WO2018134206A1 - Ensemble comprenant un système permettant de mettre en œuvre un cycle thermodynamique et un moteur à combustion interne, ainsi que procédé permettant de faire fonctionner un tel ensemble - Google Patents

Ensemble comprenant un système permettant de mettre en œuvre un cycle thermodynamique et un moteur à combustion interne, ainsi que procédé permettant de faire fonctionner un tel ensemble Download PDF

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Publication number
WO2018134206A1
WO2018134206A1 PCT/EP2018/051024 EP2018051024W WO2018134206A1 WO 2018134206 A1 WO2018134206 A1 WO 2018134206A1 EP 2018051024 W EP2018051024 W EP 2018051024W WO 2018134206 A1 WO2018134206 A1 WO 2018134206A1
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WO
WIPO (PCT)
Prior art keywords
internal combustion
combustion engine
arrangement
exhaust gas
heat
Prior art date
Application number
PCT/EP2018/051024
Other languages
German (de)
English (en)
Inventor
Daniel Stecher
Tim Horbach
Gerald Fast
Original Assignee
Mtu Friedrichshafen 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 Mtu Friedrichshafen Gmbh filed Critical Mtu Friedrichshafen Gmbh
Publication of WO2018134206A1 publication Critical patent/WO2018134206A1/fr

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Classifications

    • 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
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • Circular process and an internal combustion engine and method for operating such an arrangement
  • the invention relates to an arrangement with a system for carrying out a
  • thermodynamic cycle and an internal combustion engine thermodynamic cycle and an internal combustion engine, and a method for operating such an arrangement.
  • the internal combustion engine with the system is thermally operatively connected so that waste heat of the internal combustion engine in the system for the implementation of the thermodynamic cycle is available.
  • the system comprises a working fluid circuit in which a working medium flows during operation of the system, wherein the
  • the working medium is conveyed in liquid phase from the working medium conveyor to the evaporator, where it absorbs waste heat of the internal combustion engine and is evaporated. In the vapor phase, the working fluid continues to flow to the expansion device where it is expanded, thereby performing mechanical work on the expansion device.
  • the relaxed working medium flows from the expansion device on to the condenser, in which it is cooled and preferably re-liquefied. From the condenser, the working medium in turn flows on to the working medium conveyor, so that the working medium circuit is closed.
  • the working medium preferably drives one
  • Output shaft which can be drive-connected in an embodiment of the system with an electric machine, so that the electric machine is driven by the output shaft.
  • the electric machine is preferably designed as a generator for generating electrical power.
  • the output shaft of the expansion device mechanically with a
  • Internal combustion engine in particular with the same internal combustion engine whose waste heat in the System is used, is operatively connected, so that the internal combustion engine can be supported by the expansion device.
  • the expansion device can apply an additional torque to the internal combustion engine and thus additionally contribute to the power output of the internal combustion engine.
  • the output shaft is the
  • Expansion device preferably with a crankshaft of the internal combustion engine
  • the internal combustion engine is in particular thermally connected to the evaporator of the working fluid circuit, wherein particularly preferably exhaust gas of the internal combustion engine by the
  • Evaporator flows, so that waste heat from the exhaust gas of the internal combustion engine is used to evaporate the working medium in the evaporator. It is possible that
  • the exhaust gas flows - as seen along an exhaust line of the internal combustion engine - preferably downstream of optionally arranged in the exhaust line exhaust gas turbines,
  • exhaust gas-carrying components are provided which are acted upon by the coolant of the coolant circuit of the internal combustion engine to prevent an unacceptably high component temperature.
  • These components may be, for example, an exhaust manifold, an exhaust pipe section between a cylinder head of the internal combustion engine and a first exhaust gas turbine along the exhaust line, a turbine housing of the exhaust gas turbine and the like.
  • This active cooling exhaust gas components reduces the enthalpy in the exhaust both for the exhaust turbine and for subsequent use in the system, so that in particular its potential use is reduced. It also shows that due to the comparatively low flow temperature of the coolant, a relatively extensive
  • the invention is based on the object, an arrangement with a system for carrying out a thermodynamic cycle and with an internal combustion engine, and a
  • At least one heat source on or in the internal combustion engine which is conventionally cooled with coolant, is now cooled via the fluid path, whereby, on the one hand, the heat transfer can take place at a higher temperature level
  • Heat source on the other hand, in operation of the internal combustion engine may have a higher temperature level, which proves to be particularly advantageous if the heat source is designed as an exhaust gas line or component upstream of an exhaust gas turbine, so the exhaust gas at this point less enthalpy is removed, which is then available to the one in the exhaust turbine and on the other hand downstream of the same in the evaporator of the system. This also increases the efficiency of the internal combustion engine at the same time. If at least one heat source to the internal combustion engine now instead of by means of
  • Coolant circuit cooled by the fluid path the refrigerant circuit can be simplified and relieved. This makes tuning the cooling of the internal combustion engine easier and more flexible.
  • the arrangement has a first thermal active connection between the internal combustion engine and the system, in particular the working fluid circuit, wherein the first thermal active connection is realized by the evaporator preferably designed as an exhaust gas heat exchanger.
  • the arrangement has a second thermal active connection between the internal combustion engine and the system, wherein the second thermal active compound preferably has a temperature level of more than 130 ° C, more preferably more than 150 ° C, preferably at most 210 ° C.
  • the second thermal active compound is preferably realized by the fluid path, which is the
  • Heat transfer fluid leads, which is in particular adapted for heat transfer in said temperature ranges.
  • the internal combustion engine has a coolant circuit in which a
  • the coolant circuit is in particular of the fluid path
  • the arrangement is preferred in which a heat transfer fluid is used, which is different from the substance or mixture of substances which is used as the coolant of the internal combustion engine. According to a preferred embodiment, the arrangement has the first thermal
  • the arrangement having a third thermal active connection between the internal combustion engine and the system, which is realized via the coolant as a heat transport medium.
  • a coolant heat exchanger in which the coolant is used to preheat the working medium.
  • the system is preferably set up to carry out an organic Rankine
  • Circular process (Organic Rankine Cycle - ORC).
  • This thermodynamic cycle is particularly suitable for waste heat utilization in connection with internal combustion engines.
  • an organic substance or an organic substance mixture in particular ethanol or an ethanol-water mixture, is preferably used as the working medium in the working medium cycle.
  • a hydrofluorocarbon or a working medium is preferably used as the working medium in the working medium cycle.
  • Chlorofluorocarbon is used.
  • the at least one heat source is flowed through by the working medium of the system.
  • the heat transfer fluid is the working medium of the system, which in operation of the arrangement immediately along the
  • the at least one heat source can be directly and immediately integrated into the thermodynamic cycle of the system as a heat source without detour via an additional fluid circuit, wherein in this embodiment in particular the heat transfer in the at least one
  • Heat source can be done at a high temperature level.
  • the at least one heat source is flowed through by a thermal oil as heat transport fluid during operation of the arrangement.
  • the heat transfer fluid is thus formed in this case as a thermal oil, wherein a thermal oil intermediate circuit between the working fluid circuit and the internal combustion engine may be established.
  • the heat transfer by means of a thermal oil can on a
  • Coolant circuit of the internal combustion engine In this case, an immediate fluidic connection between the internal combustion engine and the working fluid circuit is avoided, which may necessitate a simpler structure of the arrangement and in particular also favorable for retrofit solutions.
  • the system has an exhaust gas heat exchanger, in the exhaust gas of the internal combustion engine in thermal contact with Working medium of the system can be brought.
  • the ex gas heat exchanger is in particular the previously described evaporator of the working fluid circuit.
  • the fluid path is arranged fluidically parallel to the exhaust gas heat exchanger.
  • this configuration makes it possible to vaporize the working fluid directly in the at least one heat source, wherein the evaporation can be carried out in parallel in the exhaust gas heat exchanger on the one hand and in the at least one heat source on the other hand, allowing an additional degree of freedom for a steam control.
  • a fluid path heat exchanger connected to the fluid path and in particular through which the heat transport fluid flows on the one hand and the working fluid on the other hand is arranged fluidically parallel to the exhaust gas heat exchanger.
  • parallel to the exhaust gas heat exchanger preferably additionally takes place evaporation in the fluid path heat exchanger, which also has a
  • the fluid path is fluidically arranged in series with the exhaust gas heat exchanger, in particular upstream of the exhaust gas heat exchanger.
  • the fluid path forms a portion of the working fluid circuit upstream of the exhaust gas heat exchanger.
  • the working cycle medium can thus be preheated in the fluid path.
  • an evaporation of the working medium in the at least one heat source is avoided, which is particularly by a suitable choice of
  • Heat transport fiiuid is achieved in the fluid path.
  • the fluid path heat exchanger connected to the fluid path may be arranged fluidically in series with the exhaust gas heat exchanger, in particular upstream of the exhaust gas heat exchanger, in the working medium circuit.
  • the fluid path heat exchanger preferably serves to preheat the working medium, which is preferably not evaporated in the fluid path heat exchanger, which, for example, via a suitable temperature difference setting between the working medium and the
  • the at least one heat source is selected from a group consisting of an exhaust pipe between a combustion chamber of the internal combustion engine and an exhaust gas turbine, in particular an exhaust gas turbocharger, an exhaust gas turbine housing, a compressor housing, and a charge air line between a compressor and a charge air cooler.
  • an exhaust pipe between a combustion chamber of the internal combustion engine and an exhaust gas turbine in particular an exhaust gas turbocharger, an exhaust gas turbine housing, a compressor housing, and a charge air line between a compressor and a charge air cooler.
  • these elements are cooled by means of coolant through the coolant circuit of the internal combustion engine in order to avoid an unacceptably high component temperature.
  • these elements can be safely operated at a significantly higher temperature level than corresponds to the temperature level of the coolant. If these heat sources are now thermally connected to the system via the fluid path in which the heat transfer fluid flows, in which case they are cooled in particular by the heat transfer fluid, the temperature level of the component surfaces can be significantly increased, the heat transfer being at a higher temperature level and thus with lower exergy losses and higher efficiency can be done. This has a positive effect on the efficiency and performance of the system.
  • the enthalpy not dissipated due to the higher temperature level is available in an exhaust gas turbine, in particular an exhaust gas turbocharger, so that the efficiency of the internal combustion engine itself also increases.
  • the at least one heat source is selected from a group consisting of a cylinder head of the internal combustion engine, a crankcase of the
  • Components can be cooled by the heat transfer fluid, and their waste heat can be utilized in the system.
  • the arrangement has a controllable or controllable bypass path - in particular for the working medium or for as
  • Heat transfer fluid used has thermal oil - wherein the bypass path is arranged to thermally at least partially decouple the at least one heat source from the system.
  • the working medium or the heat transfer fluid may then at least partially along the bypass path at the at least one heat source or a fluid path heat exchanger are passed, so that the second thermal active connection
  • Heat extraction from the at least one heat source can be selectively controlled or regulated, which in particular allows thermal management of the internal combustion engine. For a more flexible tuning and optimization of the cold start, warm-up and / or transient behavior of the internal combustion engine is possible.
  • one separate, preferably separately controllable or controllable, bypass path is provided per heat source provided on the internal combustion engine, which enables a particularly efficient thermal management for the internal combustion engine.
  • the bypass path is preferably controlled or regulated by means of a controllable valve device with respect to its flow cross-section.
  • the system has a steam control device which is set up to adjust a working medium quantity flowing through the exhaust gas heat exchanger and a working fluid quantity flowing in parallel to the exhaust gas heat exchanger in order to carry out a vapor control of a steam quality of the working medium.
  • the steam control device can in particular have a controllable valve device,
  • the working medium is preferred - in particular as a function of a momentary steam quality and / or a desired steam quality - divisible to the
  • Exhaust gas heat exchanger on the one hand and the path parallel to this on the other.
  • a per unit of time, the exhaust gas heat exchanger and the parallel path flowing total amount of working fluid is preferably adjustable, to adjust this total preferably the working media conveyor is variably controlled in their flow rate.
  • an adjustment throttle or the like is provided for setting this total amount.
  • a steam quality of the working medium is in particular a temperature thereof, overheating thereof, and / or a proportion of vaporous working medium on the Total working fluid downstream of the evaporator and the path parallel thereto, understood.
  • the at least one bypass path around the at least one heat source can preferably be used for steam control of the steam quality of the working medium, in particular by being locked as required or at least partially released.
  • the object is also solved by a method for operating an arrangement with a system for performing a thermodynamic cycle and with a
  • waste heat of the internal combustion engine is used in the system for carrying out the thermodynamic cycle.
  • Fluid path supplied wherein in the fluid path, a heat transfer fluid is guided, which is not used in the internal combustion engine as a coolant and no exhaust gas of the
  • a working medium of the system is used as the heat transport fluid in the fluid path. It is preferred that
  • Working medium evaporates in the at least one heat source.
  • Heat source is thus used directly as - in particular additional - evaporator of the system.
  • the working medium in the fluid path - in particular in the heat source - is kept liquid.
  • this can be achieved by suitably setting a temperature difference and / or by setting a suitable pressure level for the working medium at the location of the heat transfer into the working medium.
  • a thermal oil is used as the heat transport fluid in the fluid path. This is suitable - as well as the use of the Working medium as a heat transfer fluid - for heat transfer to a particular in comparison with the coolant circuit of the engine higher temperature level.
  • Embodiment of the method is preferably characterized by at least one method step, which is due to at least one feature of an inventive or preferred embodiment of the arrangement.
  • the arrangement is preferably characterized by at least one feature which is due to at least one step of a preferred or preferred embodiment of the method according to the invention.
  • Figure 1 is a schematic representation of a first embodiment of an arrangement with a system for carrying out a thermodynamic cycle and an internal combustion engine;
  • Figure 2 is a schematic representation of a second embodiment of such
  • Figure 3 is a schematic representation of a third embodiment of such
  • Figure 4 is a schematic representation of a fourth embodiment of such
  • thermodynamic cycle in particular an organic Rankine cycle (ORC)
  • ORC organic Rankine cycle
  • internal combustion engine 5 which is not explicitly shown in FIG Way with the system 3 is thermally operatively connected so that waste heat of the internal combustion engine 5 in the system 3 for the implementation of the thermodynamic cycle is available.
  • the system 3 has a working medium circuit 7, along which - in the flow direction of a working medium in the working medium circuit 7 in the order given - a working medium conveyor 9, an evaporator 11, an expansion device 13 and a condenser 15 are arranged.
  • Working medium preferably an organic medium, in particular ethanol, an ethanol-water mixture, a fluorohydrocarbon or a chlorofluorocarbon is conveyed in liquid phase through the working medium conveyor 9 to the evaporator 11 and evaporated there, after which it flows on to the expansion device 13 , In this it is relaxed, wherein the working medium performs mechanical work on the expansion device 13, so that in particular an output shaft 17 is driven.
  • the relaxed working fluid continues to flow to the condenser 15 where it is cooled and, in particular, liquefied. From there, the now liquid working medium returns to the working medium conveyor 9, so that the working fluid circuit 7 is closed.
  • Expansion device 13 mechanically operatively connected to the internal combustion engine 5, so that the expansion device 13 perform mechanical work on the internal combustion engine 5 and in particular can support this.
  • the output shaft 17 is particularly preferably operatively connected to a crankshaft of the internal combustion engine 5, in particular via a gear drive on the opposite side of the engine 5 of the internal combustion engine.
  • the output shaft 17 is drivingly connected to an electric machine, wherein the preferably designed as a generator electric machine can be driven by the output shaft 17, so that electric power is generated by the electric machine.
  • the internal combustion engine 5 is preferably - in a manner not explicitly shown here - thermally operatively connected to the evaporator 11, wherein particularly preferably the exhaust gas
  • Internal combustion engine 5 flows through the evaporator 11, there to heat the working fluid of the working fluid circuit 7 and in particular to evaporate.
  • the system 3 is here additionally thermally connected via at least one schematically illustrated heat source 19, which is arranged on or in the internal combustion engine 5, via a fluid path 21, wherein the fluid path 21 carries a heat transport fluid which is neither coolant of the internal combustion engine nor exhaust gas.
  • the internal combustion engine 5 preferably has a coolant circuit in which coolant flows for cooling the internal combustion engine 5. It is possible that the
  • Coolant circuit of the internal combustion engine 5 is involved in an additional manner not shown here as additional heat source in the working fluid circuit 7, in particular for preheating the working fluid upstream of the evaporator 11.
  • additional heat source in the working fluid circuit 7, in particular for preheating the working fluid upstream of the evaporator 11.
  • such a configuration need not necessarily be provided.
  • the thermal integration of the at least one heat source 19 via the fluid path 21 has the advantage that heat can be absorbed at the heat source 19 with a higher temperature level by the heat transfer fluid, because this is not the coolant of the internal combustion engine, wherein the entry of this heat in the
  • Working medium circuit 7 can be done at a higher temperature level, so that total exergy losses are reduced and the efficiency of the system 3 in particular in
  • thermodynamically Compared to a configuration may increase, in which the heat source 19 mediated via the coolant circuit of the internal combustion engine 5 is thermally connected to the working fluid circuit 7.
  • a further advantage is that the heat source 19 can be maintained at a higher temperature level than if it were acted upon by coolant of the internal combustion engine 5.
  • the heat source 19 is an exhaust gas-carrying component upstream of an exhaust gas turbine, the advantage that the exhaust gas flowing in the component is withdrawn less enthalpy, so that this additional enthalpy can be used in the exhaust gas turbine.
  • the exhaust gas can flow hotter through the evaporator 11, so that additional enthalpy in the evaporator 11 for the thermodynamic
  • Circular process can be used.
  • the heat source 19 is not cooled by the cooling circuit of the internal combustion engine 5, this can be made simpler and easier. This also simplifies tuning the engine cooling and makes it more flexible.
  • the heat source 19 is particularly preferably an exhaust pipe of the
  • Internal combustion engine 5 which connects a combustion chamber thereof with an exhaust gas turbine, in particular the exhaust gas turbine of an exhaust gas turbocharger, to an exhaust gas turbine housing
  • Compressor housing a arranged in a charge air line compressor for compressing the charge air or a combustion air-charge air mixture, or to a charge air line between the compressor and a charge air cooler.
  • the heat source 19 is a cylinder head, a crankcase or a cylinder liner of the internal combustion engine 5.
  • the arrangement 1 has a plurality of such heat sources 19, which may preferably be selected from the aforementioned heat sources, in particular in any desired combination.
  • the heat source 19 is flowed through by the working medium of the system 3 as a heat transfer fluid.
  • the evaporator 11 is designed here as an exhaust gas heat exchanger 12, in which the exhaust gas of the internal combustion engine 5 is brought into thermal contact with the working medium of the system 3.
  • the fluid path 21 is fluidically parallel to the exhaust gas heat exchanger 12, that is, to the evaporator 11, respectively.
  • Working medium is evaporated in parallel both in the evaporator 11 and in the heat source 19.
  • the system 3 preferably has a steam control device 23 which is adapted to the amount of working fluid flowing through the exhaust gas heat exchanger 12 and a
  • the steam control device 23 is particularly adapted to a quality of steam at the location of the junction 25 in the
  • the steam control device 23 is additionally set up to also the Total amount of working medium, which flows along the working fluid circuit 7 to influence.
  • the steam control device 23 is preferably operatively connected to the working medium conveyor 9, in order to control them in a suitable manner.
  • a control or controllable bypass path is provided which is adapted to thermally decouple the at least one heat source 19 from the system 3 at least partially.
  • a valve device 27 can be used for this purpose, in order to supply the heat source 19 to the heat source 19
  • Venting path 29 to an environment 33 back can relieve.
  • Fig. 2 shows a schematic representation of a second embodiment of the arrangement 1.
  • the fluid path 21 is fluidly arranged in series with the exhaust gas heat exchanger 12, in particular upstream thereof.
  • the working medium initially flows along the fluid path 21 through the
  • Heat source 19 and then through the exhaust gas heat exchanger 12. It is preferred
  • Heat source 19 or - particularly preferably - is ensured by a corresponding pressure level for the working fluid in the heat source 19. That way that can
  • Working medium in the heat source 19 absorb heat and thus preheated quasi, without it is already evaporated, where it is then subsequently transferred in the evaporator 11 in the vapor phase.
  • the connection of the heat source 19 in the working fluid circuit 7 according to Figure 2 is particularly suitable for incorporating an exhaust gas recirculation cooler as a heat source 19 in the working fluid circuit 7.
  • a bypass path 35 is shown, by means of a bypass valve device 37, the two particular Three-way valves may be provided, one of which is arranged upstream and downstream of the heat source 19, controllably configured and arranged to thermally at least partially decouple the at least one heat source 19 from the system 3. This way you can
  • Bypass path valve device 37 preferably by a not shown here
  • Control device in particular a control device of the internal combustion engine 5, can be controlled.
  • Fig. 3 shows a schematic representation of a third embodiment of the arrangement 1. The same and functionally identical elements are provided with the same reference numerals, so far as reference is made to the preceding description. Unlike the
  • the heat source 19 is traversed by a thermal oil as a heat transfer fluid here.
  • the fluid path 21 is therefore not part of the working medium circuit 7, but forms a separate circuit between the heat source 19 and a fluid path heat exchanger 39, which is traversed on the one hand by the thermal oil and on the other hand by the working medium of the system 3, so that in the fluid path heat exchanger 39 heat exchange between the thermal oil and the working medium can be done.
  • the steam control device 23 is provided.
  • Fig. 4 shows a schematic representation of a fourth embodiment of the arrangement 1.
  • the fluid path heat exchanger 39 is arranged in fluid communication with the exhaust gas heat exchanger 12 and in particular upstream of the exhaust gas heat exchanger 12 in the working fluid circuit 7.
  • a thermal oil flows as
  • the third exemplary embodiment according to FIG. 3 structurally corresponds to the first exemplary embodiment according to FIG. 1, the fourth exemplary embodiment according to FIG. 4 corresponding to the second exemplary embodiment according to FIG.

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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 ensemble (1) comprenant un système (3) permettant de mettre en œuvre un cycle thermodynamique et un moteur à combustion interne (5), le moteur à combustion interne (5) étant en liaison fonctionnelle thermiquement avec le système (3) de telle sorte que la chaleur perdue du moteur à combustion interne (5) puisse être utilisée dans le système (3) pour mettre en œuvre le cycle thermodynamique, le système (3) pouvant être relié thermiquement à au moins une source de chaleur (19) sur ou dans le moteur à combustion interne (5) par le biais d'un trajet de fluide (21) qui guide un fluide caloporteur qui n'est ni un liquide de refroidissement du moteur à combustion interne (5) ni un gaz d'échappement. L'invention concerne en outre un procédé permettant de faire fonctionner un tel ensemble.
PCT/EP2018/051024 2017-01-19 2018-01-16 Ensemble comprenant un système permettant de mettre en œuvre un cycle thermodynamique et un moteur à combustion interne, ainsi que procédé permettant de faire fonctionner un tel ensemble WO2018134206A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017200887.3A DE102017200887A1 (de) 2017-01-19 2017-01-19 Anordnung mit einem System zur Durchführung eines thermodynamischen Kreisprozesses und einer Brennkraftmaschine, sowie Verfahren zum Betreiben einer solchen Anordnung
DE102017200887.3 2017-01-19

Publications (1)

Publication Number Publication Date
WO2018134206A1 true WO2018134206A1 (fr) 2018-07-26

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WO (1) WO2018134206A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11480101B1 (en) * 2020-01-17 2022-10-25 William Honjas Waste heat gathering and transfer system and method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010000284A2 (fr) * 2008-07-03 2010-01-07 Fev Motorentechnik Gmbh Utilisation de l'énergie des gaz d'échappement au moyen d'un cycle fermé à vapeur
WO2012088532A1 (fr) * 2010-12-23 2012-06-28 Cummins Intellectual Property, Inc. Système et procédé de régulation de refroidissement par re-circulation de gaz d'échappement en utilisant un cycle de rankine
US20130086902A1 (en) * 2011-10-10 2013-04-11 Faurecia Emissions Control Technologies Method And Apparatus For Recovering Energy From Coolant In A Vehicle Exhaust System
DE102011117057A1 (de) * 2011-10-27 2013-05-02 Daimler Ag Abwärmenutzungsvorrichtung
EP2752573A1 (fr) * 2011-08-31 2014-07-09 Kabushiki Kaisha Toyota Jidoshokki Dispositif d'utilisation de chaleur perdue
DE102013021394A1 (de) * 2013-12-13 2014-07-31 Daimler Ag Abwärmenutzungsanordnung eines Kraftfahrzeuges sowie Verfahren zur Nutzung von Abwärme eines Kraftfahrzeuges in einer Abwärmenutzungsanordnung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2449780A1 (fr) 1979-02-22 1980-09-19 Semt Procede et dispositif de recuperation d'energie thermique dans un moteur a combustion interne suralimente
DE3333069A1 (de) 1983-09-14 1985-03-21 Rudolf Dr. 6800 Mannheim Wieser Verbrennungsmotor mit dampferzeugungsanlage
DE102009035522B4 (de) 2009-07-31 2013-09-19 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verfahren und Vorrichtung zur verbesserten Energieausnutzung der Wärmeenergie von Brennkraftmaschinen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010000284A2 (fr) * 2008-07-03 2010-01-07 Fev Motorentechnik Gmbh Utilisation de l'énergie des gaz d'échappement au moyen d'un cycle fermé à vapeur
WO2012088532A1 (fr) * 2010-12-23 2012-06-28 Cummins Intellectual Property, Inc. Système et procédé de régulation de refroidissement par re-circulation de gaz d'échappement en utilisant un cycle de rankine
EP2752573A1 (fr) * 2011-08-31 2014-07-09 Kabushiki Kaisha Toyota Jidoshokki Dispositif d'utilisation de chaleur perdue
US20130086902A1 (en) * 2011-10-10 2013-04-11 Faurecia Emissions Control Technologies Method And Apparatus For Recovering Energy From Coolant In A Vehicle Exhaust System
DE102011117057A1 (de) * 2011-10-27 2013-05-02 Daimler Ag Abwärmenutzungsvorrichtung
DE102013021394A1 (de) * 2013-12-13 2014-07-31 Daimler Ag Abwärmenutzungsanordnung eines Kraftfahrzeuges sowie Verfahren zur Nutzung von Abwärme eines Kraftfahrzeuges in einer Abwärmenutzungsanordnung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11480101B1 (en) * 2020-01-17 2022-10-25 William Honjas Waste heat gathering and transfer system and method

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