WO2014103977A1 - Dispositif d'utilisation de chaleur perdue pour moteur à combustion interne - Google Patents

Dispositif d'utilisation de chaleur perdue pour moteur à combustion interne Download PDF

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Publication number
WO2014103977A1
WO2014103977A1 PCT/JP2013/084405 JP2013084405W WO2014103977A1 WO 2014103977 A1 WO2014103977 A1 WO 2014103977A1 JP 2013084405 W JP2013084405 W JP 2013084405W WO 2014103977 A1 WO2014103977 A1 WO 2014103977A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
combustion engine
internal combustion
working fluid
expander
Prior art date
Application number
PCT/JP2013/084405
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English (en)
Japanese (ja)
Inventor
英文 森
井口　雅夫
榎島　史修
文彦 石黒
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.)
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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 WO2014103977A1 publication Critical patent/WO2014103977A1/fr

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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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 apparatus for an internal combustion engine.
  • Patent Document 1 discloses a waste heat utilization apparatus in which a working fluid circulation pipe in a Rankine cycle circuit is connected in parallel to a plurality of heat exchangers respectively corresponding to a plurality of heat sources for the purpose of recovering waste heat from a plurality of heat sources.
  • EGR exhaust gas recirculation
  • FIG. 6 of Patent Document 1 EGR (exhaust gas recirculation) gas, supply air pressurized by a supercharger, cooling water, and internal combustion engine oil (for example, engine oil) are respectively used.
  • Working fluid circulation pipes are connected in parallel to four heat exchangers used as heat sources.
  • Patent Document 1 since the flow pipe connected to the pump that supplies the working fluid is connected in parallel to the four heat exchangers, each heat exchanger simply has a quarter of the total amount of the working fluid. 1 is supplied. Therefore, compared with the case where all the working fluids are supplied to one heat exchanger, the heat exchange efficiency in each heat exchanger is simply a quarter. Therefore, in the heat exchanger that uses the supply air and the cooling water as heat sources, respectively, although the heat exchanger is also expected to have a cooling effect on the supply air and the cooling water, the configuration of Patent Document 1 provides sufficient cooling. The effect cannot be obtained.
  • This invention aims at improving the heat exchange efficiency in heat sources other than pressurized air, improving the cooling function of the pressurized air sent out from a supercharger.
  • An apparatus for using waste heat of an internal combustion engine for solving the above problems includes an air supply circuit having a supercharger that supplies pressurized air to the internal combustion engine, an expander, and a pump that supplies working fluid to the expander.
  • a Rankine cycle circuit having a charge air heat exchanger configured to exchange heat between the pressurized air and the working fluid, between the pump and the expander in the Rankine cycle circuit; and A charge air heat exchanger disposed between the supercharger and the internal combustion engine in the air supply circuit, and configured to perform heat exchange between the exhaust gas discharged from the internal combustion engine and the working fluid.
  • An exhaust gas heat exchanger, and a recirculation gas heat exchanger configured to exchange heat between the exhaust gas recirculated to the internal combustion engine and the working fluid.
  • the discharge gas heat exchanger and the recirculation gas heat exchanger are arranged in parallel between the charge air heat exchanger and the expander in the Rankine cycle circuit.
  • the charge air heat exchanger can perform heat exchange using all of the working fluid sent from the pump of the Rankine cycle circuit, it is sent from the supercharger.
  • the pressurized air to be cooled can be sufficiently cooled. Therefore, it is not necessary to provide a special air-type heat supply heat exchanger.
  • heat exchange is performed downstream of the charge air heat exchanger with both the exhaust gas discharged to the outside and the exhaust gas to be recirculated, so that the heat of the exhaust gas can be passed to the Rankine cycle circuit without excess, and the heat exchange efficiency Is expensive.
  • heat exchange with each exhaust gas is performed in parallel rather than in series, there is little reduction in heat exchange efficiency due to mutual influence.
  • a flow pipe that connects the charge air heat exchanger, the discharge gas heat exchanger, the recirculation gas heat exchanger, and the expander and through which a working fluid flows is further provided.
  • the flow pipe is preferably branched inside the charge air heat exchanger and joined outside the charge air heat exchanger. According to the waste heat utilization apparatus for an internal combustion engine, in the charge air heat exchanger, in order to divert the working fluid before being heated to the maximum by pressurized air, in the heat exchanger provided in the diverted flow path The heat exchange efficiency can be maintained at a high level.
  • the Rankine cycle circuit includes the working fluid between the charge air heat exchanger and the discharge gas heat exchanger, and the working fluid downstream of the expander. It is preferable to provide an internal heat exchanger that exchanges heat with each other. According to the waste heat utilization apparatus for an internal combustion engine, since the working fluid sent from the expander can be cooled by the internal heat exchanger, the load for cooling the working fluid in the condenser can be reduced.
  • a flow rate adjustment valve configured to adjust a ratio between a flow rate of the working fluid flowing through the recirculation gas heat exchanger and a flow rate of the working fluid flowing through the discharge gas heat exchanger It is preferable to further provide.
  • the waste heat utilization apparatus for an internal combustion engine when the temperature of the recirculation gas flowing out from the recirculation gas heat exchanger is high, a large amount of working fluid is caused to flow through the recirculation gas heat exchanger, The temperature can be lowered. For this reason, it is easy to keep the temperature of the recirculation gas supplied to the internal combustion engine appropriately.
  • the flow rate adjusting valve is provided between the charge air heat exchanger and the discharge gas heat exchanger. According to the waste heat utilization apparatus for an internal combustion engine, the maximum flow rate of the working fluid supplied to the recirculation gas heat exchanger can be increased.
  • the invention of the present application can enhance the cooling function of the pressurized air sent from the supercharger, and can improve the heat exchange efficiency in a heat source other than the pressurized air.
  • the first embodiment shown in FIG. 1 shows a waste heat utilization device in an internal combustion engine 1 such as a gasoline engine or a diesel engine mounted on a vehicle, for example.
  • the internal combustion engine 1 includes a coolant circulation circuit 2 that cools the internal combustion engine 1, a discharge gas circuit 3 that discharges exhaust gas from the internal combustion engine 1 to the outside, and an exhaust gas that is branched from the discharge gas circuit 3 and recirculated to the internal combustion engine 1.
  • a flowing recirculation gas circuit 4 and an air supply circuit 5 for supplying pressurized air to the internal combustion engine 1 are provided.
  • the internal combustion engine 1 is connected to a Rankine cycle circuit 6 that circulates a working fluid including a refrigerant and lubricating oil in order to use waste heat.
  • the cooling water circulation circuit 2 includes a circulation pipe 7 for cooling water circulated through the internal combustion engine 1, a cooling water pump 8 and a radiator 9 disposed in the circulation pipe 7.
  • the cooling water pump 8 supplies cooling water to the internal combustion engine 1 to cool the internal combustion engine 1.
  • the cooling water heated by the internal combustion engine 1 is cooled by the radiator 9.
  • the cooled cooling water is supplied again to the internal combustion engine 1 by the cooling water pump 8 and circulates to cool the internal combustion engine 1.
  • the discharge gas circuit 3 has a discharge gas pipe 10 having one end connected to the internal combustion engine 1.
  • the other end of the discharge gas pipe 10 is provided in the Rankine cycle circuit 6 and opens to the atmosphere outside the vehicle through a discharge gas heat exchanger 11 that performs heat exchange using the discharge gas and a muffler (not shown).
  • the recirculation gas pipe 12 of the recirculation gas circuit 4 is branched from the discharge gas circuit 3.
  • the recirculation gas pipe 12 is provided in the Rankine cycle circuit 6, extends through a recirculation gas heat exchanger 13 that performs heat exchange using the recirculation gas, and is connected to the air supply pipe 14 of the air supply circuit 5.
  • a recirculation gas which is a part of the exhaust gas is supplied from the supply pipe 14 to the internal combustion engine 1.
  • the air supply circuit 5 includes a supercharger 15 to which an air supply pipe 14 is connected.
  • the supercharger 15 includes a turbine and a compressor (not shown). In the supercharger 15, the turbine is rotated by the exhaust gas supplied from the discharge gas pipe 10 of the discharge gas circuit 3, the compressor is rotated by the rotation of the turbine, and the air sucked from the atmosphere is compressed by the suction pipe 16. The pressurized air is sent out to the air supply pipe 14.
  • the air supply pipe 14 is provided in the Rankine cycle circuit 6 for cooling the pressurized air whose temperature has been raised by compression, and passes through a supply air heat exchanger 17 that performs heat exchange using the pressurized air (supply air). It extends and is connected to the internal combustion engine 1.
  • the Rankine cycle circuit 6 includes a main flow pipe 18 as a flow pipe through which a working fluid flows, a first diversion pipe 18A, a second diversion pipe 19, a pump 20 that is mechanically or electrically driven to supply the working fluid, An air heat exchanger 17, a recirculation gas heat exchanger 13, an expander 21, an internal heat exchanger 22, a condenser 23 and a receiver 24 are provided.
  • the main flow pipe 18 is branched into a first diversion pipe 18 ⁇ / b> A and a second diversion pipe 19 inside the charge air heat exchanger 17.
  • the recirculation gas heat exchanger 13 is connected to the first diversion pipe 18A, and the internal heat exchanger 22 and the discharge gas heat exchanger 11 are connected to the second diversion pipe 19 in this order.
  • the first branch pipe 18 ⁇ / b> A and the second branch pipe 19 are joined together on the upstream side of the expander 21 outside the charge air heat exchanger 17.
  • a generator 25 is connected to the expander 21.
  • the working fluid flowing through the pipe 18 is used as a heat source for the Rankine cycle circuit 6.
  • the cooling water circulation circuit 2, the air supply circuit 5, and the Rankine cycle circuit 6 start to operate.
  • the working fluid supplied from the pump 20 flows through the main flow pipe 18, and the entire flow rate is supplied to the charge air heat exchanger 17.
  • the supply air heat exchanger 17 heat exchange is performed between the working fluid flowing through the main flow pipe 18 and the pressurized air sent from the supercharger 15 and flowing through the supply pipe 14, so that the pressurized air is desired.
  • the working fluid is heated while being cooled to a temperature.
  • the cooled pressurized air is supplied to the internal combustion engine 1 through the air supply pipe 14.
  • the working fluid heated by the charge air heat exchanger 17 is supplied to the recirculation gas heat exchanger 13 through the first branch pipe 18A branched from the main flow pipe 18.
  • the recirculation gas flowing through the recirculation gas pipe 12 is hotter than the pressurized air supplied from the supercharger 15. For this reason, even if it is the working fluid heated by the supply air heat exchanger 17, high heat exchange efficiency is maintained in the recirculation gas heat exchanger 13, and a working fluid can be heated further.
  • the working fluid heated by the recirculation gas heat exchanger 13 flows through the first branch pipe 18 ⁇ / b> A toward the expander 21. Further, the recirculation gas that has passed through the recirculation gas heat exchanger 13 joins from the recirculation gas pipe 12 to the air supply pipe 14 and is supplied to the internal combustion engine 1 together with the pressurized air.
  • the second branch pipe 19 is branched from the main flow pipe 18 at an intermediate position inside the supply air heat exchanger 17, the second branch pipe 19 is heated to a high temperature in the supply air heat exchanger 17.
  • the working fluid divided from the main flow pipe 18 is supplied to the internal heat exchanger 22 through the second flow pipe 19.
  • the high-temperature working fluid sent from the expander 21 is supplied to the internal heat exchanger 22 by the main flow pipe 18. For this reason, heat exchange is performed between the high-temperature working fluid flowing through the main flow pipe 18 and the low-temperature working fluid flowing through the second branch pipe 19, and the working fluid in the main flow pipe 18 is cooled and the second branch pipe 19 is cooled. The working fluid is heated.
  • the working fluid in the main flow pipe 18 cooled in the internal heat exchanger 22 is supplied to the condenser 23 and further cooled. Therefore, in the condenser 23, the load for cooling the working fluid is greatly reduced.
  • the working fluid in the second branch pipe 19 heated in the internal heat exchanger 22 is supplied to the discharge gas heat exchanger 11.
  • the exhaust gas supplied to the discharge gas heat exchanger 11 by the discharge gas pipe 10 is extremely high in temperature compared to the temperature of the working fluid sent from the expander 21. For this reason, heat exchange is efficiently performed between the exhaust gas flowing through the discharge gas pipe 10 and the working fluid flowing through the second branch pipe 19, and the working fluid is heated.
  • the exhaust gas flowing in the discharge gas pipe 10 and the recirculation gas flowing in the recirculation gas pipe 12 are at the same high temperature.
  • the discharge gas heat exchanger 11 and the recirculation gas heat exchanger 13 are provided in series, the working fluid is sufficiently heated by the heat exchanger that performs heat exchange with the working fluid first. For this reason, the temperature difference between the working fluid and the exhaust gas or the recirculation gas in the heat exchanger where heat exchange is performed later becomes small, and heat exchange cannot be performed sufficiently.
  • the discharge gas heat exchanger 11 and the recirculation gas heat exchanger 13 are provided in parallel, a high temperature difference is set between the exhaust gas and the recirculation gas and each working fluid.
  • the discharge gas heat exchanger 11 and the recirculation gas heat exchanger 13 can each obtain high heat exchange efficiency.
  • the working fluid heated in the discharge gas heat exchanger 11 joins the working fluid flowing through the first diversion pipe 18A because the second diversion pipe 19 is connected to the first diversion pipe 18A.
  • the working fluid heated and vaporized in the supply air heat exchanger 17 and the heat exchangers 22, 11, 13 is supplied to the expander 21 through the first branch pipe 18 ⁇ / b> A.
  • the expander 21 generates a mechanical driving force by the expansion of the working fluid and drives the generator 25 connected to the expander 21.
  • the working fluid sent out from the expander 21 is cooled in the internal heat exchanger 22 and the condenser 23 to be condensed and liquefied.
  • the condensed working fluid is separated into two layers of gas and liquid at the receiver 24, and only the liquefied working fluid is introduced into the pump 20.
  • the main pipe 18 passes through the supply air heat exchanger 17 without branching, and instead of the second branch pipe 19, as shown by a virtual line in FIG.
  • a second branch pipe 19A branched from the main flow pipe 18 may be provided.
  • the working fluid introduced into the second branch pipe 19 ⁇ / b> A is in a heated state as compared with the case where the working fluid is branched from the main flow pipe 18 inside the charge air heat exchanger 17.
  • heat exchange can be performed if there is a temperature difference between the heat source of the internal heat exchanger 22 or the discharge gas heat exchanger 11 provided in the second branch pipe 19A and the working fluid.
  • FIG. 2 shows the second embodiment.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
  • the discharge gas heat exchanger 11 using the exhaust gas flowing through the discharge gas pipe 10 as a heat source is provided in the second branch pipe 26 branched from the main flow pipe 18 inside the charge air heat exchanger 17. It has been.
  • the second diversion pipe 26 that has passed through the discharge gas heat exchanger 11 is connected to the first diversion pipe 18A on the upstream side of the expander 21, and the working fluid in the second diversion pipe 26 becomes the working fluid in the first diversion pipe 18A. Have joined.
  • the exhaust gas which is a heat source, and the recirculated gas are in the same high temperature state.
  • the discharge gas heat exchanger 11 and the recirculation gas heat exchanger 13 in parallel, it is possible to make a high temperature difference between the exhaust gas and the recirculation gas and each working fluid, and the discharge gas heat exchanger 11 and Each of the recirculation gas heat exchangers 13 can obtain high heat exchange efficiency.
  • the second branch pipe 26 branched from the main flow pipe 18 inside the charge air heat exchanger 17, as shown in FIG. 3, it branches from the main flow pipe 18 after passing through the supply air heat exchanger 17.
  • a second branch pipe 26A may be provided. Since the second branch pipe 26A branches outside the supply air heat exchanger 17, the outlet of the supply air heat exchanger 17 becomes one place, the structure can be simplified, and the amount of heat exchange with the supply air As a result, the temperature of the supply air can be lowered.
  • the flow rate of the working fluid flowing through the recirculation gas heat exchanger 13 and the working fluid flowing through the discharge gas heat exchanger 11 are disposed in the first branch pipe 18A or the second branch pipe 26A on the downstream side of the charge air heat exchanger 17.
  • a flow rate adjusting valve 27 that adjusts the ratio to the flow rate may be provided.
  • the flow regulating valve 27 is provided in the second branch pipe 26A.
  • the flow regulating valve 27 is provided in the first branch pipe 18A, at least a constant amount of the working fluid always flows to the discharge gas heat exchanger 11, and the maximum amount of the working fluid flowing to the recirculation gas heat exchanger 13 decreases. . Therefore, from the viewpoint of securing the flow rate of the working fluid to the recirculation gas heat exchanger 13, it is desirable to provide the flow rate adjustment valve 27 in the second branch pipe 26A.
  • the present invention is not limited to the configuration of each of the embodiments described above, and various modifications are possible within the scope of the gist of the present invention, and can be implemented as follows.
  • the cooling water circulation circuit 2 is connected to the first branch pipe 18A or the second branch pipes 19, 19A, 26, 26A on the downstream side of the charge air heat exchanger 17.
  • a heat exchanger using cooling water as a heat source may be provided.
  • the discharge gas heat exchanger 11 is provided in the first branch pipe 18A, and the recirculation gas heat exchanger 13 is provided in the second branch pipes 19 and 26. You may do it.
  • the working fluid circulation pipe is not limited to the two rows of the first branch pipe 18A and the second branch pipes 19, 19A, 26, and 26A. May be arranged in parallel.
  • the first and second embodiments can also be implemented in an internal combustion engine installed in a machine other than a vehicle.

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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)

Abstract

L'invention porte sur un dispositif d'utilisation de chaleur perdue pour un moteur à combustion interne, qui comporte : un circuit d'alimentation en air ayant un compresseur de suralimentation qui fournit de l'air mis sous pression au moteur à combustion interne ; un circuit à cycle de Rankine ayant un détendeur et une pompe qui fournit un fluide de travail au détendeur ; un échangeur de chaleur d'alimentation en air construit de manière à échanger de la chaleur entre l'air mis sous pression et le fluide de travail et agencé entre la pompe et le détendeur dans le circuit à cycle de Rankine, ainsi qu'entre le compresseur de suralimentation dans le circuit d'alimentation en air et le moteur à combustion interne ; un échangeur de chaleur de gaz rejeté construit de manière à échanger de la chaleur entre le fluide de travail et le gaz d'échappement rejeté à l'extérieur par le moteur à combustion interne ; et un échangeur de chaleur de gaz remis en circulation construit de manière à échanger de la chaleur entre le fluide de travail et le gaz d'échappement qui a été remis en circulation dans le moteur à combustion interne. L'échangeur de chaleur de gaz rejeté et l'échangeur de chaleur de gaz remis en circulation sont disposés en parallèle entre le détendeur et l'échangeur de chaleur d'alimentation en air dans le circuit à cycle de Rankine.
PCT/JP2013/084405 2012-12-27 2013-12-24 Dispositif d'utilisation de chaleur perdue pour moteur à combustion interne WO2014103977A1 (fr)

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JP2012284149A JP2016033331A (ja) 2012-12-27 2012-12-27 内燃機関の廃熱利用装置
JP2012-284149 2012-12-27

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016056611A1 (fr) * 2014-10-09 2016-04-14 サンデンホールディングス株式会社 Dispositif de récupération de chaleur
JP2016061199A (ja) * 2014-09-17 2016-04-25 株式会社神戸製鋼所 エネルギー回収装置及び圧縮装置並びにエネルギー回収方法
WO2020126837A1 (fr) * 2018-12-19 2020-06-25 Robert Bosch Gmbh Cycle thermodynamique servant à la production d'air comprimé

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6503510B2 (ja) 2016-02-24 2019-04-17 日立オートモティブシステムズ株式会社 シリンダ装置およびその製造方法

Citations (3)

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Publication number Priority date Publication date Assignee Title
JP2008008224A (ja) * 2006-06-29 2008-01-17 Denso Corp 廃熱利用装置
JP2009236014A (ja) * 2008-03-27 2009-10-15 Isuzu Motors Ltd 廃熱回収装置
JP2011012625A (ja) * 2009-07-03 2011-01-20 Mitsubishi Electric Corp 排熱回生システムおよびその制御方法

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008008224A (ja) * 2006-06-29 2008-01-17 Denso Corp 廃熱利用装置
JP2009236014A (ja) * 2008-03-27 2009-10-15 Isuzu Motors Ltd 廃熱回収装置
JP2011012625A (ja) * 2009-07-03 2011-01-20 Mitsubishi Electric Corp 排熱回生システムおよびその制御方法

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016061199A (ja) * 2014-09-17 2016-04-25 株式会社神戸製鋼所 エネルギー回収装置及び圧縮装置並びにエネルギー回収方法
WO2016056611A1 (fr) * 2014-10-09 2016-04-14 サンデンホールディングス株式会社 Dispositif de récupération de chaleur
JP2016075263A (ja) * 2014-10-09 2016-05-12 サンデンホールディングス株式会社 廃熱回収装置
CN107110066A (zh) * 2014-10-09 2017-08-29 三电控股株式会社 废热回收装置
US10378391B2 (en) 2014-10-09 2019-08-13 Sanden Holdings Corporation Waste heat recovery device
WO2020126837A1 (fr) * 2018-12-19 2020-06-25 Robert Bosch Gmbh Cycle thermodynamique servant à la production d'air comprimé

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