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WO2013172293A1 - Dispositif d'utilisation de chaleur perdue - Google Patents

Dispositif d'utilisation de chaleur perdue Download PDF

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Publication number
WO2013172293A1
WO2013172293A1 PCT/JP2013/063264 JP2013063264W WO2013172293A1 WO 2013172293 A1 WO2013172293 A1 WO 2013172293A1 JP 2013063264 W JP2013063264 W JP 2013063264W WO 2013172293 A1 WO2013172293 A1 WO 2013172293A1
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WO
WIPO (PCT)
Prior art keywords
boiler
working fluid
exhaust
pipe
passage
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2013/063264
Other languages
English (en)
Japanese (ja)
Inventor
文彦 石黒
井口　雅夫
英文 森
榎島　史修
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of WO2013172293A1 publication Critical patent/WO2013172293A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • 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
    • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/02—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a heat exchanger
    • 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
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
    • 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 present invention relates to a waste heat utilization device.
  • FIG. 2 of patent document 1 The conventional waste heat utilization apparatus is disclosed by FIG. 2 of patent document 1.
  • FIG. 2 of patent document 1 The conventional waste heat utilization apparatus is disclosed by FIG. 2 of patent document 1.
  • FIG. 2 of patent document 1 The conventional waste heat utilization apparatus is disclosed by FIG. 2 of patent document 1.
  • FIG. 2 of patent document 1 The conventional waste heat utilization apparatus is disclosed by FIG. 2 of patent document 1.
  • FIG. 2 of patent document 1 The conventional waste heat utilization apparatus is disclosed by FIG. 2 of patent document 1.
  • FIG. This waste heat utilization device is provided with a Rankine cycle device used for a drive system.
  • the Rankine cycle device has first and second boilers and circulates a working fluid.
  • the drive system has an engine and a turbocharger that supplies pressurized air to the engine.
  • the first boiler in the Rankine cycle device heat exchange is performed between the pressurized air and the working fluid, using the pressurized air as a heat source.
  • the second boiler heat exchange is performed between the coolant and the working fluid using the cool
  • waste heat utilization apparatus since the working fluid can be heated by the first and second boilers, it is possible to increase the temperature of the working fluid flowing into the expander. Further, in this waste heat utilization device, it is possible to cool the compressed air and the cooling water by heat exchange in the first and second boilers, so it is also possible to improve the output of the engine.
  • the exhaust gas includes exhaust gas emitted to the atmosphere (exhaust gas in a narrow sense) and recirculated exhaust gas recirculated to an internal combustion engine such as an engine.
  • the recirculation exhaust be suitably cooled before being recirculated to the internal combustion engine. If the recirculating exhaust gas is recirculated to the internal combustion engine with its density increased due to cooling, it is possible to reduce the content of nitrogen oxides in the exhaust gas produced by the internal combustion engine and finally released to the atmosphere.
  • the waste heat utilization apparatus of the said patent document 1 it is possible to change the heat source in a 1st boiler from pressurized air to reflux exhaust, and to comprise.
  • the condensed water may stay in the intake manifold after being generated in the first boiler.
  • the boiler is made of a material such as stainless steel having high corrosion resistance
  • the intake manifold is generally made of cast iron or aluminum alloy that is weak to corrosion, so the condensed water causes corrosion in the intake manifold. It may occur. For this reason, in the waste heat utilization apparatus as described above, the durability of the intake manifold is reduced, and as a result, the durability of the entire waste heat utilization apparatus is reduced.
  • An object of the present invention is to provide a waste heat utilization device which realizes improvement of the performance of an internal combustion engine while improving the recovery amount of energy in a Rankine cycle device and which is excellent in durability.
  • an internal combustion engine an exhaust passage through which exhaust generated by the internal combustion engine flows, and a part of the exhaust flowing through the exhaust passage are used as reflux exhaust gas.
  • a waste heat utilization device for use in a drive system having an exhaust gas recirculation passage recirculating to an internal combustion engine.
  • the waste heat utilization device comprises a Rankine cycle device.
  • the Rankine cycle device has a pump, a boiler, an expander, a condenser, and piping, and circulates a working fluid.
  • the boiler includes a first boiler, a second boiler, and a third boiler. The first boiler exchanges heat between the exhaust flowing through the exhaust passage and the working fluid.
  • the second boiler performs heat exchange between the reflux exhaust and the working fluid.
  • the third boiler performs heat exchange between the working fluid and a heat medium having a temperature lower than that of the return exhaust gas.
  • the third boiler is located at a portion of the Rankine cycle device upstream of the second boiler in the circulation direction of the working fluid.
  • the piping is configured to circulate the working fluid from the pump through the third boiler, the second boiler, and the expander to the condenser, and the pump further includes the first boiler and the expander. Are configured to circulate the working fluid to the condenser.
  • the waste heat utilization apparatus of this invention is equipped with the Rankine cycle. And, this Rankine cycle has the first to third boilers. As a result, in the Rankine cycle in this waste heat utilization device, the working fluid can be suitably heated by the first to third boilers, and the pressure energy of the working fluid becomes large. For this reason, in this waste heat utilization apparatus, it is possible to increase the amount of energy recoverable in the Rankine cycle. Examples of the recoverable energy include electric power generated based on pressure energy and power regenerated by the internal combustion engine.
  • the third boiler is located upstream of the second boiler in the working fluid circulation direction.
  • the first boiler and the third and second boilers are disposed in parallel by the piping, the first boiler is disposed upstream of the second boiler in the circulation direction of the working fluid. There is no That is, the working fluid suitably heated to the temperature according to heat exchange by the third boiler flows into the second boiler, and the working fluid heated by the first boiler flows into the second boiler Absent.
  • the waste heat utilization device of the present invention achieves improvement in performance of the internal combustion engine while improving the amount of energy recovery in the Rankine cycle, and is excellent in durability. Furthermore, in the waste heat utilization device of the present invention, it is possible to sufficiently heat the working fluid to the superheated steam temperature (superheat) level exceeding the temperature to be saturated steam by heat exchange with the first to third boilers. is there. As a result, in the Rankine cycle in this waste heat utilization device, the working fluid expanded and depressurized in the expander becomes difficult to liquefy, and energy recovery efficiency at the time of expansion of the working fluid becomes high. In addition, in this waste heat utilization device, damage to the expander is less likely to occur.
  • the waste heat utilization apparatus of the present invention since the first boiler and the third and second boilers are arranged in parallel, not only for the third boiler but also for the first boiler
  • the working fluid that has passed through the condenser, that is, the working fluid of low temperature flows in.
  • the exhaust temperature after the heat exchange in the first boiler does not have a problem with the exhaust which is finally discharged to the atmosphere.
  • a diesel engine or the like can be employed as the internal combustion engine.
  • these engines may be hybrid engines combining motors, and the engines may be air-cooled or water-cooled.
  • the drive system may be provided with a supercharger capable of supplying pressurized air to the internal combustion engine.
  • a turbocharger, a supercharger or the like can be employed as the turbocharger.
  • a plurality of internal combustion engines and superchargers may be provided.
  • a coolant for an internal combustion engine can be adopted.
  • the coolant for example, it is possible to adopt LLC (long life coolant) or the like in addition to water.
  • pressurized air it is also possible to use pressurized air as a heat source.
  • the coolant and the pressurized air can be cooled by heat exchange with the working fluid in the third boiler.
  • the internal combustion engine can be suitably cooled.
  • a plurality of third boilers may be provided, and the third boiler using the above-described coolant as a heat source and the third boiler using the above-described pressurized air as a heat source may be added to the second boiler, respectively. It may be located upstream of the working fluid circulation direction.
  • a plurality of third boilers using the coolant as a heat source and a plurality of third boilers using the pressurized air as a heat source may be provided.
  • the waste heat utilization device further includes a first flow control valve and a first control valve control unit.
  • the first flow control valve is provided at a portion of the Rankine cycle device downstream of the pump in the circulation direction of the working fluid.
  • the first flow rate adjustment valve can adjust the flow rate of the working fluid flowing from the pump into the first boiler and the flow rate of the working fluid flowing from the pump into the third boiler.
  • the first adjusting valve control unit controls the first flow rate adjusting valve.
  • the flow rate of the working fluid flowing into the first boiler can be made an appropriate flow rate according to the cooling demand amount of the reflux exhaust gas, etc., and the reflux exhaust gas is suitably used in the second boiler Can be cooled.
  • the waste heat utilization device further includes a bypass, a second flow rate adjustment valve, and a second adjustment valve control unit.
  • the bypass path extends around the third boiler.
  • the bypass path branches from the portion of the pipe downstream of the first flow rate adjustment valve in the circulation direction of the working fluid and joins the portion of the pipe upstream of the second boiler.
  • the second flow rate adjustment valve can adjust the flow rate of the working fluid flowing into the third boiler and the flow rate of the working fluid flowing into the bypass passage.
  • the second control valve control unit controls the second flow control valve.
  • the exhaust passage is provided with a purification device for purifying the exhaust flowing through the exhaust passage.
  • the first boiler is disposed at a portion of the exhaust passage downstream of the purification device in the flow direction of the exhaust gas.
  • the waste heat utilization device of the present invention there is a possibility that condensed water may be generated in the first boiler by heat exchange in the first boiler.
  • the exhaust gas in order to discharge the exhaust gas to the atmosphere, it is required that the exhaust gas be subjected to a certain treatment from the viewpoint of air pollution countermeasures and the like.
  • the purification device of the present invention it is possible to remove nitrogen oxides, soot and the like from the exhaust gas. Further, since the first boiler is disposed downstream of the purification device, even if the condensed water is generated in the first boiler, the condensed water does not flow into the purification device. For this reason, in this waste heat utilization device, it becomes possible to preferably suppress the deterioration of the purification device.
  • FIG. 1 is a schematic structural view showing a waste heat utilization device according to an embodiment of the present invention.
  • FIG. 2 is a schematic structural view showing a state in which a working fluid flows into a refluxing exhaust boiler through a coolant boiler according to the waste heat utilization device of FIG. 1;
  • FIG. 2 is a schematic structural view showing a state in which a working fluid flows into a reflux exhaust boiler through a coolant boiler or a bypass according to the waste heat utilization device of FIG. 1;
  • the waste heat utilization apparatus of an embodiment is mounted in a vehicle, and as shown in FIG. 1, it is used for the drive system 1 of a vehicle.
  • the waste heat utilization device includes a Rankine cycle device 3, a first temperature sensor 10, a first flow control valve 43, a bypass passage 44, a second flow control valve 45, and a control device 11.
  • the drive system 1 includes an engine 5 as an internal combustion engine, a turbocharger 7 as a supercharger, a radiator 9, pipes 12 to 14 as an exhaust passage, and pipes 15 and 16 as an exhaust gas recirculation passage. ing.
  • the engine 5 is a known water-cooled diesel engine. Inside the engine 5 is formed a water jacket (not shown) through which LLC as a coolant as a heat medium can flow.
  • the engine 5 is formed with an outlet 5a and an inlet 5b in communication with the water jacket. Further, the engine 5 is formed with an exhaust port 5c for exhausting the exhaust gas and an intake port 5d for sucking in pressurized air as a heat medium to be described later.
  • the turbocharger 7 is operated by the exhaust generated from the engine 5 and supplies the engine 5 with pressurized air obtained by pressurizing air outside the vehicle.
  • the radiator 9 is formed with an inlet 9a for introducing the coolant into the radiator 9 and an outlet 9b for discharging the coolant.
  • the radiator 9 exchanges heat between the coolant flowing inside and the air outside the vehicle.
  • an electric fan 9c is provided in the vicinity of the radiator 9.
  • the electric fan 9 c is electrically connected to the control device 11.
  • the engine 5 and the turbocharger 7 are connected by a pipe 12, a pipe 17 and a pipe 18. Further, a pressurized air boiler 27 described later is connected to the pipe 17 and the pipe 18.
  • the pipe 12 allows exhaust gas to flow therethrough, and is connected to the exhaust port 5 c of the engine 5 and the turbocharger 7.
  • the pipe 17 is configured so that pressurized air can flow therethrough, and the pipe 18 is configured such that pressurized air and recirculated exhaust can flow therethrough.
  • the pipe 17 is connected to the turbocharger 7 and a first inlet 27 a of a pressurized air boiler 27 described later.
  • the pipe 18 is connected to the first outlet 27 b of the pressurized air boiler 27 and the inlet 5 d of the engine 5.
  • each first end of the pipes 13 and 19 is connected to the turbocharger 7.
  • the second end of the pipe 13 is connected to a seventh inlet 30 a of an exhaust boiler 30 described later.
  • the pipe 13 is configured such that exhaust gas can flow therethrough.
  • the pipe 13 is provided with a purifier 131 for removing nitrogen oxides, soot and the like in the exhaust gas flowing through the pipe 13.
  • a first end of the pipe 14 is connected to the seventh outlet 30 b of the exhaust boiler 30 described above.
  • the second end of the pipe 14 is open to the outside of the vehicle.
  • the pipe 12 communicates with the pipes 13 and 14 via the turbocharger 7.
  • the second end of the pipe 19 is open to the air intake of the vehicle (not shown).
  • the pipe 19 is configured to allow air to flow therethrough, and is in communication with the pipe 17 via the turbocharger 7.
  • the pipes 15 and 16 are configured such that reflux exhaust which is a part of the exhaust can flow through the inside.
  • the first end of the pipe 15 is connected to the pipe 12.
  • the first end of the pipe 16 is connected to the pipe 18.
  • the second end of the pipe 15 is connected to a fifth inlet 29 a of a reflux exhaust boiler 29 described later.
  • the second end of the pipe 16 is connected to the fifth outlet 29 b of the reflux exhaust boiler 29.
  • the piping 16 is provided with a variable valve 21.
  • the variable valve 21 is electrically connected to the controller 11.
  • the pipes 15 and 16 join the reflux exhaust to the pipe 18 while passing the reflux exhaust boiler 29 so that a part of the exhaust discharged from the exhaust port 5c of the engine 5 is used as the reflux exhaust from the intake port 5d to the engine 5 Reflux into the inside.
  • the first end of the pipe 15 may be connected to the pipe 13.
  • the first end of the pipe 16 is connected to the pipe 19.
  • the engine 5 and the radiator 9 are connected by pipes 23-25. Further, a coolant boiler 28 described later is connected to the pipe 23 and the pipe 24.
  • the pipes 23 to 25 are configured such that the coolant can flow therethrough.
  • the pipe 23 is connected to the outlet 5 a of the engine 5 and the third inlet 28 a of the coolant boiler 28.
  • the pipe 24 is connected to the third outlet 28 b of the coolant boiler 28 and the inlet 9 a of the radiator 9.
  • the pipe 25 is connected to the outlet 9 b of the radiator 9 and the inlet 5 b of the engine 5.
  • the pipe 24 is provided with a first electric pump P1.
  • the first electric pump P1 is electrically connected to the control device 11.
  • the first electric pump P1 may be provided in the pipe 23 or the pipe 25.
  • the first temperature sensor 10 is provided in the pipe 16.
  • the first temperature sensor 10 is electrically connected to the control device 11.
  • the first temperature sensor 10 detects the temperature of the reflux exhaust flowing out of the fifth outlet 29 b of the reflux exhaust boiler 29 and circulating the pipe 16, and transmits the detected value to the control device 11.
  • the Rankine cycle device 3 includes a second electric pump P2, a pressurized air boiler 27, a coolant boiler 28, a reflux exhaust boiler 29, an exhaust boiler 30, an expander 31, a condenser 32, and piping 33 to And 41.
  • the first and second flow control valves 43 and 45 and the bypass passage 44 are integrally assembled to the Rankine cycle device 3.
  • An HFC 134 a as a working fluid can flow through the pipes 33 to 42 and the bypass passage 44.
  • the second electric pump P2 corresponds to the pump in the waste heat utilization device of the present invention.
  • the pressurized air boiler 27 is formed with a first inlet 27a and a first outlet 27b, and a second inlet 27c and a second outlet 27d. Further, in the pressurized air boiler 27, a first passage 27e having both ends respectively communicating with the first inlet 27a and the first outlet 27b, and a second inlet 27c and the second outlet 27d respectively. A second passage 27f having both ends is provided. In the pressurized air boiler 27, the pressurized air is cooled and the working fluid is heated by heat exchange between the pressurized air in the first passage 27e and the working fluid in the second passage 27f.
  • a third inlet 28a and a third outlet 28b, and a fourth inlet 28c and a fourth outlet 28d are formed.
  • a third passage 28e having both ends communicating with the third inlet 28a and the third outlet 28b, and both ends communicating with the fourth inlet 28c and the fourth outlet 28d, respectively.
  • a fourth passage 28f In the coolant boiler 28, heat exchange between the coolant in the third passage 28e and the working fluid in the fourth passage 28f performs cooling of the coolant and heating of the working fluid.
  • the reflux exhaust boiler 29 is provided with a fifth inlet 29a and a fifth outlet 29b, and a sixth inlet 29c and a sixth outlet 29d.
  • a fifth passage 29e having both ends communicating with the fifth inlet 29a and the fifth outlet 29b, respectively, and a fifth passage 29e communicating with the sixth inlet 29c and the sixth outlet 29d, respectively.
  • 6 passages 29f are provided.
  • heat exchange between the reflux exhaust in the fifth passage 29e and the working fluid in the sixth passage 29f cools the reflux exhaust and heats the working fluid.
  • the exhaust boiler 30 is formed with a seventh inlet 30a and a seventh outlet 30b, and an eighth inlet 30c and an eighth outlet 30d.
  • a seventh passage 30e having both ends communicating with the seventh inlet 30a and the seventh outlet 30b, and both ends communicating with the eighth inlet 30c and the eighth outlet 30d, respectively And an eighth passage 30f.
  • the working fluid is heated by heat exchange between the exhaust in the seventh passage 30e and the working fluid in the eighth passage 30f, and the exhaust is additionally cooled.
  • the reflux exhaust boiler 29 performs heat exchange between the reflux exhaust and the working fluid using the reflux exhaust as a heat source. It corresponds to 2 boilers.
  • the exhaust boiler 30 corresponds to the first boiler because heat exchange is performed between the exhaust gas and the working fluid, using the exhaust gas flowing through the exhaust passage, that is, the pipe 13 as a heat source.
  • both the pressurized air (heat medium) and the coolant (heat medium) that exchange heat with the working fluid are lower in temperature than the recirculating exhaust gas, respectively.
  • the pressurized air boiler 27 and the coolant boiler 28 correspond to a second boiler. As shown in FIGS.
  • the pressurized air boiler 27 and the coolant boiler 28 are illustrated so that the heat source (the pressurized air and the coolant) and the working fluid flow in the same direction,
  • the heat sources (the pressurized air and the coolant) and the working fluid may flow in different directions (opposite flow) as in the reflux exhaust boiler 29 and the exhaust boiler 30.
  • the expander 31 is formed with an inlet 31a through which the working fluid flows, and an outlet 31b through which the working fluid flows out.
  • a rotary driving force is generated by expanding the working fluid heated through the pressurized air boiler 27, the coolant boiler 28, the reflux exhaust boiler 29, and the exhaust boiler 30.
  • a known generator not shown is connected to the expander 31. The generator generates electric power by the driving force of the expander 31, and charges a battery (not shown) with electric power.
  • the condenser 32 is formed with an inlet 32 a for introducing the working fluid therein and an outlet 32 b for discharging the working fluid.
  • the condenser 32 exchanges heat between the working fluid flowing inside and the air outside the vehicle, and cools and liquefies the working fluid decompressed by the expansion in the expander 31.
  • An electric fan 32 c is provided in the vicinity of the condenser 32. The electric fan 32 c is electrically connected to the control device 11.
  • the first flow rate adjustment valve 43 is a flow rate of the working fluid discharged from the second electric pump P2 and flowing into the exhaust boiler 30, and a flow rate of the working fluid discharged from the second electric pump P2 and flowing into the pressurized air boiler 27 And adjust.
  • the first flow rate adjustment valve 43 is electrically connected to the controller 11.
  • the bypass passage 44 allows the working fluid to bypass the coolant boiler 28 by circulating the working fluid therein.
  • the second flow rate adjustment valve 45 adjusts the flow rate of the working fluid flowing into the coolant boiler 28 and the flow rate of the working fluid flowing into the bypass passage 44.
  • the second flow rate adjustment valve 45 is electrically connected to the controller 11.
  • the outlet 32 b of the condenser 32 and the second electric pump P 2 are connected by a pipe 33.
  • the second electric pump P2 and the first flow rate adjustment valve 43 are connected by a pipe.
  • the first flow control valve 43 and the second inlet 27 c of the pressurized air boiler 27 are connected by a pipe 35.
  • the second outlet 27 d of the pressurized air boiler 27 and the second flow control valve 45 are connected by a pipe 36.
  • the second flow rate adjustment valve 45 and the fourth inlet 28 c of the coolant boiler 28 are connected by a pipe 37.
  • the fourth outlet 28 d of the coolant boiler 28 and the sixth inlet 29 c of the reflux exhaust boiler 29 are connected by a pipe 38.
  • the sixth outlet 29 d of the reflux exhaust boiler 29 and the inlet 31 a of the expander 31 are connected by a pipe 39.
  • the outlet 31 b of the expander 31 and the inlet 32 a of the condenser 32 are connected by a pipe 40.
  • first end of the pipe 41 is connected to the first flow rate adjustment valve 43, and the second end of the pipe 41 is connected to the eighth inlet 30 c of the exhaust boiler 30.
  • the first end of the pipe 42 is connected to the eighth outlet 30 d of the exhaust boiler 30, and the second end of the pipe 42 is connected to the above-described pipe 39.
  • the first end of the bypass passage 44 is connected to the second flow rate adjustment valve 45, and the second end of the bypass passage 44 is connected to the above-described pipe 38.
  • this Rankine cycle device 3 by operating the second electric pump P2, as shown in FIGS. 2 and 3, the working fluid from the second electric pump P2 to the pressurized air boiler 27, the coolant boiler 28 or the bypass Through the passage 44, the reflux exhaust boiler 29 and the expander 31, the condensers 32 are circulated in the order from the pipes 33 to 40 in this order. Further, the working fluid circulates in the pipes 33, 34, 41, 42, 40 in the order from the second electric pump P2 through the exhaust boiler 30 to the pipe 39 and then through the expander 31 to the condenser 32. Do.
  • the pressurized air boiler 27 is positioned most upstream in the circulation direction of the working fluid among the pressurized air boiler 27, the coolant boiler 28 and the reflux exhaust boiler 29.
  • the coolant boiler 28 is located downstream of the pressurized air boiler 27, and the reflux exhaust boiler 29 is located downstream of the coolant boiler 28. Further, the exhaust boiler 30, the pressurized air boiler 27, the coolant boiler 28 and the reflux exhaust boiler 29 are arranged in parallel.
  • the pressurized air boiler 27 and the coolant boiler 28 corresponding to the third boiler are located upstream of the circulation exhaust boiler 29 in the circulating direction of the working fluid than the reflux exhaust boiler 29 corresponding to the second boiler
  • An exhaust boiler 30 corresponding to the above, a pressurized air boiler 27 corresponding to the third and second boilers, a coolant boiler 28 and a reflux exhaust boiler 29 are arranged in parallel. Further, the exhaust boiler 30 is disposed downstream of the purification device 131 in the flow direction of the exhaust gas.
  • the control device 11 controls the operation of the electric fans 9 c and 32 c to adjust the amount of heat that the coolant or the working fluid radiates to the outside air. Further, the control device 11 performs open / close control of the variable valve 21 and operation control of the first and second electric pumps P1, P2. Furthermore, the control device 11 determines the required cooling amount for the reflux exhaust based on the temperature of the reflux exhaust detected by the first temperature sensor 10. Then, the control device 11 performs operation control of the first and second flow rate adjustment valves 43 and 45 based on the required amount of cooling. That is, the control device 11 functions as a first adjustment valve control unit and a second adjustment valve control unit.
  • the waste heat utilization apparatus configured in this way operates as follows by driving the vehicle.
  • the engine 5 By driving the vehicle, as shown in FIG. 2, the engine 5 is operated in the driveline 1.
  • the exhaust gas discharged from the exhaust port 5 c flows in the pipe 12.
  • the control device 11 controls the variable valve 21 to open so that part of the exhaust flowing through the inside of the pipe 12 flows into the pipe 15 (see the dashed dotted arrow in FIG. 2).
  • the controller 11 appropriately controls the opening degree of the variable valve 21 to adjust the flow rate of the exhaust flowing into the pipe 15.
  • the exhaust gas flowing into the pipe 15, that is, the recirculated exhaust gas reaches the pipe 18 through the fifth passage 29 e of the reflux exhaust boiler 29 and the pipe 16, and is sucked into the engine 5 together with the pressurized air in the pipe 18.
  • the first temperature sensor 10 detects the temperature of the recirculating exhaust flowing through the pipe 16, and transmits the detected value to the control device 11.
  • the exhaust gas flowing out of the turbocharger 7 reaches the pipe 13.
  • the exhaust gas flowing through the pipe 13 reaches the inside of the seventh passage 30e, that is, the inside of the exhaust boiler 30, from the seventh inlet 30a after nitrogen oxides, soot and the like are removed by the purification device 131.
  • the exhaust gas flowing in the seventh passage 30e and flowing out from the seventh outlet 30b is discharged to the outside of the vehicle through the pipe 14 (see the dashed-dotted arrow in FIG. 2).
  • the control device 11 also operates the first and second electric pumps P1 and P2 and the electric fans 9c and 32c.
  • the coolant that has cooled the engine 5 flows out from the outlet 5 a, passes through the piping 23, the third passage 28 e of the cooling liquid boiler 28 and the piping 24, and from the inlet 9 a of the radiator 9.
  • the inside of the radiator 9 is reached.
  • the coolant in the radiator 9 exchanges heat with the air around the radiator 9, that is, is dissipated and cooled.
  • the control device 11 appropriately changes the operation amount of the electric fan 9c to radiate the cooling liquid suitably.
  • the coolant that has been radiated and cooled flows out from the outlet 9b and flows into the engine 5 from the inlet 5b of the engine 5 through the pipe 25 to cool the engine 5 (see the broken arrow in FIG. 2).
  • the control device 11 determines the required cooling amount for the recirculated exhaust gas.
  • the controller 11 determines that the required amount of cooling for the recirculating exhaust is smaller than the threshold value, that is, the required amount of cooling for the recirculating exhaust is small, and controls the first and second flow control valves 43 and 45 accordingly. I do.
  • the control device 11 performs the first operation so that the flow rate flowing to the pipe 35 and the flow rate flowing to the pipe 41 become equal.
  • the flow control valve 43 is controlled.
  • the controller 11 controls the second flow control valve 45 so that all the working fluid flowing through the pipe 36 flows toward the pipe 37 and the flow rate of the working fluid flowing to the bypass passage 44 decreases or the flow rate becomes zero.
  • FIG. 2 shows the case where the flow rate of the working fluid flowing to the bypass passage 44 is zero.
  • the working fluid discharged by the second electric pump P2 passes through the pipe 35 and the second inlet 27c of the pressurized air boiler 27 to the second passage.
  • the working fluid discharged by the second electric pump P2 passes through the pipe 41 from the eighth inlet 30c of the exhaust boiler 30 to the eighth passage 30f.
  • the pressurized air boiler 27 heat exchange between the pressurized air flowing in the first passage 27e and the working fluid flowing in the second passage 27f is performed. At this time, since the compressed air flowing through the first passage 27e has heat of about 150 ° C. by being compressed by the turbocharger 7, the working fluid flowing through the second passage 27f is preferably heated. Be done. On the other hand, the pressurized air flowing through the first passage 27e radiates heat to the working fluid flowing through the second passage 27f, and thus reaches the engine 5 while being cooled to a temperature according to the heat radiation.
  • the working fluid heated in the pressurized air boiler 27 flows out from the second outlet 27d, passes through the piping 36 and the piping 37, and reaches the fourth passage 28f from the fourth inlet 28c of the coolant boiler 28. Then, the working fluid exchanges heat with the coolant in the coolant boiler 28. At this time, the coolant flowing through the third passage 28 e has heat of about 80 to 90 ° C. due to the waste heat of the engine 5. Further, since the working fluid flowing through the fourth passage 28 f is already heated in the pressurized air boiler 27, the working fluid is further heated in the coolant boiler 28 and has a temperature corresponding to the heating. On the other hand, the coolant flowing through the third passage 28e radiates heat to the working fluid flowing through the fourth passage 28f, and thus reaches the radiator 9 in a state of being cooled to a temperature according to the heat radiation.
  • the working fluid heated in the coolant boiler 28 flows out from the fourth outlet 28 d and passes through the pipe 38 from the sixth inlet 29 c to the sixth passage 29 f of the reflux exhaust boiler 29. Then, the working fluid is heat-exchanged with the reflux exhaust in the reflux exhaust boiler 29. At this time, the recirculated exhaust gas flowing through the fifth passage 29e has heat of about 500 ° C. depending on the operating condition of the engine 5. For this reason, the working fluid heated in the pressurized air boiler 27 and the coolant boiler 28 is sufficiently heated in the reflux exhaust boiler 29.
  • the working fluid flows out from the sixth outlet 29 d in a high temperature and high pressure state, and reaches the expander 31 from the inlet 31 a of the expander 31 through the pipe 39.
  • the recirculated exhaust gas flowing through the fifth passage 29e dissipates heat to the working fluid flowing through the sixth passage 29f, it is returned to the engine 5 together with the pressurized air in a state cooled to a temperature according to the heat radiation. .
  • the working fluid flowing through the eighth passage 30f of the exhaust boiler 30 exchanges heat with the exhaust flowing through the seventh passage 30e.
  • path 30e has a heat
  • path 30f is also heated sufficiently.
  • the working fluid flows out from the eighth outlet 30 d in a high temperature and high pressure state, and merges with the working fluid heated by the reflux exhaust boiler 29 or the like in the pipe 39.
  • the working fluid flowing through the pipe 39 extends from the inlet 31 a of the expander 31 into the expander 31. Then, the high temperature and high pressure working fluid is expanded in the expander 31 and decompressed. The pressure energy at this time causes the generator connected to the expander 31 to generate power.
  • the working fluid reduced in pressure in the expander 31 flows out from the outlet 31 b and passes through the pipe 40 to the inlet 32 a of the condenser 32 and into the condenser 32.
  • the working fluid of the condenser 32 dissipates heat to the air around the condenser 32 and is cooled.
  • the control device 11 changes the amount of operation of the electric fan 32c as appropriate to suitably dissipate heat of the working fluid and liquefy it.
  • the cooled working fluid flows out from the outlet 32b and is discharged through the pipe 35 by the second electric pump P2 again.
  • the control device 11 determines that the required cooling amount for the recirculated exhaust is larger than the threshold value, that is, the required cooling amount for the recirculated exhaust is large. Thereby, the control device 11 controls the first and second flow rate adjustment valves 43, 45 accordingly. Specifically, for the working fluid discharged from the second electric pump P2 and flowing through the pipe 34, the controller 11 sets the first flow rate so that the flow rate flowing to the pipe 35 is larger than the flow rate flowing to the pipe 41 The control valve 43 is controlled. Further, the control device 11 controls the second flow rate adjustment valve 45 so that the flow rate of the working fluid flowing through the bypass passage 44 is larger than the flow rate of the working fluid flowing into the coolant boiler 28.
  • the working fluid having flowed through the bypass passage 44 flows into the reflux exhaust boiler 29 at a lower temperature than the state shown in FIG. 2 described above.
  • the recirculating exhaust gas in the fifth passage 29e is sufficiently cooled to such an extent that the cooling demand is satisfied.
  • the working fluid heated in the refluxing exhaust boiler 29 or the like and the exhaust boiler 30 is expanded and reduced in pressure by the expander 31 as in the case shown in FIG.
  • the Rankine cycle device 3 in this waste heat utilization apparatus it is possible to suitably heat the working fluid with the pressurized air boiler 27, the coolant boiler 28, the reflux exhaust boiler 29 and the exhaust boiler 30, It is possible to increase the pressure energy of the fluid. For this reason, in this waste heat utilization apparatus, it is possible to increase the amount of power that can be recovered by the Rankine cycle device 3.
  • this waste heat utilization apparatus it is possible to cool the recirculating exhaust gas by heat exchange in the reflux exhaust boiler 29. For this reason, in this waste heat utilization device, it is possible to reflux the reflux exhaust gas to the engine 5 while increasing the density of the reflux exhaust gas.
  • the pressurized air boiler 27 and the coolant boiler 28 are located upstream of the return flow exhaust boiler 29 in the circulation direction of the working fluid.
  • the exhaust boiler 30, the pressurized air boiler 27, the coolant boiler 28 and the reflux exhaust boiler 29 are arranged in parallel by the pipes 33 to 42.
  • the exhaust boiler 30 is not disposed upstream of the reflux exhaust boiler 29 in the circulation direction of the working fluid. That is, the working fluid suitably heated to the temperature according to the heat exchange by the pressurized air boiler 27 and the coolant boiler 28 flows into the reflux exhaust boiler 29, and the working fluid heated by the exhaust boiler 30 is It does not flow into the reflux exhaust boiler 29.
  • the control device 11 determines the required cooling amount for the reflux exhaust based on the temperature of the reflux exhaust detected by the first temperature sensor 10 and the flow rate of the working fluid flowing into the reflux exhaust boiler 29 Control the first and second flow control valves 43, 45 to adjust the temperature and the temperature. Under the present circumstances, it is possible for the control apparatus 11 to judge correctly the cooling request
  • the pressurized air can be cooled by heat exchange in the pressurized air boiler 27, and the coolant can be cooled by heat exchange in the coolant boiler 28.
  • the pressurized air boiler 27 is positioned most upstream in the circulation direction of the working fluid. Therefore, in this waste heat utilization device, the temperature of the working fluid flowing into the pressurized air boiler 27 is low. Thereby, in this waste heat utilization apparatus, it becomes possible to cool pressurized air suitably, and it is possible to supply engine 5 in the state which made the density of pressurized air large enough.
  • the purification device 131 can remove nitrogen oxides, soot, and the like from the exhaust gas. Further, since the exhaust boiler 30 is disposed downstream of the purification device 131, even if the condensed water is generated in the exhaust boiler 30, the condensed water does not flow into the purification device 131. For this reason, in this waste heat utilization apparatus, deterioration of the purification device 131 can be suitably suppressed. Even when condensed water is generated in the exhaust boiler 30, if the discharge port is provided at an appropriate place of the exhaust boiler 30, it is possible to discharge the condensed water. Under the present circumstances, since it passes through the purification apparatus 131, the air pollution by discharging condensed water can be suppressed suitably. Moreover, in addition to the purification device 131, if the pipe 13 is provided with a silencer, it is possible to preferably suppress the generation of noise and the like when discharging the condensed water.
  • the waste heat utilization device of the embodiment achieves the performance improvement of the engine 5 while improving the recovery amount of the power in the Rankine cycle device 3, and is excellent in the durability. Furthermore, in this waste heat utilization apparatus, the temperature of the superheated steam exceeding the temperature at which saturated steam is obtained for the working fluid by heat exchange with the pressurized air boiler 27, the coolant boiler 28, the reflux exhaust boiler 29 and the exhaust boiler 30 (super It is possible to heat sufficiently to the extent of heat). As a result, in the Rankine cycle device 3 in this waste heat utilization device, the working fluid expanded and decompressed in the expander 31 becomes difficult to liquefy, and the power recovery efficiency is high. Moreover, damage to the expander 31 is less likely to occur in this waste heat utilization device.
  • only one of the pressurized air boiler 27 or the cooling liquid boiler 28 may be disposed upstream of the working fluid in the reflux exhaust boiler 29.
  • one of the pressurized air boiler 27 or the coolant boiler 28 is disposed upstream of the working fluid in the reflux exhaust boiler 29, and the other is disposed in the vicinity of the outlet of the second electric pump P2 (pipe 34). good.
  • pressurized air boiler 27 and the coolant boiler 28 are disposed in series in the waste heat utilization device of the embodiment, they may be disposed in parallel. Further, on the upstream side of the working fluid in the reflux exhaust boiler 29, a boiler different from the pressurized air boiler 27 or the coolant boiler 28 may be disposed. In this case, it is possible to employ, for example, an oil boiler or the like which performs heat exchange between the lubricating oil and the working fluid, using the lubricating oil heated by the engine 5 or the like as a heat source. In addition, a boiler that uses a high temperature working fluid flowing downstream of the expander 31, that is, the pipe 40 as a heat source may be employed.
  • the displacement of the second electric pump P2 may be configured to be changeable.
  • the control device 11 controls the second electric pump P2 so as to reduce the discharge capacity, when it is determined that the cooling request for the recirculated exhaust gas is small.
  • the control device 11 can control the second electric pump P2 so that the discharge capacity becomes large.
  • first and second flow rate adjustment valves 43 and 45 are adopted for the first and second flow rate adjustment valves 43 and 45, and flow rate adjustment is performed so that all the working fluid flows in only one and the working fluid flowing in the other is zero by switching the flow path.
  • only one of the first flow control valve 43 and the second flow control valve 45 may be a three-way valve.
  • the first temperature sensor 10 may be provided in the pipe 15, and the control device 11 may determine the required cooling amount for the reflux exhaust based on the temperature of the reflux exhaust before flowing into the reflux exhaust boiler 29.
  • the first temperature sensor 10 may be provided in the pipe 38, and the control device 11 may determine the required cooling amount for the reflux exhaust based on the temperature of the working fluid before flowing into the reflux exhaust boiler 29.
  • the first temperature sensor 10 may be provided in the pipe 33, and the control device 11 may determine the required cooling amount for the reflux exhaust based on the temperature of the reflux exhaust before flowing into the second electric pump P2.
  • a pressure detection unit such as a pressure sensor is provided in the pipe 33, and the control device 11 controls the pressure of the working fluid from the downstream of the expander 31 to the upstream of the second electric pump P2.
  • the required cooling amount for the reflux exhaust may be determined based on the pressure).
  • the first temperature sensor 10 is not provided, and by configuring the control device 11 so as to be able to detect an output request to the engine 5, the control device 11 requests a cooling exhaust amount for the reflux exhaust based on the output request to the engine You may judge Further, the control device 11 may determine the cooling demand for the reflux exhaust by combining the temperature of the reflux exhaust, the temperature of the working fluid, the pressure of the working fluid, the output demand for the engine 5 and the like.
  • the pipe 33 may be provided with a known receiver.
  • the working fluid since the working fluid is suitably liquefied by the receiver, the working fluid having passed through the condenser 32 is suitably discharged by the second electric pump P2, and suitably circulates through the pipes 33 to 42 and the bypass passage 44.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Exhaust Gas After Treatment (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Control Of Turbines (AREA)
PCT/JP2013/063264 2012-05-14 2013-05-13 Dispositif d'utilisation de chaleur perdue Ceased WO2013172293A1 (fr)

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JP2012-110171 2012-05-14
JP2012110171A JP2013238131A (ja) 2012-05-14 2012-05-14 廃熱利用装置

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EP2886820A1 (fr) * 2013-12-23 2015-06-24 Hyundai Motor Company Système de recyclage de la chaleur d'échappement d'un moteur à combustion interne
WO2017021033A1 (fr) * 2015-08-03 2017-02-09 Robert Bosch Gmbh Système de récupération de chaleur d'un moteur à combustion interne et procédé de fonctionnement du système de récupération de chaleur
JP2017101566A (ja) * 2015-11-30 2017-06-08 ダイムラー・アクチェンゲゼルシャフトＤａｉｍｌｅｒ ＡＧ 車両用冷却装置
US20190368383A1 (en) * 2018-03-28 2019-12-05 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Internal combustion engine with evaporative cooling and waste heat utilization

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US9140209B2 (en) * 2012-11-16 2015-09-22 Cummins Inc. Rankine cycle waste heat recovery system
JP6194273B2 (ja) * 2014-04-04 2017-09-06 株式会社神戸製鋼所 排熱回収装置及び排熱回収方法
JP2016014339A (ja) * 2014-07-01 2016-01-28 いすゞ自動車株式会社 廃熱回生システム
KR101755838B1 (ko) * 2015-09-09 2017-07-07 현대자동차주식회사 엔진 예열장치 및 그 예열방법
KR101911139B1 (ko) * 2016-04-28 2018-10-23 재단법인 건설기계부품연구원 건설기계의 페열 회수를 통한 연비 향상 시스템
KR101816021B1 (ko) * 2017-06-09 2018-01-08 한국전력공사 복합 발전장치

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EP2886820A1 (fr) * 2013-12-23 2015-06-24 Hyundai Motor Company Système de recyclage de la chaleur d'échappement d'un moteur à combustion interne
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