EP3320190B1 - Method for controlling a waste-heat utilization system for an internal combustion engine - Google Patents

Method for controlling a waste-heat utilization system for an internal combustion engine Download PDF

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Publication number
EP3320190B1
EP3320190B1 EP16740953.1A EP16740953A EP3320190B1 EP 3320190 B1 EP3320190 B1 EP 3320190B1 EP 16740953 A EP16740953 A EP 16740953A EP 3320190 B1 EP3320190 B1 EP 3320190B1
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EP
European Patent Office
Prior art keywords
expander
operating mode
waste heat
internal combustion
heat utilization
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Application number
EP16740953.1A
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German (de)
French (fr)
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EP3320190A1 (en
Inventor
Klemens Neunteufl
Oswald LACKNER
Gerald GRADWOHL
Michael Bucher
Fabio COCOCCETTA
Ivan CALAON
Michael Glensvig
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AVL List GmbH
Mahle Amovis GmbH
FPT Industrial SpA
Iveco SpA
Original Assignee
AVL List GmbH
Mahle Amovis GmbH
FPT Industrial SpA
Iveco SpA
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Publication of EP3320190A1 publication Critical patent/EP3320190A1/en
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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
    • F01K23/12—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
    • F01K23/14—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled including at least one combustion 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
    • F01K23/065—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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases

Definitions

  • the invention relates to a method for controlling a waste heat utilization system for an internal combustion engine of a vehicle, wherein the waste heat recovery system at least one torque to the engine transferable and bypassable via a bypass flow expander, at least one evaporator and at least one pump for a resource, in particular ethanol, and wherein at least the evaporator is arranged in the region of the exhaust system of the internal combustion engine, wherein the expander operable in a plurality of operating modes is drive-connected in at least one operating mode with a secondary drive shaft of the internal combustion engine, and selected on the basis of at least one input variables in each case an operating mode of at least two operating modes of the waste heat recovery system by the controller is and the waste heat recovery system, preferably by controlling at least one arranged in a bypass flow path of the expander Umgehungsve ntils of the expander, is operated in this operating mode.
  • the invention further relates to a waste heat utilization system for a motor vehicle driven by an internal combustion engine via a drive train, with a control device for controlling the waste heat recovery system, wherein the waste heat recovery system at least one torque to the internal combustion engine and bypassable via a bypass flow expander, at least one evaporator and at least one pump for a resource, in particular ethanol, and wherein at least the evaporator in the region of the exhaust system of the internal combustion engine is arranged, wherein the operable in a plurality of operating modes expander is drivingly connected in at least one operating mode with a PTO shaft of the internal combustion engine and due to at least one input by the control device in each case Operating mode of at least two operating modes of the expander is selectable, and the expander - preferably by controlling at least one in e inem bypass flow path of the expander arranged bypass valve - is operable in this mode of operation.
  • WHR Wash Heat Recovery
  • the WO 2006/138459 A2 discloses an organic Rankine cycle which is mechanically and thermally coupled to an internal combustion engine.
  • the drive shaft of the internal combustion engine is coupled to a turbine of a waste heat recovery system, which removes waste heat of the intake air, the coolant, the oil and the exhaust gas of the internal combustion engine.
  • Bypass valves control the engine temperature.
  • various system parameters, in particular the turbine pressure ratio can be controlled via bypass valves via a control unit.
  • an overflow clutch is provided, which allows rotation of the internal combustion engine without simultaneously driving the turbine.
  • the US 2009/0071156 A1 shows a waste heat recovery device having a Rankine cycle with a compressor and an expander, wherein the expander is bypassed via a bypass line.
  • a temperature sensor and a pressure sensor Upstream of the turbine, a temperature sensor is arranged.
  • a pressure sensor Downstream of the turbine, a pressure sensor is arranged.
  • the speed of the expansion device is controlled.
  • a mechanical connection of the expansion device with the drive shaft of an internal combustion engine is not provided.
  • the object of the invention is to ensure a safe and reliable operation of the waste heat recovery system.
  • this is achieved by selecting the input variable from the group expander speed, gear information, coasting information, pressure and temperature of the equipment upstream of the expander and / or pressure and temperature downstream of the expander by the control device, wherein a first operating mode of a warm-up phase of the expander, and a second operating mode associated with a normal operating phase of the expander is opened, wherein in the first operating mode, the bypass flow path is opened and the expander is not connected to a PTO of the internal combustion engine, and wherein in the second operating mode, the bypass flow path is closed and the expander is connected to the internal combustion engine, the second operating mode is selected when the pressure and / or the temperature of the equipment downstream of the expander exceeds a defined value. Conversely, it is possible to switch from the second operating mode to the first operating mode when the pressure and / or the temperature of the operating means downstream and / or upstream of the expander exceeds a defined value.
  • the bypass valve In the first operating mode, the bypass valve is opened, the starting device is deactivated. The equipment is thus passed past the expander, whereby the expander generates no torque. In the second operating mode, the bypass valve is closed, the starting device also deactivated. When the bypass valve is closed, the operating medium flows through the expander, which makes this work.
  • a third operating mode is associated with at least one gear change phase.
  • the waste heat recovery system is operated in response to the shift direction in this third mode of operation.
  • the position of the bypass valve depends on the switching operation, in particular on the direction of the switching operation.
  • the bypass flowpath of the expander remains closed and the power takeoff shaft is driven by the expander.
  • the bypass flowpath of the expander is opened and / or the expander is disconnected from the power takeoff shaft.
  • the gear information in particular whether a downshift or an upshift is present, is supplied to the control device by a gearbox sensor of the transmission.
  • the waste heat utilization system is operated in a fourth operating mode during at least one sailing operation of the vehicle, during at least one warm-up operation of the internal combustion engine and / or during at least one engine brake operation of the internal combustion engine. It is particularly advantageous if, in the fourth operating mode, the expander is not disconnected from the auxiliary drive shaft. Preferably, the expander of the secondary drive shaft is not separated until the torque of the expander falls below a defined value.
  • Sailing operation is a torque-free operation of the vehicle understood in which the clutch between the engine and transmission is opened to reduce the resistance in the drive train.
  • the control unit of the transmission or the clutch is communicated by means of Ausroll so.
  • the centrifugal clutch (overrunning clutch) separates the expander from the PTO shaft when the PTO shaft speed becomes higher than the speed of the expander. This is not possible to start the expander by the internal combustion engine.
  • a fifth operating mode for the start of the expander is provided.
  • the waste heat utilization system is operated in the fifth operating mode, which provides that the expander is started by activating a starting device connected to the expander.
  • the expander In the first mode of operation and / or with the heat recovery system inactive, the expander is bypassed via the bypass flowpath and / or disconnected (by the shiftable clutch or centrifugal clutch) from the PTO shaft when the bypass valve is open.
  • the bypass flow path of the expander be closed when the waste heat recovery system resource is in an overheated condition.
  • a shiftable clutch between the secondary drive shaft and expander may additionally be provided that the expander is drivingly connected to the PTO shaft when the resources of the waste heat recovery system downstream of the expander is in an overheated state and / or if the Expanderwindiere exceeds a defined value and / or the speed of the internal combustion engine exceeds a defined value.
  • the expander When the waste heat recovery system resource is in a non-overheated condition upstream of the expander, or when the engine is shut down, the expander may be disconnected from the power take off shaft without the risk of exceeding a critical speed.
  • Fig. 1 and Fig. 3 each show an internal combustion engine 10 with an exhaust system 11, in which an exhaust aftertreatment device 12 - for example, a diesel oxidation catalyst 12, a diesel particulate filter 12b and an SCR catalyst 12c (SCR - selective catalytic reduction) - is arranged.
  • the internal combustion engine 10 has a drive train 13 with a crankshaft 14, a clutch 15 and a (gear) transmission 16, which acts on the drive shaft 17 of the drive wheels 18.
  • the internal combustion engine 10 has a waste heat utilization system 20 for utilizing the exhaust gas values of the exhaust system 11 of the internal combustion engine 10.
  • the waste heat utilization system 20 has an evaporator 21, which is arranged downstream of the exhaust gas aftertreatment device 12 in the region of the exhaust system 11.
  • the example according to the organic Rankine cycle (ORC) functioning waste heat recovery system 20 has downstream of the evaporator 21 in the resource cycle an expander 22 and a condenser 23, and a pump 24 for the resource.
  • a resource for example, ethanol can be used.
  • an environmental conduit 25 with a bypass valve 26 is provided.
  • the evaporator 21 can be bypassed on the exhaust side via a bypass line 36 and a bypass valve 37, when the exhaust heat for the evaporator 21 is too high, or the system pressure exceeds a defined value, or the cooling system is excessively loaded, or the waste heat recovery system 20 is in a failure mode , or in pure engine operation, without engine brake.
  • the activation of the bypass valve 37 takes place as a function of at least one of the operating parameters from the group of fan power, system pressure, system temperature and mass flow of the equipment.
  • a control device 30 For controlling the waste heat utilization system 20, a control device 30 is provided which has a program logic 31 which is designed to select the most suitable operating mode from the plurality of operating modes 1 to 4 or 1 to 5 for the operation of the waste heat recovery system 20.
  • the selection of the most suitable operating mode takes place on the basis of at least one of the input variables of the control device 30, namely: Expanderfeliere n, gear information GI, Ausrollinformation CI, pressure p 1 , temperature T 1 of the resource upstream of the expander 22, and the pressure p 2 , and the temperature T 2 of the equipment downstream of the expander 22.
  • pressure sensors 32, 33 and temperature sensors 34, 35 upstream and downstream of the expander 22 in the operating-medium circuit of the waste heat utilization system 20 provided.
  • the pressure sensors 32, 33 and temperature sensors 34, 35 are in communication with the control device 30.
  • the gear information GI and Ausrollinforation CI are made available for example by suitable encoders in the transmission 16 of the control device 30.
  • the expander 22 is connected to the PTO shaft 19 of the internal combustion engine 10 via a switchable coupling 28.
  • the switchable clutch 28 is controlled by the controller 30. It makes it possible to start the expander 22 via the internal combustion engine 10 by closing the clutch 28.
  • the bypass valve 26 is closed.
  • the PTO shaft 19 is driven by the expander 22 and the torque of the expander 22 is used, while the rotational speed of the crankshaft 14 of the internal combustion engine 10 and the rotational speed of the transmission 16 are synchronized.
  • the clutch 15 is open. Thereby, the amount of fuel for acceleration of the internal combustion engine 10 can be reduced. Furthermore, during the switching process, a certain engine speed can be maintained. Thus, the exhaust heat can be used downstream of the exhaust aftertreatment device 12 for bridging torque drops during switching breaks.
  • This operating mode 4 is used during the sailing operation, the warm-up operation, and / or the engine braking operation of the internal combustion engine 10. In sailing operation, the vehicle rolls without torque transmission between internal combustion engine 10 and drive wheels 18, generally with the clutch 15 open.
  • the bypass valve 26 is closed in operating mode 4 in order to transmit torque from the expander 22 to the internal combustion engine 10. As a result - especially when the clutch 15 is open - the fuel consumption at idle reduced. If a high torque is available from the expander 22, the clutch 15 may be closed until the torque of the expander 22 falls below a defined value.
  • Fig. 3 illustrated second embodiment differs from Fig. 1 in that, instead of the shiftable clutch 28, an overrunning clutch 29a and a centrifugal braking device 29b are provided for connecting the expander 22 to the auxiliary drive shaft 19 of the internal combustion engine 10.
  • the controller 30 may perform a fifth operation mode 5 in addition to the above-mentioned operation modes 1 to 4 to start the expander 22 with an internal or external starting device 27 (see FIG Fig. 3, Fig. 4 ).
  • the control device 30 provides special security measures.
  • the bypass valve 26 is closed only when the resource is in an overheated condition, such as when the resource, ethanol, is in the gas phase.
  • Another safety measure is that the bypass valve 26 is opened when a gear shift to a higher gear is performed.
  • bypass valve 26 and the switchable coupling 28 are closed only when the equipment is in an overheated state, that is, for example, when the resource ethanol is in the gas phase.
  • both the bypass valve 26, and the switchable clutch 28 are opened.
  • the switchable clutch 28 is thus closed when the operating means is in an overheated state, or when the speed n of the expander 22 and / or the speed of the internal combustion engine 10 is above a defined value.
  • the switchable clutch 28 is thus opened when the expander 22 is in a non-overheated condition.
  • the clutch 28 is also then opened, and the operating state of the internal combustion engine 10 from an activated to a deactivated state in, so when the internal combustion engine 10 is turned off.

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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)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Description

Die Erfindung betrifft ein Verfahren zur Steuerung eines Abwärmenutzungssystems für eine Brennkraftmaschine eines Fahrzeuges, wobei das Abwärmenutzungssystem zumindest einen Drehmoment an die Brennkraftmaschine übertragbaren und über einen Umgehungsströmungsweg umgehbaren Expander, zumindest einen Verdampfer und zumindest eine Pumpe für ein Betriebsmittel, insbesondere Ethanol, aufweist, und wobei zumindest der Verdampfer im Bereich des Abgassystems der Brennkraftmaschine angeordnet ist, wobei der in mehreren Betriebsmodi betreibbare Expander in zumindest einem Betriebsmodus mit einer Nebenantriebswelle der Brennkraftmaschine antriebsverbunden wird, und aufgrund zumindest einer Eingangsgrößen jeweils ein Betriebsmodus von zumindest zwei Betriebsmodi des Abwärmenutzungssystems durch eine die Steuerungseinrichtung ausgewählt wird und das Abwärmenutzungssystem, vorzugsweise durch Ansteuerung zumindest eines in einem Umgehungsströmungsweg des Expanders angeordneten Umgehungsventils des Expanders, in diesem Betriebsmodus betrieben wird.The invention relates to a method for controlling a waste heat utilization system for an internal combustion engine of a vehicle, wherein the waste heat recovery system at least one torque to the engine transferable and bypassable via a bypass flow expander, at least one evaporator and at least one pump for a resource, in particular ethanol, and wherein at least the evaporator is arranged in the region of the exhaust system of the internal combustion engine, wherein the expander operable in a plurality of operating modes is drive-connected in at least one operating mode with a secondary drive shaft of the internal combustion engine, and selected on the basis of at least one input variables in each case an operating mode of at least two operating modes of the waste heat recovery system by the controller is and the waste heat recovery system, preferably by controlling at least one arranged in a bypass flow path of the expander Umgehungsve ntils of the expander, is operated in this operating mode.

Weiters betrifft die Erfindung ein Abwärmenutzungssystem für ein durch eine Brennkraftmaschine über einen Antriebsstrang angetriebenes Kraftfahrzeug, mit einer Steuerungseinrichtung zur Steuerung des Abwärmenutzungssystems, wobei das Abwärmenutzungssystem zumindest einen Drehmoment an die Brennkraftmaschine übertragbaren und über einen Umgehungsströmungsweg umgehbaren Expander, zumindest einen Verdampfer und zumindest eine Pumpe für ein Betriebsmittel, insbesondere Ethanol, aufweist, und wobei zumindest der Verdampfer im Bereich des Abgassystems der Brennkraftmaschine angeordnet ist, wobei der in mehreren Betriebsmodi betreibbare Expander in zumindest einem Betriebsmodus mit einer Nebenantriebswelle der Brennkraftmaschine antriebsverbindbar ist und aufgrund zumindest einer Eingangsgröße durch die Steuerungseinrichtung jeweils ein Betriebsmodus von zumindest zwei Betriebsmodi des Expanders auswählbar ist, und der Expander - vorzugsweise durch Ansteuerung zumindest eines in einem Umgehungsströmungsweg des Expanders angeordneten Umgehungsventils - in diesem Betriebsmodus betreibbar ist.The invention further relates to a waste heat utilization system for a motor vehicle driven by an internal combustion engine via a drive train, with a control device for controlling the waste heat recovery system, wherein the waste heat recovery system at least one torque to the internal combustion engine and bypassable via a bypass flow expander, at least one evaporator and at least one pump for a resource, in particular ethanol, and wherein at least the evaporator in the region of the exhaust system of the internal combustion engine is arranged, wherein the operable in a plurality of operating modes expander is drivingly connected in at least one operating mode with a PTO shaft of the internal combustion engine and due to at least one input by the control device in each case Operating mode of at least two operating modes of the expander is selectable, and the expander - preferably by controlling at least one in e inem bypass flow path of the expander arranged bypass valve - is operable in this mode of operation.

Es ist bekannt, Abwärme von Brennkraftmaschinen zu nutzen. Solche als WHR (Waste Heat Recovery)-Systeme bekannten Einrichtungen wandeln die Abwärme des Abgases der Brennkraftmaschine in beispielsweise mechanische oder elektrische Energie um. Derartige WHR-Systeme sind beispielsweise aus den Veröffentlichungen US 8 635 871 A1 , US 2011/0209473 A1 oder US 2013/0186087 A1 bekannt.It is known to use waste heat from internal combustion engines. Such known as WHR (Waste Heat Recovery) systems convert the waste heat of the exhaust gas of the internal combustion engine into, for example, mechanical or electrical energy. Such WHR systems are for example from the publications US 8 635 871 A1 . US 2011/0209473 A1 or US 2013/0186087 A1 known.

Die WO 2006/138459 A2 offenbart einen organischen Rankine-Zyklus, welcher mechanisch und thermisch an eine Brennkraftmaschine gekoppelt ist. Dabei ist die Antriebswelle der Brennkraftmaschine an eine Turbine eines Abwärmenutzungssystems gekoppelt, welches Abwärme der Einlassluft, des Kühlmittels, des Öls und des Abgases der Brennkraftmaschine entzieht. Über Bypassventile wird die Motortemperatur gesteuert. Zur Anpassung an unterschiedliche Lastzustände, Druckverhältnisse, Drehzahlen und Temperaturen der Turbine können über eine Steuereinheit verschiedene Systemparameter, insbesondere das Turbinendruckverhältnis, über Bypassventile gesteuert werden. Zwischen der Brennkraftmaschine und der Turbine ist eine Überlaufkupplung vorgesehen, welche ein Drehen der Brennkraftmaschine ohne gleichzeitiges Antreiben der Turbine ermöglicht. Aus der WO 2006/138459 A2 ist es nicht bekannt, in einem ersten Betriebsmodus den Umgehungsströmungsweg der Turbine zu öffnen, wobei die Turbine mit einer Nebenantriebswelle der Brennkraftmaschine nicht verbunden ist und in einem zweiten Betriebsmodus den Umgehungsströmungsweg zu schließen, wobei der Expander mit der Brennkraftmaschine verbunden wird. Weiters geht aus dieser Veröffentlichung nicht hervor, dass der zweite Betriebsmodus gewählt wird, wenn der Druck oder die Temperatur des Betriebsmittels stromabwärts des Expanders einen definierten Wert überschreitet.The WO 2006/138459 A2 discloses an organic Rankine cycle which is mechanically and thermally coupled to an internal combustion engine. In this case, the drive shaft of the internal combustion engine is coupled to a turbine of a waste heat recovery system, which removes waste heat of the intake air, the coolant, the oil and the exhaust gas of the internal combustion engine. Bypass valves control the engine temperature. To adapt to different load conditions, pressure conditions, rotational speeds and temperatures of the turbine, various system parameters, in particular the turbine pressure ratio, can be controlled via bypass valves via a control unit. Between the internal combustion engine and the turbine, an overflow clutch is provided, which allows rotation of the internal combustion engine without simultaneously driving the turbine. From the WO 2006/138459 A2 it is not known to open the bypass flow path of the turbine in a first operating mode, wherein the turbine is not connected to a secondary drive shaft of the internal combustion engine and to close the bypass flow path in a second operating mode, wherein the expander is connected to the internal combustion engine. Furthermore, it is not apparent from this publication that the second mode of operation is selected when the pressure or the temperature of the equipment downstream of the expander exceeds a defined value.

Die US 2009/0071156 A1 zeigt eine Abwärmerückgewinnungseinrichtung, welche einen Rankine-Kreislauf mit einem Verdichter und einem Expander aufweist, wobei der Expander über eine Bypassleitung umgehbar ist. Stromaufwärts der Turbine ist ein Temperatursensor und ein Drucksensor, stromabwärts der Turbine ein Drucksensor angeordnet. In Abhängigkeit der Informationen über den Überhitzungszustand des Mediums des Rankine-Kreislaufes stromaufwärts der Expansionseinrichtung wird die Drehzahl der Expansionseinrichtung geregelt. Eine mechanische Verbindung der Expansionseinrichtung mit der Antriebswelle einer Brennkraftmaschine ist nicht vorgesehen.The US 2009/0071156 A1 shows a waste heat recovery device having a Rankine cycle with a compressor and an expander, wherein the expander is bypassed via a bypass line. Upstream of the turbine, a temperature sensor and a pressure sensor, downstream of the turbine, a pressure sensor is arranged. Depending on the information about the superheat state of the Rankine cycle medium upstream of the expansion device, the speed of the expansion device is controlled. A mechanical connection of the expansion device with the drive shaft of an internal combustion engine is not provided.

Aufgabe der Erfindung ist es, einen sicheren und zuverlässigen Betrieb des Abwärmenutzungssystems zu gewährleisten.The object of the invention is to ensure a safe and reliable operation of the waste heat recovery system.

Erfindungsgemäß erfolgt dies dadurch, dass die Eingangsgröße aus der Gruppe Expanderdrehzahl, Ganginformation, Ausrollinformation, Druck und Temperatur des Betriebsmittels stromaufwärts des Expanders und/oder Druck und Temperatur stromabwärts des Expanders durch die Steuerungseinrichtung ausgewählt wird, wobei ein erster Betriebsmodus einer Warmlaufphase des Expanders, und ein zweiter Betriebsmodus einer Normalbetriebsphase des Expanders zugeordnet wird, wobei im ersten Betriebsmodus der Umgehungsströmungsweg geöffnet und der Expander mit einer Nebenantriebswelle der Brennkraftmaschine nicht verbunden ist, und wobei im zweiten Betriebsmodus der Umgehungsströmungsweg geschlossen wird und der Expander mit der Brennkraftmaschine verbunden wird, wobei der zweite Betriebsmodus gewählt wird, wenn der Druck und/oder die Temperatur des Betriebsmittels stromabwärts des Expanders einen definierten Wert überschreitet. Umgekehrt kann vom zweiten Betriebsmodus in den ersten Betriebsmodus gewechselt werden, wenn der Druck und/oder die Temperatur des Betriebsmittels stromabwärts und/oder stromaufwärts des Expanders einen definierten Wert überschreitet.According to the invention, this is achieved by selecting the input variable from the group expander speed, gear information, coasting information, pressure and temperature of the equipment upstream of the expander and / or pressure and temperature downstream of the expander by the control device, wherein a first operating mode of a warm-up phase of the expander, and a second operating mode associated with a normal operating phase of the expander is opened, wherein in the first operating mode, the bypass flow path is opened and the expander is not connected to a PTO of the internal combustion engine, and wherein in the second operating mode, the bypass flow path is closed and the expander is connected to the internal combustion engine, the second operating mode is selected when the pressure and / or the temperature of the equipment downstream of the expander exceeds a defined value. Conversely, it is possible to switch from the second operating mode to the first operating mode when the pressure and / or the temperature of the operating means downstream and / or upstream of the expander exceeds a defined value.

Im ersten Betriebsmodus ist das Umgehungsventil geöffnet, die Starteinrichtung deaktiviert. Das Betriebsmittel wird somit am Expander vorbeigeleitet, wodurch der Expander kein Drehmoment erzeugt. Im zweiten Betriebsmodus ist das Umgehungsventil geschlossen, die Starteinrichtung ebenfalls deaktiviert. Bei geschlossenem Umgehungsventil strömt das Betriebsmedium durch den Expander, wodurch dieser Arbeit leistet.In the first operating mode, the bypass valve is opened, the starting device is deactivated. The equipment is thus passed past the expander, whereby the expander generates no torque. In the second operating mode, the bypass valve is closed, the starting device also deactivated. When the bypass valve is closed, the operating medium flows through the expander, which makes this work.

Besonders ist es, wenn ein dritter Betriebsmodus zumindest einer Gangwechselphase zugeordnet ist. Während eines Gangwechsels wird das Abwärmenutzungssystems in Abhängigkeit der Schaltrichtung in diesem dritten Betriebsmodus betrieben. Die Stellung des Umgehungsventils hängt vom Schaltvorgang, insbesondere von der Richtung des Schaltvorgangs ab.It is particularly when a third operating mode is associated with at least one gear change phase. During a gear change, the waste heat recovery system is operated in response to the shift direction in this third mode of operation. The position of the bypass valve depends on the switching operation, in particular on the direction of the switching operation.

Während zumindest eines Runterschaltvorganges bleibt der Umgehungsströmungsweg des Expanders geschlossen und die Nebenantriebswelle durch den Expander angetrieben. Während zumindest eines Hochschaltvorganges wird der Umgehungsströmungsweg des Expanders geöffnet und/oder der Expander von der Nebenantriebswelle getrennt. Die Ganginformation, insbesondere ob ein Runter- oder ein Hochschaltvorgang vorliegt, wird von einem Gangsensor des Getriebes an die die Steuerungseinrichtung geliefert.During at least one downshift, the bypass flowpath of the expander remains closed and the power takeoff shaft is driven by the expander. During at least one upshift, the bypass flowpath of the expander is opened and / or the expander is disconnected from the power takeoff shaft. The gear information, in particular whether a downshift or an upshift is present, is supplied to the control device by a gearbox sensor of the transmission.

Besonders vorteilhaft ist es, wenn das Abwärmenutzungssystem in einem vierten Betriebsmodus während zumindest eines Segelbetriebs des Fahrzeugs, während zumindest eines Warmlaufbetriebs der Brennkraftmaschine und/oder während zumindest eines Motorbremsbetriebs der Brennkraftmaschine betrieben wird. Besonders vorteilhaft ist es, wenn im vierten Betriebsmodus der Expander nicht von der Nebenantriebswelle getrennt wird. Vorzugsweise wird der Expander von der Nebenantriebswelle erst dann getrennt, wenn das Drehmoment des Expanders einen definierten Wert unterschreitet.It is particularly advantageous if the waste heat utilization system is operated in a fourth operating mode during at least one sailing operation of the vehicle, during at least one warm-up operation of the internal combustion engine and / or during at least one engine brake operation of the internal combustion engine. It is particularly advantageous if, in the fourth operating mode, the expander is not disconnected from the auxiliary drive shaft. Preferably, the expander of the secondary drive shaft is not separated until the torque of the expander falls below a defined value.

Als Segelbetrieb wird ein drehmomentfreier Betrieb des Fahrzeuges verstanden, bei welchem die Schaltkupplung zwischen Brennkraftmaschine und Getriebe geöffnet wird, um den Widerstand im Antriebsstrang zu verringern.Sailing operation is a torque-free operation of the vehicle understood in which the clutch between the engine and transmission is opened to reduce the resistance in the drive train.

Ob ein Segelbetrieb des Fahrzeuges vorliegt oder nicht, wird der Steuerungseinheit vom Getriebe bzw. der Schaltkupplung mittels Ausrollinformationen mitgeteilt.Whether a sailing operation of the vehicle is present or not, the control unit of the transmission or the clutch is communicated by means of Ausrollinformationen.

Über die Fliehraftkupplung (Überholkupplung) wird der Expander von der Nebenantriebswelle getrennt, wenn die Drehzahl der Nebenantriebswelle höher als die Drehzahl des Expanders wird. Damit ist ein Starten des Expanders durch die Brennkraftmaschine aber nicht möglich.The centrifugal clutch (overrunning clutch) separates the expander from the PTO shaft when the PTO shaft speed becomes higher than the speed of the expander. This is not possible to start the expander by the internal combustion engine.

Daher ist insbesondere in Ausführungen, bei denen der Expander über eine Fliehkraftkupplung mit der Nebenantriebswelle verbindbar ist, ein fünfter Betriebsmodus für den Start des Expanders vorgesehen. Für den Start des Expanders wird das Abwärmenutzungssystem im fünften Betriebsmodus betrieben, welcher vorsieht, dass der Expander durch Aktivieren einer mit dem Expander verbundenen Starteinrichtung gestartet wird.Therefore, especially in embodiments in which the expander is connectable via a centrifugal clutch with the PTO shaft, a fifth operating mode for the start of the expander is provided. For the start of the expander, the waste heat utilization system is operated in the fifth operating mode, which provides that the expander is started by activating a starting device connected to the expander.

Im ersten Betriebsmodus und/oder bei inaktivem Wärmenutzungssystem wird der Expander - bei geöffnetem Umgehungsventil - über den Umgehungsströmungsweg umgangen und/oder (durch die schaltbare Kupplung oder die Fliehkraftkupplung) von der Nebenantriebswelle getrennt.In the first mode of operation and / or with the heat recovery system inactive, the expander is bypassed via the bypass flowpath and / or disconnected (by the shiftable clutch or centrifugal clutch) from the PTO shaft when the bypass valve is open.

Um eine Beschädigung des Abwärmenutzungssystems sicher zu vermeiden, ist im Rahmen der Erfindung vorgesehen, dass der Umgehungsströmungsweg des Expanders geschlossen wird, wenn sich das Betriebsmittel des Abwärmenutzungssystems in einem überhitzten Zustand befindet. Im Falle einer schaltbaren Kupplung zwischen Nebenantriebswelle und Expander kann zusätzlich vorgesehen sein, dass der Expander mit der Nebenantriebswelle antriebsverbunden wird, wenn das Betriebsmittel des Abwärmenutzungssystems stromabwärts des Expanders sich in einem überhitzten Zustand befindet und/oder wenn die Expanderdrehzahl einen definierten Wert überschreitet und/oder die Drehzahl der Brennkraftmaschine einen definierten Wert überschreitet.To safely avoid damage to the waste heat recovery system, it is contemplated by the invention that the bypass flow path of the expander be closed when the waste heat recovery system resource is in an overheated condition. In the case of a shiftable clutch between the secondary drive shaft and expander may additionally be provided that the expander is drivingly connected to the PTO shaft when the resources of the waste heat recovery system downstream of the expander is in an overheated state and / or if the Expanderdrehzahl exceeds a defined value and / or the speed of the internal combustion engine exceeds a defined value.

Wenn sich das Betriebsmittel des Abwärmenutzungssystems stromaufwärts des Expanders in einem nicht überhitzten Zustand befindet oder wenn die Brennkraftmaschine abgestellt wird, kann der Expander von der Nebenantriebswelle getrennt werden, ohne dass Gefahr besteht, dass eine kritische Drehzahl überschritten wird.When the waste heat recovery system resource is in a non-overheated condition upstream of the expander, or when the engine is shut down, the expander may be disconnected from the power take off shaft without the risk of exceeding a critical speed.

Die Erfindung wird im Folgenden anhand der nicht einschränkenden Figuren näher beschrieben. Es zeigen schematisch:

Fig. 1
ein Abwärmenutzungssystem für eine Brennkraftmaschine mit einer erfindungsgemäßen Steuerungseinrichtung in einer ersten Ausführungsvariante;
Fig. 2
die Betriebsmodi dieser Steuerungseinrichtung;
Fig. 3
ein Abwärmenutzungssystem für eine Brennkraftmaschine mit einer erfindungsgemäßen Steuerungseinrichtung in einer zweiten Ausführungsvariante; und
Fig. 4
die Betriebsmodi dieser Steuerungseinrichtung.
The invention will be described in more detail below with reference to the non-limiting figures. They show schematically:
Fig. 1
a waste heat recovery system for an internal combustion engine with a control device according to the invention in a first embodiment;
Fig. 2
the operating modes of this controller;
Fig. 3
a waste heat recovery system for an internal combustion engine with a control device according to the invention in a second embodiment; and
Fig. 4
the operating modes of this controller.

In den dargestellten Ausführungsvarianten sind funktionsgleiche Bauteile mit gleichen Bezugszeichen versehen.In the illustrated embodiments, functionally identical components are provided with the same reference numerals.

Fig. 1 und Fig. 3 zeigen jeweils eine Brennkraftmaschine 10 mit einem Abgassystem 11, in welchem eine Abgasnachbehandlungseinrichtung 12 - beispielsweise ein Diesel-Oxidationskatalysator 12, ein Dieselpartikelfilter 12b und ein SCR-Katalysator 12c (SCR - selective catalytic reduction) - angeordnet ist. Die Brennkraftmaschine 10 weist ein Antriebsstrang 13 mit einer Kurbelwelle 14, einer Schaltkupplung 15 und einen (Schalt-)Getriebe 16 auf, welches auf die Antriebswelle 17 der Antriebsräder 18 einwirkt. Fig. 1 and Fig. 3 each show an internal combustion engine 10 with an exhaust system 11, in which an exhaust aftertreatment device 12 - for example, a diesel oxidation catalyst 12, a diesel particulate filter 12b and an SCR catalyst 12c (SCR - selective catalytic reduction) - is arranged. The internal combustion engine 10 has a drive train 13 with a crankshaft 14, a clutch 15 and a (gear) transmission 16, which acts on the drive shaft 17 of the drive wheels 18.

Weiters weist die Brennkraftmaschine 10 ein Abwärmenutzungssystem 20 zur Nutzung der Abgaswerte des Abgassystems 11 der Brennmaschine 10 auf. Das Abwärmenutzungssystem 20 weist einen Verdampfer 21 auf, welcher stromabwärts der Abgasnachbehandlungseinrichtung 12 im Bereich des Abgassystems 11 angeordnet ist. Das beispielsweise nach dem organischen Rankine Kreislauf (ORC) funktionierende Abwärmenutzungssystem 20 weist stromabwärts des Verdampfers 21 im Betriebsmittelkreislauf einen Expander 22 und einen Kondensator 23, sowie eine Pumpe 24 für das Betriebsmittel auf. Als Betriebsmittel kann beispielsweise Ethanol verwendet werden. Zur Umgehung des Expanders 22 ist eine Umgebungsleitung 25 mit einem Umgehungsventil 26 vorgesehen. Der Verdampfer 21 kann abgasseitig über eine Bypassleitung 36 und ein Bypassventil 37 umgangen werden, wenn die Abgaswärme für den Verdampfer 21 zu hoch wird, oder der Systemdruck einen definierten Wert überschreitet, oder das Kühlsystem übermäßig belastet wird, oder das Abwärmenutzungssystem 20 in einem Fehlermodus ist, oder bei reinem Motorbetrieb, ohne Motorbremse. Die Ansteuerung des Bypassventils 37 erfolgt in Abhängigkeit zumindest eines der Betriebsparameter aus der Gruppe Lüfterleistung, Systemdruck, Systemtemperatur und Massenstrom des Betriebsmittels.Furthermore, the internal combustion engine 10 has a waste heat utilization system 20 for utilizing the exhaust gas values of the exhaust system 11 of the internal combustion engine 10. The waste heat utilization system 20 has an evaporator 21, which is arranged downstream of the exhaust gas aftertreatment device 12 in the region of the exhaust system 11. The example according to the organic Rankine cycle (ORC) functioning waste heat recovery system 20 has downstream of the evaporator 21 in the resource cycle an expander 22 and a condenser 23, and a pump 24 for the resource. As a resource, for example, ethanol can be used. To bypass the expander 22, an environmental conduit 25 with a bypass valve 26 is provided. The evaporator 21 can be bypassed on the exhaust side via a bypass line 36 and a bypass valve 37, when the exhaust heat for the evaporator 21 is too high, or the system pressure exceeds a defined value, or the cooling system is excessively loaded, or the waste heat recovery system 20 is in a failure mode , or in pure engine operation, without engine brake. The activation of the bypass valve 37 takes place as a function of at least one of the operating parameters from the group of fan power, system pressure, system temperature and mass flow of the equipment.

Zur Steuerung des Abwärmenutzungssystems 20 ist eine Steuerungseinrichtung 30 vorgesehen, welche eine Programmlogik 31 aufweist, die ausgebildet ist, um für den Betrieb des Abwärmenutzungssystems 20 den geeignetsten Betriebsmodus aus mehreren Betriebsmodi 1 bis 4 bzw. 1 bis 5 auszuwählen. Die Auswahl des geeignetsten Betriebsmodus erfolgt dabei auf der Basis zumindest einer der Eingangsgrößen der Steuerungseinrichtung 30, nämlich: Expanderdrehzahl n, Ganginformation GI, Ausrollinformation CI, Druck p1, Temperatur T1 des Betriebsmittels stromaufwärts des Expanders 22, sowie des Druckes p2, und der Temperatur T2 des Betriebsmittels stromabwärts des Expanders 22. Für die Erfassung der Parameter Drücke p1, p2 und Temperaturen T1, T2 sind Drucksensoren 32, 33 und Temperatursensoren 34, 35 stromaufwärts und stromabwärts des Expanders 22 im Betriebsmittelkreislauf des Abwärmenutzung Systems 20 vorgesehen. Die Drucksensoren 32, 33 und Temperatursensoren 34, 35 stehen mit der Steuerungseinrichtung 30 in Verbindung. Die Ganginformation GI und Ausrollinforation CI werden beispielsweise von geeigneten Gebern im Getriebe 16 der Steuerungseinrichtung 30 zur Verfügung gestellt.For controlling the waste heat utilization system 20, a control device 30 is provided which has a program logic 31 which is designed to select the most suitable operating mode from the plurality of operating modes 1 to 4 or 1 to 5 for the operation of the waste heat recovery system 20. The selection of the most suitable operating mode takes place on the basis of at least one of the input variables of the control device 30, namely: Expanderdrehzahl n, gear information GI, Ausrollinformation CI, pressure p 1 , temperature T 1 of the resource upstream of the expander 22, and the pressure p 2 , and the temperature T 2 of the equipment downstream of the expander 22. For the detection of the parameters pressures p 1, p 2 and temperatures T 1, T 2, pressure sensors 32, 33 and temperature sensors 34, 35 upstream and downstream of the expander 22 in the operating-medium circuit of the waste heat utilization system 20 provided. The pressure sensors 32, 33 and temperature sensors 34, 35 are in communication with the control device 30. The gear information GI and Ausrollinforation CI are made available for example by suitable encoders in the transmission 16 of the control device 30.

Bei der in Fig. 1 dargestellten ersten Ausführungsvariante ist der Expander 22 mit der Nebenantriebswelle 19 der Brennkraftmaschine 10 über eine schaltbare Kupplung 28 verbunden. Die schaltbare Kupplung 28 wird über die Steuerungseinrichtung 30 gesteuert. Sie ermöglicht es, den Expander 22 über die Brennkraftmaschine 10 zu starten, indem die Schaltkupplung 28 geschlossen wird.At the in Fig. 1 the first embodiment shown, the expander 22 is connected to the PTO shaft 19 of the internal combustion engine 10 via a switchable coupling 28. The switchable clutch 28 is controlled by the controller 30. It makes it possible to start the expander 22 via the internal combustion engine 10 by closing the clutch 28.

In Fig. 2 sind die Betriebsmodi dieser ersten Ausführungsvariante dargestellt. Es können mit der in Fig. 1 dargestellten Ausführungsvariante folgende Betriebsmodi durchgeführt werden:

  • Erster Betriebsmodus 1 wird während der Aufwärmphase des Expanders 22 durchgeführt; im Betriebsmodus 1 ist das Umgehungsventil 26 geöffnet, sodass das Betriebsmittel am Expander 22 vorbeigeführt wird.
  • Zweiter Betriebsmodus 2: Dieser Betriebsmodus 2 ist dem Normalbetrieb des Expanders 22 zugeordnet. Sobald der Druck p2 und/oder die Temperatur T2 des Betriebsmittels stromabwärts des Expanders 22 einen definierten Wert bzw. definierte Werte überschreiten, wird der Betriebsmodus 2 aktiviert.
  • Dritter Betriebsmodus 3: dieser Betriebsmodus 3 dient für Gangwechselvorgänge des Getriebes 16.
In Fig. 2 the operating modes of this first embodiment are shown. It can with the in Fig. 1 illustrated embodiment, the following operating modes are performed:
  • First mode of operation 1 is performed during the warm-up phase of the expander 22; In operating mode 1, the bypass valve 26 is opened, so that the operating medium is guided past the expander 22.
  • Second Operating Mode 2 : This operating mode 2 is assigned to the normal operation of the expander 22. As soon as the pressure p 2 and / or the temperature T 2 of the operating medium downstream of the expander 22 exceeds a defined value or defined values, the operating mode 2 is activated.
  • Third Operation Mode 3 : This operation mode 3 is for gear change operations of the transmission 16.

Während des Runterschaltvorganges wird das Umgehungsventil 26 geschlossen. Die Nebenantriebswelle 19 wird durch den Expander 22 angetrieben und das Drehmoment des Expanders 22 genutzt, während die Drehzahl der Kurbelwelle 14 der Brennkraftmaschine 10 und die Drehzahl des Getriebes 16 synchronisiert werden. Die Schaltkupplung 15 ist dabei geöffnet. Dadurch kann die Kraftstoffmenge zur Beschleunigung der Brennkraftmaschine 10 reduziert werden. Weiters kann während des Schaltvorganges eine gewisse Motordrehzahl gehalten werden. Somit kann die Abgaswärme stromabwärts der Abgasnachbehandlungseinrichtung 12 zur Überbrückung von Drehmomenteinbrüchen bei Schaltpausen verwendet werden.During the downshift, the bypass valve 26 is closed. The PTO shaft 19 is driven by the expander 22 and the torque of the expander 22 is used, while the rotational speed of the crankshaft 14 of the internal combustion engine 10 and the rotational speed of the transmission 16 are synchronized. The clutch 15 is open. Thereby, the amount of fuel for acceleration of the internal combustion engine 10 can be reduced. Furthermore, during the switching process, a certain engine speed can be maintained. Thus, the exhaust heat can be used downstream of the exhaust aftertreatment device 12 for bridging torque drops during switching breaks.

Während des Hochschaltvorganges wird das Umgehungsventil 26 des Expanders 22 geöffnet und - bei schaltbarer Kupplung 28 - der Expander 22 durch Öffnen der schaltbaren Kupplung 28 von der Nebenantriebswelle 19 getrennt. Dadurch wird vermieden, dass Drehmoment vom Expander 22 auf die Brennkraftmaschine 10 übertragen wird.
Vierter Betriebsmodus 4: dieser Betriebsmodus 4 wird während des Segelbetriebs, des Warmlaufbetriebs und/oder des Motorbremsbetriebs der Brennkraftmaschine 10 verwendet. Im Segelbetrieb rollt das Fahrzeug ohne Drehmomentübertragung zwischen Brennkraftmaschine 10 und Antriebsräder 18, im Allgemeinen bei geöffneter Schaltkupplung 15. Das Umgehungsventil 26 ist im Betriebsmodus 4 geschlossen, um vom Expander 22 Drehmoment an die Brennkraftmaschine 10 zu übertragen. Dadurch wird - insbesondere bei geöffneter Schaltkupplung 15 - der Kraftstoffverbrauch im Leerlauf vermindert. Wenn ein hohes Drehmoment vom Expander 22 zur Verfügung steht, kann die Schaltkupplung 15 geschlossen werden, bis das Drehmoment des Expanders 22 einen definierten Wert unterschreitet.During the upshift, the bypass valve 26 of the expander 22 is opened and - with switchable clutch 28 - the expander 22 separated by opening the switchable clutch 28 of the PTO shaft 19. This avoids that torque is transmitted from the expander 22 to the internal combustion engine 10.
Fourth Operating Mode 4 : This operating mode 4 is used during the sailing operation, the warm-up operation, and / or the engine braking operation of the internal combustion engine 10. In sailing operation, the vehicle rolls without torque transmission between internal combustion engine 10 and drive wheels 18, generally with the clutch 15 open. The bypass valve 26 is closed in operating mode 4 in order to transmit torque from the expander 22 to the internal combustion engine 10. As a result - especially when the clutch 15 is open - the fuel consumption at idle reduced. If a high torque is available from the expander 22, the clutch 15 may be closed until the torque of the expander 22 falls below a defined value.

Die in Fig. 3 dargestellte zweite Ausführungsvariante unterscheidet sich von Fig. 1 dadurch, dass anstelle der schaltbaren Kupplung 28 eine Freilaufkupplung 29a und eine Fliehkraftbremseinrichtung 29b zur Verbindung des Expanders 22 mit der Nebenantriebswelle 19 der Brennkraftmaschine 10 vorgesehen sind.In the Fig. 3 illustrated second embodiment differs from Fig. 1 in that, instead of the shiftable clutch 28, an overrunning clutch 29a and a centrifugal braking device 29b are provided for connecting the expander 22 to the auxiliary drive shaft 19 of the internal combustion engine 10.

Zum Starten des Expanders 22 kann die Steuerungseinrichtung 30 zusätzlich zu den oben genannten Betriebsmodi 1 bis 4 einen fünften Betriebsmodus 5 ausführen, um den Expander 22 mit einer internen oder externen Starteinrichtung 27 zu starten (siehe Fig. 3, Fig. 4).To start the expander 22, the controller 30 may perform a fifth operation mode 5 in addition to the above-mentioned operation modes 1 to 4 to start the expander 22 with an internal or external starting device 27 (see FIG Fig. 3, Fig. 4 ).

Um zu vermeiden, dass der Expander 22 mit Überdrehzahl betrieben und dadurch geschädigt werden kann, sieht die Steuerungseinrichtung 30 spezielle Sicherheitsmaßnahmen vor. So wird das Umgehungsventil 26 nur dann geschlossen, wenn sich das Betriebsmittel in einem überhitzten Zustand befindet, also beispielsweise wenn das Betriebsmittel Ethanol sich in der Gasphase befindet. Eine weitere Sicherheitsmaßnahme ist, dass das Umgehungsventil 26 geöffnet wird, wenn ein Gangwechsel in einen höheren Gang durchgeführt wird. Insbesondere bei der in Fig. 3 dargestellten Ausführungsvariante mit Freilaufkupplung 29a und Fliehkraftbremseinrichtung 29b sind keine weiteren Schritte erforderlich.In order to avoid that the expander 22 can be operated at overspeed and thereby damaged, the control device 30 provides special security measures. Thus, the bypass valve 26 is closed only when the resource is in an overheated condition, such as when the resource, ethanol, is in the gas phase. Another safety measure is that the bypass valve 26 is opened when a gear shift to a higher gear is performed. Especially at the in Fig. 3 illustrated embodiment with overrunning clutch 29a and centrifugal braking device 29b no further steps are required.

Bei der in Fig. 1 dargestellten Ausführungsvariante mit einer schaltbaren Kupplung 28 werden das Umgehungsventil 26 und die schaltbare Kupplung 28 nur dann geschlossen, wenn sich das Betriebsmittel in einem überhitzten Zustand befindet, also beispielsweise, wenn das Betriebsmittel Ethanol sich in Gasphase befindet. Bei einem Gangwechsel in einen höheren Gang werden sowohl das Umgehungsventil 26, als auch die schaltbare Kupplung 28 geöffnet.At the in Fig. 1 illustrated embodiment with a switchable coupling 28, the bypass valve 26 and the switchable coupling 28 are closed only when the equipment is in an overheated state, that is, for example, when the resource ethanol is in the gas phase. In a gear change to a higher gear both the bypass valve 26, and the switchable clutch 28 are opened.

Die schaltbare Kupplung 28 wird somit geschlossen, wenn sich das Betriebsmittel in einem überhitzten Zustand befindet, oder wenn die Drehzahl n des Expanders 22 und/oder die Drehzahl der Brennkraftmaschine 10 über einem definierten Wert liegt. Die schaltbare Kupplung 28 wird also geöffnet, wenn sich der Expander 22 in einem nicht überhitzten Zustand befindet. Die Schaltkupplung 28 wird auch dann geöffnet, und sich der Betriebszustand der Brennkraftmaschine 10 von einem aktivierten in einen deaktivierten Zustand in, wenn also die Brennkraftmaschine 10 abgestellt wird.The switchable clutch 28 is thus closed when the operating means is in an overheated state, or when the speed n of the expander 22 and / or the speed of the internal combustion engine 10 is above a defined value. The switchable clutch 28 is thus opened when the expander 22 is in a non-overheated condition. The clutch 28 is also then opened, and the operating state of the internal combustion engine 10 from an activated to a deactivated state in, so when the internal combustion engine 10 is turned off.

Claims (18)

  1. Method for controlling a waste heat utilization system (20) for an internal combustion engine (10) of a vehicle, wherein the waste heat utilization system (20) comprises at least one expander (22) which can transmit a torque to the internal combustion engine (10) and which can be bypassed via a bypass flow path (25), at least one evaporator (21) and at least one pump (24) for an operating means, in particular ethanol, and wherein at least the evaporator (21) is disposed in the region of the exhaust gas system (11) of the internal combustion engine (10), wherein the expander (22) which can be operated in several operating modes is drive-connected in at least one operating mode to an auxiliary drive shaft (19) of the internal combustion engine and on the basis of at least one input quantity, in each case one operating mode is selected from at least two operating modes (1, 2, 3, 4, 5) of the waste heat utilization system (20) by a control device (30) and the waste heat utilization system (20) is operated in this operating mode preferably by triggering at least one bypass valve (26) of the expander (22) disposed in the bypass flow path (25) of the expander (22), characterized in that the input quantity is selected from the group expander speed (n), gear information (GI), coasting information (CI), pressure (p1) and temperature (T1) of the operating means upstream of the expander (22) and/or pressure (p2) and temperature (T2) downstream of the expander (22) by the control device (30), wherein a first operating mode (1) is assigned to a warm-up phase of the expander (22) and a second operating mode (2) is assigned to a normal operating phase of the expander (22), wherein in the first operating mode (1) the bypass flow path (26) is opened and the expander (22) is not connected to the auxiliary drive shaft (19) of the internal combustion engine (10) and wherein in the second operating mode the bypass flow path (25) is closed and the expander (22) is connected to the internal combustion engine (10), wherein the second operating mode (2) is selected when the pressure (p2) and/or the temperature (T2) of the operating means exceeds a defined value downstream of the expander (22).
  2. The method according to claim 1, characterized in that a change is made from the second operating mode into the first operating mode when the pressure (p1) and/or the temperature (T1) of the operating means upstream of the expander (22) exceeds a defined value.
  3. The method according to claim 1 or 2, characterized in that the waste heat utilization system (20) is operated in a third operating mode (3) during at least one gear change, wherein preferably during at least one shift-down process a bypass flow path (25) of the expander (22) is closed and the auxiliary drive shaft (19) is driven by the expander (22), wherein especially preferably during at least one shift-up process a bypass flow path (25) of the expander (22) is opened and/or the expander (22) is separated from the auxiliary drive shaft (19).
  4. The method according to any one of claims 1 to 3, characterized in that the waste heat utilization system (20) is operated in a fourth operating mode (4) during at least one coasting mode of the vehicle, during at least one warm-up mode of the internal combustion engine (10) and/or at least one engine braking mode of the internal combustion engine (10), wherein the bypass flow path (25) is preferably closed in the fourth operating mode (4).
  5. The method according to claim 4, characterized in that in the fourth operating mode the expander (22) is separated from the auxiliary drive shaft (19), wherein preferably the expander (22) is only separated from the auxiliary drive shaft (19) when the torque of the expander (22) falls below a defined value.
  6. The method according to any one of claims 1 to 5, characterized in that the waste heat utilization system (20) is operated in a fifth operating mode (5) during at least one starting phase of the expander (22), wherein the expander (22) is started by activating a starting device (27) connected to the expander (22).
  7. The method according to any one of claims 1 to 6, characterized in that the expander (22) is separated from the auxiliary drive shaft (19) in the first operating mode (1) and/or when the waste heat utilization system (20) is inactive.
  8. The method according to any one of claims 1 to 7, characterized in that the bypass flow path (25) of the expander (22) is closed when the operating means of the waste heat utilization system (20) is in an overheated state.
  9. The method according to any one of claims 1 to 8, characterized in that the expander (22) is drive-connected to the auxiliary drive shaft (19) when the operating means of the waste heat utilization system (20) downstream of the expander (22) is in an overheated state and/or when the expander speed (n) exceeds a defined value and/or the speed of the internal combustion engine (10) exceeds a defined value.
  10. The method according to any one of claims 1 to 9, characterized in that expander (22) is separated from the auxiliary drive shaft (19) when the operating means of the waste heat utilization system (20) upstream of the expander (22) is in a non-overheated state or when the internal combustion engine (10) is stopped.
  11. Waste heat utilization system (20) for a vehicle driven by an internal combustion engine (10) via a drive train (13), comprising a control device (30) for controlling the waste heat utilization system (20), wherein the waste heat utilization system (20) comprises at least one expander (22) which can transmit a torque to the internal combustion engine (10) and which can be bypassed via a bypass flow path (25), at least one evaporator (21) and at least one pump (24) for an operating means, in particular ethanol, and wherein at least the evaporator (21) is disposed in the region of the exhaust gas system (11) of the internal combustion engine (10), wherein the expander (22) which can be operated in several operating modes can be drive-connected in at least one operating mode to an auxiliary drive shaft (19) of the internal combustion engine (10) and on the basis of at least one input quantity, in each case one operating mode can be selected from at least two operating modes (1, 2, 3, 4, 5) of the expander (22) by the control device (30) and the expander (22) can be operated in this operating mode preferably by triggering at least one bypass valve (26) of the expander (22) disposed in the bypass flow path (25) of the expander (22), characterized in that the input quantity can be selected from the group expander speed (n), gear information (GI), coasting information (CI), pressure (p1) and temperature (T1) of the operating means upstream of the expander (22) and/or pressure (p2) and temperature (T2) downstream of the expander (22), wherein a first operating mode (1) is assigned to a warm-up phase of the waste heat utilization system (20) and a second operating mode (2) is assigned to a normal operating phase of the expander (22), and in at least one operating mode the expander (22) can be separated from the auxiliary drive shaft (19), wherein in the first operating mode (1) the bypass flow path (25) is opened and the expander (22) is separated from the auxiliary drive shaft (19) and in the second operating mode the bypass flow path (25) is closed and the expander (22) is connected to the internal combustion engine (10), and wherein the second operating mode (2) can be selected when the pressure (p2) and/or the temperature (T2) of the operating means exceeds a defined value downstream of the expander (22).
  12. The waste heat utilization system (20) according to claim 11, characterized in that a third operating mode (3) is assigned to at least one gear change phase.
  13. The waste heat utilization system (20) according to claim 11 or 12, characterized in that a fourth operating mode (4) is assigned to at least one coasting mode of the motor vehicle, at least one warm-up mode of the internal combustion engine (10) and/or at least one engine braking mode of the internal combustion engine (10), wherein preferably in the fourth operating mode (4) the bypass flow path (25) can be closed.
  14. The waste heat utilization system (20) according to any one of claims 11 to 13, characterized in that in the fourth operating mode (4) the expander (22) can be separated from the auxiliary drive shaft (19).
  15. The waste heat utilization system (20) according to any one of claims 11 to 14, characterized in that the expander (22) can be separated from the auxiliary drive shaft (19) in the first operating mode and/or when the waste heat utilization system (20) is inactive.
  16. The waste heat utilization system (20) according to any one of claims 11 to 15, characterized in that t the expander (22) is at least connected to a starting device (27), wherein in a fifth operating mode assigned to at least one starting phase of the expander (22) the expander (22) can be started by activating the external starting device (27). (Fig. 3, 4)
  17. The waste heat utilization system (20) according to any one of claims 11 to 16, characterized in that the expander (22) can be connected to the auxiliary drive shaft (19) or separated from this by means of at least one disengageable clutch (28).
  18. The waste heat utilization system (20) according to any one of claims 11 to 17, characterized in that the expander (22) can be connected to the auxiliary drive shaft (19) by means of at least one overrunning clutch (29a) wherein at least one centrifugal force braking device (29b) is preferably disposed between the overrunning clutch (29a) and the expander (22).
EP16740953.1A 2015-07-10 2016-07-11 Method for controlling a waste-heat utilization system for an internal combustion engine Active EP3320190B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50608/2015A AT517911B1 (en) 2015-07-10 2015-07-10 METHOD AND CONTROL OF A WASTE-USE SYSTEM FOR AN INTERNAL COMBUSTION ENGINE
PCT/AT2016/050246 WO2017008094A1 (en) 2015-07-10 2016-07-11 Method for controlling a waste-heat utilization system for an internal combustion engine

Publications (2)

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EP3320190A1 EP3320190A1 (en) 2018-05-16
EP3320190B1 true EP3320190B1 (en) 2019-03-20

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EP16740953.1A Active EP3320190B1 (en) 2015-07-10 2016-07-11 Method for controlling a waste-heat utilization system for an internal combustion engine

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US (1) US10858961B2 (en)
EP (1) EP3320190B1 (en)
CN (1) CN107896502B (en)
AT (1) AT517911B1 (en)
WO (1) WO2017008094A1 (en)

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Publication number Priority date Publication date Assignee Title
FR3069882A1 (en) * 2017-08-07 2019-02-08 Exoes RANKINE CYCLE VOLUMETRIC HOLDING MACHINE AND METHOD OF CONTROLLING THE SAME
CN107893710A (en) 2017-12-28 2018-04-10 朱珍珍 Combustion engine high-performance energy conservation residual-heat utilization technology
CN110259925B (en) * 2019-05-22 2020-12-22 潍柴动力股份有限公司 Vehicle gear shifting device, vehicle and vehicle gear shifting method

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US8528333B2 (en) * 2007-03-02 2013-09-10 Victor Juchymenko Controlled organic rankine cycle system for recovery and conversion of thermal energy
US7950230B2 (en) * 2007-09-14 2011-05-31 Denso Corporation Waste heat recovery apparatus
JP4302759B2 (en) * 2007-09-14 2009-07-29 株式会社デンソー Waste heat utilization equipment
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Publication number Publication date
AT517911A1 (en) 2017-05-15
EP3320190A1 (en) 2018-05-16
WO2017008094A1 (en) 2017-01-19
CN107896502B (en) 2019-12-17
US20200088069A1 (en) 2020-03-19
US10858961B2 (en) 2020-12-08
CN107896502A (en) 2018-04-10
AT517911B1 (en) 2018-03-15

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