WO2012130421A2 - Système à cycle de rankine organique direct, système de génération de puissance à cycle combiné de conversion de la biomasse, et procédé de fonctionnement d'un cycle de rankine organique direct - Google Patents

Système à cycle de rankine organique direct, système de génération de puissance à cycle combiné de conversion de la biomasse, et procédé de fonctionnement d'un cycle de rankine organique direct Download PDF

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Publication number
WO2012130421A2
WO2012130421A2 PCT/EP2012/001291 EP2012001291W WO2012130421A2 WO 2012130421 A2 WO2012130421 A2 WO 2012130421A2 EP 2012001291 W EP2012001291 W EP 2012001291W WO 2012130421 A2 WO2012130421 A2 WO 2012130421A2
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WIPO (PCT)
Prior art keywords
working medium
boiler
organic rankine
waste heat
heat
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Ceased
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PCT/EP2012/001291
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English (en)
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WO2012130421A3 (fr
Inventor
Jens-Uwe Reeh
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Caterpillar Motoren GmbH and Co KG
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Caterpillar Motoren GmbH and Co KG
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Priority to CN201280014938.8A priority Critical patent/CN103443406B/zh
Publication of WO2012130421A2 publication Critical patent/WO2012130421A2/fr
Publication of WO2012130421A3 publication Critical patent/WO2012130421A3/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • 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
    • 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

Definitions

  • the present disclosure generally refers to power generation from waste heat and more particularly to using an organic Rankine cycle (ORC) for converting waste heat of multiple waste heat sources to electric power.
  • ORC organic Rankine cycle
  • the engine can be increased, for example, by additionally generating power from waste heat of the combustion engine, such as the heat of exhaust gas.
  • waste heat of the combustion engine such as the heat of exhaust gas.
  • the generation of power from waste heat is used in combined cycle power generation, which combines the generation of power from steam or combustion turbines with at least one additional stage deriving power from waste heat of the steam or combustion turbine using, e.g. an ORC.
  • combined cycle is to be understood to include the combination of an ORC with combustion based power generating systems, such as combustion engines, e.g. gas or liquid fuel genset, as well as the combination of an ORC with steam or combustion turbine based power generating systems.
  • ORC technology has been developed. ORC uses a working medium that changes into gas phase at the available temperature of the waste heat and is used to drive an ORC turbine.
  • ORC turbine In general, there are two types of ORC: Indirect ORC uses an intermediate liquid cycle to transfer the waste heat to the working medium, whereby the working medium circulates in a closed cycle of an ORC unit. These types of system are referred to as closed loop ORC systems.
  • direct ORC also referred to as open loop ORC
  • direct ORC systems are disclosed, for example, in US 2007/0240420 Al and US 2008/0289313 Al .
  • a multi-component working-fluid system for low temperature direct Rankine cycles is disclosed, for example, in US 201 1/001 1089 Al .
  • the present disclosure is directed, at least in part, to improving or overcoming one or more aspects of prior systems.
  • a direct organic Rankine cycle system for generating power using a working medium may comprise a boiler sub-system comprising a pump and a boiler, the pump configured to pump the working medium through the boiler, a vapor separator connected to a working medium outlet of the boiler and configured for separating a gaseous phase of the working medium, an organic Rankine turbine module fluidly connected to the vapor separator for refilling the vapor separator with the working medium haven been used in the organic Rankine turbine module, the organic Rankine turbine module comprising a turbine driven by the separated working medium gaseous phase, and a control system configured to control the pump for adjust the circulation speed of the working medium through the boiler such that at least 15%, 20 %, 30 %, 40 %, or 50% of the working medium are maintained in the liquid phase when exiting the boiler.
  • a direct organic Rankine cycle system for generating power using a working medium may comprise a boiler subsystem comprising a pump and a boiler, the pump configured to pump the working medium through the boiler; a vapor separator connected to a working medium outlet of the boiler and configured for separating a gaseous phase of the working medium; an organic Rankine turbine module fluidly connected to the vapor separator, the organic Rankine turbine module comprising a turbine driven by the separated working medium gaseous phase; a control system configured to control the pump for adjust the circulation speed of the working medium through the boiler such that at least 15%, 20 %, 30 %, 40 %, or 50% of the working medium are maintained in the liquid phase when exiting the boiler.
  • a biomass combined cycle power generating system may comprise a pyrolysis reactor generating pyrolysis oil and pyrolysis gas from biomass; a pyrolysis oil engine for generating power from the pyrolysis oil, thereby producing waste heat; a pyrolysis gas engine for generating power from the pyrolysis gas, thereby producing waste heat; and a direct organic rankine cycle system (e.g. as indicated above) comprising two boiler sub-systems for generating power from the waste heat of the pyrolysis oil engine and the pyrolysis gas engine, wherein the waste heat is supplied to a respective boiler of the boiler sub-systems.
  • a direct organic rankine cycle system e.g. as indicated above
  • a method for operating a direct Rankine cycle may comprise circulating an organic working medium through a boiler at a circulation speed such that at least 15%, 20 %, 30 %, 40 %, or 50% of the organic working medium are maintained in the liquid phase when exiting the boiler.
  • control system may be connected with a temperature sensor for receiving temperature data of the working medium and configured for receiving a load parameter of a genset, which provides waste heat to the boiler sub-system, and wherein the control system may be further configured for deriving a pump speed control parameter for controlling the speed of the pump from the load parameter and the temperature parameter, in particular using a load/temperature depending flow curve tables associated with the boiler sub-system.
  • a boiler may be configured for heating the working medium with waste heat of exhaust gas of a combustion and/or waste heat of a high temperature cooling cycle of a combustion engine. The boiler may be operable as a Lamont boiler.
  • the boiler may comprise a super-heating system connected with a gaseous phase outlet of the vapor separator.
  • the super-heating system may be configured for super-heating the separated working medium gaseous phase and providing the super-heated separated working medium gaseous phase to the organic Rankine turbine module.
  • the working medium may be selected from the group of organic working media comprising saturated and unsaturated hydrocarbons, fluorated hydrocarbons, silicon oils such as siloxane, ammonia, and ammonia- water mixture.
  • the separator may be part of a modular heat rejection system of the direct organic Rankine cycle system, and the modular heat rejection system may comprise a plurality of boiler sub-systems and the pumps of the boiler sub-systems are controlled by the control system such that at least 15%, 20 %, 30 %, 40 %, or 50% of the working medium are maintained in the liquid phase when exiting the respective boiler.
  • the waste heat may include at least one of heat of exhaust gas and heat of a coolant system of the pyrolysis oil engine and at least one of heat of exhaust gas and heat of a coolant system of the pyrolysis gas engine.
  • the method may comprise circulating an organic working medium through a boiler at a circulation speed such that at least 15%, 20 %, 30 %, 40 %, or 50% of the organic working medium are maintained in the liquid phase when exiting the boiler.
  • the method may further comprise heating the working medium in the boiler using waste heat such as heat of an exhaust gas or a cooling circuit of an combustion engine; separating a working medium gas phase and a working medium liquid phase from the heated working medium, eventually additionally super-heating the separated working medium gas phase; deriving power from the separated working medium gas phase; regenerating a working medium liquid phase of the working medium after power generation; and returning a mix of the regenerated working medium liquid phase and the separated working medium liquid phase to the boiler.
  • the method may further comprise receiving information on a load parameter of a genset, which provides waste heat to the boiler sub-system; receiving temperature data of the working medium; and deriving a pump speed control parameter from the load parameter and the temperature parameter for controlling the circulation speed.
  • various types of heat sources such as high temperature charge air cooling systems can alternatively or additionally be used to preheat the working medium.
  • control concept for controlling direct ORC.
  • the control concept may avoid or at least reduce the amount of overheating of the working medium and, thereby, provide long term use of the working medium.
  • FIG. 1 is a schematic overview of a combined system including a direct ORC system using the waste heat of three gensets;
  • FIG. 2 is a schematic overview of a combined system for a
  • pyrolysis-based power plant including a direct ORC system using waste heat from a gas genset and a liquid genset;
  • FIG. 3 is a schematic illustration of a direct ORC system with a modular heat rejection system and an ORC turbine module;
  • FIG. 4 is a schematic diagram illustrating a direct ORC system with a modular heat rejection system comprising three heat rejection modules;
  • FIG. 5 is a schematic illustration of a direct ORC system including a super-heating zone
  • FIG. 6 is a schematic illustration of a direct ORC system including pre-heating of a working medium before being supplied to the modular heat rejection system and a super- heating zone;
  • FIG. 7 is a schematic illustration of an air system and a cooling system of a genset.
  • the present disclosure may be based in part on the realization that to increase the efficiency of a power plant, e.g. a biomass based power plant, the waste heat of various gensets or various types of waste heat of one or more genset may be turned into electric power via a common organic Rankine cycle.
  • a power plant e.g. a biomass based power plant
  • the waste heat of various gensets or various types of waste heat of one or more genset may be turned into electric power via a common organic Rankine cycle.
  • rejection cycle as disclosed herein may be based on a common vapor separator and a common ORC turbine module with a turbine and a regenerator.
  • the common vapor separator may be connectable to the common
  • the common vapor separator may be configured as an interface between the ORC turbine module and the modular heat rejection cycles. Moreover, configuring the common vapor separator as an interface that receives the working medium from the ORC turbine module and then distributes the working medium to the various heat rejection cycles may allow a simple control concept of an ORC.
  • the common vapor separator may be configured to provide the working medium at a common preset temperature prior supplying the working medium to the various heat rejection cycles.
  • the common vapor separator may receive the working medium preheated, for example, using a cooling system of the engine and a low temperature region of a boiler.
  • the preheating using the engine cooling system may be performed prior a working medium regeneration unit while the preheating using the low temperature region of the boiler may be performed after the working medium regeneration unit but prior supplying the working medium to the common vapor separator.
  • waste heat at different temperature levels may be used during different stages of the working medium cycle.
  • a low temperature waste heat source such as coolant of the low and/or high temperature cooling circuit of an engine may be used for preheating the working medium following the condensation to supporting the regeneration with the preheated working medium.
  • high temperature waste heat sources such as exhaust gas
  • a highest temperature zone within a boiler may be used for superheating the gaseous phase of the working medium prior being supplied to the turbine.
  • a medium temperature zone vaporizing zone
  • the main energy transfer may take place and initiate the liquid - gaseous phase transition of the working medium.
  • a lowest temperature zone (preheating zone) of a boiler may be used for (additionally) preheating the working medium prior being supplied into a vapor separator and being mixed therein with the liquid phase generated in the vapor separated.
  • the superheating zone, the vaporizing zone, and the preheating zone of the boiler may be arranged in flow direction of the high temperature waste heat source.
  • each heat rejection cycle may comprise its own pump and boiler and provide a heating cycle that begins and ends at the common vapor separator.
  • the flow within the heat rejection cycles may be adjusted as described herein for protecting the working medium.
  • a control concept as described herein may adjust the circulation rate within the heat rejection cycle to a value of 1.3 to 1.5.
  • a value of 1.0 is defined as a circulation rate that results in heating the working medium such that 100% of the working medium changes into the gas phase, i.e. the complete amount of working medium that passes through a boiler is evaporated.
  • a value above 1.0 indicates that more working medium is circulated.
  • 130 % of the amount of working medium, which correspond to the value of 1 .00 are circulated. This corresponds to operating the heat rejection cycles under the Lamont principle.
  • the boiler may be considered to be operated as a Lamont boiler.
  • control strategy as described herein may be any control strategy as described herein.
  • an energy buffer may be provided in form of the not yet evaporated working medium such that in case the temperature is further increased the liquid phase can receive that energy.
  • control concept may control the pump speed
  • multiple gensets 10 may provide waste heat to a direct ORC system 20.
  • a single genset 10 may provide different types of waste heat to direct ORC system 20 such as heat of exhaust gas, heat of a coolant of a charge-air cooling system, e.g. a high-temperature charge- air coolant cycle and/or a low- temperature charge-air coolant cycle, and heat of jacket water.
  • Fig. 2 shows a flow chart for a pyrolysis-based power plant 100 as an example of a power system using biomass integrated liquidation. Pyrolysis- based power plant 100 may be adapted to include an ORC system using waste heat.
  • Pyrolysis-based power plant 100 may include a pyrolysis reactor
  • pyrolysis reactor 1 10 may generate pyrolysis gas 1 12 A, pyrolysis oil 1 12B, and char 1 14. Flash-pyrolysis is a specific type of conventional slow pyrolysis that is performed with the task to maximize te liquid fraction (here pyrolysis oil).
  • Pyrolysis gas 1 12A and pyrolysis oil 1 12B may be provided to conditioning units 120 A, 120B.
  • the PCT application PCT/EP2010/0021 14 of Caterpillar Motoren GmbH & Co. KG filed on 1. April 2010 and published as WO 201 1/120542 Al discloses an exemplary method for preparing
  • conditioning pyrolysis oil for an internal combustion engine.
  • the conditioning of the pyrolysis gas may include, for example, cleaning, cooling, and
  • Gensets 130A and 130B may each provide an electricity output 132A, 132B, respectively.
  • Gas genset 130A may be, for example, a conventional gas engine adapted to run with pyrolysis gas.
  • Liquid genset 130B may be, for example, a conventional diesel engine adapted to run with pyrolysis oil.
  • gas genset 130A and liquid genset 130B may generate one or more types of waste heat outputs 134A and 134B, respectively.
  • Waste heat outputs 134A and 134B may be provided to an organic Rankine system 140 that uses the waste heat outputs 134A and 134B to additionally provide an electricity output 142.
  • Organic Rankine system 140 may be based on a direct ORC system, examples of which are described in the following in connection with Figs. 3 to 6. Specifically, direct ORC systems may be based on a modular concept.
  • an exemplary direct ORC system 200 of a modular concept may include an ORC turbine module 210 and a modular heat rejection system 230.
  • Direct ORC system 200 may be configured such that in a closed cycle, a working medium passes through ORC turbine module 210 and modular heat rejection system 230. Accordingly, the heating of the working medium is performed directly within modular heat rejection system 230 from one ore more waste heat types of one or more gensets (see also Fig. 7). Depending on the energy content and temperature, some types of waste heat may be used to preheat the working medium within ORC turbine module 210 (for example, low temperature and high temperature engine cooling circles) or in-between ORC turbine module 210 and modular heat rejection system 230 (for example, preheating zone of an exhaust gas boiler). Waste heat sources having a large energy content and temperature may be used for vaporizing the working medium within the modular heat rejection system 230 (for example, the higher
  • the ORC working medium is of organic nature instead of water
  • organic working medium examples include saturated and unsaturated hydrocarbons, fluorated hydrocarbons, silicon oils such as siloxane, ammonia, and ammonia- water mixture.
  • the type of working medium defines inter alia the temperature range in which the ORC may be performed. Silicone base fluids may, for example, be applied with pyrolysis-based power plant 100.
  • ORC turbine module 210 may include a turbine 212 for driving a generator 214.
  • ORC turbine module 210 may further include a regeneration unit 216 and a condenser unit 218.
  • Regeneration unit 216 may transfer heat of the working medium being still in the gaseous phase after having driven turbine 212 to regenerated working medium in the liquid phase.
  • Condenser unit 218 may be connected to a water cycle 220 and further cool down and condense the working medium until it is in the liquid phase again.
  • ORC turbine module 210 may further include one or more control valves 226 and one or more pumps 228.
  • ORC turbine module 210 may further include a working medium inlet 222 and a working medium outlet 224 for a fluid connection between a working medium cycle section within in ORC turbine module 210 and a working medium cycle section within modular heat rejection system 230.
  • Modular heat rejection system 230 may include a common vapor separator 232 with an inlet 252 and a plurality of boiler sub-systems 234.
  • working medium outlet 224 of ORC turbine module 210 may be fluidly connected to inlet 252 of vapor separator 232. Accordingly, the working medium may directly flow from in particular regeneration unit 216 into vapor separator 232.
  • preheating of the working medium pior being supplied to vapor separator 232 may be performed within the working medium cycle section within in ORC turbine module 210 or in-between ORC turbine module 210 and modular heat rejection system 230, specifically prior being supplied to vapor separator 232. Preheating is described , for example, in connection with Fig. 6 and 7.
  • Vapor separator 232 may be configured for separating a gaseous phase from a liquid phase of working medium that was heated in boiler subsystems 234.
  • the working medium returned from ORC turbine module 210 may be mixed in vapor separator 232 with the separated liquid working medium having passed boiler sub-systems 234, resulting in a further heating of the working medium returned from ORC turbine module 210.
  • the vapor separator (232) may comprise a section for deriving the working medium liquid phase and the working medium gaseous phase and a section for mixing the derived working medium liquid phase and the working medium received from the organic rankine turbine module (210, 410).
  • the mixing within vapor separator 232 may have the further advantage of a simple piping configuration and symmetric conditions when supplying various boiler sub-systems 234 within a combined cycle power generating system.
  • Each boiler sub-system 234 may include a pump 236 and a boiler
  • Boiler 238 may be configured for transferring heat of a waste heat output of a genset such as exhaust gas 237 or cooling water of an increased temperature onto the working medium.
  • a genset such as exhaust gas 237 or cooling water of an increased temperature onto the working medium.
  • One or more boiler sub-system 234 may be operated according to the Lamont principle. Then, boiler 238 of boiler sub-systems 234 may be considered a Lamont boiler.
  • Lamont boiler may further be based on small size pipes, which may also positively affect the response time.
  • multiple boiler sub-systems 234 may be fluidly connected to vapor separator 232 via one or more boiler sub-system connection lines 240.
  • a separator outlet 242 of vapor separator 232 may be connected to a pump 236 of boiler sub-systems 234 via boiler sub-system connection line 240.
  • pump 236 may be connected to a boiler inlet 244 of respective boiler 238.
  • a boiler outlet 246 of boiler 238 may be connected to a separator inlet 248 of vapor separator 232.
  • a vaporizing pipe system
  • the vaporizing pipe system may be configured to transfer heat of the high
  • temperature waste heat source e.g. exhaust gas
  • a gas phase outlet 250 of vapor separator 232 may be connected via a connection line 254 to working medium inlet 222 of ORC turbine module 210 such that the gaseous phase working medium may be provided to turbine 212 for driving generator 214, thereby closing the working medium cycle.
  • Super heating of the gas phase may additionally be performed between the gas phase outlet 250 and working medium inlet 222 of ORC turbine module as described below in connection with Fig. 5.
  • exhaust gas at a temperature of e.g. 310°C and a mass of e.g. 75000-1 12000 kg/h may be supplied through boiler 238.
  • Pump 236 may pump the working medium through boiler 238 such that the working medium partially changes into the gas phase and a mixture of working medium in the gaseous phase and the liquid phase is generated.
  • the exhaust gas may exit boiler 238 at a temperature of about 180°C.
  • the working medium may exit ORC turbine module 210 at a
  • the gaseous working medium enters the ORC turbine module 210 at a
  • the mixture of gas phase and liquid phase of the heated working medium may be supplied to and separated in vapor separator 232 so that only the gas phase may be provided to ORC turbine module 210.
  • turbine 212 may drive generator 214 by the gaseous working medium, which thereby expands and decreases in temperature. Downstream of turbine 212, working medium may pass regeneration unit 216, in which heat of the still gaseous working medium may be transferred to the liquid working medium, which has been generated in condenser 218 from the gaseous phase of the working medium using water cycle 220.
  • working medium in vapor separator 232 and the supplying of the gas phase to turbine 212 results in liquid working medium at (referring to the above example) 250 °C that than may be mixed in vapor separator 232 with (potentially preheated) working medium being received from ORC turbine module 210 (in the embodiment shown in Fig. 3 being received from regeneration unit 216).
  • additional boiler sub-systems 234 may be fluidly connected to vapor separator 232. Specifically, distributing the working medium to additional boiler sub-systems 234 may be performed via boiler subsystem connection line 240 (see also Fig. 4).
  • Fig. 4 illustrates the flow of the working medium within boiler sub-systems 234.
  • Fig. 4 illustrates the control of pumps 236 of boiler sub-systems 234.
  • regenerated working medium may be provided to vapor separator 232, specifically through inlet 252, and mixed in vapor separator 232 with the working medium originating from the separation process of vapor separator 232.
  • the regenerated working medium and the separated working medium may be mixed external to vapor separator 232.
  • working medium may exit vapor separator 232 along boiler sub-system connection line 240, which may distribute the working medium to three boiler sub-systems 234, each including at least one pump 236 and at least one boiler 238.
  • Pumps 236 may be controlled via a control unit 305 to adjust the circulation speed of the working medium through boilers 238 such that at least 15%, 20%, 30%, 40%, or 50% of the working medium are maintained in the liquid phase when exiting respective boilers 238.
  • control unit 305 may receive information of physical parameters (such as temperature and pressure) of the working medium after the heating process in boilers 238.
  • respective sensors may be provided at or downstream of outlets 246.
  • control unit may receive information on the current performance and/or future performance of the gensets.
  • the load refers to the load of the genset of which the waste heat is used in the respective boiler sub-system.
  • the temperature refers to the temperature of the working medium measured within the working medium loop of that respective boiler sub-system.
  • Fig. 4 shows schematically a temperature measurement line 307 connecting control unit 305 with a temperature sensor 308 installed downstream of boiler 238. In Fig. 4, only one temperature measurement line 307 is shown exemplarily. In general, temperature measurement lines may be provided for one or more boiler sub-systems.
  • the load /temperature depending flow curve may be used to control the speed of respective pump 236 within a predefined range of throughput through boiler 238.
  • control unit 305 may assess the parameter load of the genset and temperature of the working medium and derive there from a control parameter for controlling the pump speed.
  • the control output parameter may be limited such that the speed of pump 236 may only be adjustable within a range of, e.g., 70-100%.
  • Control unit 305 may comprise a memory unit for providing load
  • Control system may further be connected via control lines 306 to pumps 236 of each of the boiler sub-systems.
  • control unit 305 may allow adjusting individually the circulation speed for each boiler and associated waste heat source such that the organic working medium is protected, e.g., from thermal decomposition.
  • the pump speed may be increased as well.
  • an increase of, e.g., the exhaust gas temperature may be expected and, accordingly, the pump speed can be increased to avoid, to limit or at least to slow down the increase of temperature and phase transition of the working medium.
  • by-pass lines may be provided that allow the waste heat carrying medium to by-pass respective boiler(s) such that also by controlling the flow of the waste heat carrying medium the temperature and phase transition of the working medium may be ensured to be within acceptable limits.
  • the heated working medium may then be combined and provided to inlet 248 of vapor separator 232.
  • Vapor separator 232 may separate the gaseous phase of the working medium from the liquid phase and provide the gaseous phase via outlet 250 and line 254 to inlet 222 of ORC turbine module 210.
  • heat rejection system 230 may include a boiler 438 that includes a superheating zone 460.
  • ORC turbine module 210 as well as the heat transfer in boiler sub-systems 234 onto the liquid phase working medium may work essentially as described in connection with Figs. 3 and 4.
  • gaseous phase outlet 250 may be connected to an inlet 462 of a superheating pipe system (schematically indicated by dashed lines) within superheating zone 460 of boiler 438.
  • the superheating pipe system may be configured to transfer heat of the high temperature waste heat source (e.g. exhaust gas) to the gaseous phase of the working medium
  • Superheated gaseous phase working medium may exit superheating zone 460 at outlet 464, which may then be fluidly connected to inlet 222 of ORC turbine module 210, such that the gaseous phase working medium may be provided at a higher temperature to increase the efficiency of turbine 212.
  • additional boiler sub-systems 234 may include boilers 438 with superheating zones 460. Accordingly, gaseous phase may be distributed to additional superheating zones as indicated by line 466. In that case, superheated gaseous phase working medium exiting additional superheating zones 460 at outlet 464 may be combined with superheated working medium from other superheating zones as indicated by line 468. In some boiler sub-systems 234 may not have a superheating zone and mixtures of superheated and not superheated gas phases may be supplied to ORC turbine module 210.
  • additional boiler subsystems 234 may be provided such that heated working medium from a plurality of boiler sub-systems 234 is combined before entering vapor separator 232 at inlet 248.
  • Fig. 6 shows a direct ORC system that includes an ORC turbine module 510 and a boiler sub-system 534 including a superheating zone 460 as described in connection with Fig. 5.
  • Fig. 6 shows two types of preheating of the regenerated working medium: a heat transfer unit 570 interacting with ORC turbine module 510 and a preheating zone 580 of boiler sub-system 534.
  • a heat transfer unit 570 interacting with ORC turbine module 510
  • a preheating zone 580 of boiler sub-system 534 One or more of those types of preheating may be performed to adapt the temperature of the working medium coming from ORC turbine module 510 to the temperature of the separated liquid phase working medium provided by vapor separator 232.
  • heat transfer unit 570 may receive heat from a coolant medium 571 of a coolant cycle of a genset, e.g. a combustion engine, and transfer that heat to the regenerated working medium exiting pump 228.
  • heat transfer unit 570 may be fluidly connected with pump 228 and regeneration unit 216.
  • the working medium exiting condenser 218 at a temperature of, e.g., about 50°C may be heated in heat transfer unit 570 to a temperature of, e.g., about 120°C.
  • heat transfer unit 570 may be heated in heat transfer unit 570 to a temperature of, e.g., about 120°C.
  • multiple heat transfer units associated with the same or different gensets may be employed, for example, using a parallel arrangement of those heat transfer units.
  • the working medium may be further be heated by regeneration unit 216 to a temperature of, e.g., about 190°C.
  • preheating may be performed using, e.g., the low-temperature section of at least one boiler 538 of boiler sub-systems 524.
  • the working medium may pass preheating zone 580.
  • outlet 224 of ORC turbine module 510 may be fluidly connected with inlet 582 of a preheating pipe system of preheating zone 580.
  • the preheating pipe system (schematically indicated by dashed lines) may be configured to transfer heat of the high temperature waste heat source (e.g. exhaust gas) to the, for example preheated, working medium prior being supplied to vapor separator 232.
  • the preheated working medium may leave preheating zone 580 at outlet 584 at a temperature of, e.g., about 260°C.
  • the preheating within preheating zone 580 may be structurally associated with boiler sub-systems 534, in a funktional point of view, vapor separator 232 may be considered as an interface between ORC turbine module 510 and the working medium cycle section within boiler sub-systems 534. In that point of view, preheating within preheating zone 580 may be either considered to belong to the working medium cycle section of ORC turbine module 510 or to be an inserted additional working medium cycle section.
  • Outlet 584 may be fluidly connected to inlet 252 of vapor
  • boiler 538 may provide a heating cycle of the liquid working medium controlled by pump 236 such that the circulation speed of the working medium may provide the working medium to vapor separator 232 in a gas liquid mixed state.
  • the separated gas phase may be provided to superheating zone 460 of boiler 538 to further heat the gaseous phase working medium, for example, to a temperature of, e.g., 270°C before providing the super-heated gaseous phase working medium to turbine 212.
  • Rankine cycle systems disclosed herein are illustrated in Fig. 7 based on a schematic medium-sized diesel or gas engine.
  • Fig. 7 shows an exemplary air system and cooling systems of a conventional combustion engine 700 such as gas engine 130A or liquid fuel engine 130B used in pyrolysis-based power plant 100 described in connection with Fig. 2.
  • a conventional combustion engine 700 such as gas engine 130A or liquid fuel engine 130B used in pyrolysis-based power plant 100 described in connection with Fig. 2.
  • dual line arrows refer to the air system, e.g. stream of the charge air and exhaust gas
  • single line arrows refer to the cooling systems, e.g. the stream of a coolant medium, usually water.
  • Engine 700 may comprise a turbocharger system 710 (single or double stage), a high temperature cooling circle 720, and a low temperature cooling circle 730.
  • the compression of the charge air in turbocharger system 710 may increase the temperature of the charge air from 25°C to 225°C.
  • High temperature cooling circle 720 may reduce the temperature of the charge air from 225°C to 90°C and low temperature cooling circle may reduce the temperature of the charge air further from 90°C to 45°C such that engine 700 is charged with air at a temperature of about 45°C.
  • exhaust gas at a temperature of several hundred degrees may exit the combustion chamber and may be used to drive turbocharger system 710.
  • the temperature of the exhaust gas may be reduced to about 310°C.
  • heat can be recovered from coolant medium 571 of high temperature cooling circle 720 and/or low temperature cooling circle 730 as well as from high temperature exhaust gas 237 before or after turbocharger system 710.
  • boiler 238 is indicated to use the waste heat of exhaust gas 237 after turbocharger system 710 (for example, for preheating, evaporating, and superheating of the working medium in respective sections) and heat transfer unit 570 is indicated to use the waste heat of coolant medium 571 of high temperature cooling circle 720 and/or low temperature cooling circle 730 (for example, within the working medium cycle section within the ORC turbine module).
  • the term "genset” as used herein comprises inter alia internal combustion engines and steam or combustion turbine based power generating systems.
  • internal combustion engine as used herein is not specifically restricted and comprises any engine, in which a fuel combustion process is performed. Examples of fuel include gas or liquid fuel such as diesel, marine diesel, and pyrolysis oil. Examples of internal combustion engines for the herein disclosed configuration of a two-stage turbocharged system include medium speed internal combustion diesel engines, like inline and V-type engines of the series M20, M25, M32, M43 manufactured by Caterpillar Motoren GmbH & Co. KG, Kiel, Germany, operated in a range of 500 to 1000 rpm as well as high speed gas engines, e.g. provided by Caterpillar Motoren GmbH & Co. KG, Kiel
  • mixing the derived working medium liquid phase and the working medium received from the organic rankine turbine module may be a mixing chamber supplied, from the section for deriving the liquid and gaseous phases, with the derived working medium liquid phase and, from the organic rankine turbine module, with the working medium.
  • the modular ORC systems disclosed herein may allow increasing the over all efficiency (e.g. the generated power) of diesel, gas, biomass power plants as well as reducing the operation costs.
  • Percentages indicated herein with respect to the working medium being maintained in the liquid phase relate to volume percentages (% by volume), which in the case of a liquid does essentially not differ from mass percentages.
  • volume percentages % by volume
  • the working medium supplied to the boiler is in the liquid phase and represents 100% of the volume.
  • at least 15% by volume of the working medium is still in the liquid phase and 85% by volume or less of the working medium supplied to the boiler evaporated and are in the gaseous phase.

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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)

Abstract

La présente invention concerne, selon un aspect, un système à cycle de Rankine organique direct destiné à la génération de puissance en utilisant un fluide moteur. Selon un aspect de l'invention, le système à cycle de Rankine organique direct peut comprendre : un sous-système de chaudière comprenant une pompe et une chaudière, la pompe étant configurée pour pomper le fluide moteur à travers la chaudière ; un séparateur de vapeur raccordé à un orifice de sortie du fluide moteur de la chaudière, et configuré pour séparer une phase gazeuse du fluide moteur ; un module de turbine de Rankine organique raccordé de manière fluidique au séparateur de vapeur pour remplir à nouveau le séparateur de vapeur avec le fluide moteur qui a été utilisé dans le module de turbine de Rankine organique, le module de turbine de Rankine organique comprenant une turbine entraînée par la phase gazeuse du fluide moteur après sa séparation ; et un système de régulation, configuré pour commander la pompe en vue de régler la vitesse de circulation du fluide moteur à travers la chaudière de façon à ce qu'au moins 15 %, 20 %, 30 %, 40 %, ou 50 % du fluide moteur soient maintenus dans la phase liquide en sortant de la chaudière.
PCT/EP2012/001291 2011-03-25 2012-03-23 Système à cycle de rankine organique direct, système de génération de puissance à cycle combiné de conversion de la biomasse, et procédé de fonctionnement d'un cycle de rankine organique direct Ceased WO2012130421A2 (fr)

Priority Applications (1)

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CN201280014938.8A CN103443406B (zh) 2011-03-25 2012-03-23 直接有机朗肯循环系统及其操作方法、生物质联合循环发电系统

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EP11159901.5 2011-03-25
EP11159901.5A EP2503113B1 (fr) 2011-03-25 2011-03-25 Système de cycle de Rankine organique direct, système de génération d'énergie à cycle combiné avec la biomasse et procédé pour l'exploitation d'un cycle de Rankine organique direct

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WO2012130421A3 WO2012130421A3 (fr) 2013-01-24

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CN105143612A (zh) * 2013-03-25 2015-12-09 株式会社神户制钢所 排热回收装置
WO2015193580A1 (fr) 2014-06-16 2015-12-23 Arkema France Systeme de controle d'un cycle de rankine

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EP2781719A1 (fr) 2013-03-20 2014-09-24 Caterpillar Motoren GmbH & Co. KG Fonctionnement de moteurs à combustion interne sur des produits de pyrolyse
WO2017136735A1 (fr) * 2016-02-05 2017-08-10 Eaton Corporation Système de récupération de chaleur perdue utilisant un post-traitement de gaz d'échappement à base d'urée
CN107701250A (zh) * 2017-11-16 2018-02-16 山西易通环能科技集团有限公司 分布式生物质直燃热电联产系统
US11643949B1 (en) 2021-11-29 2023-05-09 Trane International Inc. Energy generation system for non-traditional combustible fluid source

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US20080289313A1 (en) 2005-10-31 2008-11-27 Ormat Technologies Inc. Direct heating organic rankine cycle
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CN105143612A (zh) * 2013-03-25 2015-12-09 株式会社神户制钢所 排热回收装置
WO2015193580A1 (fr) 2014-06-16 2015-12-23 Arkema France Systeme de controle d'un cycle de rankine

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CN103443406A (zh) 2013-12-11
EP2503113B1 (fr) 2016-03-23
WO2012130421A3 (fr) 2013-01-24
CN103443406B (zh) 2016-04-27
EP2503113A1 (fr) 2012-09-26

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