382A EP 2217793 B1 EP2217793 B1 EP 2217793B1
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EP
European Patent Office
Prior art keywords
working medium
evaporator
medium circuit
circuit
heater
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EP08844382.5A
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German (de)
English (en)
French (fr)
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EP2217793A2 (de
Inventor
Ulli Drescher
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GMK Gesellschaft fuer Motoren und Kraftanlagen mbH
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GMK Gesellschaft fuer Motoren und Kraftanlagen mbH
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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
    • 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
    • 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

Definitions

  • the invention relates to a device for power generation according to the ORC principle according to the preamble of claim 1.
  • low-temperature heat sources for energy generation devices are preferably used according to the principle of Organic Rankine Cycle (ORC).
  • ORC Organic Rankine Cycle
  • As a working medium in contrast to energy from high-temperature heat sources, water being used as a working fluid, organic fluids, especially silicone oils, alkanes, alkenes, aromatics, (partially) halogenated hydrocarbons and others used.
  • the working fluid is selected according to the temperatures of the heat source, so that the most effective use of heat energy takes place.
  • devices which have two separate working medium circuits, wherein both circuits are connected to the heat source.
  • the two working medium circuits are connected substantially in series, so that the heating means from the heat source initially transmits a first part of the heat energy to the first working medium circuit and in the following another part of the heat energy to the second working medium circuit.
  • the heating medium first flows through the two evaporators, it reaches the two partial preheaters at a relatively low temperature, which has the disadvantage that the heating medium flows through the partial preheater of the first working medium circuit to the extent that the working medium in this circuit is no longer heated to the evaporation temperature can.
  • the function of the preheating is therefore partially taken in addition in the first working fluid circuit of the evaporator, which is not optimally adapted to both functions (preheating and evaporation) due to its design.
  • DE 10 2006 028 746 A1 describes an ORC system with a working fluid circuit having an evaporator and a preheater, wherein the preheater is preceded by a Rekuperatur.
  • JP 61 132710A discloses a high-temperature working fluid circuit of an ORC plant in which the evaporator are assigned two preheaters. The heating medium flow is supplied completely and serially to all preheaters and evaporators in the system.
  • the invention is therefore based on the object to provide a device for power generation, which causes an improved heat transfer between the heating means and the working fluid of the first working fluid circuit and thus has a higher efficiency.
  • the invention is therefore based on the idea to provide a device for power generation according to the ORC principle with at least two, in particular three, working medium circuits, each comprising at least one capacitor, an evaporator and a Generalvortuder and are coupled by a common Schuffenniklauf such that a Walkerstoffstrom the evaporators is completely and the Generalvorskarn proportionately supplied, wherein a first working medium circuit has at least one further preheater, which is coupled to the Schuffenniklauf such that the Schuffenstrom is completely supplied to the further preheater.
  • the heating medium flow is essentially a mass flow of fluid. Accordingly, the complete supply of the heating medium flow does not relate to an energy transfer to the working medium based on the heat content of the heating medium source, but rather says that substantially the entire mass flow of the heating medium is supplied to the further preheater, the heat content of which is generally already absorbed by the transport of the source was reduced to another preheater.
  • the term "complete supply of Schuffenstroms” does not exclude that before the further preheater part of the Schuffenstroms is diverted, provided that the effect is maintained that the first evaporator is mainly used for steam generation such that the heat energy of the heating means as optimal as possible the working fluid of the first working fluid circuit is discharged and used for energy generation or conversion.
  • the working fluid of the first working fluid circuit is preheated by the complete mass flow of the heating means at a relatively high temperature, so that the working fluid is heated in the first working fluid circuit to the evaporation temperature.
  • the additional preheater can be adapted optimally and economically to the heat transfer between the two fluids.
  • the further preheater is arranged in the first working medium circuit between a Generalvor Anlagenr and a first evaporator.
  • This arrangement is energetically advantageous because the further preheater only the temperature difference between the preheating temperature of the partial preheater and the evaporation temperature to be reached must be bridged.
  • the further preheater is arranged in the heating medium circuit between the first evaporator of a first working medium circuit and the second evaporator of a second working medium circuit.
  • the further preheater comprises a plate and / or tube bundle heat exchanger.
  • Such heat exchangers allow a particularly efficient heat transfer.
  • At least one of the working medium circuits has an internal recuperator.
  • Internal recuperators have the advantage that the residual heat of the working fluid is used after power generation in the form of heat energy recovery for preheating the working fluid, whereby an increase in efficiency is achieved.
  • the working medium circuits preferably each have an engine, in particular a turbine, so that the heat energy of the heating medium flow is used in the form of mechanical energy.
  • the engines in particular turbines, can be coupled by one shaft each with a generator.
  • the mechanical energy generated by the engine is converted into electrical energy, with multiple generators ensure high reliability.
  • At least two prime movers in particular turbines, can be coupled by a common shaft to a generator, whereby the maintenance and control effort, in particular with respect to the synchronization of the generator to the power grid, is minimized.
  • the working medium circuits each have different working means.
  • the different tools generally have different boiling temperatures, so that the most effective use of the heat energy of the heating medium is guaranteed.
  • the heating medium circuit has a branch with at least two branch lines downstream of the second evaporator of the second working medium circuit, wherein the branch lines are coupled to a partial preheater of the first working medium circuit and a partial preheater of the second working medium circuit.
  • the heating medium circuit has a further branch, each having at least three branch lines, which is arranged downstream of the third evaporator of the third working fluid circuit, wherein the branch lines are coupled to a Sectionvorowskir the first working fluid circuit, a Crystalvor lockerr the second working fluid circuit and a Generalvor lockerr the third working fluid circuit.
  • the Thompsonschstrom can be divided after passing through the third evaporator on three working fluid circuits. Analogously, it is possible to realize a distribution of the heating medium flow to a plurality of working medium circuits.
  • Fig. 1 shows a process diagram of a device for power generation according to the prior art, wherein a first working fluid circuit 10 is coupled by a common heating medium circuit 50 with a second working fluid circuit 20.
  • the two working medium circuits 10, 20 have an identical structure, each with a feed pump 41, downstream in the flow direction recuperator 45, a subsequent Partvortuder 12, 22, each upstream of an evaporator 11, 21, an engine 43 and one each Condenser 42.
  • the working fluid in the working fluid circuits 10, 20 thus flows from the feed pump 41 to the recuperator 45, where it is heated by residual heat of the working fluid that has already produced mechanical work in the engine, and further to Partvormaschiner 12, 22, the causes a further heating of the working fluid.
  • the working fluid continues to the evaporator 11, 21 and is passed in the course in the form of steam to the engine 43.
  • the vaporous working medium performs mechanical work, whereby the steam is released and the now partially cooled working fluid flows back to the recuperator 45.
  • the recuperator 45 the residual heat energy of the working fluid is used to heat the counterflowing working fluid before being supplied to the partial preheater 12, 22.
  • the effluent from the engine 43 working fluid is thus further cooled in the recuperator 45 and fed to the condenser 42, where the working fluid is liquefied and recycled to the feed pump 41.
  • the working fluid first flows to the first evaporator 11 of the first working medium circuit 10, wherein heat is transferred from the heating means to the working fluid of the first working fluid circuit 10, so that the working fluid is transferred to the vaporous state.
  • the heating means continues to the second evaporator 21 of the second Working medium circuit 20 passed and causes there also an evaporation of the working fluid.
  • the heating medium flow is split at the branch 51 and fed to the two partial preheaters 12, 22 of the two working medium circuits 10, 20.
  • the heating means causes heating of the working medium circuits 10, 20.
  • the cooled heating means from the two Operavormaschinern 12, 22 is brought together again and discharged.
  • Fig. 2 shows a device according to the invention for power generation as a process diagram, wherein the structure of the device substantially the structure according to Fig. 1 equivalent.
  • the device comprises two working medium circuits 20, each of which has a feed pump 41, an internal recuperator 45, a partial preheater 12, 22, an evaporator 11, 21, an engine 43 and a condenser 42.
  • a further preheater 15 is arranged in the first working medium circuit 10 between the partial preheater 12 and the first evaporator 11 such that the working medium is conducted from the preheater 12 to the further preheater 15 and subsequently to the first evaporator 11.
  • a further preheater 15 is arranged in the first working medium circuit 10 between the partial preheater 12 and the first evaporator 11 such that the working medium is conducted from the preheater 12 to the further preheater 15 and subsequently to the first evaporator 11.
  • the course of the heating medium circuit 50 is changed such that the heating means after passing through the first evaporator 11 of the first working medium circuit 10 is first supplied to the further preheater 15 before the heating medium flows to the second evaporator 21 of the second working medium circuit 20.
  • the heating medium flow is then split at the branch 51 and proportionally fed to the two partial preheaters 12, 22 of the two working medium circuits 10, 20, then brought together again and discharged.
  • the main advantage of the arrangement of the further preheater 15 is that the further preheater 15 in this way the entire mass flow of the heating medium is supplied, whereby the energy available for heating the working fluid in the first working fluid circuit 10 energy is significantly increased.
  • the use of the complete heating medium current causes the heat energy of the heating medium, which already compared to the original heat energy of the heat source through the energy exchange in the first Evaporator 11 is reduced, sufficient to heat the working fluid of the first working fluid circuit 10 to the evaporation temperature.
  • the heating up to the evaporation temperature is partially effected by the first evaporator 11, which, however, is not or can not be adapted to preheat the working fluid.
  • Fig. 3 shows a temperature / Enthalpiestrom diagram of a device according to the invention, wherein thermal water is used as an example heating means.
  • the heat flow of the thermal source is fixed, since the mass flow is limited.
  • the mass flow of the cooling water supplied to the condenser 42 from outside to cool the working fluid may be adjusted.
  • the thermal water cools down, while during the evaporation of the working fluid, the temperature remains constant. Accordingly, takes place in the evaporators 11, 21 an isothermal energy transfer, while in the Generalvormaschinern 12, 22 and the further preheater 15, the energy transfer is substantially isobaric.
  • a pinch point arises between the thermal water and the working medium.
  • the pinch point is defined as the state point with the minimum temperature difference between two heat fluxes during heat transfer.
  • the position of the pinch point in the temperature / enthalpy current diagram results from the ratio of mass flow and evaporation temperature, so that at high working mass flow, the upper process temperature and thus the efficiency of the cycle is low, while at a low mass flow, the efficiency of the cycle is increased , Since the output of the cycle is calculated from the product of specific work and mass flow, there is an optimal upper process temperature associated with a mass flow, which allows the energy of the thermal water to be used efficiently up to a certain temperature.
  • the device according to the invention makes it possible, through the further preheater 15, that the largest possible proportion of the heat energy of the heat source is utilized.
  • the diagram according to Fig. 3 shows that the further preheater 15 ( Fig. 3 : second preheater, first module), the temperature of the working fluid significantly increased, so that in the first evaporator 11 of the first working fluid circuit 10, a substantially isothermal energy transfer occurs.
  • the additional preheater 15 thus causes, on the one hand, the temperature difference between the thermal water heat flow and the working medium of the first working medium circuit to be minimized and, on the other hand, no isobaric energy transfer in the first evaporator 11, for which the first evaporator 11 is not constructed.
  • the heat absorption thus takes place in comparison to previously known ORC cycle processes at a higher energy level, so that the usable heat content of the cycle increases.
  • Fig. 4 shows a further embodiment of a device according to the invention for power generation, wherein three working medium circuits 10, 20, 30 are provided.
  • the first working medium circuit 10 comprises a feed pump 41, which conveys the working fluid to a first Partvortuder 13, on to a second Partvortuder 12, on to another preheater 15 and in the following to a first evaporator 11. From the first evaporator 11, the working fluid of the first working medium circuit 10 flows to an engine 43, in particular a turbine, which is coupled to a generator 44. The relaxed working fluid is supplied in the further course of the engine 43 to a condenser 42 and again the pump 41.
  • the second working fluid circuit 20 has a similar structure and also has a feed pump 41, which directs the working fluid to a first Partvorowskir 23, on to a second Partvor lockerr 22, on to a second evaporator 21 and further to an engine 43.
  • the engine 43 in particular a turbine, is connected to a shaft with a generator 44. After passing through the engine 43, the relaxed working fluid of the second working fluid circuit 20 flows into the condenser 42 and from there back to the feed pump 41.
  • the third working fluid circuit 30 also includes a feed pump 41, which is followed by a Generalvormaschiner 33, which in turn upstream of a third evaporator 31 is.
  • the third evaporator 31, an engine 43, in particular turbine, downstream, which is connected to a shaft with a generator 44 and by the working means of the third working medium circuit 30 is operated before the working fluid flows through the condenser 42 back to the pump 41.
  • the working medium circuits 10, 20, 30 at least partially have an internal recuperator 45.
  • the recuperator 45 at least a Sectionvortuder 12, 13, 22, 23, 33 both upstream or downstream, as well as between at least two Partvor lockerrn 12, 13, 22, 23, 33 may be arranged.
  • the position of the recuperator 45 generally depends on the heating medium temperatures in the respective partial preheaters 12, 13, 22, 23, 33, so that the working medium absorbs heat energy when passing through the recuperator or at least does not transfer heat energy to the heating medium.
  • the three working medium circuits 10, 20, 30 are coupled by a common Walkerstoff kausburg so.
  • the heating medium in the heating medium circuit 50 first flows through the first evaporator 11 of the first working medium circuit 10, further through the preheater 15 of the first working medium circuit 10 and subsequently through the second evaporator 21 of the second working medium circuit 20 before the heating medium stream is split at the branch 51 and over the two branch lines 52a, 52b are supplied to the two partial preheaters 12, 22 of the first and second working medium circuits 10, 20.
  • the Wienstoffteilströme After passing through the two Operavormaschiner 12, 22, the Schuffenteilströme be merged and passed to the third evaporator 31 of the third working fluid circuit 30.
  • the working medium circuits 10, 20, 30 each have an arbitrary number of preheaters 15 or partial preheaters 12, 13, 22, 23, 33.
  • the distribution of the heating medium flow in Walkerstoffteilströme is accordingly adapt.
  • the heating medium flow between the first working medium circuit 10 and the second working medium circuit 20 is divided into two branch lines 52a, 52b, which are coupled to the partial preheaters 12, 22 of the first and second working medium circuits 10, 20, whereby a halving distribution of the total mass heating medium flow is possible; so that the two partial streams are identical.
  • Other divisions are possible.
  • the distribution to the Generalvor Anlagenrn 13, 23, 33 of the three working medium circuits 10, 20, 30 are also designed at the branch 53 in such a way that the three Schuffenteilströme are identical.
  • the branch 53 is represented in the form of two partial branches 53a, 53b.
  • the structural design of the branch 53 is not fixed. Rather, the embodiment is essentially dependent on the desired distribution of Schuffenteilströme.
  • the branch 53 is formed such that the connection to the Generalvormaschinern 13, 23, 33 is energetically effective. This can be achieved for example by the branch line 54a, 54b, 54c, which promotes the partial flow with the lowest heat capacity, as short as possible, so that heat losses are minimized by the transport.
  • the coupling between the engine 43 and the generator 44 is preferably carried out by a shaft, wherein at least one, in particular all, engines 43 may have a common shaft which is coupled to at least one generator, so that rotational energy is transmitted and converted into electrical energy.
  • the engines 43 may be designed as turbines, screw or piston engines.
  • the boiling temperature of the working fluid in the first working fluid circuit 10 is highest and decreases with each further, downstream working medium circuit.
  • the heat energy loss of the heating medium when passing through the individual heat exchangers, in particular the preheater 15, the Generalvorezer 12, 13, 22, 23 and the evaporator 11, 21, carried in the upstream working fluid circuits 10, 20 and the efficiency of the entire device can be increased, since the pinch point of the individual heat exchanger can be optimized to the minimum temperature difference between the two fluid streams.

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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)
  • General Induction Heating (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP08844382.5A 2007-11-02 2008-10-31 Vorrichtung zur energieerzeugung Active EP2217793B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200720015236 DE202007015236U1 (de) 2007-11-02 2007-11-02 Vorrichtung zur Energieerzeugung
PCT/EP2008/009221 WO2009056341A2 (de) 2007-11-02 2008-10-31 Vorrichtung zur energieerzeugung

Publications (2)

Publication Number Publication Date
EP2217793A2 EP2217793A2 (de) 2010-08-18
EP2217793B1 true EP2217793B1 (de) 2018-03-21

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Country Status (4)

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EP (1) EP2217793B1 (tr)
DE (2) DE202007015236U1 (tr)
TR (1) TR201808721T4 (tr)
WO (1) WO2009056341A2 (tr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008051849A1 (de) * 2008-10-17 2010-04-22 Bauer, Christian Energieerzeugerkopplung
EP2765281B1 (en) * 2013-02-07 2015-07-08 Ingenieria I Mas D-Tec Ratio, S.L. A rankine cycle apparatus
DE102014201116B3 (de) * 2014-01-22 2015-07-09 Siemens Aktiengesellschaft Vorrichtung und Verfahren für einen ORC-Kreisprozess
US10436075B2 (en) * 2015-01-05 2019-10-08 General Electric Company Multi-pressure organic Rankine cycle
CN105443175A (zh) * 2016-01-07 2016-03-30 上海维尔泰克螺杆机械有限公司 串级式有机朗肯循环系统
DE102016112601A1 (de) 2016-07-08 2018-01-11 INTEC GMK GmbH Vorrichtung zur Energieerzeugung nach dem ORC-Prinzip, Geothermieanlage mit einer solchen Vorrichtung und Betriebsverfahren
CN108223315A (zh) * 2018-01-30 2018-06-29 中国华能集团清洁能源技术研究院有限公司 一种双级闪蒸与有机朗肯循环联合的地热发电装置及方法
IT201900006589A1 (it) 2019-05-07 2020-11-07 Turboden Spa Ciclo rankine organico a cascata ottimizzato
US11976575B2 (en) * 2020-05-29 2024-05-07 Turboden S.p.A. Cascade organic Rankine cycle plant

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GB2162583A (en) 1984-07-16 1986-02-05 Ormat Turbines Improved cascaded power plant using low and medium temperature source fluid
JPS61132710A (ja) 1984-11-30 1986-06-20 Toshiba Corp デユアルランキンサイクル
US5531073A (en) 1989-07-01 1996-07-02 Ormat Turbines (1965) Ltd Rankine cycle power plant utilizing organic working fluid
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JPS61132710A (ja) 1984-11-30 1986-06-20 Toshiba Corp デユアルランキンサイクル
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Also Published As

Publication number Publication date
TR201808721T4 (tr) 2018-07-23
WO2009056341A2 (de) 2009-05-07
WO2009056341A3 (de) 2010-08-12
EP2217793A2 (de) 2010-08-18
DE202007015236U1 (de) 2008-01-24
DE202008018661U1 (de) 2018-01-23

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