EP3521576A1 - Thermal energy recovery device - Google Patents

Thermal energy recovery device Download PDF

Info

Publication number
EP3521576A1
EP3521576A1 EP18204810.8A EP18204810A EP3521576A1 EP 3521576 A1 EP3521576 A1 EP 3521576A1 EP 18204810 A EP18204810 A EP 18204810A EP 3521576 A1 EP3521576 A1 EP 3521576A1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
heater
working medium
passage
temperature
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.)
Withdrawn
Application number
EP18204810.8A
Other languages
German (de)
English (en)
French (fr)
Inventor
Shigeto Adachi
Yutaka Narukawa
Kazumasa Nishimura
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.)
Kobe Steel Ltd
Original Assignee
Kobe Steel 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 Kobe Steel Ltd filed Critical Kobe Steel Ltd
Publication of EP3521576A1 publication Critical patent/EP3521576A1/en
Withdrawn legal-status Critical Current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
    • F01K15/00—Adaptations of plants for special use
    • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
    • F01K15/04—Adaptations of plants for special use for driving vehicles, e.g. locomotives the vehicles being waterborne vessels
    • F01K15/045—Control thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • 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
    • F01K13/003—Arrangements for measuring or testing
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/02—Arrangements or modifications of condensate or air pumps
    • F01K9/023—Control thereof
    • 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

Definitions

  • the present invention relates to a thermal energy recovery device.
  • JP 2015-232424 A JP 2016-160868 A , and JP 2016-160870 A
  • a circulation circuit of a working medium forming the Rankine cycle is formed.
  • an evaporator in which heat exchange is performed between the exhaust gas and the working medium is provided.
  • the working medium is evaporated whereas the exhaust gas is cooled.
  • the working medium evaporated in the evaporator drives an expander. By generating electric power by a generator connected to the expander, the thermal energy of the exhaust gas is recovered as the electric power.
  • the exhaust gas is cooled in the evaporator. Therefore, on the downstream side of the evaporator in an exhaust gas passage through which the exhaust gas flows, there is a concern that the exhaust gas passage is corroded following condensation of a SOX component contained in the exhaust gas.
  • the present invention is achieved in consideration with the above related art, and an object thereof is to take a precaution against corrosion of an exhaust gas passage following condensation of a SOX component contained in exhaust gas.
  • the present invention is a thermal energy recovery device including a heater in which a working medium flowing through a circulation flow passage is heated with exhaust gas flowing through an exhaust gas passage as a heat source, a power recovery machine to be driven by the working medium on the downstream side of the heater in the circulation flow passage, a temperature detector that detects a temperature of the exhaust gas on the downstream side of the heater in the exhaust gas passage, and a heat input amount control unit that performs control for adjusting a heat transfer amount from the exhaust gas to the working medium in the heater so that the detected temperature by the temperature detector is maintained to be not less than a set temperature.
  • heat received from the exhaust gas by the working medium in the heater is recovered as energy in the power recovery machine.
  • the heat input amount control unit performs the control for adjusting the heat transfer amount from the exhaust gas to the working medium in the heater so that the detected temperature by the temperature detector is maintained to be not less than the set temperature. Therefore, the temperature of the exhaust gas on the downstream side of the heater in the exhaust gas passage is maintained to be not less than a predetermined temperature.
  • the thermal energy recovery device may further include a SOX meter that measures a content rate of sulfur oxide in the exhaust gas on the downstream side of the heater in the exhaust gas passage.
  • the heat input amount control unit may perform the control for adjusting the heat transfer amount so that the detected temperature is maintained to be not less than a sulfuric acid dew point of the exhaust gas as the set temperature based on a detection result by the temperature detector and a measurement result by the SOX meter.
  • the heat input amount control unit performs the control of adjusting the heat transfer amount from the exhaust gas to the working medium in the heater based on the detection result by the temperature detector and the measurement result by the SOX meter.
  • the temperature of the exhaust gas on the downstream side of the heater in the exhaust gas passage is maintained to be not less than the sulfuric acid dew point of the exhaust gas. Therefore, in comparison to a case where the heat transfer amount from the exhaust gas to the working medium in the heater is controlled simply based on the detection result of the temperature of the exhaust gas by the temperature detector, it is possible to improve precision of control for suppressing the dropwise condensation of the corrosive component from the exhaust gas.
  • it is possible to perform control of more increasing a heat release amount from the exhaust gas to the working medium in the heater and hence, it is possible to increase an exhaust heat recovery amount.
  • the thermal energy recovery device may further include a SOX meter that measures a content rate of sulfur oxide in the exhaust gas on the downstream side of the heater in the exhaust gas passage, and a sulfuric acid dew point development unit that develops a sulfuric acid dew point of the exhaust gas on the downstream side of the heater in the exhaust gas passage based on a measured value by the SOX meter.
  • the heat input amount control unit may perform the control for adjusting the heat transfer amount so that with the sulfuric acid dew point developed by the sulfuric acid dew point development unit as the set temperature, the detected temperature is maintained to be not less than the temperature.
  • the heat input amount control unit performs the control of adjusting the heat transfer amount from the exhaust gas to the working medium in the heater by using the sulfuric acid dew point developed by the sulfuric acid dew point development unit.
  • the temperature of the exhaust gas on the downstream side of the heater in the exhaust gas passage is maintained to be not less than the developed sulfuric acid dew point. Therefore, in comparison to a case where the heat transfer amount from the exhaust gas to the working medium in the heater is controlled simply based on the detection result of the temperature of the exhaust gas by the temperature detector, it is possible to improve the precision of the control for suppressing the dropwise condensation of the corrosive component from the exhaust gas.
  • the heater may include an intermediate medium heater that heats an intermediate medium flowing through a medium flow passage with the exhaust gas flowing through the exhaust gas passage, and a working medium heater that heats the working medium with the intermediate medium heated by the intermediate medium heater.
  • the temperature detector may be formed to detect a temperature of the exhaust gas on the downstream side of the intermediate medium heater in the exhaust gas passage.
  • the power recovery machine 26 is connected to the expander 18.
  • the power recovery machine 26 has a driving unit (not shown) combined to a rotor of the expander 18.
  • the power recovery machine 26 is formed as a generator that generates electric power by driving the driving unit with the rotor of the expander 18. That is, the power recovery machine 26 converts the expansion energy of the working medium into electric energy. Therefore, the thermal energy recovery device 10 can recover thermal energy of the exhaust gas as electric energy.
  • the power recovery machine 26 is not limited to a converter that converts the thermal energy of the exhaust gas into the electric energy, but for example, may be formed as a converter that changes into power of a compressor, etc.
  • the condenser 20 is arranged on the downstream side of the expander 18 in the circulation flow passage 12.
  • the condenser 20 is connected to the circulation flow passage 12 and a cooling medium flow passage 30. Sea water serving as a cooling medium flows through the cooling medium flow passage 30.
  • the cooling medium is not limited to sea water but only required to have a temperature at which the working medium can be condensed in the condenser 20. For example, in a case where a cooling water storage tank, etc. in which cooling water is stored is provided in the marine vessel, the cooling water may be used as the cooling medium.
  • the thermal energy recovery device 10 includes a temperature detector 34, a pressure sensor 35, a temperature sensor 36, and a controller 38.
  • the temperature detector 34 is formed to detect a temperature of the exhaust gas on the downstream side of the heater 16 in the exhaust gas passage 3.
  • the temperature detector 34 outputs a signal corresponding to the detected temperature.
  • the pressure sensor 35 and the temperature sensor 36 are arranged between the heater 16 and the expander 18 in the circulation flow passage 12.
  • the pressure sensor 35 detects pressure of the working medium flowing out of the heater 16 to the expander 18, and outputs a signal corresponding to the detected pressure.
  • the temperature sensor 36 detects a temperature of the working medium flowing out of the heater 16 to the expander 18, and outputs a signal corresponding to the detected temperature.
  • the signals outputted from the temperature detector 34, the pressure sensor 35, and the temperature sensor 36 are inputted to the controller 38.
  • the controller 38 includes a storage unit (not shown) in which a computer program, etc. are stored, and a calculation unit (not shown) that executes the computer program stored in the storage unit. By executing the computer program, the controller performs predetermined functions.
  • the functions include an operation control unit 41 and a heat input amount control unit 42.
  • the operation control unit 41 performs control (superheat degree control) of adjusting the rotational speed of the pump 14 so that a superheat degree of the working medium introduced to the expander 18 is set within a predetermined range. Specifically, the operation control unit 41 reads out a saturation temperature corresponding to the detected pressure of the pressure sensor 35 by using a map stored in the storage unit, and develops the superheat degree from a temperature difference between the detected temperature of the temperature sensor 36 and the read-out saturation temperature. When the developed superheat degree is lower than a lower limit value of the set range, the operation control unit 41 performs control of lowering the rotational speed of the pump 14. When the developed superheat degree exceeds an upper limit value of the set range, the operation control unit performs control of increasing the rotational speed of the pump 14.
  • the heat input amount control unit 42 performs control for adjusting a heat transfer amount from the exhaust gas to the working medium in the heater 16 so that the detected temperature by the temperature detector 34 is maintained to be not less than a preliminarily set temperature. Specifically, as shown in FIG. 3 , even when performing the superheat degree control (Step ST1), the heat input amount control unit 42 receives the signal outputted from the temperature detector 34 and reads in a detected temperature TE (Step ST2). The heat input amount control unit 42 determines whether or not the detected temperature TE is not less than a preliminarily set threshold value TS (Step ST3), and when the detected temperature TE is not less than the threshold value TS, the flow returns to the first step and the superheat degree control is continued without any change.
  • the heat input amount control unit 42 gives priority to the superheat degree control and performs the control of lowering the rotational speed of the pump 14 (Step ST4).
  • the heat input amount control unit 42 gives priority to the superheat degree control and performs the control of lowering the rotational speed of the pump 14 (Step ST4).
  • the heat received from the exhaust gas by the working medium in the heater 16 is recovered as the electric energy in the power recovery machine 26.
  • the heat input amount control unit 42 performs the control for adjusting the heat transfer amount from the exhaust gas to the working medium in the heater 16 so that the detected temperature by the temperature detector 34 is maintained to be not less than the preliminarily set temperature. Therefore, the temperature of the exhaust gas on the downstream side of the heater 16 in the exhaust gas passage 3 is maintained to be not less than a predetermined temperature.
  • C heavy oil is used as engine fuel, it is possible to prevent dropwise condensation of a corrosive component from the exhaust gas after the heat is recovered by the working medium. Consequently, it is possible to prevent corrosion of the exhaust gas passage 3, etc.
  • the heat input amount control unit 42 adjusting the rotational speed of the pump 14, the amount of the working medium passing through the heater 16 is adjusted. Thereby, a heat exchange amount between the exhaust gas and the working medium in the heater 16 is adjusted. Therefore, by utilizing pump rotation control which is originally included in the controller 38, it is possible to prevent the dropwise condensation of the exhaust gas.
  • the heat input amount control unit 42 is formed to perform the control of adjusting the rotational speed of the pump 14 so that the detected temperature TE of the temperature detector 34 is not less than the threshold value TS. Meanwhile, in the second embodiment, a heat input amount control unit 42 is formed to perform control of adjusting the rotational speed of a pump 14 so that a detected temperature TE is maintained to be not less than a sulfuric acid dew point estimated from a content rate of sulfur oxide (SOX) contained in exhaust gas.
  • SOX sulfur oxide
  • a SOX meter 51 that measures the content rate (weight percentage) of sulfur oxide in the exhaust gas is provided.
  • the SOX meter 51 outputs a signal corresponding to the measured content rate of sulfur oxide.
  • the heat input amount control unit 42 performs control for maintaining the detected temperature TE at not less than the sulfuric acid dew point. Specifically, as shown in FIG. 6 , even when performing superheat degree control (Step ST1), the heat input amount control unit 42 receives signals outputted from a temperature detector 34 and the SOX meter 51 and reads in the detected temperature TE and a measured value MV of the SOX meter 51 (Step ST12, ST13).
  • the sulfuric acid dew point development unit 43 estimates a sulfuric acid dew point DP of sulfur oxide contained in the exhaust gas from the read-in measured value MV by using the relational expression or the map that relates the weight percentage of sulfur oxide and the sulfuric acid dew point (Step ST14).
  • the heat input amount control unit 42 determines whether or not the detected temperature TE is not less than the sulfuric acid dew point DP developed by the sulfuric acid dew point development unit 43 (Step ST15), and when the detected temperature TE is not less than the sulfuric acid dew point DP, the flow returns to the first step and the superheat degree control is continued without any change. Meanwhile, in a case where the detected temperature TE is less than the sulfuric acid dew point DP, the heat input amount control unit 42 gives priority to the superheat degree control and performs control of lowering the rotational speed of the pump 14 (Step ST16). Thereby, in the heater 16, an amount of heat released from the exhaust gas to a working medium can be reduced. Thus, it is possible to solve a state where a temperature of the exhaust gas is too low on the downstream side of the heater 16. When the detected temperature TE becomes not less than the sulfuric acid dew point DP, the superheat degree control is resumed.
  • the heat input amount control unit 42 performs control of adjusting a heat transfer amount from the exhaust gas to the working medium in the heater 16 by using the sulfuric acid dew point DP developed by the sulfuric acid dew point development unit 43.
  • the temperature of the exhaust gas on the downstream side of the heater 16 in the exhaust gas passage 3 is maintained to be not less than the developed sulfuric acid dew point DP. Therefore, in comparison to a case where a heat exchange amount in the heater 16 is controlled simply based on a detection result of the temperature of the exhaust gas by the temperature detector 34, it is possible to improve precision of control for suppressing dropwise condensation of a corrosive component from the exhaust gas.
  • it is possible to perform control of more increasing the heat release amount from the exhaust gas to the working medium in the heater 16 that is, control of not excessively lowering the heat release amount
  • the sulfuric acid dew point DP in the exhaust gas can be estimated from a measurement result by the SOX meter 51, and based on this estimated sulfuric acid dew point DP, the control of adjusting the heat transfer amount from the exhaust gas to the working medium in the heater 16 is performed. Therefore, while suppressing an increase in cost required for estimating the sulfuric acid dew point DP, it is possible to improve the precision of the control for suppressing the dropwise condensation of the corrosive component from the exhaust gas.
  • the heat input amount control unit 42 performs the control of adjusting the heat transfer amount from the exhaust gas to the working medium in the heater 16 based on the detected temperature TE by the temperature detector 34 and the measured value MV by the SOX meter 51.
  • the temperature of the exhaust gas on the downstream side of the heater 16 in the exhaust gas passage 3 is maintained to be not less than the sulfuric acid dew point of the exhaust gas. Therefore, in comparison to a case where the heat exchange amount in the heater 16 is controlled simply based on the detection result of the temperature of the exhaust gas by the temperature detector 34, it is possible to improve the precision of the control for suppressing the dropwise condensation of the corrosive component from the exhaust gas.
  • the return passage 53 is connected to the circulation flow passage 12 so as to divert from the pump 14.
  • One end of the return passage 53 is connected to the downstream side of the pump 14 in the circulation flow passage 12.
  • the other end of the return passage 53 is connected to the upstream side of the pump 14 in the circulation flow passage 12.
  • FIG. 8 shows a fourth embodiment of the present invention.
  • the same constituent elements as those of the second embodiment will be given the same reference signs and detailed description thereof will be omitted.
  • the heat input amount control unit 42 performs the control of adjusting the rotational speed of the pump 14. Meanwhile, a heat input amount control unit 42 of the fourth embodiment does not adjust the rotational speed of a pump 14 but performs control for reducing a flow rate of a working medium flowing into a heater 16. Therefore, the pump 14 may not be formed so that the rotational speed is adjustable.
  • Step ST16 in FIG. 6 turns out to be control of increasing the opening degree of the flow rate adjusting valve 54 in place of the control of lowering the rotational speed of the pump 14. Anything other than that is the same as the second embodiment.
  • the heat input amount control unit 42 performs the control of adjusting the rotational speed of the pump 14.
  • a heat input amount control unit 42 is formed not to adjust the rotational speed of a pump 14 but to restrict a heat input amount to a working medium by reducing an inflow amount of the working medium to a heater 16.
  • a bypass passage 56 that bypasses the heater 16 is connected to a circulation flow passage 12.
  • One end of the bypass passage 56 is connected to a part of the circulation flow passage 12 on the upstream side of the heater 16, that is, a part between the pump 14 and the heater 16.
  • the other end of the bypass passage 56 is connected to a part of the circulation flow passage 12 on the downstream side of the heater 16, that is, a part between the heater 16 and an expander 18.
  • the heat input amount control unit 42 controls the bypass valve 57 so that a heat transfer amount from exhaust gas to the working medium in the heater 16 is adjusted. Specifically, when superheat degree control is executed, the bypass valve 57 is in a closed state. Therefore, the entire amount of the working medium fed from the pump 14 passes through the heater 16. As shown in FIG. 10 , even when performing the superheat degree control (Step ST1), the heat input amount control unit 42 receives a signal outputted from a temperature detector 34 and reads in a detected temperature TE (Step ST2).
  • the heater 16 is formed by a single heat exchanger. Meanwhile, in the sixth embodiment, a heater 16 includes an intermediate medium heater 61 and a working medium heater 62. That is, the heater 16 includes two separately-formed heat exchangers.
  • a medium flow passage 63 through which an intermediate medium flows is provided between an exhaust gas passage 3 and a circulation flow passage 12.
  • the intermediate medium heater 61 is connected to the exhaust gas passage 3 and the medium flow passage 63, and formed to perform heat exchange between exhaust gas and the intermediate medium.
  • the working medium heater 62 is connected to the medium flow passage 63 and the circulation flow passage 12, and formed to perform heat exchange between the intermediate medium and a working medium.
  • the intermediate medium heater 61 is formed by a shell-and-tube heat exchanger. A space in a shell 61a of the intermediate medium heater 61 communicates with the exhaust gas passage 3, and a heat transfer tube 61b provided in the shell 61a communicates with the medium flow passage 63.
  • the heat input amount control unit 42 controls the adjusting valve 65 so that the heat transfer amount from the exhaust gas to the working medium in the heater 16 (the intermediate medium heater 61 and the working medium heater 62) is adjusted. Specifically, as shown in FIG. 12 , even when performing superheat degree control (Step ST1), the heat input amount control unit 42 receives a signal outputted from a temperature detector 34 and reads in a detected temperature TE (Step ST2). In a case where the detected temperature TE is less than a threshold value TS in Step ST3, the heat input amount control unit 42 controls the adjusting valve 65 so that the current opening degree of the adjusting valve 65 is decreased by a predetermined opening degree (Step ST34).
  • the flow rate of the intermediate medium flowing through the medium flow passage 63 is reduced, and the heat exchange amount between the exhaust gas and the intermediate medium in the intermediate medium heater 61 is reduced.
  • the heat transfer amount from the exhaust gas to the working medium is reduced. Therefore, it is possible to solve a state where a temperature of the exhaust gas is too low.
  • the detected temperature TE becomes not less than the threshold value TS, the superheat degree control is resumed.
  • the heat input amount control unit 42 adjusting the flow rate of the intermediate medium, the heat transfer amount from the exhaust gas to the working medium is adjusted.
  • the heat input amount control unit 42 may be formed to adjust the heat transfer amount from the exhaust gas to the working medium by controlling the pump 14 provided in the circulation flow passage 12. In this case, a heat transfer amount from the exhaust gas to the intermediate medium is also adjusted following adjustment of a heat transfer amount from the intermediate medium to the working medium.
  • the present invention is also not limited to the configuration in which the flow rate of the intermediate medium flowing into the intermediate medium heater 61 is adjusted by adjusting the rotational speed of the intermediate pump 64.
  • a bypass flow passage (not shown) may be connected to the medium flow passage 63 so as to divert from the intermediate medium heater 61, so that the flow rate of the intermediate medium flowing into the intermediate medium heater 61 is adjusted.
  • a return flow passage (not shown) which is similar to the return passage 53 ( FIG. 7 ) may be provided in the medium flow passage 63, so that the flow rate of the intermediate medium flowing into the intermediate medium heater 61 is adjusted.
  • the heat input amount control unit 42 performs the control of maintaining the state where the detected temperature TE of the temperature detector 34 is not less than the threshold value TS.
  • the present invention is not limited to this.
  • a SOX meter 51 may be provided and the heat input amount control unit 42 may perform control of maintaining the state where the detected temperature TE of the temperature detector 34 is not less than a sulfuric acid dew point DP. That is, in a case where the detected temperature TE is less than the sulfuric acid dew point DP, the heat input amount control unit 42 controls the adjusting valve 65 so that the current opening degree of the adjusting valve 65 is decreased by a predetermined opening degree.
  • a thermal energy recovery device includes a heater in which a working medium flowing through a circulation flow passage is heated with exhaust gas flowing through an exhaust gas passage as a heat source, a power recovery machine to be driven by the working medium on the downstream side of the heater in the circulation flow passage, a temperature detector that detects a temperature of the exhaust gas on the downstream side of the heater in the exhaust gas passage, and a heat input amount control unit that performs control for adjusting a heat transfer amount from the exhaust gas to the working medium in the heater so that the detected temperature by the temperature detector is maintained to be not less than a set temperature.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Treating Waste Gases (AREA)
  • Control Of Turbines (AREA)
EP18204810.8A 2018-01-31 2018-11-07 Thermal energy recovery device Withdrawn EP3521576A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2018015166A JP6980546B2 (ja) 2018-01-31 2018-01-31 熱エネルギー回収装置

Publications (1)

Publication Number Publication Date
EP3521576A1 true EP3521576A1 (en) 2019-08-07

Family

ID=64183904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18204810.8A Withdrawn EP3521576A1 (en) 2018-01-31 2018-11-07 Thermal energy recovery device

Country Status (4)

Country Link
EP (1) EP3521576A1 (ja)
JP (1) JP6980546B2 (ja)
KR (1) KR20190093125A (ja)
CN (1) CN110094240B (ja)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013181398A (ja) * 2012-02-29 2013-09-12 Kobe Steel Ltd バイナリー発電装置の制御方法及びバイナリー発電装置
JP2015232424A (ja) 2014-06-10 2015-12-24 サムソン ヘビー インダストリーズ カンパニー，リミテッド 船舶用廃熱回収装置
JP2016160870A (ja) 2015-03-03 2016-09-05 三井造船株式会社 低温熱回収システム
JP2016160868A (ja) 2015-03-03 2016-09-05 三井造船株式会社 低温熱回収システム
EP3124755A1 (en) * 2014-03-28 2017-02-01 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Generator device
US20170284231A1 (en) * 2015-03-05 2017-10-05 Fuji Electric Co., Ltd. Binary power generation system and control apparatus

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2455658B1 (de) * 2010-11-17 2016-03-02 Orcan Energy AG Verfahren und Vorrichtung zur Verdampfung organischer Arbeitsmedien
JP6670123B2 (ja) * 2016-02-19 2020-03-18 株式会社神戸製鋼所 排熱回収装置及びバイナリ発電装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013181398A (ja) * 2012-02-29 2013-09-12 Kobe Steel Ltd バイナリー発電装置の制御方法及びバイナリー発電装置
EP3124755A1 (en) * 2014-03-28 2017-02-01 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Generator device
JP2015232424A (ja) 2014-06-10 2015-12-24 サムソン ヘビー インダストリーズ カンパニー，リミテッド 船舶用廃熱回収装置
JP2016160870A (ja) 2015-03-03 2016-09-05 三井造船株式会社 低温熱回収システム
JP2016160868A (ja) 2015-03-03 2016-09-05 三井造船株式会社 低温熱回収システム
US20170284231A1 (en) * 2015-03-05 2017-10-05 Fuji Electric Co., Ltd. Binary power generation system and control apparatus

Also Published As

Publication number Publication date
CN110094240B (zh) 2022-06-24
CN110094240A (zh) 2019-08-06
KR20190093125A (ko) 2019-08-08
JP6980546B2 (ja) 2021-12-15
JP2019132192A (ja) 2019-08-08

Similar Documents

Publication Publication Date Title
JP6670123B2 (ja) 排熱回収装置及びバイナリ発電装置
US9441576B2 (en) Waste heat utilization device for internal combustion engine
EP3514339A1 (en) Thermal energy recovery device
JP5338730B2 (ja) 廃熱回生システム
JP2008231981A (ja) 内燃機関の廃熱利用装置
KR101708109B1 (ko) 폐열 회수 장치 및 폐열 회수 방법
MX2011005084A (es) Procedimiento para operar un generador de vapor con calor residual.
WO2007104970A2 (en) Working fluid control in non-aqueous vapour power systems
US9714581B2 (en) Rankine cycle apparatus
JP6029533B2 (ja) バイナリー発電装置の運転方法及びバイナリー発電装置
JP6335859B2 (ja) 熱エネルギー回収システム
CN102691538B (zh) 动力产生装置及其控制方法
JP5725913B2 (ja) 複合サイクルプラント
JP6406583B2 (ja) ランキンサイクル装置
JP7111525B2 (ja) 貫流式排熱回収ボイラおよび貫流式排熱回収ボイラの制御システム
EP3521576A1 (en) Thermal energy recovery device
JP5951593B2 (ja) 排熱回収装置、排熱回収型船舶推進装置および排熱回収方法
US11346255B2 (en) Method and controller for preventing formation of droplets in a heat exchanger
EP2926064B1 (en) Pressure control for refrigerant system
JP5609707B2 (ja) ランキンサイクルシステムの制御装置
EP3375989A1 (en) Waste heat recovery apparatus and method for controlling waste heat recovery apparatus
JP5457779B2 (ja) プラントシステムとその給水温度制御方法
US10851678B2 (en) Thermal energy recovery device and startup operation method for the same
JP2020029779A (ja) バイナリー発電装置およびバイナリー発電方法
JP5890221B2 (ja) 石炭ガス化複合発電プラントとその運転制御方法

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20181107

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20200208