WO2012016647A1 - Moteur à combustion interne doté d'un dispositif de récupération de chaleur et procédé pour faire fonctionner un moteur à combustion interne - Google Patents

Moteur à combustion interne doté d'un dispositif de récupération de chaleur et procédé pour faire fonctionner un moteur à combustion interne Download PDF

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Publication number
WO2012016647A1
WO2012016647A1 PCT/EP2011/003693 EP2011003693W WO2012016647A1 WO 2012016647 A1 WO2012016647 A1 WO 2012016647A1 EP 2011003693 W EP2011003693 W EP 2011003693W WO 2012016647 A1 WO2012016647 A1 WO 2012016647A1
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WO
WIPO (PCT)
Prior art keywords
internal combustion
combustion engine
heat
working medium
heat exchangers
Prior art date
Application number
PCT/EP2011/003693
Other languages
German (de)
English (en)
Inventor
Manuel Jung
Eugen Krebs
Alexander Kropp
Thomas Streule
Original Assignee
Daimler Ag
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 Daimler Ag filed Critical Daimler Ag
Publication of WO2012016647A1 publication Critical patent/WO2012016647A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • 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
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0089—Oil coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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

  • the invention relates to an internal combustion engine with a heat recovery device according to the features of the preamble of claim 1. Furthermore, the invention relates to a method for operating an internal combustion engine according to the features of the preamble of claim 6.
  • Heat recovery device described wherein a plurality of heat exchangers is assigned in each case a separate pump, with the help of which the respective
  • the working medium can be fed.
  • WO 2004/033859 A1 relates to a method and a device for recovering energy from the waste heat of thermal or chemical processes, wherein at least a portion of this waste heat evaporates a liquid via at least one heat exchanger or heats a vapor or a gas and increases its pressure, and this pressure is converted into mechanical energy in a work machine.
  • the invention is based on the object, an improved, in particular
  • the object is achieved by a
  • a working fluid flow heat exchanger In an internal combustion engine having a heat recovery device with a conveyor unit, at least two parallel arranged in a working fluid circuit and can be traversed by a working fluid flow heat exchangers, a
  • Expansion device and a condenser is arranged between the delivery unit and the heat exchangers in the working fluid circuit at least a first distribution device such that the working fluid flow is divided into partial working medium flows and controlled by the respective heat exchanger working medium partial flow is controlled and / or regulated.
  • Heat exchanger to adjust a working fluid flow operating point dependent and individually.
  • an active control and / or regulation for the distribution of the working medium flow in a Rankine cycle with several heat exchangers, evaporators and / or heat sources connected in parallel and consequently an active influencing of the evaporation process of the individual heat exchangers, evaporators and / or heat sources is possible.
  • the first distribution device comprises at least one first multi-way flow control device.
  • the first distribution device comprises at least one first multi-way flow control device.
  • a simple division of the working medium flow into a plurality of working medium partial flows is made possible, wherein the respective working medium partial flows can be individually opened or closed.
  • the first distribution device with at least one first multi-path flow control device upstream of the heat exchangers, there is a second distribution device with at least one of the heat exchangers
  • the upstream first multi-way flow control device serves to divide the working medium flow into a number of working medium partial flows corresponding to the number of heat exchangers.
  • the downstream second multi-way flow control device serves to bring together the working medium partial flows flowing out of the heat exchangers into the total or working medium flow.
  • the first distribution device may comprise a number of flow control devices corresponding to the number of heat exchangers.
  • the flow control devices are the flow input side of the
  • a further embodiment provides that the heat exchangers are preceded by a corresponding number of flow control devices and a first multi-way flow control device arranged upstream of them, and a second multi-way flow control device is connected downstream.
  • the working medium flow through each heat exchanger is by means of the first
  • Distribution device in a simple manner adjustable and to a
  • Heat loss output of the internal combustion engine is adjusted.
  • the heat exchangers can be used, for example, as an exhaust gas heat exchanger,
  • These heat exchangers allow a particularly effective use of heat loss of the internal combustion engine.
  • the vaporous working medium generated by the heat exchanger is expanded in an expansion device, wherein in the expansion device, a kinetic energy of the vaporous working fluid in a Rotational energy is converted.
  • the expansion device is z. B. coupled to a generator that generates electrical energy. Also, the
  • Expansion device directly support the internal combustion engine by means of a coupled mechanical connection with a drive train of a vehicle.
  • the heat loss of the internal combustion engine is used so that a fuel economy of the internal combustion engine and a reduction in the amount of exhaust gas and operating costs of the vehicle can be achieved.
  • the parallel arranged in the working fluid circuit heat exchanger are with
  • a coolant circuit of the internal combustion engine and / or a charge air guide of the internal combustion engine and / or an exhaust gas recirculation of the internal combustion engine and / or an exhaust system of the internal combustion engine is assigned a separate heat exchanger, thereby almost all, resulting in operation of the internal combustion engine heat loss in the heat exchangers and the resulting can be used in the Clausius-Rankine cycle.
  • the working medium flow through the respective heat exchanger by means of the heat exchangers assigned
  • Heat exchangers controlled and / or regulated.
  • Flow control devices pressure-dependent, for example, depending on the respective working fluid pressure before and / or after each heat exchanger, controlled and / or regulated.
  • the flow control devices associated with the respective heat exchangers are advantageously controlled and / or regulated independently of one another.
  • the working fluid flow through the respective heat exchanger to the heat absorbed by the heat exchanger amount of heat can be adjusted.
  • the heat exchangers are acted upon by thermal energy of a single or with heat energy of different heat sources of the internal combustion engine. For example, a first heat exchanger is flowed through by the exhaust gas of the internal combustion engine, while a second heat exchanger of compressed and thus heated charge air is flowed through and a third heat exchanger of coolant from the
  • Coolant circuit is flowed through.
  • an arrangement is a plurality of heat exchangers, for example in the
  • Exhaust system of the internal combustion engine possible, which are all flowed through by the exhaust gas.
  • the method enables a reduction of the thermal load for the vehicle cooling system and thus a relief of the vehicle cooling system.
  • the method can be used particularly advantageously in any internal combustion engine in order to realize an optimized loading of the parallel heat exchangers.
  • the invention advantageously makes it possible to influence pressures and / or densities of the gaseous working fluid at the exits of the heat exchangers by means of the adjustment and control of the supplied quantities of the liquid working fluid.
  • a risk of circulation of the working fluid between the output sides of the heat exchangers is reduced by the invention.
  • an advantage of the invention an increase in efficiency of the Clausius-Rankine cycle is achieved.
  • the efficiency of the internal combustion engine is further increased.
  • FIG. 1 shows schematically a block diagram of an internal combustion engine with a heat recovery device based on the principle of a Rankine cycle
  • Fig. 2 shows schematically a detail view of a first embodiment of a
  • FIG. 3 is a schematic detail view of a second embodiment of a
  • Fig. 4 shows schematically a detail view of a third embodiment of a
  • the heat exchanger assembly, Fig. 5 shows schematically a detail view of a fourth embodiment of a
  • Fig. 6 schematically shows a detail view of a fifth embodiment of a
  • the heat exchanger assembly The heat exchanger assembly.
  • FIG. 1 schematically shows a block diagram of an internal combustion engine 1 with a heat recovery device 2.
  • the internal combustion engine 1 is designed as a conventional diesel or gasoline engine and thermally coupled to a heat exchanger assembly 3.
  • Heat exchanger assembly 3 an expansion device 5 and a capacitor 6 connected in a working fluid circuit AK, wherein in this working fluid circuit AK a working fluid is performed and performed in the working fluid circuit AK process sequence corresponds to a so-called Clausius-Rankine cycle.
  • the liquid working fluid is supplied in a working fluid flow AS from the delivery unit 4 to the heat exchanger arrangement 3.
  • the liquid working fluid is heated under approximately constant pressure using the heat loss of the internal combustion engine 1 such that it evaporates.
  • the heat exchanger assembly 3 may be, for example, as an exhaust gas heat exchanger, charge air heat exchanger, exhaust gas recirculation heat exchanger and / or
  • Coolant heat exchanger use an exhaust heat and / or heat of a coolant of the internal combustion engine 1 to heat the liquid working fluid and evaporate.
  • the high-pressure vaporous working fluid is supplied to the expansion device 5 and is expanded in an adiabatic expansion to a vaporized working fluid at normal pressure.
  • the z. B. is designed as a turbine or piston expansion machine, while a kinetic energy of the vaporous working fluid is converted into a mechanical energy.
  • Expansion device 5 are converted into an electrical energy with an electric generator, not shown.
  • This electrical energy can z. B. are used to drive an electric motor, not shown, which acts to support the internal combustion engine 1. Furthermore, the means of the
  • Expansion device 5 generated mechanical energy directly via unspecified arrangements of the internal combustion engine 1 are supplied to support.
  • the vaporous working fluid After expansion, the vaporous working fluid is fed to a condenser 6, in which the vaporous working fluid is condensed approximately isobarically by means of cooling and thus converted into a liquid state of aggregation, so that the delivery unit 4 can be supplied with the liquid working fluid on the input side.
  • FIG. 2 schematically shows a detailed view of a first exemplary embodiment of a heat exchanger arrangement 3 '.
  • the heat exchanger assembly 3 comprises a plurality of individual ones
  • Heat exchangers 3.1 to 3.x which are arranged in parallel in the working fluid circuit AK of the Clausius-Rankine cycle and can be acted upon with working medium substreams TS1 to TSx.
  • the individual heat exchangers 3.1 to 3.x in the exhaust gas flow AG of the internal combustion engine 1 can be arranged one behind the other and / or successively with the heat loss of the exhaust gas flow AG
  • the individual heat exchangers 3.1 to 3.x are designed as exhaust gas heat exchangers and arranged in an exhaust system, not shown, of the internal combustion engine 1.
  • the plurality of individual heat exchangers 3.1 to 3.x in this embodiment the heat loss of a single heat source - the exhaust gas of the internal combustion engine 1 - acted upon.
  • Heat exchangers 3.1 to 3.x can not be specified exactly. This can lead to a circulation of the vaporous working fluid between the output sides of the heat exchangers 3.1 to 3.x. Thus, undefined and low-efficiency states become established in the Clausius-Rankine cycle.
  • the invention proposes to arrange a first distribution device V1 between the conveying unit 4 and the heat exchangers 3.1 to 3.x, by means of which the conveyed working medium flow AS is divided into working medium partial flows TS1 to TSx which are individually controlled and / or regulated respective heat exchangers 3.1 to 3.x are supplied.
  • a first distribution device V1 between the conveying unit 4 and the heat exchangers 3.1 to 3.x, by means of which the conveyed working medium flow AS is divided into working medium partial flows TS1 to TSx which are individually controlled and / or regulated respective heat exchangers 3.1 to 3.x are supplied.
  • conveyor unit 4 Due to the combination of conveyor unit 4 and first distribution device V1, a single conveyor unit is sufficient. But it can also be provided in combination with the first distribution means a plurality of conveyor units (not shown in detail).
  • the first distribution device V1 comprises at least one multiway flow control device.
  • a second distribution device V2 can be used to collect the working medium partial flows TS1 to TSx.
  • a multi-way distribution device may be arranged.
  • the multi-way distribution devices are designed as conventional distribution devices which divide the working fluid flow AS into individual working medium partial flows TS1 to TSx and downstream to the heat exchangers 3.1 to 3.x again
  • each working medium input 9.1 to 9.x of each heat exchanger 3.1 to 3.x can be individually supplied with a working medium partial flow TS1 to TSx of the liquid working medium.
  • the control unit is suitably also provided, which is electrically coupled to the / the distribution / V1 and / or V2, so that the distribution device / s V1 and / or V2 depending on the operating state is individually controlled / are ,
  • the working medium partial flow TS1 to TSx can be adjusted operating point-dependent and individually for each heat exchanger 3.1 to 3.x. In this way, an optimized operation of the heat exchangers 3.1 to 3.x is made possible, which is adapted in particular to the loss heat output of the internal combustion engine 1.
  • FIG. 3 schematically shows a detailed view of a second exemplary embodiment of a heat exchanger arrangement 3 ".
  • the first distribution device V1 comprises a first multi-way flow control device 8.1 and this downstream of the number of heat exchangers 3.1 to 3.x corresponding number of flow control devices 7.1 to 7.x.
  • z. B. as a function of the working fluid temperature, and / or event-dependent, for. B. operating point dependent, stepwise and / or steplessly controlled and / or regulated.
  • the flow control devices 7.1 to 7.x are for example simple
  • Passage valves whose flow passages are individually adjustable. Alternatively, these may be pressure valves, check valves or directional control valves.
  • the flow control devices 7.1 to 7.x are designed as a conventional, controllable distribution or metering and branching device.
  • the flow control devices 7.1 to 7.x can be controlled electrically, mechanically, pneumatically or hydraulically.
  • the flow control devices 7.1 to 7.x can be controlled electrically, mechanically, pneumatically or hydraulically.
  • Flow control devices 7.1 to 7.x be designed as a flap, slide, valve or valve, which are controlled by means of a control unit, not shown.
  • FIG. 4 schematically shows a detailed view of a third exemplary embodiment of a heat exchanger arrangement 3 "'.
  • the heat exchanger arrangement 3 ' comprises at least two individual heat exchangers 3.1 and 3.2, which are arranged in parallel in the working medium cycle AK of the Rankine cycle process
  • the heat exchanger 3.1 is designed as an exhaust gas heat exchanger and arranged in an exhaust system, not shown, of the internal combustion engine 1, wherein the heat exchanger 3.1 uses the exhaust heat of the internal combustion engine 1.
  • the second heat exchanger 3.2 is designed as a coolant heat exchanger and arranged in a coolant circuit, not shown, of the internal combustion engine 1, wherein the heat exchanger 3.2 uses the coolant heat of a coolant KM of the internal combustion engine 1.
  • the heat exchanger can be 3.2 as
  • Exhaust gas recirculation system of the internal combustion engine 1 are arranged, wherein the heat exchanger 3.2, the exhaust heat of the recirculated exhaust gas of the
  • Internal combustion engine 1 uses.
  • Internal combustion engine 1 can be acted upon. As a result, advantageously, the entire, in operation of the internal combustion engine 1 resulting heat loss energy in the
  • Heat exchangers 3.1 and 3.2 and resulting in the Rankine Rank cycle can be used.
  • the respective heat exchangers 3.1 and 3.2 is for individual control and / or regulation of the associated working medium partial flows TS1 and TS2 a
  • Working fluid flow AS is connected upstream of the associated working medium sub-streams TS1 and TS2.
  • Stromungsausgang prepare the working medium for TS1 and TS2.
  • the working medium partial flows TS1 to TSx are temperature-dependent controlled by the respective heat exchangers 3.1 to 3.x by means of the flow regulators 7.1 to 7.x associated with the heat exchangers 3.1 to 3.x. or regulated.
  • the respective working medium partial flows TS1 to TSx are controlled and / or regulated as a function of the respective outlet temperature of the working medium from the respective heat exchanger 3.1 to 3.x.
  • each working fluid outlet 10.1 to 10.x of each heat exchanger 3.1 to 3.x is assigned a respective temperature sensor 11.1 to 11.x, which transmits a corresponding temperature signal to the control unit, not shown.
  • the control unit determines as a function of the temperature signals of the individual temperature sensors 11.1 to 11.x and / or in dependence on the temperature
  • Operating state of the internal combustion engine 1 each have a separate control signal for the flow control devices 7.1 to 7.x and / or the multi-way flow control devices 8.1 to 8.2.
  • the working medium partial flows TS1 to TSx are pressure-dependent controlled and / or regulated by the respective heat exchangers 3.1 to 3.x by means of the flow control devices 7.1 to 7.x.
  • the Working medium partial flows TS1 to TSx as a function of the working medium pressures before and / or after each heat exchanger 3.1 to 3.x controlled and / or regulated.
  • each work input is 9.1 to 9.x and each
  • the control unit determines a separate control signal for the flow control devices 7.1 to 7.x and / or the multiway flow control devices 8.1 to 8.2 depending on the pressure signals of the individual pressure sensors 12.1 to 12.n.
  • the working medium partial flows TS1 to TSx are set by the parallel arranged heat exchangers 3.1 to 3.x by individual control of the flow control devices 7.1 to 7.x so that in the lines downstream of the individual heat exchangers 3.1 to 3.x largely identical
  • Adjust flow conditions of the working fluid can be achieved by a corresponding control of the flow control devices 7.1 to 7.x that the working fluid in the lines output side of the individual heat exchanger 3.1 to 3.x has a substantially equal pressure and / or a substantially same density. In this way, defined flow conditions of the working fluid in the conduit system downstream of the heat exchangers 3.1 to 3.x can be achieved.
  • Exhaust gas recirculation heat exchanger and a coolant heat exchanger which are acted upon by the heat loss of various heat sources.
  • Heat exchangers are arranged 3.1 to 3.x. LIST OF REFERENCE NUMBERS
  • V1 first distribution device.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un moteur à combustion interne (1) doté d'un dispositif de récupération de chaleur (2), équipé d'une unité d'alimentation (4), d'au moins deux échangeurs de chaleur (3.1 à 3.x) disposés parallèlement dans un circuit de fluide de travail (AK) et traversés par un flux de fluide de travail (AS), d'un dispositif d'expansion (5) et d'un condensateur (6). Selon l'invention, au moins un premier appareil de répartition (V1) est disposé entre l'unité d'alimentation (4) et les échangeurs de chaleur (3.1 à 3.x) dans le circuit de fluide de travail (AK) de manière telle que le flux de fluide de travail (AS) est réparti en flux partiels (TS1 à TSx) de fluide de travail et le flux partiel (TS1 à TSx) de fluide de travail s'écoulant à travers chaque échangeur de chaleur (3.1 à 3.x) étant contrôlable et/ou régulable. De plus, l'invention concerne un procédé pour faire fonctionner un moteur à combustion interne (1).
PCT/EP2011/003693 2010-08-03 2011-07-22 Moteur à combustion interne doté d'un dispositif de récupération de chaleur et procédé pour faire fonctionner un moteur à combustion interne WO2012016647A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010033124.4 2010-08-03
DE102010033124A DE102010033124A1 (de) 2010-08-03 2010-08-03 Brennkraftmaschine mit einer Wärmerückgewinnungsvorrichtung und Verfahren zum Betrieb einer Brennkraftmaschine

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Publication Number Publication Date
WO2012016647A1 true WO2012016647A1 (fr) 2012-02-09

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WO (1) WO2012016647A1 (fr)

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US20180245788A1 (en) * 2015-09-08 2018-08-30 Atlas Copco Airpower, Naamloze Vennootschap Orc for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an orc
US20190234343A1 (en) * 2018-01-30 2019-08-01 International Engine Intellectual Property Company, Llc. Organic rankine cycle waste heat recovery system having two loops

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ITPR20120006A1 (it) * 2012-02-17 2013-08-18 Giovanni Sicurello Dispositivo di generazione di potenza motrice
EP2917512A2 (fr) * 2012-10-17 2015-09-16 Norgren Limited Système de récupération de chaleur perdue avec deux ou plusieurs evaporateurs
EP2993316A1 (fr) * 2012-10-17 2016-03-09 Norgren Limited Systeme de recuperation de la chaleur des dechets
DE102014006909B3 (de) * 2014-05-09 2015-07-09 Maschinenwerk Misselhorn Mwm Gmbh Anordnung mit mehreren Wärmeübertragern und Verfahren zum Verdampfen eines Arbeitsmediums
DE102014218485A1 (de) 2014-09-15 2016-03-17 Robert Bosch Gmbh Abwärmenutzungsanordnung einer Brennkraftmaschine und Verfahren zum Betrieb einer Abwärmenutzungsanordnung
KR101755808B1 (ko) * 2015-07-13 2017-07-07 현대자동차주식회사 폐열회수시스템
DE102016212679A1 (de) * 2016-07-12 2018-01-18 Robert Bosch Gmbh Abwärmerückgewinnungssystem
DE102019120358B4 (de) * 2019-07-29 2022-09-01 Ontras Gastransport Gmbh Gasentspannungsanlage

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