US20060254276A1 - Rankine cycle system - Google Patents

Rankine cycle system Download PDF

Info

Publication number
US20060254276A1
US20060254276A1 US11/373,134 US37313406A US2006254276A1 US 20060254276 A1 US20060254276 A1 US 20060254276A1 US 37313406 A US37313406 A US 37313406A US 2006254276 A1 US2006254276 A1 US 2006254276A1
Authority
US
United States
Prior art keywords
expander
rotational speed
evaporator
temperature
water supply
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.)
Abandoned
Application number
US11/373,134
Other languages
English (en)
Inventor
Akihisa Sato
Koji Fukutomi
Kensaku Yamamoto
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.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
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 Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Assigned to HONDA MOTOR CO., LTD. reassignment HONDA MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YAMAMOTO, KENSAKU, FUKUTOMI, KOJI, SATO, AKIHISA
Publication of US20060254276A1 publication Critical patent/US20060254276A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • 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

Definitions

  • the present invention relates to a Rankine cycle system that includes an evaporator for heating a liquid-phase working medium with thermal energy of an exhaust gas of an engine so as to generate a gas-phase working medium, and a displacement type expander for converting the thermal energy of the gas-phase working medium generated by the evaporator into mechanical energy.
  • Japanese Utility Model Registration Publication No. 2-38162 discloses an arrangement in which the temperature of steam generated by waste heat from a boiler using exhaust gas of an engine rotating at a constant speed as a heat source is compared with a target temperature.
  • a water supply signal obtained from this deviation is used in feedback control of the amount of water supplied to the waste heat once-through boiler, a feedforward signal obtained by correcting with steam pressure a degree of throttle opening signal of the engine is added to the above-mentioned feedback signal, thus compensating for variation in the load of the engine and thereby improving the precision of control.
  • the arrangement provided in WO03/031775 discloses steam temperature that is controlled by manipulating the amount of water supplied to an evaporator of a Rankine cycle system.
  • the steam pressure is controlled by manipulating the rotational speed of a displacement type expander into which steam flows.
  • the steam temperature and the steam pressure can be controlled by a conventional technique to a degree corresponding to load variation accompanying normal acceleration/deceleration after an engine and a Rankine cycle system are warmed up.
  • a conventional technique to a degree corresponding to load variation accompanying normal acceleration/deceleration after an engine and a Rankine cycle system are warmed up.
  • there are unstable states involving the effect of phase changes of a working medium within a system in going from water to saturated steam and then to superheated steam, and control of the amount of water supplied until the temperature gradient of the interior of the evaporator becomes stable.
  • the present invention has been accomplished under the above-mentioned circumstances, and it is an object of an embodiment thereof to effectively utilize thermal energy remaining in the interior of an evaporator when an engine stops and to allow a Rankine cycle system to make a transition to a stable stopped state.
  • a Rankine cycle system including an evaporator for heating a liquid-phase working medium with thermal energy of exhaust gas of an engine so as to generate a gas-phase working medium with a displacement type expander for converting the thermal energy of the gas-phase working medium generated by the evaporator into mechanical energy.
  • a temperature control means is provided for manipulating the amount of liquid-phase working medium supplied to the evaporator so that the temperature of the gas-phase working medium supplied from the evaporator to the expander coincides with a target temperature.
  • Pressure control means are provided for manipulating the rotational speed of the expander by changing a load of the expander so that the pressure of the gas-phase working medium supplied from the evaporator to the expander coincides with a target pressure.
  • the temperature control means and/or the pressure control means continues to control the amount of liquid-phase working medium supplied to the evaporator and/or the rotational speed of the expander in set ranges at least in a state in which the engine has stopped and the thermal energy of the exhaust gas has disappeared.
  • the temperature control means manipulates the amount of liquid-phase working medium supplied to the evaporator in order to make the temperature of the gas-phase working medium coincide with the target temperature
  • the pressure control means manipulates the rotational speed by changing the load of the expander in order to make the pressure of the gas-phase working medium coincide with the target pressure
  • the temperature control means continues to supply the liquid-phase working medium to the evaporator until the temperature of the gas-phase working medium decreases to at least a temperature at which the expander does not generate an output.
  • the temperature control means continues to supply the liquid-phase working medium to the evaporator until the temperature of the gas-phase working medium decreases to the temperature at which the expander does not generate an output. Therefore, it is possible to use the thermal energy remaining in the evaporator efficiently to the very end.
  • the pressure control means continues to control the rotational speed of the expander until the pressure of the gas-phase working medium decreases to at least a pressure at which the expander does not generate an output.
  • the pressure control means continues to control the rotational speed of the expander until the pressure of the gas-phase working medium decreases to the pressure at which the expander does not generate an output. Therefore, it is possible to use the thermal energy remaining in the evaporator efficiently to the very end.
  • the pressure control means when the rotational speed of the expander decreases to a set rotational speed, the pressure control means maintains the set rotational speed; and when the expander attains a state in which no output is generated, the pressure control means stops controlling the rotational speed of the expander and allows the expander to rotate freely in a non-load state.
  • the pressure control means when the rotational speed of the expander decreases to the set rotational speed, the pressure control means maintains this set rotational speed; and when the expander attains a state in which no output is generated the pressure control means stops controlling the rotational speed of the expander and allows it to rotate freely in a non-load state. Therefore, it is possible to recover energy by allowing the expander to rotate at a stable rotational speed while inhibiting a rapid increase in the rotational speed of the expander due to the thermal energy remaining in the evaporator, and to allow the Rankine cycle system to make a smooth transition to a stable stopped state while inhibiting a rapid increase in the rotational speed of the expander due to the thermal energy remaining in the evaporator.
  • FIG. 1 is a diagram showing the overall arrangement of a Rankine cycle system
  • FIG. 2 is a layout diagram of the Rankine cycle system
  • FIG. 3 is a control block diagram of temperature control means
  • FIG. 4 is a detail of part A in FIG. 3 ;
  • FIG. 5 is a control block diagram of pressure control means
  • FIG. 6 is a detail of part B in FIG. 5 ;
  • FIG. 7 is a diagram for explaining a method for estimating the internal density of an evaporator
  • FIG. 8 is a graph showing the relationship between optimum steam temperature and maximum efficiency of an evaporator and an expander
  • FIG. 9 is a diagram showing a map in which a target steam pressure is looked up from steam energy and steam temperature
  • FIG. 10 is a time chart for explaining control in a case in which the internal density of the evaporator is normal when an ignition switch is turned ON;
  • FIG. 11 is a time chart for explaining control in a case in which the interior of the evaporator is empty when the ignition switch is turned ON;
  • FIG. 12 is a time chart for explaining control in a case in which the interior of the evaporator is full of water when the ignition switch is turned ON;
  • FIG. 13 is a time chart for explaining control when the ignition switch is turned OFF.
  • FIG. 14 is a time chart for explaining conventional control when an ignition switch is turned OFF.
  • FIG. 1 shows the overall arrangement of a Rankine cycle system R to which the present invention is applied.
  • the Rankine cycle system R recovers thermal energy of exhaust gas of an engine E and converts it into mechanical energy.
  • the Rankine cycle system R includes an evaporator 11 , an expander 12 , a condenser 13 , and a water supply pump 14 .
  • the evaporator 11 heats water with the exhaust gas discharged by the engine E so as to generate high temperature, high pressure steam.
  • the expander 12 is operated by the high temperature, high pressure steam generated by the evaporator 11 so as to generate mechanical energy.
  • the condenser 13 cools decreased temperature, decreased pressure steam that has completed work in the expander 12 so as to turn it back into water.
  • the water supply pump 14 pressurizes water discharged from the condenser 13 , and supplies it to the evaporator 11 again.
  • an open/close valve 15 for cutting off the supply of water is disposed between the evaporator 11 and the water supply pump 14
  • an open/close valve 16 for cutting off the supply of steam is disposed between the evaporator 11 and the expander 12 .
  • a motor/generator 17 is connected to the expander 12 , and the rotational speed of the expander 12 is controlled by regulating a load of the motor/generator 17 .
  • a Rankine controller Cr controls, based on a signal such as ON/OFF of an ignition switch, a fuel injection quantity Ti, or an engine rotational speed Ne, the rotational speed of a motor 18 for driving the water supply pump 14 , the load of the motor/generator 17 , and opening/closing of the two open/close valves 15 and 16 .
  • FIG. 3 shows the arrangement of temperature control means 21 included in the Rankine controller Cr.
  • the temperature control means 21 includes feedforward water supply amount calculation means 22 , feedback water supply amount calculation means 23 , water supply amount control changeover means 24 , and rotational speed calculation means 25 .
  • the feedforward water supply amount calculation means 22 calculates a feedforward water supply amount for the evaporator 11 from the engine rotational speed Ne, the fuel injection quantity Ti, and the exhaust gas temperature of the engine E.
  • the feedback water supply amount calculation means 23 calculates a feedback water supply amount by multiplying a deviation of the steam temperature at the exit of the evaporator 11 from a target steam temperature at the entrance of the expander 12 by a predetermined gain.
  • the water supply amount control changeover means 24 changes the control of the water supply amount for the evaporator 11 according to the internal density of the evaporator 11 when the ignition switch of the engine E is turned ON or the internal energy of the evaporator 11 when the ignition switch is turned OFF.
  • the rotational speed calculation means 25 calculates a target rotational speed for the water supply pump 14 from a target water supply amount outputted by the water supply amount control changeover means 24 and a steam pressure at the exit of the evaporator 11 , and controls the rotational speed of the motor 18 for driving the water supply pump 14 so that the rotational speed coincides with the target rotational speed.
  • the target steam temperature is determined as follows: as shown in FIG. 8 , the efficiency of the evaporator 11 and the efficiency of the expander 12 of the Rankine cycle system change according to the steam temperature.
  • the efficiency of the evaporator decreases and the efficiency of the expander increases, whereas when the steam temperature decreases, the efficiency of the evaporator increases and the efficiency of the expander decreases. Therefore, there is an optimum steam temperature (a target temperature) at which the overall efficiency of the two becomes a maximum.
  • FIG. 5 shows the arrangement of pressure control means 26 included in the Rankine controller Cr.
  • the pressure control means 26 includes feedforward rotational speed calculation means 27 , feedback rotational speed calculation means 28 , rotational speed control changeover means 29 , and PI feedback term calculation means 30 .
  • the feedforward rotational speed calculation means 27 calculates a feedforward rotational speed based on a target pressure of steam supplied to the expander 12 , a commanded water supply amount, and a steam temperature at the entrance of the expander 12 .
  • the feedback rotational speed calculation means 28 calculates a feedback rotational speed by multiplying a deviation of the steam pressure at the entrance of the expander 12 from the target pressure for steam at the entrance of the expander 12 by a predetermined gain.
  • the target pressure is set by applying the energy (flow rate) and temperature of steam supplied from the evaporator 11 to the expander 12 to the map of FIG. 9 .
  • This target pressure corresponds to a steam pressure at which the expander 12 is operated at maximum efficiency.
  • the rotational speed control changeover means 29 controls the entrance steam pressure of the expander 12 by changing, based on an ON/OFF signal of the ignition switch, a positive torque (a torque in a direction that assists rotation of the expander 12 ) or a negative torque (a torque in a direction that inhibits rotation of the expander 12 ) generated by the motor/generator 17 .
  • the PI feedback term calculation means 30 calculates a target torque for the motor/generator 17 from a deviation of the rotational speed of the motor/generator 17 (that is, the rotational speed of the expander 12 ) from a target rotational speed outputted by the rotational speed control changeover means 29 .
  • the rotational speed of the expander 12 is feedback-controlled at the target rotational speed by generating the above target torque in the motor/generator 17 .
  • the amount of water supplied to the evaporator 11 is temporarily increased simultaneously with an increase in the exhaust gas energy (ref. region j), thus preventing any response lag in the steam temperature.
  • the amount of water supplied is not an amount that would make the evaporator 11 full of water, but is somewhat larger than when normal in order to make an easy transition to a stable control state, and the amount of water supplied is decreased accompanying an increase in the internal density of the evaporator 11 .
  • Torque control of the motor/generator 17 is carried out in the same manner as for the above-mentioned case where the internal density of the evaporator 11 is normal, and starting rotation of the expander 12 at the lowest rotational speed allowing stable rotation enables a smooth start.
  • normal water supply control for the evaporator 11 is started based on a value obtained by adding the feedforward water supply amount and the feedback water supply amount
  • normal rotational speed control is started based on a value obtained by adding the feedforward rotational speed and the feedback rotational speed.
  • the steam pressure is maintained at the target pressure for a predetermined period of time after the ignition switch is turned OFF, the expander 12 is rotated efficiently, and energy can be recovered.
  • the expander 12 is rotated at the lowest rotational speed allowing stable rotation, thus further recovering energy (ref. region o).
  • the regenerative torque of the motor/generator 17 becomes 0, rotation of the expander 12 is stopped, and recovery of energy is completed (ref. region p).
  • the amount of water supplied to the evaporator 11 is controlled based on the rotational speed of the water supply pump 14 , but it may be controlled by the degree of opening of the open/close valve 15 shown in FIG. 2 .
US11/373,134 2005-03-11 2006-03-13 Rankine cycle system Abandoned US20060254276A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005069367A JP2006250075A (ja) 2005-03-11 2005-03-11 ランキンサイクル装置
JP2005-69367 2005-03-11

Publications (1)

Publication Number Publication Date
US20060254276A1 true US20060254276A1 (en) 2006-11-16

Family

ID=37090822

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/373,134 Abandoned US20060254276A1 (en) 2005-03-11 2006-03-13 Rankine cycle system

Country Status (2)

Country Link
US (1) US20060254276A1 (ja)
JP (1) JP2006250075A (ja)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040231330A1 (en) * 2001-10-09 2004-11-25 Shigeru Ibaraki Rankine cycle system and vehicle therewith
US20060168963A1 (en) * 2005-01-24 2006-08-03 Honda Motor Co., Ltd. Rankine cycle system
US20060179841A1 (en) * 2005-01-25 2006-08-17 Honda Motor Co., Ltd. Rankine cycle system
US20080168781A1 (en) * 2005-02-10 2008-07-17 Yuuichi Yakumaru Refrigerating Machine
DE102008017407A1 (de) 2008-04-05 2009-10-08 Daimler Ag Verbrennungskraftmaschine mit einer Wärmerückgewinnungsvorrichtung und Verfahren zum Betrieb derselben
EP2204902A1 (en) * 2007-10-17 2010-07-07 Sanden Corporation Waste heat utilization device for internal combustion engine
EP2249017A1 (en) * 2008-02-14 2010-11-10 Sanden Corporation Waste heat utilization device for internal combustion engine
WO2012085093A1 (de) * 2010-12-24 2012-06-28 Robert Bosch Gmbh Abwärmenutzungsanlage
WO2012085262A1 (de) * 2010-12-24 2012-06-28 Robert Bosch Gmbh Abwärmenutzungsanlage
WO2012110893A1 (en) * 2011-02-17 2012-08-23 Toyota Jidosha Kabushiki Kaisha Abnormality detection apparatus and abnormality detection method for rankine cycle system
WO2012159829A1 (de) * 2011-05-24 2012-11-29 Robert Bosch Gmbh Verfahren und thermodynamischer arbeitskreis zur nutzung der abwärme einer brennkraftmaschine
CN102834679A (zh) * 2010-03-31 2012-12-19 大金工业株式会社 制冷装置
WO2013007530A1 (de) * 2011-07-14 2013-01-17 Avl List Gmbh Verfahren zur regelung einer wärmenutzungsvorrichtung bei einer brennkraftmaschine
WO2014023295A2 (de) 2012-08-06 2014-02-13 Ixetic Bad Homburg Gmbh Vorrichtung zum betreiben eines clausius-rankine-prozess
US20140102103A1 (en) * 2012-10-16 2014-04-17 Hitachi Industrial Equipment Systems Co., Ltd. Gas Compressor
US20150084346A1 (en) * 2013-09-20 2015-03-26 Panasonic Corporation Power generation control system, power generation apparatus, and control method for rankine cycle system
WO2015149916A1 (de) * 2014-03-31 2015-10-08 Mtu Friedrichshafen Gmbh Verfahren zum betreiben eines systems für einen thermodynamischen kreisprozess, steuereinrichtung für ein system für einen thermodynamischen kreisprozess, system, und anordnung aus einer brennkraftmaschine und einem system
US20160376932A1 (en) * 2014-03-12 2016-12-29 Orcan Energy Ag Orc stack-system control
RU2609273C2 (ru) * 2015-06-17 2017-02-01 Общество С Ограниченной Ответственностью "Промвектор" Электрогенерирующий комплекс "СКАТ"
WO2017135865A1 (en) * 2016-02-04 2017-08-10 Scania Cv Ab A method for controlling a waste heat recovery system and such a waste heat recovery system
US20170306804A1 (en) * 2014-10-09 2017-10-26 Sanden Holdings Corporation Waste heat recovery device
US10641203B2 (en) 2017-03-17 2020-05-05 Toyota Jidosha Kabushiki Kaisha Waste heat recovery apparatus and method for controlling waste heat recovery apparatus
US10662894B2 (en) 2016-02-04 2020-05-26 Scania Cv Ab Method for controlling the temperature of a waste heat recovery system and such a waste heat recovery system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4983777B2 (ja) * 2008-11-26 2012-07-25 トヨタ自動車株式会社 エンジンの廃熱回収装置
JP5163620B2 (ja) * 2009-10-15 2013-03-13 株式会社豊田自動織機 廃熱回生システム
JP6637280B2 (ja) * 2015-09-29 2020-01-29 株式会社Ｓｕｂａｒｕ 車両の制御装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4827429A (en) * 1987-06-16 1989-05-02 Westinghouse Electric Corp. Turbine impulse chamber temperature determination method and apparatus
US4969084A (en) * 1988-12-22 1990-11-06 The Babcock & Wilcox Company Superheater spray flow control for variable pressure operation
US5172654A (en) * 1992-02-10 1992-12-22 Century Controls, Inc. Microprocessor-based boiler controller

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4827429A (en) * 1987-06-16 1989-05-02 Westinghouse Electric Corp. Turbine impulse chamber temperature determination method and apparatus
US4969084A (en) * 1988-12-22 1990-11-06 The Babcock & Wilcox Company Superheater spray flow control for variable pressure operation
US5172654A (en) * 1992-02-10 1992-12-22 Century Controls, Inc. Microprocessor-based boiler controller

Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7475541B2 (en) * 2001-10-09 2009-01-13 Honda Giken Kogyo Kabushiki Kaisha Rankine cycle system and vehicle therewith
US20040231330A1 (en) * 2001-10-09 2004-11-25 Shigeru Ibaraki Rankine cycle system and vehicle therewith
US20060168963A1 (en) * 2005-01-24 2006-08-03 Honda Motor Co., Ltd. Rankine cycle system
US20060179841A1 (en) * 2005-01-25 2006-08-17 Honda Motor Co., Ltd. Rankine cycle system
US20080168781A1 (en) * 2005-02-10 2008-07-17 Yuuichi Yakumaru Refrigerating Machine
US7730729B2 (en) * 2005-02-10 2010-06-08 Panasonic Corporation Refrigerating machine
EP2204902A4 (en) * 2007-10-17 2010-11-10 Sanden Corp HEAT EXHAUST DEVICE FOR A COMBUSTION ENGINE
US8959914B2 (en) 2007-10-17 2015-02-24 Sanden Corporation Waste heat utilization device for internal combustion engine
EP2204902A1 (en) * 2007-10-17 2010-07-07 Sanden Corporation Waste heat utilization device for internal combustion engine
US20100205959A1 (en) * 2007-10-17 2010-08-19 Junichiro Kasuya Waste Heat Utilization Device for Internal Combustion Engine
US9441576B2 (en) * 2008-02-14 2016-09-13 Sanden Holdings Corporation Waste heat utilization device for internal combustion engine
US20100307155A1 (en) * 2008-02-14 2010-12-09 Junichiro Kasuya Waste Heat Utilization Device for Internal Combustion Engine
EP2249017A4 (en) * 2008-02-14 2011-03-23 Sanden Corp APPARATUS FOR USING RESIDUAL HEAT FOR INTERNAL COMBUSTION ENGINE
EP2249017A1 (en) * 2008-02-14 2010-11-10 Sanden Corporation Waste heat utilization device for internal combustion engine
DE102008017407A1 (de) 2008-04-05 2009-10-08 Daimler Ag Verbrennungskraftmaschine mit einer Wärmerückgewinnungsvorrichtung und Verfahren zum Betrieb derselben
US8966920B2 (en) 2010-03-31 2015-03-03 Daikin Industries, Ltd. Refrigeration system
CN102834679A (zh) * 2010-03-31 2012-12-19 大金工业株式会社 制冷装置
WO2012085093A1 (de) * 2010-12-24 2012-06-28 Robert Bosch Gmbh Abwärmenutzungsanlage
WO2012085262A1 (de) * 2010-12-24 2012-06-28 Robert Bosch Gmbh Abwärmenutzungsanlage
CN103270254A (zh) * 2010-12-24 2013-08-28 罗伯特·博世有限公司 废热利用设备
CN103370521A (zh) * 2011-02-17 2013-10-23 丰田自动车株式会社 用于朗肯循环系统的异常检测装置和异常检测方法
WO2012110893A1 (en) * 2011-02-17 2012-08-23 Toyota Jidosha Kabushiki Kaisha Abnormality detection apparatus and abnormality detection method for rankine cycle system
WO2012159829A1 (de) * 2011-05-24 2012-11-29 Robert Bosch Gmbh Verfahren und thermodynamischer arbeitskreis zur nutzung der abwärme einer brennkraftmaschine
WO2013007530A1 (de) * 2011-07-14 2013-01-17 Avl List Gmbh Verfahren zur regelung einer wärmenutzungsvorrichtung bei einer brennkraftmaschine
US9482150B2 (en) 2011-07-14 2016-11-01 Avl List Gmbh Method for controlling a heat recovery device in an internal combustion engine
WO2014023295A2 (de) 2012-08-06 2014-02-13 Ixetic Bad Homburg Gmbh Vorrichtung zum betreiben eines clausius-rankine-prozess
US20140102103A1 (en) * 2012-10-16 2014-04-17 Hitachi Industrial Equipment Systems Co., Ltd. Gas Compressor
US10030646B2 (en) 2012-10-16 2018-07-24 Hitachi Industrial Equipment Systems Co., Ltd. Gas compressor
US9347338B2 (en) * 2012-10-16 2016-05-24 Hitachi Industrial Equipment Systems Co., Ltd. Gas compressor
EP2851524B1 (en) * 2013-09-20 2017-05-10 Panasonic Intellectual Property Management Co., Ltd. Power generation control system, power generation apparatus, and control method for rankine cycle system
US20150084346A1 (en) * 2013-09-20 2015-03-26 Panasonic Corporation Power generation control system, power generation apparatus, and control method for rankine cycle system
US9359915B2 (en) * 2013-09-20 2016-06-07 Panasonic Intellectual Property Management Co., Ltd. Power generation control system, power generation apparatus, and control method for rankine cycle system
US20160376932A1 (en) * 2014-03-12 2016-12-29 Orcan Energy Ag Orc stack-system control
US10570782B2 (en) * 2014-03-12 2020-02-25 Orcan Energy Ag ORC stack-system control
WO2015149916A1 (de) * 2014-03-31 2015-10-08 Mtu Friedrichshafen Gmbh Verfahren zum betreiben eines systems für einen thermodynamischen kreisprozess, steuereinrichtung für ein system für einen thermodynamischen kreisprozess, system, und anordnung aus einer brennkraftmaschine und einem system
US20170306804A1 (en) * 2014-10-09 2017-10-26 Sanden Holdings Corporation Waste heat recovery device
US10378391B2 (en) * 2014-10-09 2019-08-13 Sanden Holdings Corporation Waste heat recovery device
RU2609273C2 (ru) * 2015-06-17 2017-02-01 Общество С Ограниченной Ответственностью "Промвектор" Электрогенерирующий комплекс "СКАТ"
WO2017135865A1 (en) * 2016-02-04 2017-08-10 Scania Cv Ab A method for controlling a waste heat recovery system and such a waste heat recovery system
US10662894B2 (en) 2016-02-04 2020-05-26 Scania Cv Ab Method for controlling the temperature of a waste heat recovery system and such a waste heat recovery system
US10662820B2 (en) 2016-02-04 2020-05-26 Scania Cv Ab Method for controlling a waste heat recovery system and such a waste heat recovery system
US10641203B2 (en) 2017-03-17 2020-05-05 Toyota Jidosha Kabushiki Kaisha Waste heat recovery apparatus and method for controlling waste heat recovery apparatus

Also Published As

Publication number Publication date
JP2006250075A (ja) 2006-09-21

Similar Documents

Publication Publication Date Title
US20060254276A1 (en) Rankine cycle system
US20060242961A1 (en) Rankine cycle system
CN103216314B (zh) 利用船舶用废热回收系统的发电方法及其废热回收系统
CN102099560B (zh) 排热再生系统
RU2638890C2 (ru) Способ регулирования системы утилизации тепла в транспортном средстве
US20110203290A1 (en) Control method and control device for exhaust heat recovery system for marine vessel
US7007473B2 (en) Temperature control device of evaporator
US20060201154A1 (en) Rankine cycle system
JP6604355B2 (ja) 廃熱回収装置
CN106555624A (zh) 热能回收系统
KR20170034130A (ko) 마일드 하이브리드 차량의 엔진 냉각 시스템 및 방법
US20060168963A1 (en) Rankine cycle system
US20060086091A1 (en) Rankine cycle apparatus
JP2017145799A (ja) ランキンサイクルシステム
US20060101821A1 (en) Rankine cycle system
US20060179841A1 (en) Rankine cycle system
US20120096857A1 (en) Heat utilization device an operating method
WO2003031775A1 (fr) Dispositif a circuit rankine
JP4939612B2 (ja) 圧縮機の制御装置と制御方法
EP1361342A1 (en) Working medium feed and control device for heat exchanger
JP2006200492A (ja) 車両用ランキンサイクル装置
KR20190022748A (ko) 폐열 회수 시스템 내 팽창기의 회전 속도 제어 방법 및 제어 시스템
JP2019039371A (ja) 廃熱回収装置
JPH0337304A (ja) タービンバイパス装置を備えた蒸気タービン発電プラントの起動方法
JP7334634B2 (ja) エンジンの排熱回収システム

Legal Events

Date Code Title Description
AS Assignment

Owner name: HONDA MOTOR CO., LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SATO, AKIHISA;FUKUTOMI, KOJI;YAMAMOTO, KENSAKU;REEL/FRAME:017627/0933;SIGNING DATES FROM 20060414 TO 20060418

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE