WO2013046853A1 - Système de récupération de la chaleur perdue - Google Patents

Système de récupération de la chaleur perdue Download PDF

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Publication number
WO2013046853A1
WO2013046853A1 PCT/JP2012/067495 JP2012067495W WO2013046853A1 WO 2013046853 A1 WO2013046853 A1 WO 2013046853A1 JP 2012067495 W JP2012067495 W JP 2012067495W WO 2013046853 A1 WO2013046853 A1 WO 2013046853A1
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WO
WIPO (PCT)
Prior art keywords
expander
waste heat
regeneration system
intercooler
refrigerant
Prior art date
Application number
PCT/JP2012/067495
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English (en)
Japanese (ja)
Inventor
小田　和孝
井口　雅夫
英文 森
榎島　史修
文彦 石黒
清 上辻
裕之 武井
Original Assignee
株式会社豊田自動織機
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 株式会社豊田自動織機 filed Critical 株式会社豊田自動織機
Publication of WO2013046853A1 publication Critical patent/WO2013046853A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0437—Liquid cooled heat exchangers
    • F02B29/0443—Layout of the coolant or refrigerant circuit
    • 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • 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

  • This invention relates to a waste heat regeneration system, and more particularly to a waste heat regeneration system using a Rankine cycle.
  • a waste heat regeneration system using a Rankine cycle that recovers mechanical energy (power) from heat related to a vehicle engine has been developed.
  • a general Rankine cycle includes a pump that pumps refrigerant, a heat exchanger that heats the refrigerant by waste heat from the engine, an expander that expands the heated refrigerant to recover mechanical energy, and a post-expansion machine. And a condenser for condensing the refrigerant.
  • Patent Document 1 describes a waste heat utilization apparatus having a Leikin cycle that includes a heat exchanger (intercooler) that heats a refrigerant using heat of intake air compressed by a supercharger as a heat source.
  • the Rankine cycle 200 of this waste heat utilization apparatus includes a heat exchanger 212 that is an intercooler that heats the refrigerant by exchanging heat with the intake air pressurized by the supercharger 40. I have.
  • the refrigerant pumped from the pump 240 absorbs the heat of the intake air compressed by the supercharger 40 as waste heat in the intercooler 212, generates mechanical energy in the process of expanding in the expander 220, and cooler It is condensed in (capacitor) 230.
  • Patent Document 2 describes a waste heat utilization apparatus having a Rankine cycle that includes a heat exchanger (EGR cooler) that heats a refrigerant using heat of the reflux exhaust gas of EGR as a heat source.
  • EGR cooler heat exchanger
  • the present invention has been made to solve such a problem, and even when the expander fails, the compressed intake air supplied to the engine via the intercooler or the EGR cooler or An object of the present invention is to provide a waste heat regeneration system capable of cooling the reflux air.
  • a waste heat regeneration system is configured to pump a working fluid by a pump, heat the pumped working fluid with engine waste heat by a heat exchanger, and heat the working fluid.
  • a waste heat regeneration system having a Rankine cycle device that recovers mechanical energy by an expander and condenses the expanded working fluid by a condenser, and the heat exchanger uses compressed intake air as a heat source.
  • an exhaust gas boiler may be provided as a second heat exchanger between the first branch point and the expander.
  • an exhaust gas boiler may be provided as a second heat exchanger between the intercooler and the first branch point.
  • a controller for controlling the on-off valve is provided, and the controller can also control the on-off valve based on the evaporation pressure of the refrigerant between the pump and the expander.
  • evaporation pressure refers to the pressure from the downstream of the pump to the upstream of the expander.
  • a pressure sensor for measuring the evaporation pressure can be provided on the inlet side of the expander.
  • the waste heat regeneration system according to the present invention can provide a waste heat regeneration system that can cool the intake air of the engine via the intercooler even if the expander fails.
  • FIG. 1 A configuration of a waste heat regeneration system 100 according to Embodiment 1 of the present invention is shown in FIG.
  • the waste heat regeneration system 100 includes a pump 122, an intercooler 124, an expander 126, and a condenser 128, and these constitute a Rankine cycle device. Furthermore, the Rankine cycle device is provided with a receiver 125 and a subcooler 123. Further, the waste heat regeneration system 100 includes a first branch point 131a provided on the downstream side of the intercooler 124 and upstream of the expander 126, and a first branch point 131a provided on the downstream side of the expander 126 and upstream of the condenser 128. It has a bypass flow path 131 that connects the two branch points 131b. Further, an on-off valve 132 is provided in the middle of the bypass flow path 131.
  • the pump 122 pumps a refrigerant as a working fluid in the Rankine cycle device in the waste heat regeneration system 100.
  • the intercooler 124 heats the refrigerant by exchanging heat between intake air to the engine 150 (to be described later) and the refrigerant.
  • a pressure sensor 127 for measuring the evaporation pressure of the refrigerant is attached in the vicinity of the inlet of the expander 126.
  • the “evaporation pressure” refers to the pressure from the downstream of the pump 122 to the upstream of the expander 126.
  • the expander 126 expands the refrigerant that is heated and vaporized in the intercooler 124 to generate mechanical energy (power).
  • the condenser 128 cools and condenses the vaporized refrigerant by exchanging heat with the outside air.
  • the receiver 125 separates the gas-liquid mixed refrigerant into a gas and a liquid, and the refrigerant exiting the receiver 125 is in a saturated liquid state.
  • the subcooler 123 puts the refrigerant in a supercooled state by exchanging heat with the refrigerant in the saturated liquid state and further cooling the refrigerant.
  • the bypass flow path 131 includes a first branch point 131 a provided on the downstream side of the intercooler 124 and upstream of the expander 126, and a second branch point provided on the downstream side of the expander 126 and upstream of the condenser 128. 131b is connected.
  • the on-off valve 132 allows the refrigerant to flow through the bypass flow path 131 when it is open, and prevents the refrigerant from flowing through the bypass flow path 131 when it is closed.
  • the controller 160 is electrically connected to the pressure sensor 127 and the on-off valve 132. The controller 160 opens the on-off valve 132 when the evaporation pressure acquired from the pressure sensor 127 exceeds a certain value.
  • the intake system 141 and the exhaust system 142 of the engine 150 will be described in relation to the intercooler 124.
  • the air sent into the engine 150 is taken in from the intake system 141 and exhausted from the exhaust system 142 as indicated by the arrows in FIG.
  • the intake system 141 is provided with a compressor of the supercharger 144 and an intercooler 124, which are sequentially connected to the intake side of the engine 150.
  • the exhaust system 142 is provided with a turbine of a supercharger 144 and a muffler 146.
  • the supercharger 144 is driven by the exhaust force of the exhaust gas flowing through the exhaust system 142 to compress the intake air that is taken into the engine 150 through the intake system 141.
  • the intercooler 124 cools the intake air pressurized by the supercharger 144 and having a high temperature by heat exchange with the refrigerant flowing in the Rankine cycle device in the waste heat regeneration system 100.
  • the pump 122 is driven by a driving source (not shown), and the refrigerant is pumped toward the downstream side of the pump 122.
  • the refrigerant pumped from the pump 122 absorbs heat from the intake air sent from the intake system 141 to the engine 150 in the process of flowing through the intercooler 124 and becomes high-temperature gas.
  • the evaporating pressure of the refrigerant that has become a high-temperature gas is measured by the pressure sensor 127.
  • the evaporation pressure measured by the pressure sensor 127 is transmitted to the controller 160.
  • the controller 160 determines that the expander 126 has failed.
  • the refrigerant heated and vaporized in the intercooler 124 flows into the expander 126 and expands to generate mechanical energy.
  • the refrigerant exiting the expander 126 is cooled and condensed by exchanging heat with the outside air in the condenser 128.
  • the refrigerant exiting the condenser 128 is separated into gas and liquid at the receiver 125.
  • the refrigerant in the saturated liquid state coming out of the receiver 125 flows into the subcooler 123 and is further cooled (supercooled), then sucked into the pump 122 and pumped back toward the intercooler 124 again.
  • the controller 160 keeps the on-off valve 132 open.
  • the refrigerant that has exited the intercooler 124 flows through the bypass passage 131 via the first branch point 131a and flows into the capacitor 128 via the second branch point 131b.
  • the refrigerant cooled and condensed by the condenser 128 flows through the receiver 125, the subcooler 123 and the pump 122, flows into the intercooler 124 again, and cools the intake air that has been compressed to a high temperature.
  • FIG. FIG. 2 shows the configuration of a waste heat regeneration system 200 according to Embodiment 2 of the present invention.
  • the waste heat regeneration system 200 according to the second embodiment is the same as the waste heat regeneration system 100 according to the first embodiment, on the downstream side of the first branch point 131a of the intercooler 124 and the bypass passage 131 and on the upstream side of the expander 126.
  • An exhaust gas boiler 229 is added.
  • the exhaust gas boiler 229 is a second heat exchanger that heats the refrigerant by exchanging heat with the exhaust gas discharged from the engine 150 through the exhaust system 142.
  • the same reference numerals as those in FIG. 1 are the same or similar components, and thus detailed description thereof is omitted.
  • the pump 122 is driven by a drive source (not shown), and the refrigerant is pumped toward the downstream side of the pump 122.
  • the refrigerant pumped from the pump 122 absorbs heat from the intake air sent from the intake system 141 to the engine 150 in the process of flowing through the intercooler 124.
  • the refrigerant that has flowed through the intercooler 124 then flows into the exhaust gas boiler 229 and absorbs heat from the exhaust gas discharged from the engine 150 to the exhaust system 142.
  • the refrigerant that has absorbed heat by the intercooler 124 and the exhaust gas boiler and has become a high-temperature gas is measured for evaporation pressure by the pressure sensor 127. If the evaporation pressure measured by the pressure sensor 127 is equal to or greater than a predetermined value, the controller 160 determines that the expander 126 has failed. When a failure of the expander 126 is not detected, the refrigerant flows into the expander 126 according to normal operation.
  • the controller 160 opens the on-off valve 132.
  • the refrigerant heated by the intercooler 124 flows through the bypass passage 131 without flowing through the exhaust gas boiler 229 and the expander 126.
  • the refrigerant circulates in the Rankine cycle device and continues to cool the intake air to the engine 150 in the intercooler 124.
  • the refrigerant circulates without passing through the exhaust gas boiler 229, thereby reducing the heat absorption amount of the refrigerant as a whole. Therefore, when the refrigerant flows through the intercooler 124, the intake air supplied to the engine 150 can be cooled more efficiently. That is, when the intake air is further cooled, the density of the intake air is increased and the charging efficiency of the engine 150 is also increased.
  • FIG. 3 shows the configuration of a waste heat regeneration system 300 according to Embodiment 3 of the present invention.
  • the waste heat regeneration system 300 according to Embodiment 3 is provided with a bypass passage 331 and an opening / closing valve 332 instead of the bypass passage 131 and the opening / closing valve 132 in the waste heat regeneration system 200 according to Embodiment 2. is there.
  • the bypass flow path 331 communicates the downstream side of the exhaust gas boiler 229 and the upstream side of the expander 126 with the downstream side of the expander 126 and the upstream side of the condenser 128.
  • the on-off valve 332 is attached in the middle of the bypass flow path 331 and is electrically connected to the controller 160.
  • the same reference numerals as those in FIGS. 1 and 2 are the same or similar components, and thus detailed description thereof is omitted.
  • the operation of the waste heat regeneration system 300 according to Embodiment 3 will be described.
  • the operation in which the refrigerant is pumped from the pump 122 and flows through the intercooler 124, the exhaust gas boiler 229, and the pressure sensor 127 is the same as that of the waste heat regeneration system 200 in the second embodiment.
  • the operation after the refrigerant has flowed into the expander 126 is also performed by the waste heat regeneration system 100 in the first embodiment and the waste heat regeneration system 200 in the second embodiment. The operation is the same. Therefore, detailed description of these operations is omitted.
  • the controller 160 opens the on-off valve 332.
  • the refrigerant is heated in the intercooler 124 and the exhaust gas boiler 229, and then flows into the bypass flow path 331 and continues to circulate in the Rankine cycle device without flowing through the expander 126. Therefore, even under the situation where the expander 126 is out of order, the intercooler 124 continues to cool the intake air to the engine 150, and the refrigerant heated in the exhaust gas boiler 229 flows without stagnation. You can continue.
  • the refrigerant does not stay in the exhaust gas boiler 229 and continues to flow through the bypass passage 331. Therefore, there is no possibility that the refrigerant is thermally decomposed and deteriorated because the refrigerant is excessively heated in the exhaust gas boiler 229.
  • FIG. 4 The configuration of a waste heat regeneration system 400 according to Embodiment 4 of the present invention is shown in FIG.
  • the waste heat regeneration system 400 according to the fourth embodiment uses an EGR cooler 424 instead of the intercooler 124 as a heat exchanger in the waste heat regeneration system 100 according to the first embodiment.
  • engine 150 is connected to intake system 441 and exhaust system 442. Further, the intake system 441 and the exhaust system 442 of the engine 150 are provided with an EGR passage 443 having one end connected to the intake system 441 and the other end connected to the exhaust system 442.
  • the EGR cooler 424 is provided in the middle of the EGR passage 443. Specifically, as indicated by the arrows in FIG.
  • the air that is taken in from the intake system 441 and sent to the engine 150 is exhausted from the exhaust system 442 as high-temperature exhaust gas by combustion in the engine 150. .
  • part of the exhaust gas discharged to the exhaust system 442 circulates in the EGR passage 443 as EGR recirculation exhaust.
  • the EGR cooler 424 provided on the EGR passage 443 heat exchange is performed with the refrigerant flowing through the Rankine cycle device using the reflux exhaust of the EGR as a heat source.
  • the recirculated exhaust gas of EGR cooled by heat exchange with the refrigerant in the EGR cooler 424 merges into the intake system 441 from the EGR passage 443 and is sucked into the engine 150 again.
  • the expander 126 fails in the case where the EGR cooler 424 is used as the heat exchanger in the waste heat regeneration system 400, the refrigerant continues to flow to the Rankine cycle device. Therefore, in the EGR cooler 424, heat exchange between the EGR recirculation exhaust and the refrigerant can be performed, and the EGR recirculation exhaust can be continuously cooled. Thus, the recirculation exhaust of EGR continues to be cooled, thereby suppressing an increase in nitrogen oxides in the exhaust gas. Further, since the temperature rise of the entire intake air of the engine 150 is suppressed, the density of the intake air does not decrease.
  • the refrigerant evaporating pressure is measured by the pressure sensor 127 in order to detect the failure of the expander 126.
  • a rotation sensor may be provided in the expander 126 to detect the rotation speed of the output shaft that extracts mechanical energy.
  • the pressure sensor 127 is provided near the inlet of the expander 126, the pressure sensor 127 is not limited to this, and any other location (for example, upstream of the on-off valve 132) may be provided on the downstream side of the pump 122 and upstream of the expander 126. Side).
  • the on-off valves 132 and 332 mounted on the bypass flow paths 131 and 331 are not limited to those controlled by the controller 160.
  • a relief valve may be used that is in an open state and then remains open even when the evaporation pressure decreases.
  • Waste heat regeneration system 124 intercooler, 126 expander, 127 pressure sensor, 128 condenser, 131, 331 bypass flow path, 131a, 331a first branch point, 131b, 331b second branch point, 132 open / close Valve, 150 engine, 160 controller, 229 exhaust gas boiler, 424 EGR cooler

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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)
  • Control Of Turbines (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

L'invention porte sur la récupération de la chaleur perdue. Elle apporte la possibilité de refroidir l'air d'admission comprimé ou le gaz d'échappement mis en recirculation qui sont acheminés à un moteur, à travers un refroidisseur intermédiaire ou un refroidisseur de EGR (recirculation des gaz d'échappement), même lorsqu'un détendeur est brisé. Un système de récupération de la chaleur perdue comportant un dispositif de circuit Rankine comporte un passage d'écoulement en dérivation servant à relier un premier point de piquage placé en aval du refroidisseur intermédiaire ou du refroidisseur de EGR et en amont du détendeur, à un second point de piquage placé en aval du détendeur et en amont d'un condenseur ; et une soupape d'ouverture/fermeture intercalée dans le trajet d'écoulement de dérivation pour établir la communication avec le trajet d'écoulement en dérivation lorsque le détendeur est brisé.
PCT/JP2012/067495 2011-09-26 2012-07-09 Système de récupération de la chaleur perdue WO2013046853A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-209088 2011-09-26
JP2011209088A JP2014231738A (ja) 2011-09-26 2011-09-26 廃熱回生システム

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WO2013046853A1 true WO2013046853A1 (fr) 2013-04-04

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JP2015218635A (ja) * 2014-05-15 2015-12-07 日産自動車株式会社 エンジンの廃熱利用装置
JP2016079881A (ja) * 2014-10-16 2016-05-16 株式会社神戸製鋼所 熱エネルギー回収装置
EP3392590A1 (fr) * 2017-03-23 2018-10-24 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Unité de refroidissement d'air de suralimentation
CN108730069A (zh) * 2018-04-20 2018-11-02 天津大学 一种回收内燃机余热的小型化集成系统及其控制方法
CN109707473A (zh) * 2019-02-12 2019-05-03 郑州欧纳尔冷暖科技有限公司 一种orc循环泵系统
JP2020183732A (ja) * 2019-05-08 2020-11-12 いすゞ自動車株式会社 ランキンサイクルシステム

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Publication number Priority date Publication date Assignee Title
FR3055149B1 (fr) * 2016-08-18 2020-06-26 IFP Energies Nouvelles Circuit ferme fonctionnant selon un cycle de rankine avec un dispositif pour l'arret d'urgence du circuit et procede utilisant un tel circuit
KR101871151B1 (ko) * 2016-12-19 2018-07-02 한국전력공사 폐열회수장치 및 그 제어방법

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JP2001263004A (ja) * 2000-03-16 2001-09-26 Babcock Hitachi Kk ボイラ・タービン蒸気ラインシステム
JP2007239513A (ja) * 2006-03-06 2007-09-20 Hino Motors Ltd Ｅｇｒガスの排熱エネルギを利用した過給機の補助装置
JP2011106302A (ja) * 2009-11-13 2011-06-02 Mitsubishi Heavy Ind Ltd エンジン廃熱回収発電ターボシステムおよびこれを備えた往復動エンジンシステム

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55117054A (en) * 1979-02-22 1980-09-09 Mashiinterumitsukusu Soc Et Method and device for recovering heat energy of supercharged internal combustion engine
JP2001263004A (ja) * 2000-03-16 2001-09-26 Babcock Hitachi Kk ボイラ・タービン蒸気ラインシステム
JP2007239513A (ja) * 2006-03-06 2007-09-20 Hino Motors Ltd Ｅｇｒガスの排熱エネルギを利用した過給機の補助装置
JP2011106302A (ja) * 2009-11-13 2011-06-02 Mitsubishi Heavy Ind Ltd エンジン廃熱回収発電ターボシステムおよびこれを備えた往復動エンジンシステム

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CN104727912A (zh) * 2013-12-23 2015-06-24 现代自动车株式会社 用于回收来自内燃机的废热的系统
JP2015121206A (ja) * 2013-12-23 2015-07-02 現代自動車株式会社 内燃機関の排気熱リサイクルシステム
US9745881B2 (en) 2013-12-23 2017-08-29 Hyundai Motor Company System for recycling exhaust heat from internal combustion engine
JP2015218635A (ja) * 2014-05-15 2015-12-07 日産自動車株式会社 エンジンの廃熱利用装置
JP2016079881A (ja) * 2014-10-16 2016-05-16 株式会社神戸製鋼所 熱エネルギー回収装置
EP3392590A1 (fr) * 2017-03-23 2018-10-24 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Unité de refroidissement d'air de suralimentation
CN108730069A (zh) * 2018-04-20 2018-11-02 天津大学 一种回收内燃机余热的小型化集成系统及其控制方法
CN109707473A (zh) * 2019-02-12 2019-05-03 郑州欧纳尔冷暖科技有限公司 一种orc循环泵系统
JP2020183732A (ja) * 2019-05-08 2020-11-12 いすゞ自動車株式会社 ランキンサイクルシステム

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