WO2004011777A1 - Systeme a cycle de rankine - Google Patents

Systeme a cycle de rankine Download PDF

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Publication number
WO2004011777A1
WO2004011777A1 PCT/JP2003/009222 JP0309222W WO2004011777A1 WO 2004011777 A1 WO2004011777 A1 WO 2004011777A1 JP 0309222 W JP0309222 W JP 0309222W WO 2004011777 A1 WO2004011777 A1 WO 2004011777A1
Authority
WO
WIPO (PCT)
Prior art keywords
steam
expander
pressure
flow rate
working medium
Prior art date
Application number
PCT/JP2003/009222
Other languages
English (en)
Japanese (ja)
Inventor
Akihisa Sato
Shigeru Ibaraki
Original Assignee
Honda Giken Kogyo Kabushiki Kaisha
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 Giken Kogyo Kabushiki Kaisha filed Critical Honda Giken Kogyo Kabushiki Kaisha
Priority to US10/522,063 priority Critical patent/US20060101821A1/en
Priority to AU2003248085A priority patent/AU2003248085A1/en
Priority to EP03771275A priority patent/EP1536105A4/fr
Publication of WO2004011777A1 publication Critical patent/WO2004011777A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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

Definitions

  • the present invention relates to an evaporator that generates a gas-phase working medium by heating a liquid-phase working medium with exhaust gas of an engine, and a positive displacement type that converts heat energy of the gas-phase working medium generated by the evaporator into mechanical energy.
  • a Rankine cycle device comprising the expander.
  • Japanese Unexamined Patent Publication No. 2000-3344585 describes that in a waste heat recovery device that drives a turbine by heating refrigerant vapor of an engine cooling system by waste heat of the engine, the pressure of the cooling path or It describes that the thermal efficiency is improved by optimally controlling the temperature according to the operating state of the engine. Specifically, as the engine speed and the engine load increase, the target value of the cooling path pressure is set lower, and the discharge amount of the refrigerant circulation pump is controlled so that the actual pressure matches the target pressure. I have. In a Rankine cycle device equipped with a positive displacement expander, if the steam pressure at the inlet of the expander matches the target steam pressure (optimum steam pressure), as shown in Fig.
  • the steam pressure at the outlet of the expander Becomes a pressure commensurate with the expansion ratio of the expander, but if the steam pressure at the inlet is too high, excess energy is left in the steam discharged from the outlet of the expander, and energy is wasted. There is. Conversely, if the steam pressure at the inlet is too low, the steam discharged from the outlet of the expander will have a negative pressure. ⁇ There is a problem that the expander performs negative work and reduces efficiency.
  • the present invention has been made in view of the above circumstances, and in a Rankine cycle device, a target pressure of a gas phase working medium at an inlet of an expander is set without changing a supply amount of a liquid phase working medium to an evaporator.
  • the purpose is to precisely control the pressure.
  • an evaporator for heating a liquid-phase working medium with exhaust gas of an engine to generate a gas-phase working medium, and a heat energy of the gas-phase working medium generated by the evaporator
  • the pressure of the gas phase working medium at the inlet of the expander should be matched with the target pressure.
  • the feedforward value was calculated based on the flow rate of the phase working medium and the target pressure, and the difference between the pressure and the target pressure of the gas phase working medium at the inlet of the expander was calculated based on the flow rate of the gas phase working medium.
  • Control means is provided to calculate the feedback value by multiplying the feedback gain, and to control the rotation speed of the expander based on the feedforward value and the addition / subtraction value of the feedback value.
  • Rankine cycle system is proposed which is characterized in that the.
  • the feedforward value is calculated based on the flow rate of the gas-phase working medium at the outlet of the evaporator and the target pressure of the gas-phase working medium at the inlet of the expander, and the feedforward value at the inlet of the expander is calculated.
  • the feedback value is calculated by multiplying the deviation between the pressure of the gas phase working medium and the target pressure by the feedback gain calculated based on the flow rate of the gas phase working medium, and the expansion is performed based on the feedforward value and the addition / subtraction value of the feedback value.
  • Control the rotation speed of the expander compensating that the change characteristics of the pressure of the gas-phase working medium when the rotation speed of the expander changes vary depending on the flow rate of the gas-phase working medium.
  • the pressure of the gas phase working medium at the inlet of the expander can be made to match the target pressure with good responsiveness and high accuracy without changing the supply amount of the liquid phase working medium.
  • the controller 20 in the embodiment corresponds to the control means of the present invention.
  • Fig. 1 is a block diagram of a Rankine cycle device and its control system.
  • Fig. 2 searches for a target steam pressure from steam energy and a target steam temperature.
  • Fig. 3 is a graph showing the relationship between the optimum steam temperature and the maximum overall efficiency of the evaporator and the expander.
  • Fig. 4 is a graph showing the relationship between the inlet pressure and the outlet pressure of the expander.
  • 5A and 5B are graphs showing changes in steam pressure when the rotational speed of the expander is changed in steps, and
  • Figs. 6A and 6B are when the feedback gain is fixed.
  • 7A and 7B are diagrams showing the convergence state of the steam pressure when the feedback gain is variable, and FIG.
  • FIG. 8 is a flowchart of the main routine of the steam pressure control.
  • 9 is a flowchart of the subroutine of step S3 of the main routine
  • FIG. 10 is a flowchart of the subroutine of step S4 of the main routine
  • Figure 12 is a table for retrieving the feedback gain kp from the steam flow Q.
  • Figs. 13 to 16 show a second embodiment of the present invention.
  • Fig. 13 is a block diagram of a Rankine cycle device and its control system.
  • Fig. 14 is a flowchart of a main routine of steam pressure control.
  • 15 is a flowchart of a subroutine of step S34 of the main routine, and FIG.
  • FIG. 16 is a map for retrieving a specific volume V of steam from a steam pressure P and a steam temperature.
  • FIGS. 17 to 20 show a third embodiment of the present invention.
  • FIG. 17 is a block diagram of a Rankine cycle device and its control system.
  • FIG. 18 is a front view of a main routine of steam pressure control.
  • FIG. 19 is a flowchart of a subroutine of step S53 of the main routine
  • FIG. 20 is a flowchart of a subroutine of step S54 of the main routine.
  • FIGS. 21 to 25 show a fourth embodiment of the present invention.
  • FIG. 21 is a block diagram of a Rankine cycle ⁇ / device and its control system
  • FIG. 22 is a flow chart of a main routine of steam pressure control.
  • FIG. 23 is a flowchart of the subroutine of step S72 of the main routine.
  • FIG. 24 is a flowchart of a subroutine of step S73 of the main routine.
  • FIG. 25 is a flowchart of the subroutine of step S73.
  • 15 is a flowchart of a subroutine of step S74.
  • 1 to 12 show a first embodiment of the present invention.
  • the Rankine cycle device for recovering the thermal energy of the exhaust gas from the engine 11 of the vehicle uses a high-temperature and high-pressure gas by heating the liquid-phase working medium (water) with the exhaust gas from the engine 11.
  • An evaporator 1 2 that generates a phase working medium (steam), and a volume that converts the thermal energy of the high-temperature, high-pressure steam generated by the evaporator 1 2 into mechanical energy
  • Type expander 13 condenser 14 that cools steam discharged from expander 13 and condenses it into water
  • tank 15 that stores water discharged from condenser 14, tank
  • a water supply pump 16 for sucking water in 15 and an injector 17 for injecting water sucked by the water supply pump 16 into the evaporator 12 are arranged on a closed circuit.
  • the motor generator 18 connected to the expander 13 is arranged between the engine 11 and the driving wheels, and the motor generator 18 functions as the motor and the output of the engine 11 In addition to assisting the vehicle, when the vehicle decelerates, the motor generator 18 can function as a generator to recover the kinetic energy of the vehicle as electric energy.
  • the motor generator 18 may be connected to the expander 13 as a single unit and have only the function of generating electric energy.
  • the load applied to the expander 13 from the motor generator 18 is adjusted by adjusting the load (power generation amount) of the motor generator 18 to rotate the expander 13. Control the number.
  • the controller 20 has a signal from a steam flow sensor 21 for detecting the steam flow at the outlet of the evaporator 12 and a signal from a steam pressure sensor 22 for detecting the steam pressure at the inlet of the expander 13. And a signal.
  • the controller 20 includes target steam pressure setting means 23 for setting a target steam pressure that is a target value of the steam pressure at the inlet of the expander 13.
  • the target steam pressure setting means 23 retrieves the target steam pressure based on the target steam temperature and the steam energy (steam flow rate).
  • the steam temperature at the outlet of the evaporator 12 is adjusted so that the total efficiency of the evaporator 12 and the expander 13 is maximized (that is, the optimum steam temperature). It is controlled by adjusting the amount of water supplied from 6 to the evaporator 12. That is, as shown in FIG. 3, the efficiency of the evaporator 12 and the efficiency of the expander 13 change depending on the steam temperature.
  • the steam pressure at the inlet of the expander 13 is controlled to the target steam pressure for the following reasons. That is, as shown in FIG. 4, the steam pressure at the inlet of the expander 13 is If the steam pressure matches the target steam pressure, the steam pressure at the outlet of the expander 13 becomes a pressure corresponding to the expansion ratio of the expander 13, but if the inlet steam pressure is too high, the steam from the outlet of the expander 13 will There is a problem that excess energy is left in the discharged steam and energy is wasted. Conversely, if the inlet steam pressure is too low, the steam discharged from the outlet of the expander 13 will have a negative pressure, and there will be a problem that the expander 13 will perform negative work and reduce efficiency. .
  • the load applied to the expander 13 from the motor generator 18 may be adjusted to control the number of revolutions of the expander 13.
  • the steam pressure increases when the rotation speed of the expander 13 is reduced, and conversely, the steam pressure decreases when the rotation speed of the expander 13 is increased.
  • the response of the change in steam pressure changes depending on the steam flow rate, and when the steam flow rate is low, the response is low, and it takes more than 100 seconds for the steam pressure to reach a steady state.
  • the steam flow rate is high, the response becomes high, and it takes less than 10 seconds for the steam pressure to reach a steady state.
  • the pressure difference before and after the injector 17 is detected and the Ti value is controlled so as to match the target water supply amount, or the discharge pressure of the water supply pump 16 is detected, and the rotation speed of the water supply pump 16 is determined. If controlled, the amount of water supplied to the evaporator 12 is kept constant even if the number of revolutions of the expander 13 changes, and the steam temperature at the outlet of the evaporator 11 can be kept at the optimum steam temperature. it can.
  • the gist of the present invention is that the steam pressure at the inlet of the expander 13 is equal to the target steam pressure.
  • the feedback gain In performing feedback control of the number of revolutions of the expander 13 in order to match the feedback gain, the feedback gain must be changed according to the steam flow rate.
  • step S1 of the flowchart of FIG. 8 the steam flow rate Q at the outlet of the evaporator 12 is detected by the steam flow rate sensor 21 in step S1, and in step S2, the inlet of the expander 13 is detected by the steam pressure sensor 22.
  • the feedforward value N FF is set so as to decrease as the steam flow rate Q decreases and the target steam pressure P o increases, and to increase as the steam flow rate Q increases and the target steam pressure P o decreases. ing.
  • step S4 a feedback value N FB of the rotation speed of the expander 13 is calculated. That is, the steam pressure P at the inlet of the expander 13 detected by the steam pressure sensor 22 in step S 21 of the flowchart of FIG. 10 and the target steam pressure P o set by the target steam pressure setting means 23
  • step S23 the gain kp is multiplied by the deviation ⁇ to calculate a feedback value N FB of the rotational speed of the expander 13.
  • step S 5 if the vapor pressure P is a target steam pressure P 0 or more in step S 5, by adding the feedback value N FB to the rotational speed of the feed-forward value N FF of the expander 1 3 Step S 6 To calculate the rotation speed command value N of the expander 13, and if the steam pressure P is lower than the target steam pressure P o in step S5, the feed speed of the rotation speed of the expander 13 is determined in step S7. By subtracting the feedback value N FB from the command value N FF, the rotation speed command value N of the expander 13 is calculated.
  • the steam pressure P at the inlet of the expander 13 is set to the target steam pressure.
  • Good response to P 0 And converges with high accuracy, and as a result, excessive energy remains in the steam discharged from the outlet of the expander 13 or the steam discharged from the outlet of the expander 13 becomes negative pressure.
  • the problem that the expander 13 performs a negative work and the efficiency is reduced can be solved.
  • FIGS. 13 to 16 show a second embodiment of the present invention.
  • the second embodiment does not include the steam flow sensor 21 of the first embodiment (see FIG. 1), and instead has a water supply amount sensor 24 at the inlet side of the evaporator 12. And a steam temperature sensor 25 on the inlet side of the expander 13.
  • the steam flow rate Q is directly detected by the steam flow sensor 21, whereas in the second embodiment, the steam flow rate Q is detected by the steam pressure P detected by the steam pressure sensor 22, and the water supply amount sensor 24.
  • the calculation is performed using the detected feedwater mass flow rate Gw and the steam temperature detected by the steam temperature sensor 25, and other configurations and operations are the same as those of the first embodiment.
  • the operation of the second embodiment will be described with reference to a flowchart. First, in step S31 of the flowchart in FIG.
  • the steam temperature sensor 25 detects the steam temperature T at the inlet of the expander 13 in step S31.
  • the steam pressure P at the inlet of the expander 13 is detected by the steam pressure sensor 22 in step S32, and the mass flow rate Gw of water supply to the evaporator 12 is detected by the water supply amount sensor 24 in step S33. To detect.
  • step S34 the steam flow Q to the expander 13 is calculated without using the steam flow sensor 21. That is, in step S41 of the flow chart of FIG. 15, the specific volume V of steam is searched from the map of FIG. 16 using the steam temperature T and the steam pressure P as parameters. As is evident from Fig. 16, the specific volume V of the steam is set so as to increase as the steam pressure P decreases and the steam temperature T increases. In the following step S42, the steam flow rate Q is calculated by multiplying the specific volume V by the feedwater mass flow rate Gw detected by the feedwater sensor 24.
  • FIG. 17 to FIG. 20 show a third embodiment of the present invention.
  • the third embodiment uses the water supply amount sensor of the second embodiment (see Fig. 13).
  • the temperature controller 26 is provided in the controller 20 instead of the controller 24.
  • the water supply mass flow rate Gw is detected by the water supply amount sensor 24, whereas in the third embodiment, the command water supply mass flow rate G output by the temperature control unit 26 is used.
  • the steam mass flow rate Gs corresponding to the feedwater mass flow rate Gw is calculated, and other configurations and operations are the same as in the second embodiment.
  • step S51 of the flow chart of FIG. 18 the steam temperature T at the inlet of the expander 13 is determined by the steam temperature sensor 25 in step S51. Is detected, the steam pressure P at the inlet of the expander 13 is detected by the steam pressure sensor 22 in step S52, and the steam mass flow rate Gs is calculated in step S53.
  • the temperature control unit 26 sets the commanded feedwater mass flow rate G. This is for compensating for the time delay from when is output to when the evaporator 12 actually generates steam.
  • the steam flow rate Q is calculated in step S54 of the flowchart of FIG.
  • the subroutine of this step S54 is shown in FIG. 20, but the flowchart of FIG. 20 is substantially the same as the flowchart of FIG. 15 of the second embodiment.
  • the example feedwater mass flow Gw has only changed to the steam mass flow Gs, which is substantially the same.
  • FIGS. 21 to 25 show a fourth embodiment of the present invention.
  • the fourth embodiment does not include the steam temperature sensor 25 of the third embodiment (see FIG. 13), and instead, the temperature control unit 26 of the controller 20 issues a command. Feedwater mass flow G. And the command steam temperature T 0 is output.
  • the specific volume map contains the steam temperature T obtained by delaying the command steam temperature ⁇ 0 by the delay filter 2, and the target steam pressure P. Is input, and the specific steam volume V found there is multiplied by the steam mass flow rate G s to calculate the steam flow rate Q.
  • step S71 of the flow chart of FIG. 22 the steam pressure sensor 22 detects the flow at the inlet of the expander 13 at step S71.
  • the steam pressure P is detected, and the steam mass flow rate Gs is calculated in step S72.
  • the flowchart of FIG. 23, which is a subroutine of step S72, is substantially the same as the flowchart of FIG. 19 of the third embodiment, but distinguishes a time constant r from a second time constant 2 described later. The only difference is that the first time constant is set to 1.
  • step S73 the steam flow rate Q is calculated in step S73 of the flowchart of FIG.
  • the subroutine of this step S73 is shown in FIG. 24, and the command steam temperature T output by the temperature control unit 26 in step S91 of the flowchart of FIG. 24. Is delayed in a delay filter 2 to calculate the steam temperature T.
  • step S92 the steam temperature T and the target steam pressure P output by the target steam pressure setting means 23 are calculated. Is applied to the specific volume map to find the specific volume V of steam.
  • step S93 the steam mass flow rate Gs output from the delay filter 1 is multiplied by the steam specific volume V to calculate the steam flow rate Q.
  • the steam flow rate Q is applied to the expander rotational speed table to apply the rotational speed of the expander 13 to the rotational speed of the expander 13.
  • This expander speed table is different from the first to third embodiments in that the target steam pressure P o is not set as a parameter. However, since the target steam pressure P o is applied to the specific volume map in the process of calculating the steam flow rate Q, the target steam pressure ⁇ 0 is consequently taken into account.
  • the feedforward value N FF of the rotation speed of the expander 13 retrieved from the steam flow rate Q is proportional to the steam flow rate Q regardless of the steam temperature and the steam pressure.
  • the working medium is not limited to water (steam), and any other suitable working medium can be employed.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)

Abstract

L'invention concerne un système à cycle de Rankine, dans lequel une valeur aval (NFF) est calculée sur la base du débit (Q) d'un fluide d'actionnement en phase vapeur, à la sortie d'un évaporateur (12), et d'une pression cible (Po) telle que la pression (P) d'un fluide d'actionnement en phase vapeur, à l'entrée d'un détendeur (13) corresponde à une pression cible (Po). Une valeur de réaction (NFB) est calculée en multipliant une valeur d'écart entre la pression (P) d'un fluide d'actionnement en phase vapeur, à l'entrée du détendeur (13) et une pression cible (Po) par gain de réaction (kp) calculée sur la base du débit (Q) du fluide d'actionnement en phase gazeuse précité. La vitesse de rotation du détendeur (13) est réglée sur la base de la valeur ajoutée/soustraite de la valeur aval (NFF) et de la valeur de réaction (NFB). En conséquence, la pression d'un fluide d'actionnement en phase vapeur, à l'entrée d'un détendeur peut être réglée avec précision à une pression cible, sans changer le débit d'alimentation du fluide d'actionnement en phase liquide vers un évaporateur.
PCT/JP2003/009222 2002-07-25 2003-07-22 Systeme a cycle de rankine WO2004011777A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US10/522,063 US20060101821A1 (en) 2002-07-25 2003-07-22 Rankine cycle system
AU2003248085A AU2003248085A1 (en) 2002-07-25 2003-07-22 Rankine cycle system
EP03771275A EP1536105A4 (fr) 2002-07-25 2003-07-22 Systeme a cycle de rankine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002-216425 2002-07-25
JP2002216425A JP3901609B2 (ja) 2002-07-25 2002-07-25 ランキンサイクル装置

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WO2004011777A1 true WO2004011777A1 (fr) 2004-02-05

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US (1) US20060101821A1 (fr)
EP (1) EP1536105A4 (fr)
JP (1) JP3901609B2 (fr)
AU (1) AU2003248085A1 (fr)
WO (1) WO2004011777A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101124386B (zh) * 2005-02-21 2011-11-16 西门子公司 用于计算能量过程和工艺流程过程的方法和装置
CN102748080A (zh) * 2012-07-03 2012-10-24 山东电力研究院 基于主蒸汽压力变化的火电机组负荷控制方法

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4801810B2 (ja) * 2006-05-30 2011-10-26 株式会社デンソー 廃熱利用装置を備える冷凍装置
US7950230B2 (en) 2007-09-14 2011-05-31 Denso Corporation Waste heat recovery apparatus
DE102007062580A1 (de) * 2007-12-22 2009-06-25 Daimler Ag Verfahren zur Rückgewinnung einer Verlustwärme einer Verbrennungskraftmaschine
EP2249017B1 (fr) * 2008-02-14 2013-03-27 Sanden Corporation Dispositif d'utilisation de chaleur résiduelle pour moteur à combustion interne
JP5118578B2 (ja) * 2008-08-20 2013-01-16 サンデン株式会社 内燃機関の廃熱利用装置
DE102010056272A1 (de) * 2010-12-24 2012-06-28 Robert Bosch Gmbh Abwärmenutzungsanlage
JP5609707B2 (ja) * 2011-02-22 2014-10-22 トヨタ自動車株式会社 ランキンサイクルシステムの制御装置
JP5621721B2 (ja) * 2011-06-30 2014-11-12 株式会社豊田自動織機 ランキンサイクル
US20150136381A1 (en) * 2012-04-23 2015-05-21 Toyota Jidosha Kabushiki Kaisha Heat transport device
JP6021637B2 (ja) * 2012-12-28 2016-11-09 三菱重工業株式会社 発電システム、発電方法
SE541953C2 (en) 2016-07-12 2020-01-14 Scania Cv Ab A method for controlling a waste heat recovery system and such a waste heat recovery system
JP2019019797A (ja) * 2017-07-20 2019-02-07 パナソニック株式会社 熱電併給システム及び熱電併給システムの運転方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000345835A (ja) * 1999-06-07 2000-12-12 Nissan Motor Co Ltd 内燃機関

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3942327A (en) * 1972-05-05 1976-03-09 Thermo Electron Corporation Control system for external combustion engine
US3906731A (en) * 1973-01-24 1975-09-23 Lear Motors Corp Control system for vapor engines
US4358929A (en) * 1974-04-02 1982-11-16 Stephen Molivadas Solar power system
US4039846A (en) * 1975-08-18 1977-08-02 Allied Chemical Corporation Control of a steam-heating power plant
US4117344A (en) * 1976-01-02 1978-09-26 General Electric Company Control system for a rankine cycle power unit

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000345835A (ja) * 1999-06-07 2000-12-12 Nissan Motor Co Ltd 内燃機関

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101124386B (zh) * 2005-02-21 2011-11-16 西门子公司 用于计算能量过程和工艺流程过程的方法和装置
CN102748080A (zh) * 2012-07-03 2012-10-24 山东电力研究院 基于主蒸汽压力变化的火电机组负荷控制方法
CN102748080B (zh) * 2012-07-03 2014-12-10 山东电力研究院 基于主蒸汽压力变化的火电机组负荷控制方法

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EP1536105A1 (fr) 2005-06-01
US20060101821A1 (en) 2006-05-18
EP1536105A4 (fr) 2005-11-23
AU2003248085A1 (en) 2004-02-16
JP3901609B2 (ja) 2007-04-04
JP2004060462A (ja) 2004-02-26

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