SE543339C2 - Waste Heat Recovery System, Powertrain, and Vehicle - Google Patents

Waste Heat Recovery System, Powertrain, and Vehicle

Info

Publication number
SE543339C2
SE543339C2 SE1950451A SE1950451A SE543339C2 SE 543339 C2 SE543339 C2 SE 543339C2 SE 1950451 A SE1950451 A SE 1950451A SE 1950451 A SE1950451 A SE 1950451A SE 543339 C2 SE543339 C2 SE 543339C2
Authority
SE
Sweden
Prior art keywords
evaporator
working media
power source
condenser
heat
Prior art date
Application number
SE1950451A
Other languages
Swedish (sv)
Other versions
SE1950451A1 (en
Inventor
Ola Hall
Zoltan Kardos
Original Assignee
Scania Cv Ab
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 Scania Cv Ab filed Critical Scania Cv Ab
Priority to SE1950451A priority Critical patent/SE543339C2/en
Priority to DE102020001350.3A priority patent/DE102020001350B4/en
Publication of SE1950451A1 publication Critical patent/SE1950451A1/en
Publication of SE543339C2 publication Critical patent/SE543339C2/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • 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
    • 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
    • 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
    • F01K23/12—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
    • F01K23/14—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled including at least one combustion engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/22—Liquid cooling characterised by evaporation and condensation of coolant in closed cycles; characterised by the coolant reaching higher temperatures than normal atmospheric boiling-point
    • F01P3/2285—Closed cycles with condenser and feed pump
    • 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
    • F01P9/00—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00
    • F01P9/06—Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00 by use of refrigerating apparatus, e.g. of compressor or absorber type
    • 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
    • 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
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/182—Arrangements or mounting of liquid-to-air heat-exchangers with multiple heat-exchangers
    • 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
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/16—Outlet manifold
    • 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
    • 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

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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

A waste heat recovery system (1) for a vehicle (3) is disclosed, wherein the vehicle (3) comprises a power source (5) configured to provide motive power to the vehicle (3) and a power source radiator (7) configured to cool the power source (5). The system (1) comprises a first evaporator (11) configured to collect heat generated by the power source (5), a first expander (13) configured to provide useful work from heat collected by the first evaporator (11), a second evaporator (21), and a second expander (23) configured to provide useful work from heat collected by the second evaporator (21). The second evaporator (21) is configured to collect heat dissipated from the power source radiator (7). The present disclosure further relates to a powertrain (60) for a vehicle (3) as well as a vehicle (3) comprising a power train (60).

Description

1 Waste Heat Recovery System, Powertrain, and Vehicle TECHNICAL FIELDThe present disclosure relates to a waste heat recovery system for a vehicle. The presentdisclosure further relates to a powertrain for a vehicle and a vehicle comprising a powertrain.
BACKGROUND Some vehicles are equipped with a waste heat recovery system utilizing waste heat of thepower source of the vehicle for generating useful work. A waste heat recovery systemusually comprises an evaporator arranged to evaporate working media using waste heat andan expander arranged to provide useful work from evaporated working media. Moreover, awaste heat recovery system usually comprises a condenser arranged downstream of theexpander arranged to condense the working media before the working media is pumped tothe evaporator. ln order to condense the working media, the condenser must be cooled.
The expander may be connected to a driving shaft of the vehicle to provide the useful work inthe form of a driving torque to the driving shaft or may be arranged to power another device.ln this manner, the total energy efficiency of the vehicle is improved.
Waste heat recovery systems provide several advantages regarding the energy efficiency ofvehicles, but many challenges exist when it comes to converting waste heat into useful workin vehicles without significantly adding weight, cost, and complexity to the vehicle. Theefficiency of a waste heat recovery system partly depends on the temperature differencebetween the evaporator and the condenser. That is, if the evaporator can collect a largeamount of heat at a higher temperature level, the efficiency of the waste heat recoverysystem can be improved. Likewise, if the condenser can be efficiently cooled to a lowertemperature level, the efficiency of the waste heat recovery system can be improved. l\/lodern vehicles usually comprise numerous components and systems which generateexcess heat. However, the temperature level of the heat is usually insufficient for motivatinga separate waste heat recovery system converting the excess heat into useful work.Moreover, as is the case with numerous other types of systems, a waste heat recoverysystem has a narrow operational range in which it operates most efficiently.
Furthermore, generally, on today's consumer market, it is an advantage if products, such asvehicle systems and their associated components, have conditions and/or characteristicssuitable for being manufactured and assembled in a cost-efficient manner.
SUMMARYlt is an object of the present invention to overcome, or at least alleviate, at least some of theabove-mentioned problems and drawbacks.
According to a first aspect of the invention, the object is achieved by a waste heat recoverysystem for a vehicle, wherein the vehicle comprises a power source configured to providemotive power to the vehicle and a power source radiator configured to cool the powersource. The waste heat recovery system comprises a first evaporator configured to collectheat generated by the power source, a first expander configured to provide useful work fromheat collected by the first evaporator, a second evaporator, and a second expanderconfigured to provide useful work from heat collected by the second evaporator. The secondevaporator is configured to collect heat dissipated from the power source radiator.
Since the second evaporator is configured to collect heat dissipated from the power sourceradiator, the heat dissipated from the power source radiator can be converted into useful work by the second expander in an efficient manner.
Moreover, since the system comprises the first expander configured to provide useful workfrom heat collected by the first evaporator and the second expander configured to provideuseful work from heat collected by the second evaporator, the first and second expanderscan easily be designed to operate at an optimum operational range given the temperaturelevel and the level of heat collected by the respective first and second evaporator.Accordingly, in this manner, the relatively small amount of heat dissipated from the powersource radiator can be converted into useful work in an efficient manner by the secondexpander. Thus, conditions are provided for a more efficient conversion of heat into usefulwork and the total energy efficiency of a vehicle comprising the system can be improved.
Accordingly, a waste heat recovery system is provided overcoming, or at least alleviating, atleast some of the above-mentioned problems and drawbacks. As a result, the above-mentioned object is achieved.
Optionally, the power source radiator is configured to be subjected to an airflow having an airflow direction, and wherein the second evaporator is arranged downstream of the powersource radiator seen in the air flow direction. Thereby, the second evaporator can collectheat dissipated from the power source radiator in a simple and efficient mannercircumventing the need for further heat transferring devices or systems for transferring heat 3 from the power source radiator to the second evaporator. Thus, as a result thereof, a low-weight, a low-cost, and a non-complex solution is provided for collecting heat dissipated fromthe power source radiator.
Optionally, the power source comprises a combustion engine, and wherein the firstevaporator is configured to collect heat from exhaust gasses of the combustion engine.Thereby, a waste heat recovery system is provided in which the first expander can provideuseful work from heat collected from a source having a high amount of heat.
Optionally, the power source comprises a charge air cooler, and wherein the secondevaporator is configured to collect heat dissipated from the charge air cooler. Thereby, therelatively small amount of heat dissipated from the charge air cooler can be converted into useful work by the second expander in an efficient manner.
Optionally, the second evaporator is arranged downstream of the charge air cooler seen inthe air flow direction. Thereby, a low-weight, a low-cost, and a non-complex solution isprovided for collecting heat dissipated from the charge air cooler.
Optionally, the system comprises a first working media circuit and a second working mediacircuit, wherein the first evaporator and the first expander are arranged in the first workingmedia circuit, and the second evaporator and the second expander are arranged in thesecond working media circuit, and wherein the second working media circuit comprisesworking media having different properties than the working media of the first working mediacircuit. Thereby, a waste heat recovery system is provided having a more efficient conversionof heat from several heat sources into useful work. This because the first working mediacircuit can convert heat from a source having a higher temperature level, and the secondworking media circuit can convert heat from one or more sources having a lower temperaturelevel in an efficient manner, where the respective first and second working media circuiteasily can be optimized regarding the temperature level and amount of heat collected by therespective first and second evaporator.
Thus, due to these features, conditions are provided for a further efficient conversion of heatinto useful work and a further improved total energy efficiency of a vehicle comprising thewaste heat recovery system.
Optionally, the system comprises a first condenser configured to condense working mediaevaporated by the first evaporator, and wherein the first condenser is configured to heat the 4 second evaporator. Thereby, conditions are provided for a further efficient conversion of heatinto useful work and a further improved total energy efficiency of a vehicle comprising thewaste heat recovery system. This because the first condenser is configured to heat thesecond evaporator and as a result thereof, the heat of the first condenser can be convertedinto useful work by the second expander. |\/|oreover, a waste heat recovery system isprovided having conditions and characteristics suitable for being manufactured andassembled in a cost-efficient manner. This because the need for a further arrangementcooling the first condenser is circumvented.
Optionally, the system comprises a second condenser configured to condense workingmedia evaporated by the second evaporator, and wherein the second condenser isconfigured to be cooled by the power source radiator. Thereby, a simple and efficient coolingis provided of the second condenser.
Optionally, the system comprises an auxiliary radiator connected to an outlet of the powersource radiator, and wherein the second condenser is configured to be cooled by theauxiliary radiator. Thereby, the second condenser can be cooled to a lower temperature levelwith increased cooling efficiency. As a result thereof, conditions are provided for a furtherefficient conversion of heat into useful work and a further improved total energy efficiency ofa vehicle comprising the waste heat recovery system.
Optionally, the second evaporator and the first condenser are provided in one heatexchanger unit. Thereby, an efficient heat transfer between the first condenser and thesecond evaporator is provided. Moreover, a low-weight, a low-cost, and a non-complexsolution is provided for transferring heat between the first condenser and the second evaporator.
Optionally, the heat exchanger unit comprises coo|ant channels of the first condenser andcoo|ant channels of the second evaporator, and wherein the coo|ant channels of the firstcondenser are arranged in heat exchanging contact with the coo|ant channels of the secondevaporator. Thereby, an efficient heat transfer between the first condenser and the second evaporator is provided in a simple and efficient manner.
Optionally, the heat exchanger unit comprises coo|ant channel pairs each comprising onecoo|ant channel of the first condenser and one coo|ant channel of the second evaporator.Thereby, an efficient heat transfer between the first condenser and the second evaporator is provided in a simple and efficient manner.
Optionally, the heat exchanger unit comprises air passages between the coolant channelpairs. Thereby, air can flow through the heat exchanger unit via the air passages and provideheat to the second evaporator coliected at the power source radiator to further heat thesecond evaporator in addition to the heat transferred via the coolant channel pairs.l\/loreover, the air flowing through the air passages can provide supplementary cooling of thefirst condenser in addition to the cooling provided via the coolant channel pairs. ln thismanner, the energy efficiency of the waste heat recovery system can be further improved.
Optionally, the heat exchanger unit comprises coolant channels shared by first condenserand the second evaporator. Since the heat exchanger unit comprises coolant channelsshared by the first condenser and the second evaporator, a further efficient heat transferbetween the first condenser and the second evaporator is provided. This because workingmedia of the first condenser and the second evaporator will be mixed in the coolant channelsof the heat exchanger unit. Moreover, a low-weight, a low-cost, and a non-complex solutionis provided for transferring heat between the first condenser and the second evaporator.
Optionally, the system comprises a second condenser configured to condense workingmedia expanded by the second expander, and wherein the system comprises a mixing unitarranged upstream of the coolant channels, wherein the mixing unit is configured to mixworking media from the second condenser with working media from the first expander.Thereby, an efficient heat transfer is provided between working media from the first expanderand working media from the second condenser. This because a further mixing of the workingmedia is provided before the working media is entering the coolant channels.
Optionally, the mixing unit is an inlet tank comprised in the heat exchanger unit. Thereby, alow-cost and a non-complex solution is provided for further improving heat transfer betweenworking media from the first expander and working media from the second condenser.
Optionally, the system comprises a first working media pump configured to pump workingmedia to the first evaporator, and a separation device configured to receive working mediafrom the coolant channels, wherein the separation device comprises a first outlet connectedto the first working media pump and a second outlet connected to the second expander, andwherein the separation device is configured to separate working media in liquid phase to thefirst outlet and is configured to separate working media in gaseous phase to the secondoutlet. Thereby, the first working media pump is supplied with working media in liquid stateand the second expander is provided with working media in gaseous state. As a result 6 thereof, the first working media pump can pump working media to the first evaporator in anefficient manner and the second expander can provide useful work from the gaseous working media.
Optionaily, the separation device is a separation tank comprised in the heat exchanger unit.Thereby, a low-cost and a non-complex solution is provided for separating working media ingaseous phase from working media in liquid state.
Optionaily, the system comprises a sub-cooling pass between the first out|et and the firstworking media pump. Thereby, condensation of working media is further ensured andcavitation of working media in the first working media pump is further avoided.
Optionaily, the heat exchanger unit comprises the sub-cooling pass. Thereby, a low-cost anda non-complex solution is provided for ensuring condensation of working media and avoiding cavitation of working media in the first working media pump.
Optionaily, the vehicle comprises an air intake for conducting ambient air to power sourceradiator, and wherein the system comprises a cover arrangement controllable between anopen position, in which the cover arrangement allows flow of air through the air intake, and aclosed position in which the cover arrangement at least partially blocks flow of air through theair intake. Thereby, a waste heat recovery system is provided in which the temperature levelof the power source radiator and of the second evaporator, as well as the heat transfer fromthe power source radiator to the second evaporator, can be controlled simply by controllingthe position of the cover arrangement. ln this manner, conditions are provided for a moreefficient conversion of heat into useful work and the total energy efficiency of a vehiclecomprising the system can be improved.
According to a second aspect of the invention, the object is achieved by a powertrain for avehicle, wherein the powertrain comprises a power source configured to provide motivepower to the vehicle, a power source radiator configured to cool the power source, and awaste heat recovery system according to some embodiments of the present disclosure.
Since the powertrain comprises a waste heat recovery system according to someembodiments of the present disclosure, a powertrain is provided capable of achieving a moreefficient conversion of heat into useful work. As a result thereof, the total energy efficiency ofa vehicle comprising the powertrain can be improved. 7 Accordingly, a powertrain is provided overcoming, or at least alleviating, at least some of theabove-mentioned problems and drawbacks. As a result, the above-mentioned object isachieved.
According to a third aspect of the invention, the object is achieved by a vehicle comprising apower according to some embodiments of the present disclosure.
Since the vehicle comprises a powertrain according to some embodiments of the presentdisclosure, a vehicle is provided in which heat can be converted into useful work in a moreefficient manner. As a result thereof, a vehicle is provided having conditions for an improvedenergy efficiency.
Accordingly, a vehicle is provided overcoming, or at least alleviating, at least some of theabove-mentioned problems and drawbacks. As a result, the above-mentioned object isachieved.
Further features of, and advantages with, the present invention will become apparent whenstudying the appended claims and the following detailed description.
BRIEF DESCRIPTION OF THE DRAWINGS Various aspects of the invention, including its particular features and advantages, will bereadily understood from the example embodiments discussed in the following detaileddescription and the accompanying drawings, in which: Fig. 1 illustrates a powertrain according to some embodiments, Fig. 2 illustrates a powertrain according to some further embodiments, Fig. 3 illustrates a portion of a heat exchanger unit illustrated in Fig. 2 Fig. 4 illustrates a powertrain according to some further embodiments, Fig. 5 illustrates a heat exchanger unit according to embodiments illustrated in Fig. 4, andFig. 6 illustrates a vehicle according to some embodiments.
DETAILED DESCRIPTION Aspects of the present invention will now be described more fully. Like numbers refer to likeelements throughout. Well-known functions or constructions will not necessarily be describedin detail for brevity and/or clarity. 8 Fig. 1 illustrates a powertrain 60 according to some embodiments. The powertrain 60comprises a power source 5 configured to provide motive power to a vehicle comprising thepowertrain 60. According to the illustrated embodiments, the power source 5 comprises acombustion engine 5. The combustion engine 5 may be an internal combustion engine suchas for example a compression ignition engine, such as a diesel engine, or an Otto enginewith a spark-ignition device, wherein the Otto engine may be configured to run on gas, petrol,alcohol, similar fuels, or combinations thereof. According to further embodiments of thepresent disclosure, the power source 5, as referred to herein, may comprise another type ofpower source 5, such as an electric propulsion system, a fuel cell, or the like.
The powertrain 60 further comprises a power source radiator 7 configured to cool the powersource 5. Moreover, the powertrain 60 comprises a waste heat recovery system 1 accordingto some embodiments. The waste heat recovery system 1 is in some places herein referredto as “the system 1” for the reason of brevity and clarity. The waste heat recovery system 1comprises a first evaporator 11 configured to collect heat generated by the power source 5.According to the illustrated embodiments, the first evaporator 11 is configured to collect heatfrom exhaust gasses of the combustion engine 5. Thus, according to the illustratedembodiments, the first evaporator 11 comprises a heat exchanger arranged in an exhaustduct of the combustion engine 5. The exhaust duct is not illustrated in Fig. 1 for the reason ofbrevity and clarity.
The waste heat recovery system 1 further comprises a first expander 13 configured toprovide useful work from heat collected by the first evaporator 11. Moreover, the waste heatrecovery system 1 comprises a second evaporator 21 and a second expander 23 configuredto provide useful work from heat collected by the second evaporator 21. The secondevaporator 21 is configured to collect heat dissipated from the power source radiator 7.Thereby, conditions are provided for a more efficient conversion of heat into useful work.This because the waste heat recovery system 1 comprises two expanders 13, 23 eachconfigured to provide useful work from heat collected by a respective evaporator 11, 21operating at different temperature levels. Accordingly, the expanders 13, 23 can easily bedesigned to operate at an optimum power output given the level of heat collected by therespective evaporator 11, 21. ln this manner, the relatively small amount of heat dissipatedfrom the power source radiator 7 can be converted into useful work by the second expander 23 in an efficient manner.
The power source radiator 7 is configured to be subjected to an airflow having an air flowdirection d. According to the illustrated embodiments, the second evaporator 21 is arranged 9 downstream of the power source radiator 7 seen in the air flow direction d. Thereby, thesecond evaporator 21 can collect heat dissipated from the power source radiator 7 in asimple and efficient manner circumventing the need for further heat transferring devices orsystems for transferring heat from the power source radiator 7 to the second evaporator 21.The air flow direction d may be opposite to a heading direction of vehicle comprising thewaste heat recovery system 1 when the vehicle is travelling in a forward direction. Moreover,according to the i||ustrated embodiments, the waste heat recovery system 1 comprises a fan30 configured to selectively generate an airflow in the air flow direction d. The fan 30 may forexample be used during low speed or stand still of a vehicle comprising the waste heatrecovery system 1 when the velocity of the vehicle is insufficient for generating an airflow inthe air flow direction d. As an alternative, or in addition, fan 30 may for example be used if acooling demand of the power source radiator 7 exceeds a threshold level.
According to the i||ustrated embodiments, the power source 5 comprises a charge air cooler25. Thus, according to the i||ustrated embodiments, the power source 5 is a superchargedcombustion engine 5 comprising the charge air cooler 25. The second evaporator 21 isconfigured to collect heat dissipated from the charge air cooler 25. Thereby, the relativelysmall amount of heat dissipated from the charge air cooler 25 can be converted into usefulwork by the second expander 23 in an efficient manner. According to the i||ustratedembodiments, the second evaporator 21 is arranged downstream of the charge air cooler 25seen in the air flow direction d. Thereby, a low-weight, a low-cost, and a non-complexsolution is provided for collecting heat dissipated from the charge air cooler 25. As can beseen in Fig. 1, according to the i||ustrated embodiments, the charge air cooler 25 is arrangedin front of the power source radiator 7 seen in the air flow direction d. ln this manner, it isensured that compressed gas, compressed by a charging device of the power source 5, isefficiently cooled while the heat of the compressed gas can be converted into useful work bythe second expander 23. ln this manner, the total energy efficiency of the powertrain 60 canbe improved.
According to the i||ustrated embodiments, the system 1 comprises a first working mediacircuit 51 and a second working media circuit 52. The first evaporator 11 and the firstexpander 13 are arranged in the first working media circuit 51. The first working media circuit51 further comprises a first condenser 31 configured to condense working media evaporatedby the first evaporator 11. Moreover, the first working media circuit 51 comprises a firstworking media pump 17 configured to pump working media through the first working mediacircuit 51 in a direction from the first expander 13 to the first evaporator 11. ln the first evaporator 11, the working media is heated to a temperature in which the workingmedia evaporates from liquid phase into gaseous phase. The gaseous working media istransferred to the first expander 13. ln the first expander 13, the temperature and thepressure of the working media is partially converted into useful work. According to theillustrated embodiments, a rotor of the first expander 13 is mechanically connected to a shaftof the power source 5, via a transmission 47. According to further embodiments, the firstexpander 13 may provide useful work in another manner, such as for example by driving analternator producing electricity, or by powering a second device or system.
The working media of the first working media circuit 51 flows out from the first expander 13and into the first condenser 31. ln the first condenser 31, the temperature of the workingmedia is further reduced, and gaseous working media is condensed back into liquid phase.From the first condenser 31, the working media is pumped to the first evaporator 11 by thefirst working media pump 17. Furthermore, the first working media circuit 51 comprises a firstexpansion tank 57 acting as a reservoir holding working media and acting as a pressurereservoir for the working media in the first working media circuit 51, which can facilitatecondensation of working media also in operational conditions where it is difficult to lower the temperature of the working media in a sufficient manner.
According to the illustrated embodiments, the second evaporator 21 and the secondexpander 23 are arranged in the second working media circuit 52. The second workingmedia circuit 52 further comprises a second condenser 32 configured to condense workingmedia evaporated by the second evaporator 21. I\/|oreover, the second working media circuit52 comprises a second working media pump 18 configured to pump working media throughthe second working media circuit 52 in a direction from the second expander 23 to thesecond evaporator 21. ln the second evaporator 21, the working media is heated to a temperature in which theworking media evaporates from liquid phase into gaseous phase. The gaseous workingmedia is transferred to the second expander 23. ln the second expander 23, the temperatureand the pressure of the working media is partially converted into useful work. According tothe illustrated embodiments, a rotor of the second expander 23 is also mechanicallyconnected to the shaft of the power source 5, via the transmission 47. Moreover, accordingto the illustrated embodiments, the waste heat recovery system 1 comprises a transmission49 between the rotor of the first expander 13 and the rotor of the second expander 23allowing different rotational speeds of the rotors of the first and second expanders 13, 23. lnthis manner, the total energy efficiency of the waste heat recovery system 1 can be further 11 improved, as is further explained herein. According to further embodiments, the secondexpander 23 may provide useful work in another manner, such as for example by driving an alternator producing electricity, or by powering a second device or system.
The working media of the second working media circuit 52 flows out from the secondexpander 23 and into the second condenser 32. ln the second condenser 32, thetemperature of the working media is further reduced, and gaseous working media iscondensed back into liquid phase. From the second condenser 32, the working media ispumped to the second evaporator 21 by the second working media pump 18. Furthermore,the second working media circuit 52 comprises a second expansion tank 59 acting as areservoir holding working media and acting as a pressure reservoir for the working media inthe second working media circuit 52, which can facilitate condensation of working media alsoin operational conditions where it is difficult to lower the temperature of the working media in a sufficient manner.
As understood from the herein described, in most operational conditions, the working mediaof the first working media circuit 51 will have a higher temperature than the working media ofthe second working media circuit 52. This because the first evaporator 11 is configured tocollect heat at a higher temperature level than the second evaporator 21. Thus, thecomponents of the first working media circuit 51 will, in most operational conditions, have ahigher temperature than the components of the second working media circuit 52. Therefore,“the first working media circuit 51”, “the first evaporator 11”, and “the first condenser 31”, asreferred to herein may also be referred to as ”the high temperature working media circuit 51”,“the high temperature evaporator 11”, and “the high temperature condenser 31”. Likewise,“the second working media circuit 52”, “the second evaporator 21 and “the secondcondenser 32”, as referred to herein may also be referred to as ”the low temperature workingmedia circuit 52”, “the low temperature evaporator 21 and “the low temperature condenser32”.
According to the illustrated embodiments, the second working media circuit 52 comprisesworking media having different properties, such as a lower boiling point, than the workingmedia of the first working media circuit 51. ln this manner, the efficiency of the respectiveworking media circuit 51, 52 can be increased, and heat can in a more efficient manner becollected by the respective first and second evaporator 11, 21, and thus also more efficientlybe converted into useful work by the respective first and second expander 13, 23. 12 According to the embodiments illustrated in Fig. 1, the second condenser 32 as well as thefirst condenser 31 are configured to be cooled by the power source radiator 7. That is,according to the illustrated embodiments, the powertrain 60 comprises a power sourcecoolant circuit 6 comprising the power source radiator 7, wherein the second condenser 32and the first condenser 31 are configured to be cooled by the power source coolant circuit 6.The power source coolant circuit 6 comprises coolant channels in the power source 5, acoolant pump 8 configured to pump coolant through the power source coolant circuit 6, and afirst valve 10 arranged to direct coolant to the power source radiator 7 or to a bypass line 12bypassing the power source radiator 7.
According to the illustrated embodiments, the waste heat recovery system 1 comprises anauxiliary radiator 35 connected to an outlet 7' of the power source radiator 7, wherein the firstand second condensers 31, 32 are configured to be cooled by the auxiliary radiator 35.Thereby, it is ensured that the first and second condensers 31, 32 can be efficiently cooledwhich provides conditions for an increased efficiency of the waste heat recovery system 1.According to the illustrated embodiments, the waste heat recovery system 1 comprises a fan33 configured to selectively generate an airflow through the auxiliary radiator 35. The fan 33may for example be used during stand still of a vehicle comprising the waste heat recoverysystem 1, and/or if a cooling demand of the auxiliary radiator 35 exceeds a threshold level.
As can be seen in Fig. 1, according to the illustrated embodiments, the power source coolantcircuit 6 comprises a second valve 14, which is a three-way valve comprising a first inletfluidly connected to the bypass line 12, a second inlet fluidly connected to the outlet 7' of thepower source radiator 7, and an outlet fluidly connected to the coolant pump 8. Due to thesecond valve 14, the flow of coolant to the first and second condensers 31, 32 can beregulated, and thus also the cooling thereof. As an alternative to the auxiliary radiator 35, thefirst and second condensers 31, 32 may be cooled directly via the power source radiator 7.
Fig. 2 illustrates a powertrain 60 according to some further embodiments. Moreover, thepowertrain 60 according to the embodiments illustrated in Fig. 2 comprises a waste heatrecovery system 1 according to some further embodiments. The powertrain 60 and the wasteheat recovery system 1 illustrated in Fig. 2 comprises the same features, functions, andadvantages as the powertrain 60 and the waste heat recovery system 1 according to theembodiments illustrated in Fig. 1 with some exceptions explained below.
According to the embodiments illustrated in Fig. 2, the first condenser 31 is configured toheat the second evaporator 21. Thus, in these embodiments, the first condenser 31 is in heat 13 exchanging contact with the second evaporator 21. Thereby, the heat dissipated from thefirst condenser 31, as a result of condensation of working media in the first condenser 31, istransferred to the second evaporator 21 so as to evaporate working media in the secondevaporator. As a result thereof, the energy efficiency of the waste heat recovery system 1 isfurther improved because the heat of the first condenser 31 can be converted into usefulwork in the second expander 23.
According to the embodiments i||ustrated in Fig. 2, the second condenser 32 is configured tobe cooled by the auxiliary radiator 35. As an alternative to the auxiliary radiator 35, thesecond condenser 32 may be cooled directly via the power source radiator 7.
According to the embodiments i||ustrated in Fig. 2, the second evaporator 21 and the firstcondenser 31 are provided in one heat exchanger unit 37. The heat exchanger unit 37comprises coo|ant channels 41 of the first condenser 31 and coo|ant channels 42 of thesecond evaporator 21. The coo|ant channels 41 of the first condenser 31 are arranged inheat exchanging contact with the coo|ant channels 42 of the second evaporator 21.
Fig. 3 illustrates a portion of the heat exchanger unit 37 i||ustrated in Fig. 2. Therefore, in thefollowing, simultaneous reference is made to Fig. 2 and Fig. 3. As can be seen in Fig. 3, theheat exchanger unit 37 comprises coo|ant channel pairs 39 each comprising one coo|antchannel 41 of the first condenser 31 and one coo|ant channel 42 of the second evaporator21. The coo|ant channels 41, 42 of the coo|ant channel pairs 39 are arranged in abuttingcontact to provide high thermal conductivity therebetween.
Moreover, the heat exchanger unit 37 comprises air passages 44 between the coo|antchannel pairs 39. ln this manner, air flowing in the flow direction d, indicated in Fig. 2, canflow through the heat exchanger unit 37 and provide heat to the second evaporator 21collected at the power source radiator 7 and at the charge air cooler 25 to further heat thesecond evaporator 21 in addition to the heat transferred via the coo|ant channel pairs 39.Moreover, the air flowing through the air passages 44 can provide supplementary cooling ofthe first condenser 31 in addition to the cooling provided via the coo|ant channel pairs 39. lnthis manner, the energy efficiency of the waste heat recovery system 1 is further improved.
Fig. 4 illustrates a powertrain 60 according to some further embodiments. Moreover, thepowertrain 60 according to the embodiments i||ustrated in Fig. 4 comprises a waste heatrecovery system 1 according to some further embodiments. The powertrain 60 and the wasteheat recovery system 1 i||ustrated in Fig. 4 comprises the same features, functions, and 14 advantages as the powertrain 60 and the waste heat recovery system 1 according to theembodiments illustrated in Fig. 1 with some exceptions explained below.
According to the embodiments illustrated in Fig. 4, the second evaporator 21 and the firstcondenser 31 are provided in one heat exchanger unit 37”. Moreover, the heat exchangerunit 37” comprises coolant channels 46 shared by the first condenser 31 and the secondevaporator 21. Thus, according to the embodiments illustrated in Fig. 4, the first condenser31 and the second evaporator 21 share the same coolant channels 46 in the heat exchangerunit 37”, meaning that the working media of the first condenser 31 and the second evaporator21 are mixed in the coolant channels 46 of the heat exchanger unit 37”. Thus, according tothe embodiments illustrated in Fig. 4, the working media of the first working media circuit 51and the second working media circuit 51 are mixed in the coolant channels 46 of the heatexchanger unit 37”.
Fig. 5 illustrates the heat exchanger unit 37” according to the embodiments illustrated in Fig.4. Therefore, below, simultaneous reference is made to Fig. 4 and Fig. 5. The waste heatrecovery system 1 comprises a mixing unit 48 arranged upstream of the coolant channels 46.According to the illustrated embodiments, the mixing unit 48 is an inlet tank 48 comprised inthe heat exchanger unit 37”. The mixing unit 48 is fluidly connected to the first working mediacircuit 51 and to the second working media circuit 52. The mixing unit 48 is configured toreceive working media from the first expander 13 and working media from the secondcondenser 32, wherein the mixing unit 48 is configured to mix the working media from thesecond condenser 32 with the working media from the first expander 13. Thereby, anefficient heat transfer is provided between working media from the first expander 13 andworking media from the second condenser 32.
The working media flows from the mixing device 48 into the coolant channels 46 of the heatexchanger unit 37”. When flowing through the coolant channels 46, the working mediatherein can receive heat, or be subjected to cooling, by air flowing through the heatexchanger unit 37” in the air flow direction d indicated in Fig. 4.
As indicated in Fig. 5, the waste heat recovery system 1 comprises a separation device 55configured to receive working media from the coolant channels 46. According to theillustrated embodiments, the separation device 55 is a separation tank 55 comprised in theheat exchanger unit 37”. The separation device 55 comprises a first outlet 61. As best seen in Fig. 4, the first outlet 61 is connected to the first working media pump 17. Moreover, asindicated in Fig. 4 and Fig. 5, the separation device 55 comprises a second outlet 62. As best seen in Fig. 4, the second outlet 62 is connected to the second expander 23. The separationdevice 55 is configured to separate working media in liquid phase to the first outlet 61 and isconfigured to separate working media in gaseous phase to the second outlet 62. Thereby,the first working media pump 17 is supplied with working media in liquid state and the secondexpander 23 is supplied with working media in gaseous state. As a result thereof, the firstworking media pump 17 can pump working media to the first evaporator 11 in an efficientmanner and the second expander 23 can provide useful work from the gaseous working media in an efficient manner.
According to the embodiments illustrated in Fig. 4 and Fig. 5, the waste heat recoverysystem 1 comprises a sub-cooling pass 65 between the first outlet 61 and the first workingmedia pump 17. According to the illustrated embodiments, the heat exchanger unit 37'comprises the sub-cooling pass 65. The sub-cooling pass 65 is configured to provide furthercooling of working media flowing from the first outlet 61 towards the first working media pump17. Thereby, condensation of working media is further ensured and cavitation of workingmedia in the first working media pump 17 is further avoided.
According to the embodiments illustrated in Fig. 4 and Fig. 5, the second working mediacircuit 52 comprises working media having different properties, such as a lower boiling point,than the working media of the first working media circuit 51. ln this manner, it can be ensuredthat working media of the first working media circuit 51 evaporates the working media of thesecond working media circuit 52 in the heat exchanger unit 37”. Likewise, it can be ensuredthat working media of the second working media circuit 52 condenses the working media ofthe first working media circuit 51 in the heat exchanger unit 37”.
According to the embodiments illustrated in Fig. 4 and 5, the second condenser 32 isconfigured to be cooled by the auxiliary radiator 35. As an alternative to the auxiliary radiator35, the second condenser 32 may be cooled directly via the power source radiator 7.
According to the embodiments illustrated in Fig. 1, Fig. 2, and Fig. 4, the powertrain 60comprises an air intake 71 for conducting ambient air to power source radiator 7. l\/loreover,the waste heat recovery system 1 comprises a cover arrangement 73 controllable betweenan open position, in which the cover arrangement 73 allows flow of air through the air intake71, and a closed position in which the cover arrangement 73 at least partially blocks flow ofair through the air intake 71. Thereby, a waste heat recovery system 1 is provided in whichthe temperature level of the power source radiator 7 and of the second evaporator 21, aswell as the heat transfer from the power source radiator 7 and the charge air cooler 25 to the 16 second evaporator 21, can be controlled simply by controlling the position of the coverarrangement 73. ln this manner, conditions are provided for a more efficient conversion ofheat into useful work and the total energy efficiency of a vehicle comprising the system 1 canbe improved. ln Fig. 1 and Fig. 3, the cover arrangement 73 is illustrated in the open position.ln Fig. 2, the cover arrangement 73 is illustrated in the closed position. Moreover, accordingto these embodiments, the powertrain 60 comprises a cover 75 enclosing heat transferringsurfaces of the charge air cooler 25, the power source radiator 7, the second evaporator 21,and/or the first condenser 3 in a manner such that all air flowing into the air intake 71 passesthrough the cover 75. Accordingly, the cover 75 acts as a barrier preventing air from flowingaround heat transferring surfaces of the charge air cooler 25, the power source radiator 7,the second evaporator 21, and/or the first condenser 3. Thereby, the heat transfer from thecharge air cooler 25 and the power source radiator 7 to the second evaporator 21 is increased.
According to the embodiments illustrated in Fig. 1, Fig. 2, and Fig. 4, the waste heat recoverysystem 1 may comprise a control arrangement configured to control the speed of the firstworking media pump 17 and of the second working media pump 18. Such a controlarrangement is not illustrated in Fig. 1, Fig. 2, and Fig. 4 for the reason of brevity and clarity.The control arrangement may be configured to control the speed of the first and secondworking media pumps 17, 18 based on available heat in the first evaporator 11, availableheat in the second evaporator 21, available cooling power of the first condenser 31, and/oravailable cooling power of the second condenser 32. Furthermore, the control arrangementmay be configured to control the first valve 10, the second valve 14, the cover arrangement73, and/or one or more of the fans 30, 33. ln this manner, the conversion of heat into usefulwork can be made in an efficient manner, wherein the power split between the first andsecond working media circuits 51, 52 can be regulated by regulating the speed of the firstand second working media pumps 17, 18.
The control arrangement, as referred to therein, may comprise a calculation unit which maytake the form of substantially any suitable type of processor circuit or microcomputer, e.g. acircuit for digital signal processing (digital signal processor, DSP), a Central Processing Unit(CPU), a processing unit, a processing circuit, a processor, an Application Specific IntegratedCircuit (ASIC), a microprocessor, or other processing logic that may interpret and executeinstructions. The herein utilised expression “calculation unit” may represent a processingcircuitry comprising a plurality of processing circuits, such as, e.g., any, some or all of the ones mentioned above. 17 One skilled in the art will appreciate that the operation modes of the system 1 may beimplemented by programmed instructions. These programmed instructions are typicallyconstituted by a computer program, which, when it is executed in the control arrangement,ensures that the control arrangement carries out the desired control, such as the operationmodes of the system 1 described herein. The computer program is usually part of acomputer program product which comprises a suitable digital storage medium on which thecomputer program is stored.
The control arrangement may further comprise a memory unit, wherein the calculation unitmay be connected to the memory unit, which may provide the calculation unit with, forexample, stored program code and/or stored data which the calculation unit may need toenable it to do calculations. The calculation unit may also be adapted to store partial or finalresults of calculations in the memory unit. The memory unit may comprise a physical deviceutilised to store data or programs, i.e., sequences of instructions, on a temporary orpermanent basis. According to some embodiments, the memory unit may compriseintegrated circuits comprising silicon-based transistors. The memory unit may comprise e.g.a memory card, a flash memory, a USB memory, a hard disc, or another similar volatile ornon-volatile storage unit for storing data such as e.g. ROIVI (Read-Only l\/lemory), PROIVI(Programmable Read-Only Memory), EPROIVI (Erasable PROIVI), EEPROIVI (ElectricallyErasable PROIVI), etc. in different embodiments.
The control arrangement is connected to components of the system 1 for receiving and/orsending input and output signals. These input and output signals may comprise waveforms,pulses, or other attributes which the input signal receiving devices can detect as informationand which can be converted to signals processable by the control arrangement. Thesesignals may then be supplied to the calculation unit. One or more output signal sendingdevices may be arranged to convert calculation results from the calculation unit to outputsignals for conveying to other parts of the vehicle's control system and/or the component orcomponents for which the signals are intended. Each of the connections to the respectivecomponents of the system 1 for receiving and sending input and output signals may take theform of one or more from among a cable, a data bus, e.g. a CAN (controller area network)bus, a MOST (media orientated systems transport) bus or some other bus configuration, or a wireless connection.
As described above, the system 1 may comprise a control arrangement but mightalternatively be implemented wholly or partly in two or more control arrangements or two or more control units. 18 Control systems in modern vehicles generally comprise a communication bus systemconsisting of one or more communication buses for connecting a number of electronic controlunits (ECUs), or controllers, to various components on board the vehicle. Such a controlsystem may comprise a large number of control units and taking care of a specific functionmay be shared between two or more of them. Vehicles of the type here concerned aretherefore often provided with significantly more control arrangements, as one skilled in the artwill surely appreciate.
The computer program product may be provided for instance in the form of a data carriercarrying computer program code for performing at least some of the operation modes of thesystem 1 according to some embodiments when being loaded into one or more calculationunits of the control arrangement. The data carrier may be, e.g. a CD ROIVI disc, or a ROIVI(read-only memory), a PROIVI (programable read-only memory), an EPROIVI (erasablePROIVI), a flash memory, an EEPROIVI (electrically erasable PROIVI), a hard disc, a memorystick, an optical storage device, a magnetic storage device or any other appropriate mediumsuch as a disk or tape that may hold machine readable data in a non-transitory manner. Thecomputer program product may furthermore be provided as computer program code on aserver and may be downloaded to the control arrangement remotely, e.g., over an Internet or an intranet connection, or via other wired or wireless communication systems.
Fig. 6 illustrates a vehicle 3 according to some embodiments. The vehicle 3 may comprise apower train 60 according to any one of the embodiments illustrated in Fig. 1, Fig. 2, and Fig.4. The power train 60 is configured to provide motive power to the vehicle 3, via wheels 63 ofthe vehicle 3.
According to the illustrated embodiments, the vehicle 3 is a truck. However, according tofurther embodiments, the vehicle 3, as referred to herein, may be another type of manned orunmanned vehicle for land or water based propulsion such as a lorry, a bus, a construction vehicle, a tractor, a car, a ship, a boat, or the like. lt is to be understood that the foregoing is illustrative of various example embodiments andthat the invention is defined only by the appended claims. A person skilled in the art willrealize that the example embodiments may be modified, and that different features of theexample embodiments may be combined to create embodiments other than those describedherein, without departing from the scope of the present invention, as defined by theappended claims. 19 The first evaporator 11 and/or the second evaporator 21, may also be referred to as a heatcollector or a boiler. The working media, as referred to herein, may also be referred to asworking fluid.
As used herein, the term "comprising" or "comprises" is open-ended, and includes one ormore stated features, elements, steps, components, or functions but does not preciude thepresence or addition of one or more other features, elements, steps, components, functionsor groups thereof.

Claims (5)

1. _ A waste heat recovery system (1 ) for a vehicle (3), wherein the vehicle (3) comprises a power source (5) configured to provide motivepower to the vehicle (3) and a power source radiator (7) configured to cool the powersource (5), and wherein the waste heat recovery system (1) comprises: - a first evaporator (11) configured to collect heat generated by the power source (5), - a first expander (13) configured to provide useful work from heat collected by the first evaporator (1 1), - a second evaporator (21), and - a second expander (23) configured to provide useful work from heat collected by the second evaporator (21),wherein the second evaporator (21) is configured to collect heat dissipated from the power source radiator (7). _ The system (1) according to claim 1, wherein the power source radiator (7) is configured to be subjected to an airflow having an air flow direction (d), and wherein the secondevaporator (21) is arranged downstream of the power source radiator (7) seen in the air flow direction (d). _ The system (1) according to claim 1 or 2, wherein the power source (5) comprises a combustion engine (5), and wherein the first evaporator (11) is configured to collect heat from exhaust gasses of the combustion engine (5). _ The system (1) according to any one of the preceding claims, wherein the power source (5) comprises a charge air cooler (25), and wherein the second evaporator (21) is configured to collect heat dissipated from the charge air cooler (25). _ The system (1) according to any one of the preceding claims, wherein the system (1) comprises a first working media circuit (51) and a second working media circuit (52),wherein the first evaporator (11) and the first expander (13) are arranged in the firstworking media circuit (51 ), and the second evaporator (21) and the second expander(23) are arranged in the second working media circuit (52), and wherein the secondworking media circuit (52) comprises working media having different properties than the working media of the first working media circuit (51). 10. 11. 12.
2. The system (1) according to any one of the preceding claims, wherein the system (1)comprises a first condenser (31) configured to condense working media evaporated bythe first evaporator (11), and wherein the first condenser (31) is configured to heat the second evaporator (21 ). _ The system (1) according to c|aim 6, wherein the second evaporator (21) and the first condenser (31) are provided in one heat exchanger unit (37, 37'). The system (1) according to c|aim 7, wherein the heat exchanger unit (37) comprisescoo|ant channe|s (41) of the first condenser (31) and coo|ant channe|s (42) of the secondevaporator (21), and wherein the coo|ant channe|s (41) of the first condenser (31) arearranged in heat exchanging contact With the coo|ant channe|s (42) of the second evaporator (21). The system (1) according to c|aim 7, wherein the heat exchanger unit (37') comprisescoo|ant channe|s (46) shared by the first condenser (31) and the second evaporator (21) :av .HA .-\»$ 5:4, + ß q (u n .M .\__. .~ e! .\\_..\..mëxšwcx m: ~= ~ w ~=- w :ak-Gun \:>\..~ ~ ~ Lux-s \--Q==\===:< The system (1) according to c|aim 9, wherein the system (1) comprises a secondcondenser (32) configured to condense working media expanded by the secondexpander (23), and wherein the system (1) comprises a mixing unit (48) arrangedupstream of the coo|ant channe|s (46), wherein the mixing unit (48) is configured to mixWorking media from the first expander (13) With Working media from the second condenser (32). The system (1) according to c|aim 9 or 10, wherein the system (1) comprises a firstWorking media pump (17) configured to pump Working media to the first evaporator (11),and a separation device (55) configured to receive working media from the coo|antchanne|s (46), wherein the separation device (55) comprises a first out|et (61) connectedto the first working media pump (17) and a second out|et (62) connected to the secondexpander (23), and wherein the separation device (55) is configured to separate workingmedia in liquid phase to the first out|et (61) and is configured to separate working media in gaseous phase to the second out|et (62). The system (1) according to c|aim 11, wherein the system (1) comprises a sub-cooling pass (65) between the first out|et (61) and the first working media pump (17). 1
3. The system (1) according to any one of the preceding claims, wherein the vehicle (3)comprises an air intake (71) for conducting ambient air to power source radiator (7), andwherein the system (1) comprises a cover arrangement (73) controllable between anopen position, in which the cover arrangement (73) allows flow of air through the airintake (71 ), and a closed position in which the cover arrangement (73) at least partially blocks flow of air through the air intake (71). 1
4. A powertrain (60) for a vehicle (3), wherein the powertrain (60) comprises a powersource (5) configured to provide motive power to the vehicle (3), a power source radiator(7) configured to cool the power source (5), and a waste heat recovery system (1) according to any one of the preceding claims. 1
5. A vehicle (3) comprising a power train (60) according to claim 14.
SE1950451A 2019-04-11 2019-04-11 Waste Heat Recovery System, Powertrain, and Vehicle SE543339C2 (en)

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