WO2018050408A1 - Système de récupération de chaleur perdue - Google Patents

Système de récupération de chaleur perdue Download PDF

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Publication number
WO2018050408A1
WO2018050408A1 PCT/EP2017/071114 EP2017071114W WO2018050408A1 WO 2018050408 A1 WO2018050408 A1 WO 2018050408A1 EP 2017071114 W EP2017071114 W EP 2017071114W WO 2018050408 A1 WO2018050408 A1 WO 2018050408A1
Authority
WO
WIPO (PCT)
Prior art keywords
coolant
circuit
working fluid
fluid cooling
cooling circuit
Prior art date
Application number
PCT/EP2017/071114
Other languages
German (de)
English (en)
Inventor
Michael Richter
Axel Zuschlag
Gregory Rewers
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2018050408A1 publication Critical patent/WO2018050408A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • 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 from exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • 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
    • 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
    • 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 a waste heat recovery system with a
  • Combined internal combustion engine activated heat exchanger wherein the internal combustion engine has a cooling system with the coolant circuit and with at least one coolant pump, and a coolant radiator.
  • the waste heat recovery system has a working fluid circuit which cooperates with a heat exchanger connected in a coolant circuit of an internal combustion engine.
  • the internal combustion engine has a cooling system with the coolant circuit and with at least one coolant pump and a coolant radiator.
  • the heat exchanger is a capacitor which is switched directly into the working fluid circuit.
  • Waste heat recovery system known.
  • the condenser has a coolant supply line and a coolant discharge line, which are connected to a coolant circuit of the internal combustion engine.
  • a controllable by a bypass valve bypass is arranged between the coolant supply and thedeffenabtex Anlagen MaschinenS AG.
  • the invention has for its object to provide a waste heat recovery system, the coupling with the cooling system of an internal combustion engine is improved component optimized.
  • the heat exchanger is a cooler which is connected to a switched-on in the working fluid circuit heat exchanger in the form of a capacitor via a working fluid cooling circuit of the
  • Waste heat recovery system is connected, and that the
  • Working fluid cooling circuit is connected to the coolant circuit.
  • Coolant circuit has switched on cooler and a switched-on in the working fluid circuit condenser, and wherein the working fluid circuit and the coolant circuit are interconnected, allows several detailed improvements described in detail below
  • Waste heat recovery system with respect to its cooling and thus ultimately in terms of the efficiency of the internal combustion engine and the discharged CGremission.
  • the waste heat recovery system and the entire cooling system can be adapted to a variety of conditions resulting during operation of the internal combustion engine.
  • the coolant circuit and the coolant circuit can be adapted to a variety of conditions resulting during operation of the internal combustion engine.
  • the working fluid cooling circuit and the coolant circuit are connected in parallel with respect to the coolant pump. This is a possible embodiment that follows below possible further embodiments will be described.
  • An alternative embodiment provides that the working fluid cooling circuit and the
  • Coolant circuit based on the coolant pump are connected in series with each other.
  • the working fluid cooling circuit is the delivery side of the coolant pump via a connection with the involvement of a in the
  • Coolant circuit connected.
  • Connection is connected and thus represents a bypass to the connections.
  • the working fluid cooling circuit is connected on the delivery side of the coolant pump via a connection and the suction side of the coolant pump via a connection to the coolant circuit, and wherein the downstream
  • a 3-way valve is arranged, of which a connection via a connecting line represents a bypass of the connections.
  • Coolant circuit is connected via a connection, and that between the two connections a valve in the working fluid cooling circuit is arranged.
  • Cooling pump for the working fluid cooling circuit is typically limited to a flow rate of two kilograms per second. This may be insufficient at high ambient temperature and high load of the waste heat recovery system so as not to exceed the boiling temperature of the working fluid cooling circuit coolant.
  • the radiator can, in addition to the efficient cooling of the engine and to optimize the overall efficiency of the
  • Internal combustion engine can be used together with the waste heat recovery system.
  • the working fluid cooling circuit has a
  • Radiator bypass with a radiator bypass control valve to the radiator and / or the working fluid cooling circuit has a condenser bypass with a
  • Capacitor bypass control valve on are also advantageous in the system described above implemented and expand, for example, the control options or
  • FIG. 1 is a schematic diagram of a waste heat recovery system having a working fluid circuit and a working fluid cooling circuit connected to a coolant circuit of a cooling system of an internal combustion engine in a first embodiment
  • FIG. 2 shows a detailed view of a coupling of a working fluid cooling circuit with a coolant circuit in a further embodiment
  • FIG. 3 shows a detailed view of a coupling of a working fluid cooling circuit with a coolant circuit in a further embodiment
  • FIG. 4 is a schematic diagram of a waste heat recovery system having a working fluid circuit and a working fluid cooling circuit. the with a coolant circuit of a cooling system a
  • FIG. 5 shows a working fluid cooling circuit with a capacitor bypass in a first embodiment
  • FIG. 6 shows a working fluid cooling circuit with a condenser bypass in a second embodiment
  • FIG. 8 shows a working fluid cooling circuit with a radiator bypass in one
  • FIG. 1 shows a waste heat recovery system 3, which at a
  • Internal combustion engine 1 is installed with a cooling system 2.
  • Internal combustion engine 1 further comprises a fresh gas line 4 and a
  • Exhaust pipe 5 on. About the fresh gas line 4 of the internal combustion engine 1 combustion air is supplied, which is in the embodiment of the compressor 6 of an exhaust gas turbocharger 7, which in turn is driven by a switched-on in the exhaust pipe 5 turbine 8, is compressed.
  • the compressor 6, a charge air cooler 9 and a throttle valve 10 are connected downstream.
  • Internal combustion engine 1 is installed, is driven. About the exhaust pipe 5, the burned in the combustion chambers of the internal combustion engine 1 mixture of fuel and fresh gas as hot exhaust gas is finally discharged into the environment.
  • the exhaust pipe 5 is connected to the fresh gas line 4 via a
  • Exhaust gas recirculation line 13 with a switched exhaust gas recirculation cooler 14 and an exhaust gas recirculation valve 15 is connected. Via the exhaust gas recirculation line 13 controlled exhaust gas is recycled into the fresh gas line 4 in particular to reduce the harmful exhaust emissions.
  • an exhaust aftertreatment device 16 Downstream of the turbine 8 is an exhaust aftertreatment device 16, which has, for example, a soot filter and / or catalyst turned on.
  • Exhaust after-treatment device 16 is also provided to reduce harmful exhaust emissions. Further downstream is in the exhaust pipe 5, a heat exchanger in the form of a superheater 17 of the
  • Exhaust line bypass 18 controlled bypassed.
  • the superheater 17 is incorporated in a working fluid circuit 19 of the waste heat recovery system 3, as explained in more detail below.
  • the internal combustion engine 1 further comprises the cooling system 2 with a
  • Coolant circuit 20 on.
  • the cooling system 2 is used to cool the
  • Internal combustion engine 1 and has a built-in coolant circuit 20 coolant radiator 21 and a coolant pump 22.
  • the coolant pump 22 conveys the coolant through cooling chambers of the internal combustion engine 1 into the coolant cooler 21, which is connected on the output side to the suction side of the coolant pump 22.
  • the coolant cooler 21 is via one of a
  • Coolant bypass valve 23 controlled coolant bypass 24 bypass.
  • the passage through the coolant bypass 24 is switched in particular for cold coolant and cold internal combustion engine 1 for quickly reaching the operating temperature of the coolant and the internal combustion engine 1.
  • a lubricating oil heat exchanger 25 and a retarder heat exchanger 26 are still involved.
  • Lubricating oil heat exchanger 25 is cooled by a lubricating oil circuit 27 circulating lubricating oil of the internal combustion engine 1, while in the retarder heat exchanger 26 circulating through a retarder 28
  • the retarder 28 is for example connected to the output shaft 11 and active in the braking operation of the vehicle.
  • the lubricating oil heat exchanger 25 and the retarder heat exchanger 26 may be turned on as shown in the coolant circuit 20 or in another constellation.
  • the intercooler 9 and the exhaust gas recirculation cooler 14 is suitably incorporated into the coolant circuit 20.
  • this has the working fluid circuit 19 with the superheater 17 switched into the exhaust gas line 5. Furthermore, in the working fluid circuit 19, an expansion machine 29 is turned on, which is driven by the same in the superheater 17 transferred to the gaseous state working fluid under expansion and output power to the internal combustion engine 1 or other machine, such as a generator. In this case, the expansion machine 29 can be bypassed via a controlled working fluid bypass 30. Further, downstream of the expansion machine 29 in the working fluid circuit 19, a condenser 31 is turned on, in which the working fluid is normally cooled back to the liquid state and then a working fluid pump 32 is supplied. The working fluid pump 32 is, for example, electrically driven and promotes the recooled working fluid back to the
  • Pressure equalization tank 33 in the working fluid circuit 19 is turned on.
  • the aforementioned capacitor 31 is itself part of a
  • Working fluid cooling circuit 34 which further comprises a cooler 35.
  • the cooler 35 is arranged, for example, in front of or behind the coolant radiator 21 and is cooled by a flow of cooling air, for example from one of the
  • Internal combustion engine 1 directly or indirectly driven fan 36 flows through.
  • An essential aspect of the invention is that the
  • Working fluid cooling circuit 34 is connected to the coolant circuit 20 and the working fluid cooling circuit 34 and the coolant circuit 20 having a common coolant pump 22 for the common coolant. As a result, a separate cooling pump for the working fluid cooling circuit 34 is saved.
  • the various possibilities of interconnecting the coolant circuit 20 and the working fluid cooling circuit 34 will be explained in detail in the following. For controlling the internal combustion engine 1 and the previously described
  • an electronic control device 37 is present, the entire system, for example, according to specifications of a vehicle driver and state variables of the overall system, such as temperature readings
  • the working fluid cooling circuit 34 is connected to the coolant circuit 20 on the suction side of the coolant pump 22 on the output side of the condenser 34 via a connection 48a.
  • the working fluid cooling circuit 34 is also connected to the coolant circuit 20 via a connection 48b, wherein the conveyor side of the coolant pump 22 and the connection 48b in a supply line 49 to the radiator 35, a valve 38 is switched into the working fluid cooling circuit 34.
  • the connection 48b the common coolant of the working fluid cooling circuit 34 and the coolant circuit 20 is at a comparable temperature level.
  • the valve 38 is opened, a defined amount of coolant is conveyed from the coolant pump 22 into the coolant circuit 20 and the working fluid cooling circuit 34. Increasing closure of the valve 38 reduces the amount of coolant circulating through the working fluid cooling circuit 34 to a full stop.
  • Coolant circuit 20 and the working fluid circuit 34 with respect to the common coolant pump 22 connected in parallel.
  • Coolant circuit 20 is connected, but here in the supply line 49 to the radiator 35, no valve 38 is present. Instead, a 3-way valve 39 designed as a thermostat is arranged in the working fluid cooling circuit 34 before the suction-side connection 48a, its preferably third connection via a connecting line 40 to the supply line 49 to the radiator 35th is connected downstream of the conveyor-side connection 48a.
  • a 3-way valve 39 designed as a thermostat is arranged in the working fluid cooling circuit 34 before the suction-side connection 48a, its preferably third connection via a connecting line 40 to the supply line 49 to the radiator 35th is connected downstream of the conveyor-side connection 48a.
  • Connecting line 40 is an opening in the direction of the radiator 35
  • Coolant circuit 20 are shut off and it flows in the result no
  • the working fluid cooling circuit 34 is again connected to the coolant circuit 20 via connections 48a, 48b, as described above, and the 3-way valve 39 is arranged here in the supply line 49 in front of the cooler 35.
  • Coolant pump 22 connected. Depending on the position of the 3-way valve 39 is coolant through the radiator 35 (according to arrow 1) or through the
  • Connecting line 40 (arrow 2) promoted back to the suction side of the coolant pump 22.
  • the volume flow of the coolant removed via the connection 48b is almost the same for all positions of the 3-way valve 39.
  • the output side of the capacitor 31 in the line leading to the connecting line 40 or connection 48 a is the output side of the capacitor 31 in the line leading to the connecting line 40 or connection 48 a
  • the check valve 41 is arranged.
  • the 3-way valve 39 may be a complex valve in the embodiments of Figures 2 and 3 or consist of several valves. While in the embodiments of Figures 1 to 3 of
  • Working fluid cooling circuit 34 and the coolant circuit 20 with respect to the coolant pump 22 are connected in parallel to each other, they are connected in series in the embodiment of Figure 4 to each other.
  • the coolant pump 22 conveys coolant through the internal combustion engine 1 and then through the coolant cooler 21 or the coolant bypass 24. Subsequently, a the connection 48b to the working fluid cooling circuit 34 in front of the cooler 35 via a connection line 42.
  • the connection line 42 arranged in the working fluid cooling circuit 34 valve 38 By the downstream of the junction of the connection line 42 arranged in the working fluid cooling circuit 34 valve 38, the mass flow or volume flow of the coolant is adjusted by the working fluid cooling circuit 34.
  • connection 48a is downstream of a suction connection line 43 which connects the working fluid cooling circuit 34 to the coolant pump 22 on the suction side .
  • a check valve 41 is arranged. Otherwise, the illustrated corresponds
  • Capacitor bypass control valve 45 controlled capacitor bypass 44 to the capacitor 31 has.
  • the condenser bypass control valve 45 can be controlled both actively via, for example, the control device 37 or passively in the form of a thermostat.
  • the condenser bypass control valve 45 may be installed in the working fluid cooling circuit 34 both downstream and upstream of the condenser 31. Basically, any combination of valve types (passive or active) and any mounting position
  • Capacitor bypass 44 is also independent of a parallel or serial circuit of the working fluid cooling circuit 34 and the coolant circuit 20 with respect to the coolant pump 22.
  • condenser bypass 44 There is a decoupling of the volume flow in the cooler 35 and in the condenser 31, whereby a more flexible and simultaneously
  • Working fluid cooling circuit 34 is possible. Thus, a simpler needs-based cooling surface enlargement of the coolant radiator 21 is possible. This brings with it the advantage that, by displacing cooling demand from the coolant circuit 20 into the working fluid cooling circuit 34, commissioning of the fan 36 can be avoided or delayed. Thus, it is possible, for example, to completely use all the cooling capacities for the vehicle cooling, ie for the coolant circuit 20, by completely bypassing the capacitor 31.
  • Free cooling capacities in the working fluid cooling circuit 34 can be used for the coolant circuit 20 without the volume flow in the condenser 31 or possible pressure losses rising. This has the advantage that despite qualification of the working fluid cooling circuit 34 for the coolant circuit 20 no separate interpretation of
  • Capacitor 31 is necessary for example for higher volume flows.
  • FIGS. 7 and 8 show different embodiments of the invention
  • Working fluid cooling circuit 34 arise. These pressures in turn mean high demands on the components and the capacity. In addition, at low pressures in the working fluid cooling circuit 34, heat in the condenser 31 is very difficult to remove. A countermeasure would be to greatly reduce the mass flow in the working fluid cooling circuit 34 or the additional cooling pump. However, such a measure is not sufficient at very low coolant temperatures in the working fluid cooling circuit 34, which is why "bypassing" of the cooler 35 via the cooler bypass 46 is advantageous Training as a thermostat to be controlled
  • Radiator bypass control valve 47 may be incorporated into the working fluid cooling circuit 34 both downstream and upstream of radiator 35. each Combination of types of the cooler bypass control valve 47 (passive or active) and each installation location (downstream, upstream of the radiator 35) is possible.
  • the coolant volume flow and the coolant temperature can be controlled independently of each other by, for example, the rotational speed of an optional separate cooling pump for the working fluid cooling circuit 34 or the Zumischgrad when combined with the coolant circuit 20th
  • the heating phase of the working fluid cooling circuit 34 can be shortened.
  • the system becomes more independent of lower ambient temperatures and prevention of the occurrence of negative pressure is possible as well as the sensitivity to the filling amount of the working fluid cooling circuit 34 is lower.
  • Coolant circuit 20 is the prerequisite for a faster

Abstract

L'invention concerne un système de récupération de chaleur perdue (3) comprenant un circuit de fluide de travail (19) qui coopère avec un échangeur de chaleur inséré dans un circuit de fluide de refroidissement (20) d'un moteur à combustion interne (1), le moteur à combustion interne (1) étant équipé d'un système de refroidissement (2) comprenant le circuit de fluide de refroidissement (20) et au moins une pompe à fluide de refroidissement (22), et un radiateur à fluide de refroidissement (21). Selon l'invention, le couplage entre un système de récupération de chaleur perdue (3) et le système de refroidissement (2) du moteur à combustion interne est amélioré grâce à l'optimisation des composants. Et cela grâce au fait que l'échangeur de chaleur est un radiateur (35), qui est relié à un condenseur (31) inséré dans le circuit de fluide de travail (19) par l'intermédiaire d'un circuit de refroidissement de fluide de travail (34) du système de récupération de chaleur perdue (3), et que le circuit de refroidissement de fluide de travail (34) est relié au circuit de fluide de refroidissement (20). Le circuit de refroidissement de fluide de travail (34) et le circuit de fluide de refroidissement (20) présentent une pompe à fluide de refroidissement commune (20).
PCT/EP2017/071114 2016-09-16 2017-08-22 Système de récupération de chaleur perdue WO2018050408A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016217731.1 2016-09-16
DE102016217731.1A DE102016217731A1 (de) 2016-09-16 2016-09-16 Abwärmerückgewinnungssystem

Publications (1)

Publication Number Publication Date
WO2018050408A1 true WO2018050408A1 (fr) 2018-03-22

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Application Number Title Priority Date Filing Date
PCT/EP2017/071114 WO2018050408A1 (fr) 2016-09-16 2017-08-22 Système de récupération de chaleur perdue

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DE (1) DE102016217731A1 (fr)
WO (1) WO2018050408A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11352911B2 (en) * 2018-02-27 2022-06-07 Orcan Energy Ag Drive having an integrated ORC

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT507096A4 (de) * 2008-12-10 2010-02-15 Man Nutzfahrzeuge Oesterreich Antriebseinheit mit kühlkreislauf und separatem wärmerückgewinnungskreislauf
WO2012115572A1 (fr) * 2011-02-25 2012-08-30 Scania Cv Ab Système pour convertir l'énergie thermique en énergie mécanique dans un véhicule
DE102013205648A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
DE102014019684A1 (de) 2014-12-23 2015-06-25 Daimler Ag Anordnung zur Umwandlung thermischer Energie aus Verlustwärme einer Verbrennungskraftmaschine
EP3064734A1 (fr) * 2013-10-30 2016-09-07 Isuzu Motors Limited Système de refroidissement de moteur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT507096A4 (de) * 2008-12-10 2010-02-15 Man Nutzfahrzeuge Oesterreich Antriebseinheit mit kühlkreislauf und separatem wärmerückgewinnungskreislauf
WO2012115572A1 (fr) * 2011-02-25 2012-08-30 Scania Cv Ab Système pour convertir l'énergie thermique en énergie mécanique dans un véhicule
DE102013205648A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
EP3064734A1 (fr) * 2013-10-30 2016-09-07 Isuzu Motors Limited Système de refroidissement de moteur
DE102014019684A1 (de) 2014-12-23 2015-06-25 Daimler Ag Anordnung zur Umwandlung thermischer Energie aus Verlustwärme einer Verbrennungskraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11352911B2 (en) * 2018-02-27 2022-06-07 Orcan Energy Ag Drive having an integrated ORC

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