WO2019007622A1 - Optimiseur de performance pour système de récupération de chaleur perdue - Google Patents

Optimiseur de performance pour système de récupération de chaleur perdue Download PDF

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Publication number
WO2019007622A1
WO2019007622A1 PCT/EP2018/064855 EP2018064855W WO2019007622A1 WO 2019007622 A1 WO2019007622 A1 WO 2019007622A1 EP 2018064855 W EP2018064855 W EP 2018064855W WO 2019007622 A1 WO2019007622 A1 WO 2019007622A1
Authority
WO
WIPO (PCT)
Prior art keywords
evaporator
working medium
power optimizer
recovery system
waste heat
Prior art date
Application number
PCT/EP2018/064855
Other languages
German (de)
English (en)
Inventor
Adrian Trachte
Thomas Specker
Derya LINDENMEIER
Wolfgang Kemmetmueller
Christian Fleck
Carolina Passenberg
Andreas Kugi
Herwig KOPPAUER
Matthias Bitzer
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2019007622A1 publication Critical patent/WO2019007622A1/fr

Links

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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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

Definitions

  • the present invention relates to a power optimizer with which the efficiency of a waste heat recovery system for vehicles can be improved.
  • waste heat In a motor vehicle, most of the energy supplied to the internal combustion engine is currently lost via waste heat. Most of this waste heat is removed from the vehicle via the cooling circuit and with the exhaust gas. Various systems are known with which a part of this waste heat can be converted into a usable form of energy.
  • WO 2016/089 285 AI discloses a system which removes the waste heat from the exhaust gas via a thermoelectric generator and converts it into electrical energy, as well as an optimization method for the associated overall efficiency.
  • DE 10 2014 019 684 AI discloses an alternative system which removes waste heat from the cooling circuit of the internal combustion engine and transfers it to a working medium, which then performs mechanical work in an expansion machine.
  • Operating condition of the vehicle will be either only one of two available Heat exchangers or both heat exchangers used, so that the efficiency of the energy conversion is always optimal.
  • the waste heat recovery system comprises at least one evaporator for transferring waste heat from the exhaust gas generated by the vehicle into a
  • Expansion machine at least one condenser for condensing the relaxed in the expansion machine vaporous working medium in the liquid state, with the release of heat to the vehicle cooling system.
  • At least one conveying device is provided for increasing the pressure of the condensed working medium and conveying into the evaporator.
  • the working medium is guided in a closed circuit and can absorb waste heat again in the evaporator.
  • the expansion machine may in particular be a turbine or a scroll expander.
  • a control circuit acts at least on the delivery rate mw of the delivery device as a manipulated variable and regulates at least the temperature Tw of the working medium emerging from the evaporator to a desired value T w , s.
  • Power optimizer as a set of sizes from which at least the temperature TA and the mass flow ⁇ of the exhaust gas emerge at the location of the evaporator as input and assigns each value vector of these sizes to a setpoint Tw, s for the temperature of the effluent from the evaporator working fluid.
  • Power optimizer is designed to deliver this setpoint Tw, s to the control loop.
  • the power optimizer can in particular directly receive the temperature TA and the mass flow ⁇ of the exhaust gas as input. From the temperature TA and the mass flow ⁇ of the exhaust gas results in the
  • the control loop does not have to act exclusively on the delivery rate mw of the conveyor which conveys the working medium.
  • the control loop can also act on further manipulated variables. For example, if the condenser flows through a cooling medium, then the mass flow of the
  • Cooling medium serve as a manipulated variable.
  • switch positions for valves that redirect the flow of the exhaust gas or of the working medium can also serve as manipulated variables.
  • the evaporator connected in the exhaust gas flow can be bridged with an exhaust gas bypass line, which can be activated via an exhaust gas bypass valve.
  • the expansion machine connected in the flow of the working medium can be bridged with a working bypass line, which can be activated via a working bypass valve.
  • a possibly existing reservoir for the working medium can over
  • Tank valves to be connected to the circuit of the working fluid whose switching positions can also serve as manipulated variables. If that
  • Waste heat recovery system is an e-WHR system in which the turbine is coupled to a generator and the turbine related mechanical power is further converted into electrical power, the set by the turbine-generator unit speed can serve as another control variable.
  • the optimization goal may be that received as input
  • the power optimizer is advantageously designed to be in the
  • This state variable can be applied in particular to the
  • Waste heat recovery system refer to the vehicle or to the environment. In this way, it is advantageously avoided that the
  • State variables which may be subject to boundary conditions are, in particular, thermodynamic state variables of the circuit for the working medium, such as, for example, pressures and temperatures.
  • state variables of the exhaust gas or of the cooling system of the vehicle may also be limited by boundary conditions. These boundary conditions may differ in particular from vehicle to vehicle.
  • Optimizer takes into account such boundary conditions, thus its universal suitability for use in various vehicles is improved.
  • such boundary conditions can be established, with which it is ensured that the working medium of the expansion machine is supplied as drip-free steam, ie as steam, which is not wet steam. Since drops have a much higher density than steam, they can
  • boundary conditions for example, to a maximum temperature behind the evaporator, to a minimum overheating before Expansion machine, to a minimum subcooling behind the condenser, to a maximum high pressure, to a minimum and maximum
  • the power optimizer additionally receives at least one disturbance which has an influence on the operation of the waste heat recovery system, without itself being directly influenceable, as input.
  • the accuracy of the assignment made in the performance optimizer, which set point Tw, s for the temperature of the working medium leaving the evaporator is quantitatively improved to what operating state of the waste heat recovery system (for example, at which net power delivered by this system).
  • the optimum operating point of the waste heat recovery system is more accurately met.
  • Such disturbances can, for example, the temperature of the exhaust gas upstream of the evaporator, the total mass flow of accumulating exhaust gas, the
  • the values of the state variables, and / or the disturbances can be obtained in any manner and fed to the power optimizer, and / or the control loop. For example, they can be measured directly with sensors, but can also be derived from other variables, for example with the aid of models and / or characteristic diagrams. The values can also be obtained, for example, from other control devices in the vehicle.
  • the power optimizer may, for example, the engine speed, the
  • Exhaust gas recirculation and accordingly an exhaust gas recirculation valve, is mandatory in all modern vehicles.
  • the temperature TA and the mass flow mA of the exhaust gas at the location of the evaporator can be determined.
  • the temperature TA of the exhaust gas passes through maps or models from the
  • the switching position of the exhaust gas recirculation valve determines how much exhaust gas arrives at which evaporator.
  • the power optimizer may additionally include the
  • thermodynamic cycle of the working fluid becomes quantitative
  • the control loop of the waste heat recovery system may additionally be adapted to the pressure pw of the exiting from the evaporator
  • the power optimizer can then additionally be designed to also assign to each value vector of the quantities received as input a desired value pw, s for the pressure pw.
  • a desired value pw, s for the pressure pw is assigned to each value vector of the quantities received as input.
  • Power Optimizer is a model of the waste heat recovery system and is designed to use this model as input
  • the model may refer to the stationary state of the waste heat recovery system and be executed on a computing unit, such as a controller. This requires a corresponding entrained in the vehicle
  • model can be flexibly updated changes maximum.
  • components or supplies such as engine oil
  • Flow resistance of a particulate filter in the exhaust aftertreatment may increase with increasing filling of the filter to then abruptly drop after the burning of the filter.
  • a numerical optimization calculation can be carried out, at the end of which each value vector of the input variables is assigned a setpoint value Tw, s for the temperature Tw.
  • the model can, for example
  • balance equation for an energy derived from the principle of energy conservation can be used to calculate the balance equation for a mass flow.
  • the working fluid in the liquid state is incompressible and can not be generated or destroyed in a closed circuit.
  • the model can be used as state variables, for example, the specific enthalpy and fluid and wall temperatures of the evaporator (or the evaporator, if there are several) and the capacitor, and the pressure, the specific enthalpy and the temperatures of the high and
  • High-pressure piping is the piping from the conveyor via the evaporator or to the
  • Low-pressure piping is understood to mean the piping from the outlet of the expansion machine via the condenser to the inlet of the conveyor.
  • the model can, for example, as input by the
  • the model may include, for example, temperatures and mass flows of the exhaust gas and the ambient temperature as additional acting variables.
  • the power optimizer may include at least one map that associates a value Tw.s for the temperature of the working fluid exiting the evaporator with the value vector obtained as input.
  • a map can be calculated in advance, so that less computing capacity is required in the vehicle itself. It can also be sold, for example, as an update.
  • the power optimizer additionally assigns to the value vector obtained as input a desired value P, S for the low pressure P of the working medium after expansion in the expansion machine, and / or a desired value ns for the stationary speed n of the expansion machine.
  • the input additionally has at least one value for the
  • Cooling water temperature at the location of the capacitor include. After the above, the invention also relates to a
  • Waste heat recovery system comprises at least one evaporator for transferring waste heat from the exhaust gas generated by the vehicle into a working medium, at least one expansion machine drivable by the working medium, at least one condenser for
  • a control loop which acts at least on the delivery rate mw of the conveyor as a control variable and at least the temperature Tw of the emerging from the evaporator working fluid to a target value Tw, s controls.
  • the system is characterized in that a power optimizer according to the invention is provided and supplies the desired value Tw, s to the control loop.
  • the evaporator is in the exhaust gas flow between the outlet of a
  • Exhaust aftertreatment system and an exhaust of the vehicle switched. Then the waste heat after the exhaust aftertreatment system can still be used as process heat.
  • a second evaporator is connected in the exhaust gas flow of an exhaust gas recirculation in the engine of the vehicle.
  • Such an evaporator in addition to its actual function of energy recovery at the same time support the exhaust gas recirculation, among other things, intended cooling of the exhaust gas.
  • the waste heat recovery can then synergistically interact with the exhaust gas recirculation.
  • both evaporators feed a common expansion machine with the
  • the power optimizer according to the invention may be in a separate
  • Control unit implemented, but also for example as pure
  • a computer program product having machine readable instructions which, when executed on a computer and / or on a controller, upgrade the computer and / or the controller to a power optimizer according to the invention. Further measures improving the invention will be described in more detail below together with the description of the preferred embodiments of the invention with reference to figures.
  • FIG. 2 detailed view of the stationary optimization module 12
  • FIG. 3 Integration of the waste heat recovery system 2 into the vehicle 3.
  • control circuit 27 acts via the delivery rate mw of FIG. 1
  • Conveyor 26 as here exemplified control variable to the waste heat recovery system 2 a.
  • a temperature Tw of the working medium 23 sets.
  • This temperature Tw is fed back into the control loop 27 and there regulated by action on the manipulated variable mw to a desired value Tw, s.
  • the temperature Tw of the working medium 23 is shown by way of example only as one of the variables that change as a manipulated variable when exposed to the delivery rate mw.
  • An online parameter and state estimation 27a receives the delivery rate mw and the temperature Tw, and optionally also other, not in FIG.
  • Waste heat recovery system 2 From this state variables 27 b are determined and forwarded to both the control circuit 27 and the power optimizer 1.
  • the power optimizer 1 obtains quantities from which the temperature TA and the mass flow mA of the exhaust gas 31 at the location of the evaporator 21, 22 emerge, as input 11, wherein at any time the respective input values are combined in a value vector.
  • This value vector is first supplied to a stationary optimization module 12, which contains a stationary model 2a of the waste heat recovery system 2.
  • a desired value Tw, s for the temperature Tw is determined.
  • This setpoint value Tw, s is fed to the control loop 27.
  • FIG. 2 shows a detailed view of the stationary optimization module 12.
  • the optimization module 12 contains a quality measure module 12 a and a
  • the quality M of a candidate Tw, s * is embodied on the basis of the current engine operating point, which is embodied by the temperature TA and the mass flow ⁇ of the exhaust gas 31 obtained as input 11, in conjunction with the further state variables and measures 27b. for the setpoint Tw, s rated.
  • the model 2a is used here.
  • Essential criteria for the quality assessment is the quality criterion 14, that of the
  • Waste heat recovery system 2 net power is maximized, as well as the boundary condition 15, and that the permissible operating range is maintained.
  • the optimization algorithm 12b contains the strategy according to which candidates Tw, s * are selected and tested with the quality measure module 12a. This strategy governs that the final setpoint Tw, s, which maximizes net performance, is found much faster than the real-time impracticability of all possible numerical values.
  • the model 2a assumes that the input variables 11 are combined in a vector u and additional, not directly influenceable disturbances in a vector d.
  • the stationary states 27b are combined in a vector x, these states 27b in turn depending on the vector u of the input variables 11 and the vector d of the disturbance variables.
  • the quality criterion 14 for the net output of the waste heat recovery system to be minimized in the context of optimization can be, for example, the form -P E (x (u,), u) + P F (x (u,), u) + P K (u)
  • PE is the power output from the expansion machine 24.
  • PF is the power to be spent on the conveyor 26, and
  • ⁇ is the power to spend on coolant pumps.
  • FIG. 3 shows how the waste heat recovery system 2 can be integrated into a vehicle 3 by way of example.
  • Combustion air 30 is sucked in via a turbocharger 30b and cooled in a charge air cooler 30a, the arrows on
  • Intercooler 30a indicate the flow of the coolant.
  • the combustion air is mixed with recirculated exhaust gas 31 from the exhaust gas recirculation 33 and fed into the engine 36.
  • the exhaust gas 31 generated by the engine 36 is controlled by the
  • Exhaust gas recirculation valve 32 partially passed back into the exhaust gas recirculation 33.
  • the remaining exhaust gas 31a first drives the turbocharger 30b and is rendered harmless in the exhaust aftertreatment 34, before it in the first
  • Evaporator 21 waste heat is removed.
  • the cooled exhaust 31b is supplied to the exhaust 35.
  • an exhaust gas bypass valve 21a the evaporator 21 can be bridged and thus temporarily deactivated.
  • the working medium 23 is converted into superheated steam 23c and supplied to the expansion machine 24.
  • Working medium 23a is condensed in the condenser 25 into liquid working medium 23b, the flow of the coolant in turn being indicated by the arrows on the condenser 25.
  • the condensed working medium 23b is compressed again in the conveying device 26 and fed back into the evaporator 21.
  • a further evaporator 22 is connected in the exhaust gas flow of the exhaust gas recirculation line 33.
  • This evaporator 22 is from the same conveyor 26 with Working medium 23 supplies as the first evaporator 21, and he fed together with the evaporator 21, the same expansion machine 24th

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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 concerne un optimiseur de performance (1) pour un système de récupération de chaleur perdue (2) d'un véhicule (3), le système de récupération de chaleur perdue (2) comportant au moins un évaporateur (21, 22) pour transférer la chaleur perdue de gaz d'échappement (31) produits par le véhicule dans un fluide de travail (23), au moins une machine à expansion (24) qui peut être entraînée par le fluide de travail (23), comprenant au moins un condenseur (25) pour condenser le fluide de travail (23) expansé dans la machine d'expansion (24) à l'état liquide, et au moins un dispositif de transport (26) pour augmenter la pression du fluide de travail condensé (23a) et le transporter dans l'évaporateur (21, 22). Le système de récupération de chaleur perdue (2) comprend un circuit de régulation (27) qui agit au moins sur le débit de transport mw du dispositif de transport (26) en tant que variable manipulée et régule au moins la température Tw du fluide de travail sortant de l'évaporateur à une valeur théorique Tw,s, l'optimiseur de performance (1) comprenant un jeu de variables, à partir duquel au moins la température TA et le débit massique mA des gaz d'échappement (31) à l'emplacement de l'évaporateur (21, 22) surviennent, reçoit comme entrée (11), affecte à chaque vecteur de valeur de ces variables une valeur souhaitée Tw,s pour la température Tw du fluide de travail (23) quittant l'évaporateur (21, 22) et est conçu pour fournir cette valeur souhaitée Tw,s au circuit de régulation (27). L'invention concerne également un système de récupération de chaleur perdue ainsi qu'un produit-programme informatique.
PCT/EP2018/064855 2017-07-05 2018-06-06 Optimiseur de performance pour système de récupération de chaleur perdue WO2019007622A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017211450.9A DE102017211450A1 (de) 2017-07-05 2017-07-05 Leistungsoptimierer für Abwärmerückgewinnungssystem
DE102017211450.9 2017-07-05

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WO2019007622A1 true WO2019007622A1 (fr) 2019-01-10

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1431523A1 (fr) * 2001-09-28 2004-06-23 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande thermique d'un evaporateur
EP1443183A1 (fr) * 2001-10-09 2004-08-04 Honda Giken Kogyo Kabushiki Kaisha Dispositif a circuit rankine
EP2693001A1 (fr) * 2012-07-31 2014-02-05 MAN Truck & Bus Österreich AG Procédé de réglage d'un système de récupération de chaleur dans un véhicule automobile
DE102014019684A1 (de) 2014-12-23 2015-06-25 Daimler Ag Anordnung zur Umwandlung thermischer Energie aus Verlustwärme einer Verbrennungskraftmaschine
WO2016089285A1 (fr) 2014-12-03 2016-06-09 Scania Cv Ab Procédé de commande d'un système de récupération de chaleur perdue et système de récupération de chaleur perdue
US20170016356A1 (en) 2015-07-13 2017-01-19 Hyundai Motor Company Waste heat recovery system
DE102015217737A1 (de) * 2015-09-16 2017-03-16 Robert Bosch Gmbh Abwärmerückgewinnungssystem mit einem Arbeitsfluidkreislauf

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1431523A1 (fr) * 2001-09-28 2004-06-23 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande thermique d'un evaporateur
EP1443183A1 (fr) * 2001-10-09 2004-08-04 Honda Giken Kogyo Kabushiki Kaisha Dispositif a circuit rankine
EP2693001A1 (fr) * 2012-07-31 2014-02-05 MAN Truck & Bus Österreich AG Procédé de réglage d'un système de récupération de chaleur dans un véhicule automobile
WO2016089285A1 (fr) 2014-12-03 2016-06-09 Scania Cv Ab Procédé de commande d'un système de récupération de chaleur perdue et système de récupération de chaleur perdue
DE102014019684A1 (de) 2014-12-23 2015-06-25 Daimler Ag Anordnung zur Umwandlung thermischer Energie aus Verlustwärme einer Verbrennungskraftmaschine
US20170016356A1 (en) 2015-07-13 2017-01-19 Hyundai Motor Company Waste heat recovery system
DE102015217737A1 (de) * 2015-09-16 2017-03-16 Robert Bosch Gmbh Abwärmerückgewinnungssystem mit einem Arbeitsfluidkreislauf

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