WO2015143280A1 - Système de récupération de chaleur perdue perfectionné et procédé permettant une commande optimale générale - Google Patents

Système de récupération de chaleur perdue perfectionné et procédé permettant une commande optimale générale Download PDF

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Publication number
WO2015143280A1
WO2015143280A1 PCT/US2015/021682 US2015021682W WO2015143280A1 WO 2015143280 A1 WO2015143280 A1 WO 2015143280A1 US 2015021682 W US2015021682 W US 2015021682W WO 2015143280 A1 WO2015143280 A1 WO 2015143280A1
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WO
WIPO (PCT)
Prior art keywords
waste heat
heat recovery
recovery system
control system
internal combustion
Prior art date
Application number
PCT/US2015/021682
Other languages
English (en)
Inventor
Mark R.J. Versteyhe
Arnout R.L. DE MARE
Original Assignee
Dana Limited
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 Dana Limited filed Critical Dana Limited
Priority to EP15715035.0A priority Critical patent/EP3119996A1/fr
Priority to CN201580015199.8A priority patent/CN106103912A/zh
Priority to US15/124,739 priority patent/US20170074122A1/en
Publication of WO2015143280A1 publication Critical patent/WO2015143280A1/fr

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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
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—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 combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor

Definitions

  • the present invention relates to energy recovery systems and more specifically to control of waste heat recovery systems used with internal combustion engines.
  • a conventional internal combustion engine typically has a limited brake thermal efficiency (BTE). Energy released during a combustion process utilized by the internal combustion engine is only partially converted to useful work. A large portion of the energy released during the combustion process is rejected as waste heat to an ambient environment of the internal combustion engine. The waste heat is typically dispersed to the ambient environment of the internal combustion engine through the use of a cooling system and an exhaust system of the internal combustion engine. Efficiencies of the internal combustion alone (not accounting for any power transmission losses) typically do not exceed about 50%.
  • BTE brake thermal efficiency
  • An amount of energy that is rejected as waste heat to the ambient environment is proportional to a fuel consumption of the internal combustion engine. Further, an amount of energy that is rejected as waste heat is inversely proportional to an efficiency of the internal combustion engine. With increasing fuel costs and emission regulations becoming more and more stringent, new technologies to improve an efficiency of internal combustion engines are highly sought after.
  • FIG. 1 schematically illustrates a waste heat recovery (WHR) system 110 for use with an internal combustion engine 112 that is known in the art.
  • the WHR system 110 is in driving engagement and fluid communication with the internal combustion engine 112.
  • a portion of the WHR system 110 is in driving engagement with a portion of the internal combustion engine 112 through a mechanical connection 114.
  • the WHR system 110 may utilize the organic Rankine cycle; however, it is understood that other thermodynamic cycles may also be used with the WHR system 110.
  • the components of the WHR system 110, the components of the internal combustion engine 112, and a working fluid used with the WHR system 110 may be adapted for use with other thermodynamic cycles.
  • the internal combustion engine 112 includes a turbocharger 115.
  • the internal combustion engine 112 is used as a power source for a vehicle (not shown); however, it is understood that the internal combustion engine 112 may be used in other applications, such as in stationary power generation applications.
  • the WHR system 110 comprises a pump 116, a heat exchanger 118, an expander 120, a condenser 122, and a plurality of fluid conduits 124.
  • the pump 116 is in fluid communication with the heat exchanger 118 and the condenser 122.
  • the expander 120 is in fluid communication with the condenser 122 and the heat exchanger 118.
  • the WHR system 110 is a closed circuit, thermodynamic device that employs a liquid-vapor phase change to convert heat energy into motive power. It is understood that the WHR system 110 may include additional components not illustrated in FIG. 1 , such as, but not limited to, a working fluid reservoir, a plurality of valves, and a plurality of sensors in communication with a control system.
  • the plurality of fluid conduits 124 facilitate fluid communication to occur between each of the components 116, 118, 120, 122 and may comprise a plurality of preformed rigid tubes, flexible conduits, or conduits formed within a portion of each of the components 116, 118, 120, 122.
  • the heat exchanger 118 facilitates thermal communication between an exhaust conduit 126 of the internal combustion engine 112 and a portion of a plurality of fluid conduits 124 facilitating fluid communication between the components. It is understood that the heat exchanger 118 may comprise a plurality of heat exchangers.
  • the heat exchanger 118 is conventional and well known in the art, and may also be referred to as an evaporator.
  • the working fluid passes through a portion of the heat exchanger 18, the working fluid is heated and evaporated by energy imparted to the working fluid by the exhaust gases passing through the exhaust conduit 126.
  • the working fluid leaves the heat exchanger 118 in a gaseous state.
  • the most notable conditions that affect efficiency are temperature and pressure.
  • a source of heat used with the WHR system is typically constant and many of the working conditions the WHR system is exposed to are fixed.
  • the working conditions of the WHR system should constantly be adapted to the heat source, which will exhibit changes in temperature and flow rate.
  • Each subsystem of the WHR system has its own dynamics and optimal working range and system states and most subsystems have one or more control variables that can be manipulated to drive the subsystem dynamically to a given state.
  • each subsystem is controlled to obtain a good working condition for that particular subsystem (for example, the feed pump speed is adjusted to control evaporating temperature, and a rotational speed of the expanders is adjusted to change a pressure within the WHR system).
  • a good working condition for that particular subsystem for example, the feed pump speed is adjusted to control evaporating temperature, and a rotational speed of the expanders is adjusted to change a pressure within the WHR system.
  • all of these subsystems are coupled together either due to the working fluid or through mechanical connections. Consequently, most control inputs affect the overall system. A highest efficiency of the total system is thus only reached if all control inputs are correctly set. What such a task requires is global optimization of the system.
  • the standard practice to optimize WHR systems is to either control only the speed of the feed pump or to control the speed of the feed pump and the expander to adjust an evaporating temperature and a pressure within the WHR system.
  • the expander is typically coupled to a generator, for example, in stationary applications.
  • a plurality of set points used for the temperature and pressure are typically determined using trial-and-error methods and operator guesswork.
  • WO2011137980 and US2011203278 The method is focused on an organic Rankine cycle for stationary applications where the expander is connected to a generator, which in turn is connected to an electrical grid through the use of an inverter.
  • a waste heat recovery system for an internal combustion engine and controller that implements a control strategy that increases an efficiency of the internal combustion engine and constantly adapts a control strategy based on fluctuations of an ability to heat and cool the waste heat recovery system.
  • the present invention is directed to a waste heat recovery system and control system and method of controlling a waste heat recovery system and control system.
  • the waste heat recovery system and control system comprises a pump, a heat exchanger, an expansion device, a condenser, a plurality of sensors, and a controller.
  • the heat exchanger is in fluid communication with the pump and thermal communication with an exhaust of the internal combustion engine.
  • the expansion device is in fluid
  • the condenser is in thermal communication with the expansion device and the pump.
  • the plurality of sensors is in communication with the waste heat recovery system.
  • the controller is in communication with the plurality of sensors. In response to information obtained from the plurality of sensors, the controller calculates an efficiency of the waste heat recovery system based on models of the waste heat recovery system and implements a set of control inputs to implement the calculated efficiency on the waste heat recovery system.
  • the present invention is directed to a method of controlling a waste heat recovery system and control system for use with an internal combustion engine.
  • the method comprises the steps of providing the waste heat recovery system, providing the control system, obtaining
  • the waste heat recovery system comprises a pump, a heat exchanger in fluid communication with the pump and thermal communication with an exhaust of the internal combustion engine, an expansion device in fluid communication with the heat exchanger, and a condenser in thermal communication with the expansion device and the pump.
  • the control system comprises a plurality of sensors in communication with the waste heat recovery system and a controller in communication with the plurality of sensors.
  • FIG. 1 is a schematic illustration of a combined internal combustion engine and waste heat recovery system according to the prior art.
  • FIG. 2 is a schematic illustration of a combined internal combustion engine and waste heat recovery system including a controller according to an embodiment of the present invention.
  • DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS It is to be understood that the invention may assume various alternative orientations and step sequences, except where expressly specified to the contrary. It is also to be understood that the specific devices and processes illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the inventive concepts defined herein. Hence, specific dimensions, directions or other physical characteristics relating to the embodiments disclosed are not to be considered as limiting, unless expressly stated otherwise.
  • FIG. 2 schematically illustrates a waste heat recovery (WHR) system
  • the WHR system 200 and the combustion engine 202 are in communication with a control system 203.
  • the WHR system 200 is in driving engagement and fluid communication with the internal combustion engine 202.
  • a portion of the WHR system 200 is in driving engagement with a portion of the internal combustion engine 202 through a ratio adapting device 204.
  • the WHR system 200 may utilize the organic Rankine cycle; however, it is understood that other thermodynamic cycles may also be used with the WHR system 200.
  • the components of the WHR system 200, the components of the internal combustion engine 202, and a working fluid used with the WHR system 200 may be adapted for use with other thermodynamic cycles.
  • the internal combustion engine 202 includes a turbocharger 206.
  • the internal combustion engine 202 is used as a power source for a vehicle (not shown); however, it is understood that the internal combustion engine 202 may be used in other applications, such as in stationary power generation applications.
  • the internal combustion engine 202 comprises a primary portion 208, the turbocharger 206, and an engine output 210.
  • the primary portion 208 is in fluid communication with the turbocharger 206 through an intake 212 and an exhaust 214 of the primary portion 208.
  • the primary portion 208 is in driving engagement with the engine output 210.
  • the internal combustion engine 202 may be any type of internal combustion engine which may be fitted with a turbocharger.
  • the primary portion 208 comprises at least an engine block; however, it is understood that the primary portion 208 may also include components typically used with an internal combustion engine, such as a plurality of valves, a plurality of pistons, at least one crankshaft, a plurality of connecting rods, a clutching device, a ratio adapting device, a fuel delivery system, an ignition system, and a cooling system.
  • components typically used with an internal combustion engine such as a plurality of valves, a plurality of pistons, at least one crankshaft, a plurality of connecting rods, a clutching device, a ratio adapting device, a fuel delivery system, an ignition system, and a cooling system.
  • the turbocharger 206 includes a turbine portion 216, a compressor portion 218, and a shaft 220.
  • the turbine portion 216 and the compressor portion 218 are drivingly engaged with the shaft 220.
  • the turbine portion 216 is driven by exhaust gases via the exhaust 214.
  • the turbine portion 216 is drivingly engaged with the compressor portion 218 to provide compressed air to the intake 212.
  • the turbine portion 216 comprises a plurality of blades (not shown) attached to a rotor (not shown) which is rotatingly disposed in a housing (not shown).
  • the rotor is fixed to the shaft 220.
  • energy present in the exhaust gases leaving the exhaust 214 of the primary portion 208 is imparted to the plurality of blades, and thus to the rotor and the shaft 220.
  • the exhaust gases After exiting the turbine portion 216, the exhaust gases continue within an exhaust conduit 222 in fluid
  • the compressor portion 218 comprises an impeller (not shown) which is rotatingly disposed in a housing (not shown).
  • the impeller is fixed to the shaft 220.
  • energy is imparted to air in the housing through rotation of the impeller, which is driven by the shaft 220, thus increasing a pressure of air at the intake 212 of the primary portion 208.
  • the engine output 210 is a mechanical component driven by the primary portion 208.
  • the engine output 210 may be a vehicle driveline or a portion of a vehicle driveline, such as a driveshaft, a transmission, or a flywheel. Alternately, it is understood that the engine output 210 may merely facilitate driving engagement between the primary portion 208 and a portion of an electric generator, for example.
  • the WHR system 200 comprises a pump 224, a heat exchanger 226, an expander 228, a condenser 230, an expander bypass 232, a plurality of fluid conduits 234, and a heat exchanger bypass 235.
  • the pump 224 is in fluid communication with the heat exchanger 226 and the condenser 230.
  • the expander 228 is in fluid communication with the condenser 230 and the heat exchanger 226.
  • the expander bypass 232 allows the expander 228 to be selectively removed from the WHR system 200.
  • the WHR system 200 is a closed circuit, thermodynamic device that employs a Iiquid-vapor phase change to convert heat energy into motive power. It is understood that the WHR system 200 may include additional components not illustrated in FIG.
  • the plurality of fluid conduits 234 facilitate fluid communication to occur between each of the components 224, 226, 228, 230, 232, 234 and may comprise a plurality of preformed rigid tubes, flexible conduits, or conduits formed within a portion of each of the components 224, 226, 228, 230, 232, 234.
  • the pump 224 transfers the working fluid used with the WHR system
  • the pump 224 is conventional and well known in the art.
  • the pump 224 may be an electrically operated pump designed to transfer the working fluid in a liquid state. Alternately, it is understood that the pump 224 may be mechanically driven by a rotating component of the primary portion 208, the turbocharger 206, or the expander 228.
  • the heat exchanger 226 facilitates thermal communication between the exhaust conduit 222 and a portion of the plurality of fluid conduits 234. It is understood that the heat exchanger 226 may comprise a plurality of heat exchangers.
  • the heat exchanger 226 is conventional and well known in the art, and may also be referred to as an evaporator.
  • the heat exchanger 226 includes a heat exchanger bypass 235. As the working fluid passes through a portion of the heat exchanger 226, the working fluid is heated and evaporated by energy imparted to the working fluid by the exhaust gases passing through the exhaust conduit 222. As a result of the thermal communication between a portion of the plurality of fluid conduits 234 and the exhaust conduit 222, the working fluid leaves the heat exchanger 226 in a gaseous state.
  • the heat exchanger bypass 235 facilitates bypassing the exhaust conduit 22 around the heat exchanger 226.
  • the heat exchanger bypass 235 comprises an exhaust bypass valve 236 and an exhaust bypass conduit 237.
  • the exhaust bypass valve 236 is in communication with the control system
  • the exhaust bypass valve 236 In response to a signal received from the control system 203, the exhaust bypass valve 236 is placed in an engaged position. In the engaged position, the exhaust bypass valve 236 removes the heat exchanger 226 from fluid communication with the exhaust conduit 222. It is understood that the exhaust bypass valve 236 may be configured to only direct a portion of the exhaust passing through the heat exchanger 226 through the exhaust bypass conduit 237, and that in response to a signal received from the control system 203, the exhaust bypass valve 236 may be variably engaged.
  • the expander 228 extracts work from the working fluid in the gaseous state.
  • the expander 228 is conventional and well known in the art, and may also be referred to as a turbine.
  • the expander 228 comprises a plurality of blades (not shown) attached to a rotor (not shown) which is rotatingly disposed in a housing (not shown).
  • the rotor is fixed to a shaft 238, which is in driving engagement with the ratio adapting device 204.
  • the ratio adapting device 204 is drivingly engaged with the engine output 210 to deliver additional work thereto.
  • the expander bypass 232 facilitates fluid communication of the working fluid between a portion of the plurality of fluid conduits 234 between the heat exchanger 226 and the expander 228 and a portion of the plurality of fluid conduits 234 between the condenser 230 and the expander 228.
  • the expander bypass 232 comprises a bypass valve 239 and a bypass conduit 240.
  • the bypass valve 239 is in communication with the control system 203. In response to a signal received from the control system 203, the bypass valve 239 is placed in an engaged position. In the engaged position, the bypass valve 239 places the heat exchanger 226 in fluid communication with the condenser 230.
  • bypass valve 239 may be configured to only direct a portion of the working fluid passing through the heat exchanger 226 through the bypass conduit 240, and that in response to a signal received from the control system 203, the bypass valve 239 may be variably engaged.
  • the working fluid leaving the heat exchanger 226 is expanded in the expander 228, imparting work to the plurality of blades, and thus to the rotor and the shaft 238.
  • the working fluid drives the expander 228 and the pressure and temperature of the working fluid are reduced.
  • the working fluid continues within a portion of the plurality of fluid conduits 234 to the condenser 230.
  • the condenser 230 facilitates thermal communication between the working fluid in the gaseous state and an ambient environment of the WHR system 200.
  • the condenser 230 is a heat exchanging device and is
  • the condenser 230 may be a liquid to air type heat exchanger or a liquid to liquid type heat exchanger. As the working fluid passes through a portion of the condenser 230, the working fluid is cooled as the energy within the working fluid is distributed by the condenser 230 to the ambient environment of the WHR system 200. The condenser 230 provides further cooling for the working fluid, in addition to the temperature drop that occurs as the working fluid passes through the expander 228. As a result of the thermal communication between the working fluid and the condenser 230, the working fluid condenses and leaves the condenser 230 in a liquid state.
  • the ratio adapting device 204 is a continuously variable transmission that is drivingly engaged with the shaft 238 and the engine output 210. Further, it is understood that the ratio adapting device 204 may be drivingly engaged with a portion of the expander 228 or a portion of the turbocharger 206. The ratio adapting device 204 facilitates driving engagement between the shaft 238 and the engine output 210, despite a difference and a variability of a rotational speed of each of the shaft 238 and the engine output 210.
  • the ratio adapting device 204 may include a clutching device (not shown) for drivingly
  • the ratio adapting device 204 may be a pulley-belt style continuously variable transmission.
  • the pulley-belt style continuously variable transmission comprises of a pair of variable-diameter pulleys, each shaped like a pair of opposing cones, with a belt running between them.
  • the pulley-belt style continuously variable transmission is conventional and well known in the art.
  • the ratio adapting device 204 may comprise another type of ratio adapting device, such as a belted connection, a fixed ratio transmission, or a fixed ratio transmission paired with a slipping clutch, for example.
  • the control system 203 is in communication with the WHR system 200 and the internal combustion engine 202.
  • the control system 203 comprises a plurality of sensors 242 and actuators 244 in communication with a controller 246.
  • the plurality of sensors 242 and actuators 244 are incorporated into the WHR system 200 and the internal combustion engine 202 to facilitate
  • the control system 203 may incorporate the following sensors 242:
  • a temperature sensor 242 configured to measure a temperature of an ambient environment of the WHR system 200
  • a pressure sensor 242 configured to measure an air pressure of an ambient environment of the WHR system 200 •
  • a sensor 242 configured to measure a rotational speed of the expander 228 or a pressure at an inlet or an outlet of the expander 228
  • a sensor 242 configured to measure a rotational speed of the pump 224
  • a sensor 242 configured to measure a speed ratio of the ratio adapting device 204
  • a sensor 242 configured to measure a state of operation of the internal combustion engine 202 through an engine control unit 246
  • a sensor 242 configured to measure a state of operation of a portion of a driveline associated with the internal combustion engine 202 through a gearbox controller 248
  • the control system 203 may incorporate the following actuators 244:
  • An actuator 244 engaged with the bypass valve 239 to adjust a position thereof
  • An actuator 244 configured to actuate a cooling fan 250 to facilitate dissipation of heat using the condenser 230
  • the controller 246 is a programmable logic controller and/or a computer based system including computer-readable media containing at least one programmatic algorithm to facilitate enhanced control over the WHR system 200 using a plurality of steps, which are described hereinbelow. It is
  • the controller 246 uses the plurality of sensors, measures the various states of operation of the WHR system 200.
  • the various states of operation of the WHR system 200 that may be measured by the sensors 242 are described above.
  • the mass flow can also be estimated based on a throttle position and a rotational speed of the internal combustion engine 202.
  • the models may be such as static or dynamic models where the modeling effort is focused on the parts of the WHR system 200 with the slowest dynamics.
  • static models may include, but are not limited to, look up tables or formulae, both of which may provide some parameters on the actual conditions.
  • dynamic models may include, but are not limited to, models that take into account a history of the WHR system 200. For example, a dynamic model might take into account past performance of the WHR system 200 before and/or after a particular modeled event to determine the most efficient way to proceed in the current circumstance.
  • the heat exchanger 226 is one of the parts of the WHR system 200 that is more likely to have slow dynamics.
  • Rotating elements of the WHR system 200 such as the expander 228, may also have slow dynamics because of their rotational inertia.
  • the models may be focused on the heat exchanger 226 and/or the rotating elements because of their slow dynamics compared to other components of the WHR system 200.
  • the possible control inputs of the models may be discrete control inputs of the WHR system 200, such as enabling the expander bypass 232 or enabling the cooling fan 250, as well as continuous control inputs, such as a rotational speed of the pump 224 or a ratio of the ratio adapting device 204.
  • a maximum efficiency of the WHR system 200 is searched and applied by the controller 246.
  • the maximum efficiency of the WHR system 200 was determined using the aforementioned models. Once the maximum efficiency is determined by the models, the efficiency of the WHR system 200 is set, and the control inputs are known. The controller 246 then implements the control inputs.
  • constraints on the states of the WHR system 200 need to be maintained. These constraints include, but are not limited to, a minimal rotational speed and a maximal rotational speed of the pump 224 and the expander 228, a minimal pressure and a maximal pressure of the components of the WHR system 200, temperature limits of the components of the WHR system 200, and a presence of positive superheating, which must always be maintained by the controller 246 to avoid damage to the expander 228. It can be appreciated that controlled superheating ensures condensation of the working fluid does not occur in the expander 228, or damage of the expander 228 may result.
  • the controller 246 can use the dynamic models of the WHR system 200, or parts of the WHR system 200, and knowledge about the duty cycle of the WHR system 200 to predict a future state of the WHR system 200 and to optimize the efficiency, or power take-off, over a longer period of time.
  • the calculations performed by the controller 246 to obtain the maximum efficiency can also be executed offline or by another computer system than the controller 246 of the WHR system 200.
  • the results of the optimization can be stored in tables or functions that subsequently are stored on a computer- readable medium and be used by the controller 246 of the WHR system 200.
  • the controller 246 can also be equipped with additional connections and communication methods to other controllers including, but not limited to, global positioning system information, radio based information, among others when the controller 246 is configured for mobile applications.
  • the data obtained from these devices can be used by the controller 246 to optimize the efficiency of the WHR system 200, as described above.
  • the controller 246 can issue commands to other controllers, such as the engine control unit 246 or the gearbox controller 248, to regulate their respective controlled systems.
  • commands may be issued by the controller 246 to the engine control unit 246 regarding exhaust gas recirculation.
  • control system 203 and WHR system 200 for use with an internal combustion engine 202 have many advantages over control strategies used with WHR systems known in the art.
  • control strategies used with WHR systems known in the art control only utilize control of a speed of a feed pump or control of the speed of a feed pump and an expander to set an evaporating temperature and a pressure of the WHR system.
  • a plurality of set points used for the temperature and pressure used with these control strategies are typically determined using trial-and-error methods and operator guesswork.
  • only the optimal set points for temperature and pressure are presented. Consequently, the WHR system in total is not optimized, but rather just the above-mentioned set points.
  • the known art also suffers from other disadvantages compared to the control system 203 and WHR system 200 for use with an internal combustion engine 202 and control strategy described hereinabove.
  • the known art suffers from the following disadvantages:
  • the known art systems typically utilize a search method in an effort to optimize the WHR system.
  • the search method may be generally described as making a change to a control strategy and then measuring a resulting output of the WHR system.
  • the known art systems thus seek a desired optimization based on changes made to an input.
  • the various possible conditions are simulated in real time to determine the control inputs most likely to result in optimization based on predictive behavior. In other words, the control inputs are not changed until the optimized control inputs have been calculated using the models described hereinabove.
  • the control system 203, the WHR system 200, and the control strategy is able to perform a globalized optimal control of the WHR system 200 by using all possible control inputs in the optimization, while also taking the interactions of the subsystems into account. This means that instead of locally optimizing the subsystems, the overall efficiency of the WHR system 200 is maximized while considering the constraints of the subsystems. Moreover, the dynamics of the WHR system are explicitly used to optimize the efficiency and future efficiency is optimized by using the dynamics of the WHR system and knowledge about the duty cycle and expected operating conditions.

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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

L'invention porte sur un système de récupération de chaleur perdue et sur un système de commande ainsi que sur un procédé de commande d'un système de récupération de chaleur perdue et d'un système de commande. Le système de récupération de chaleur perdue et le système de commande comprennent une pompe, un échangeur de chaleur, un dispositif d'expansion, un condenseur, une pluralité de capteurs et un dispositif de commande. L'échangeur de chaleur est en communication thermique avec un échappement du moteur à combustion interne. Le condenseur est en communication thermique avec le dispositif d'expansion et avec la pompe. La pluralité de capteurs est en communication avec le système de récupération de chaleur perdue. Le dispositif de commande est en communication avec la pluralité de capteurs. En réponse à des informations obtenues depuis la pluralité de capteurs, le dispositif de commande calcule un rendement du système de récupération de chaleur perdue sur la base de modèles du système de récupération de chaleur perdue et met en œuvre un ensemble d'entrées de commande pour mettre en œuvre le rendement calculé sur le système de récupération de chaleur perdue.
PCT/US2015/021682 2014-03-21 2015-03-20 Système de récupération de chaleur perdue perfectionné et procédé permettant une commande optimale générale WO2015143280A1 (fr)

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Application Number Priority Date Filing Date Title
EP15715035.0A EP3119996A1 (fr) 2014-03-21 2015-03-20 Système de récupération de chaleur perdue perfectionné et procédé permettant une commande optimale générale
CN201580015199.8A CN106103912A (zh) 2014-03-21 2015-03-20 允许全局优化控制的增强型废热回收系统和方法
US15/124,739 US20170074122A1 (en) 2014-03-21 2015-03-20 Enhanced waste heat recovery system and method allowing global optimal control

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US201461968513P 2014-03-21 2014-03-21
US61/968,513 2014-03-21

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US (1) US20170074122A1 (fr)
EP (1) EP3119996A1 (fr)
CN (1) CN106103912A (fr)
WO (1) WO2015143280A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
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JP2015183595A (ja) * 2014-03-24 2015-10-22 三菱日立パワーシステムズ株式会社 排熱回収装置、これを備えているガスタービンプラント、及び排熱回収方法
JP2015183590A (ja) * 2014-03-24 2015-10-22 三菱日立パワーシステムズ株式会社 排熱回収システム、これを備えているガスタービンプラント、排熱回収方法、及び排熱回収システムの追設方法
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JP2015183590A (ja) * 2014-03-24 2015-10-22 三菱日立パワーシステムズ株式会社 排熱回収システム、これを備えているガスタービンプラント、排熱回収方法、及び排熱回収システムの追設方法
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WO2017073195A1 (fr) * 2015-10-29 2017-05-04 三菱日立パワーシステムズ株式会社 Centrale à cycle combiné et procédé pour commander le fonctionnement d'une centrale à cycle combiné
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EP3485156A4 (fr) * 2016-07-12 2020-03-11 Scania CV AB Procédé et système de commande de la vitesse de rotation d'un détendeur dans un système de récupération de chaleur perdue
WO2019166391A1 (fr) * 2018-02-27 2019-09-06 Robert Bosch Gmbh Circuit de réglage pour systèmes de récupération de chaleur dégagée
US11448099B2 (en) 2018-02-27 2022-09-20 Robert Bosch Gmbh Control circuit for waste heat recovery systems

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