WO2010074173A1 - 排熱回収システムの制御装置 - Google Patents
排熱回収システムの制御装置 Download PDFInfo
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- WO2010074173A1 WO2010074173A1 PCT/JP2009/071486 JP2009071486W WO2010074173A1 WO 2010074173 A1 WO2010074173 A1 WO 2010074173A1 JP 2009071486 W JP2009071486 W JP 2009071486W WO 2010074173 A1 WO2010074173 A1 WO 2010074173A1
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- power turbine
- control valve
- control
- turbine
- operation amount
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- 238000011084 recovery Methods 0.000 title claims abstract description 35
- 239000002918 waste heat Substances 0.000 title abstract description 7
- 230000007246 mechanism Effects 0.000 claims description 50
- 230000008859 change Effects 0.000 claims description 9
- 239000007789 gas Substances 0.000 abstract description 17
- 230000004043 responsiveness Effects 0.000 abstract description 10
- 239000000284 extract Substances 0.000 abstract 1
- 238000004364 calculation method Methods 0.000 description 12
- 238000010248 power generation Methods 0.000 description 12
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 9
- 230000007423 decrease Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 230000004044 response Effects 0.000 description 7
- 239000000498 cooling water Substances 0.000 description 5
- 230000005855 radiation Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 238000001514 detection method Methods 0.000 description 3
- 230000017525 heat dissipation Effects 0.000 description 3
- 238000012544 monitoring process Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/10—Engines with prolonged expansion in exhaust turbines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
- B63H21/14—Use of propulsion power plant or units on vessels the vessels being motor-driven relating to internal-combustion engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/32—Arrangements of propulsion power-unit exhaust uptakes; Funnels peculiar to vessels
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63J—AUXILIARIES ON VESSELS
- B63J3/00—Driving of auxiliaries
- B63J3/02—Driving of auxiliaries from propulsion power plant
-
- 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
-
- 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
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using kinetic energy
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2590/00—Exhaust or silencing apparatus adapted to particular use, e.g. for military applications, airplanes, submarines
- F01N2590/02—Exhaust or silencing apparatus adapted to particular use, e.g. for military applications, airplanes, submarines for marine vessels or naval applications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T70/00—Maritime or waterways transport
- Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system
Definitions
- the present invention relates to a control device for a marine exhaust heat recovery system, and more particularly, to a control device for an exhaust heat recovery system that sets the opening of a control valve based on a calculation by a PID controller and a rotational speed deviation of a power turbine.
- Patent Document 1 Japanese Patent Laid-Open No. 2007-1339.
- Patent Document 1 is a system that drives a power turbine using exhaust gas from an engine to cover a part of inboard load power.
- the power distribution of the steam turbine, power turbine, shaft generator, etc. is determined according to the engine load. Since power generation by a power turbine is conventionally controlled by a valve such as an ON / OFF valve, when there is a possibility that the load on the ship will suddenly decrease and a turbine trip occurs, steam that flows in by closing the valve or providing a bypass Is completely stopped, and precise flow control is impossible.
- FIG. 7 is a block diagram showing a control logic performed in a conventional exhaust heat recovery system
- FIG. 8 is a flowchart of the control logic according to FIG.
- the control logic of FIG. 7 when started in step S ⁇ b> 21, the power turbine output target value is calculated from the engine load by the power generation output command calculation 52 in step S ⁇ b> 22.
- the power turbine actual output value is measured.
- the difference between the power turbine output target value and the power turbine actual output value is calculated by the subtractor 53.
- the PID controller 54 calculates the difference in control.
- a PID control calculation is performed to derive an operation amount O 1 .
- the output signal of the feedback control (not shown) based on the rotational speed difference between the target rotational speed speed of the power turbine is converted to the operation amount O 2 at opening terms 51 in step S26, the operation amount O 1 and the operation in step S27
- the amount O 2 is calculated by the addition 55 to determine the opening degree of the control valve. Then, the process returns to the previous stage of step S22.
- the opening degree of the control valve of the power turbine is set by feedback control.
- Patent Document 2 Japanese Patent No. 3804663 is disclosed as an invention for controlling the valve opening.
- a load-side circulating water temperature sensor that is provided downstream of the exhaust heat recovery load of the load-side circulating pipe and measures the temperature of the load-side circulating water flowing therethrough, and the load-side circulating water temperature sensor
- the exhaust heat recovery amount detection means for comparing the temperature of the load side circulating water measured with the first set temperature and outputting a heat radiation signal when the temperature of the load side circulating water is equal to or higher than the first set temperature;
- a flow state detection means provided in the load side circulation pipe for detecting whether the flow state of the load side circulating water is a predetermined flow state or any other abnormal flow state and outputting a heat radiation signal upon detection of the abnormal flow state
- a holding means for outputting a heat dissipation signal until the measured temperature of the cooling water by the cooling water temperature sensor becomes lower than a second set temperature based on the heat dissipation signal, and in response to the heat dissip
- Patent Document 2 The exhaust heat recovery system disclosed in Patent Document 2 is controlled by paying attention to the water temperature in order to prevent the occurrence of overshoot due to a rapid fluctuation of the exhaust heat recovery amount.
- the inboard load suddenly decreases, surplus power is generated, so it is necessary to immediately reduce the power turbine output.
- the fluctuation of the power frequency may become large.
- surplus power is generated when the load on the ship decreases rapidly. Therefore, it is necessary to immediately control the flow rate of the valve to reduce the steam turbine output.
- the fluctuation of the power frequency becomes large depending on the response of the steam turbine output control.
- Patent Document 2 does not describe any fluctuation of the power frequency. Furthermore, when the shipboard load power is drastically reduced and the outputs of the power turbine and the steam turbine are controlled, it may take time to set the supplied power due to the difference in response speed.
- JP 2007-1339 A Japanese Patent No. 3804663
- an object of the present invention is to improve the responsiveness of the output control of the power turbine and the steam turbine with respect to a sudden change in the ship load.
- the present invention includes a power turbine that is driven by using exhaust gas from an engine, and a steam turbine that is driven by using steam generated by an exhaust gas economizer of the engine, and the power turbine and the steam.
- a first control valve mechanism comprising one or a plurality of control valves that drive a generator by a turbine, adjust the flow rate of the exhaust gas by controlling a flow rate of the exhaust gas, and control the output of the power turbine;
- a power turbine control means for controlling an operation amount of the first control valve mechanism, and a second control valve mechanism comprising one or a plurality of control valves that are disposed in a preceding stage of the steam turbine and that control an output of the steam turbine.
- a steam turbine control means for controlling an operation amount of the second control valve mechanism.
- the bin control means calculates a manipulated variable of the first control valve mechanism by calculating a deviation between a power turbine output target value calculated from the engine load and an actual power turbine output by a PID controller.
- the first control valve mechanism from a power turbine opening command map in which a relationship between the engine load, a power turbine output target value calculated from the engine load, and an operation amount of the first control valve mechanism is set in advance.
- Power turbine feedforward control means for extracting the operation amount of the power turbine, and adding the operation amount from the power turbine feedforward control means and the operation amount from the power turbine feedback control means to add the first control valve mechanism It is characterized in that it is set as the operation amount.
- the power turbine opening command map in which the relationship between the engine load, the power turbine output target value calculated from the engine load, and the operation amount of the first control valve mechanism is set in advance is created.
- the amount of operation from the feedback control means are added to set the amount of operation of the first control valve mechanism, thereby improving the power control response of the power turbine and reducing power frequency fluctuations. It becomes possible. Therefore, even when the inboard load is suddenly reduced, the responsiveness of the output control of the power turbine can be improved.
- the operation amount of the first control valve mechanism may be an opening degree of an inflow control valve that controls an inflow amount to the power turbine, or an operation amount of the first control valve mechanism.
- the opening degree of the bypass control valve for controlling the bypass amount of the power turbine may be used.
- the amount of inflow into the power turbine can be indirectly controlled by controlling the amount of bypassing the power turbine, so that the output of the power turbine can be finely controlled.
- the steam turbine control means calculates a deviation between the steam turbine output target value calculated from the engine load and the actual steam turbine output by a PID controller, and operates the operation amount of the second control valve mechanism.
- Steam turbine feedback control means for calculating The operation of the second control valve mechanism is determined from a steam turbine opening command map in which the relationship between the engine load, the steam turbine output target value calculated from the engine load and the operation amount of the second control valve mechanism is preset.
- a steam turbine feedforward control means for extracting the quantity, The operation amount of the second control valve mechanism is set by adding the operation amount from the steam turbine feedforward control means and the operation amount from the steam turbine feedback control means.
- the output control of the steam turbine is performed. Responsiveness is improved, and power frequency fluctuations can be reduced. Therefore, the responsiveness of the output control of the steam turbine can be improved even if the inboard load is suddenly reduced.
- the operation amount of the second control valve mechanism may be an opening degree of an inflow control valve that controls the inflow amount to the steam turbine, or the second control valve mechanism May be the opening degree of a bypass control valve that controls the bypass amount of the steam turbine.
- the control of the inflow control valve and the control of the bypass control valve in the case of the opening control of the inflow control valve, as in the case of the power turbine, the inflow amount to the steam turbine can be directly controlled. Since the steam turbine output can be controlled efficiently and the inflow can be completely blocked, the power generation output of the steam turbine can be immediately reduced when the inboard power is drastically reduced. Further, in the case of the bypass control valve, since the amount of inflow into the steam turbine can be indirectly controlled by controlling the amount of bypassing the steam turbine, the output of the steam turbine can be finely controlled.
- the power turbine output target value is corrected according to a change in the steam turbine load, and the power turbine output target value is corrected.
- the corrected power turbine output target value is corrected by the correction unit.
- the power turbine feedback control means and the power turbine feedforward control means are controlled based on the above.
- the power turbine and the steam turbine are not controlled independently of each other, but can be coordinated control. That is, since the response of the steam system is slow, the operation amount is set by operating the steam turbine as a master (main) and the power turbine as a slave (sub). Specifically, it has power turbine output target value correction means for monitoring the steam turbine load and correcting the power turbine output target value in accordance with the change of the steam turbine load. When shipboard power demand is drastically reduced, the output (load) of each of the steam turbine and power turbine is reduced. However, since the response of the steam system is slow, the output of the steam turbine is reduced after the power turbine output is reduced. .
- the output target value of the power turbine is increased in accordance with the output (load) state of the steam turbine, that is, the output reduction state of the steam turbine. .
- the output target value of the power turbine is corrected while monitoring the load state of the steam turbine. Therefore, the power turbine and the steam are not biased toward the output control of the power turbine with respect to the sudden decrease in the inboard power load. It is possible to control the turbine in cooperation.
- the power turbine output target value correcting means is configured to determine whether the engine load and the steam turbine are based on a corrected power turbine opening command map in which a relationship between the steam turbine load, the engine load, and the corrected power turbine output target value is set in advance.
- the corrected power turbine output target value may be calculated from the load, and the corrected power turbine output target value can be easily obtained by using the corrected power turbine opening command map in this way.
- FIG. 3 is a flowchart of control logic according to the first embodiment. It is an opening degree map of control valve B of the 1st control valve mechanism. It is a block diagram which shows the control logic performed with the waste heat recovery system which concerns on Embodiment 2.
- FIG. 10 is a flowchart of control logic according to the second embodiment. It is a block diagram which shows the control logic performed with the conventional waste heat recovery system. It is a flowchart about the control logic which concerns on FIG.
- the exhaust heat recovery system shown in FIG. 1 includes an engine 22 that propels a ship, a propeller 30 that rotates according to the output of the engine 22, a supercharger 21 that compresses air supplied to the engine 22, and a supercharger 21. It comprises a cooler 31 that cools the air, a power turbine (gas turbine) 23, a steam turbine 26, and a generator 28.
- the power turbine 23, the steam turbine 26, and the generator 28 are connected by speed reducers 24 and 27 including gears that mesh with each other with different sizes and number of teeth.
- the rotating shaft among the power turbine 23, the steam turbine 26, and the generator 28 is connected via the clutch 25, and rotational power is transmitted or interrupted.
- an exhaust gas economizer 150 is provided, and exhaust gas discharged from the engine 22 is supplied to the exhaust gas economizer through the supercharger 21 or the supercharger 21 and the power turbine 23, and is generated by the exhaust gas economizer.
- Steam is guided to the steam turbine 26 to drive the steam turbine 26, and the generator 28 is rotated together with the power of the power turbine 23.
- Steam is returned to water by a condenser 29 provided at the subsequent stage of the steam turbine 26, and this water is heated by heat of the cooler 31 or heat for cooling the wall of the engine 22, and then supplied to an exhaust gas economizer to evaporate. Steam is generated.
- Power generation by the power turbine 23 is controlled by control valves (valves) A, B, and C that constitute a first control valve mechanism, and power generation by the steam turbine 26 is control valve (valve) D that constitutes a second control valve mechanism.
- control valves (valves) A, B, and C that constitute a first control valve mechanism
- power generation by the steam turbine 26 is control valve (valve) D that constitutes a second control valve mechanism.
- an opening command of the control valve B will be described in the first control valve mechanism when the control valves A and C are fully opened or at a constant opening state.
- the opening command of the control valve E will be described with the control valves D and F fully opened or at a constant opening.
- the control apparatus 100 of the exhaust heat recovery system includes a power turbine control means 101 that controls an operation amount of a first control valve mechanism including control valves (valves) A, B, and C, and control valves (valves) D, E, and F. And a steam turbine control means 102 for controlling an operation amount of the second control valve mechanism.
- a power turbine control means 101 that controls an operation amount of a first control valve mechanism including control valves (valves) A, B, and C, and control valves (valves) D, E, and F.
- a steam turbine control means 102 for controlling an operation amount of the second control valve mechanism.
- the power turbine control means 101 calculates the operation amount of the first control valve mechanism by calculating the deviation between the target value of the power turbine output calculated from the engine load and the actual power turbine output by the PID controller. From the feedback control means 104, a power turbine opening command map 105 in which the relationship between the engine load, the power turbine output target value calculated from the engine load, and the operation amount of the first control valve mechanism is set in advance. And a power turbine feedforward control means 106 for extracting an operation amount of the control valve mechanism.
- the steam turbine control means 102 calculates a deviation between the steam turbine output target value calculated from the engine load and the actual steam turbine output by a PID controller to calculate an operation amount of the second control valve mechanism.
- Turbine feedback control means 108 From the steam turbine opening command map 109 in which the relationship between the engine load, the steam turbine output target value calculated from the engine load and the operation amount of the second control valve mechanism is preset, the operation of the second control valve mechanism And a steam turbine feedforward control means 110 for extracting the quantity.
- FIG. 2 is a block diagram illustrating a control logic performed in the exhaust heat recovery system according to the first embodiment
- FIG. 3 is a flowchart of the control logic according to the first embodiment. 2 and 3 describe the control valve B of the first control valve mechanism that controls power generation by the power turbine 26.
- FIG. 4 shows a control valve opening map (power turbine opening command map) 105 of the control valve B.
- the control valve opening map is determined by the engine load and the power turbine output target value calculated from the engine load.
- the target output of the power turbine is determined according to the engine load, and the opening of the control valve B can be adjusted with respect to the output.
- FIG. 4 shows the control valve opening map when the engine load is 50%, 60%, and 100%.
- a power turbine output target value is calculated from the engine load by the power generation output command calculator 2 (see FIG. 2).
- the actual power turbine output value is measured.
- step S5 the deviation between the power turbine output target value and the actual power turbine output value is calculated by the subtractor 3 (see FIG. 2).
- step S6 the deviation is calculated.
- a PID control calculation is performed by the PID controller 4 (see FIG. 2) to derive an operation amount O 1 .
- step S7 an output signal of feedback control (not shown) is converted into an operation amount O 2 by the opening degree converter 1 (see FIG. 2) based on the rotational speed deviation from the target rotational speed of the power turbine.
- step S8 Using the control valve opening degree map 105 of the control valve B prepared in Step 1, the opening operation amount of the control valve B from which the power turbine output target value is obtained by the opening degree calculator 5 (see FIG. 2) is extracted from the map. Then, an operation amount O 3 is obtained.
- Step S9 in the sum of the manipulated variable O 1 and the operation amount O 2 and the operation amount O 3 is calculated by the adder 6 and 7 (see FIG. 2) sets the opening degree of the control valve B, again in front of the step S2 Repeat back.
- the control valve opening degree map showing the relationship between the engine load, the power turbine output target value, and the opening degree of the control valve is created, and the opening degree command is generated by the feedforward control described above.
- the operation amount of opening of the control valve B is relative to the operation amount O 1 and O off calculated by feedback control, further sum and an operation amount O 3 calculated by the feed-forward control of the power turbine 23 Is set as the opening command value. Therefore, the responsiveness of the output control of the power turbine is improved by adding the operation amount O 3 calculated by the feedforward control, and the power frequency fluctuation can be reduced.
- the steam turbine control unit 102 executes the same control as the control in the power turbine control unit 101. That is, the flowchart of FIG. 3 is read as follows.
- an opening map of the control valve E that obtains a desired steam turbine bin output for each engine load is calculated or measured in step S2.
- a control valve opening map (steam turbine opening command map) 109 of the control valve E corresponding to the control valve opening map 105 of the control valve B shown in FIG. 4 is prepared.
- step S3 the power turbine output target value is set as the steam turbine output target value.
- step S4 the actual steam turbine output value is measured.
- step S5 the actual steam turbine output value is subtracted from the target steam turbine output value.
- step S6 the PID control calculation is performed to derive the operation amount O 1 ′.
- step S7 based on the rotational speed deviation from the target rotational speed of the steam turbine.
- An output signal of feedback control (not shown) is converted into an operation amount O 2 ′ by the opening converter 1, and in step S 8, the steam turbine output is obtained using the control valve opening map 109 of the control valve E prepared in step 1.
- the opening operation amount of the control valve E from which the target value can be obtained is extracted, and the operation amount O 3 ′ is obtained.
- step S9 the sum of the operation amount O 1 ′, the operation amount O 2 ′, and the operation amount O 3 ′ is calculated and set as the opening degree of the control valve E.
- the opening degree of the control valve E of the steam turbine 26 is also calculated for the steam turbine 26 by the feedforward control with respect to the operation amounts O 1 ′ and O 2 ′ calculated by the feedback control.
- the opening command value is set as an operation amount obtained by adding the operation amount O 3 ′. Therefore, the responsiveness of the output control of the steam turbine is improved by adding the operation amount O 3 ′ calculated by the feedforward control, and the power frequency fluctuation can be reduced.
- control valve B is provided as an inflow control valve provided at a position for directly controlling the inflow amount to the power turbine 23, and the control valve E is provided at a position for directly controlling the inflow amount to the steam turbine 26. Since the inflow control valve is provided, the power turbine 23 and the steam turbine 26 can be efficiently controlled, and the inflow can be completely blocked. The power generation output of the steam turbine 26 can be immediately reduced.
- control valves B and E have been described.
- control valve C bypass control valve
- control for controlling the bypass amount for bypassing the steam turbine 26 are described.
- the opening degree of the valve F may be controlled. In this case, the output of the power turbine 23 and the steam turbine 26 can be finely controlled.
- the example using the control valve opening map of the control valve B has been described.
- the calculation may be performed sequentially using a calculation model instead of the map.
- FIG. 5 is a block diagram illustrating a control logic performed by the control device of the exhaust heat recovery system according to the second embodiment
- FIG. 6 is a flowchart of the control logic according to the second embodiment. 5 and 6 describe the control valve B that controls power generation by the power turbine.
- a control algorithm that is linked is constructed instead of controlling the power turbine and the steam turbine independently. Since the response of the steam system is generally slow, the steam turbine control is operated as a master and the power turbine is operated as a slave to create a power turbine command.
- step S11 when started in step S11, an opening map of the control valve B that provides a desired power turbine output for each engine load is prepared by numerical calculation or measurement in step S12. .
- the control valve opening map of the control valve B is the same as that of FIG. 4 described in the first embodiment, but the calculation of the power turbine output target value is different in this embodiment compared to the first embodiment.
- a power turbine output target value is calculated from the engine load and the steam turbine load by the power generation output command calculator 12 (see FIG. 5).
- the power turbine output target value is calculated only from the engine load.
- the power turbine output target value is corrected in accordance with the change in the load of the steam turbine. Specifically, the power turbine output target value is increased as the steam turbine load decreases and the steam turbine output decreases.
- Correcting means 120 for correcting the power turbine output target value is provided.
- the correction by the correction means may be performed using a calculation formula, or a correction map (corrected power turbine opening command map) 122 in which the relationship between the steam turbine load, the engine load, and the corrected power turbine output target value is set in advance. You may make it calculate based on. By using the correction map, the corrected power turbine output target value can be easily obtained.
- step S14 the power turbine actual output value is measured in step S14, and in step S15, the deviation between the power turbine output target value and the power turbine actual output value is calculated by the subtractor 13 (see FIG. 5). In step S16, the control deviation is calculated.
- the PID controller 14 (see FIG. 5) performs PID control calculation to derive the manipulated variable O 1 .
- step S17 based on the rotational speed deviation from the target rotational speed of the power turbine, an output signal of feedback control (not shown) is converted into an operation amount O 2 by the opening degree converter 11 (see FIG. 5). 11 is used to extract the opening operation amount of the control valve B from which the corrected power turbine output target value is obtained by the opening calculator 15 (see FIG. 5). The operation amount O 3 is obtained. The sum of the manipulated variable O 1 and the operation amount O 2 and the operation amount O 3 sets the opening degree of the control valve B is calculated by the adder 16, 17 (see FIG. 5) at step S9, and repeats the process returns to step S12.
- the power turbine output target value is corrected corresponding to the change in the load of the steam turbine, that is, the control valve opening is controlled while monitoring the load on the steam turbine side on the power turbine side. Therefore, the opening degree command of the control valve can be issued so that the surplus power fluctuation is not directed toward the power turbine.
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Abstract
Description
このようにして、パワータービンの制御バルブの開度がフィードバック制御により設定されていた。
しかしながら、船内負荷が急減した場合は、余剰電力が発生するため、直ちにパワータービン出力を小さくする必要がある。このとき、パワータービン出力制御の応答性によっては電力周波数の変動が大きくなる可能性がある。
同様に、蒸気タービンによる発電においても船内負荷が急減すると余剰電力が発生するため、直ちにバルブの流量制御を行い、蒸気タービン出力を小さくする必要がある。このときも同様に蒸気タービン出力制御の応答性によっては電力周波数の変動が大きくなる可能性がある。
よって、船内負荷が急減してもパワータービンの出力制御の応答性を向上させることができる。
前記流入制御弁の開度制御の場合には、パワータービンへの流入量を直接的に制御できるため、効率よくパワータービンの出力制御を行うことができるとともに、流入を完全に遮断することができるため、船内電力の激減時のパワータービンの発電出力低下を直ちに行うことができる。
また、バイパス制御弁の場合には、パワータービンへの流入量を、パワータービンをバイパスする量を制御することで間接的に制御できるため、パワータービンの出力を細やかに制御できる。
前記エンジン負荷と該エンジン負荷から算出される蒸気タービン出力目標値と前記第2制御弁機構の操作量との関係が予め設定された蒸気タービン開度指令マップから、前記第2制御弁機構の操作量を抽出する蒸気タービンフィードフォワード制御手段とを備え、
前記蒸気タービンフィードフォワード制御手段からの操作量と、前記蒸気タービンフィードバック制御手段からの操作量とを加算して前記第2制御弁機構の操作量を設定することを特徴とする。
この流入制御弁の制御、バイパス制御弁の制御については、前記パワータービンの場合と同様に、流入制御弁の開度制御の場合には、蒸気タービンへの流入量を直接的に制御できるため、効率よく蒸気タービンの出力制御を行うことができるとともに、流入を完全に遮断することができるため、船内電力の激減時の蒸気タービンの発電出力低下を直ちに行うことができる。
また、バイパス制御弁の場合には、蒸気タービンへの流入量を、蒸気タービンをバイパスする量を制御することで間接的に制御できるため、蒸気タービンの出力を細やかに制御できる。
すなわち、蒸気系の応答は遅いため、蒸気タービンをマスタ(主)、パワータービンをスレーブ(副)として動作させて、操作量を設定する。
具体的には、蒸気タービン負荷を監視して、蒸気タービン負荷の変化に対応させてパワータービン出力目標値を補正するパワータービン出力目標値補正手段を有する。
船内電力需要が激減した場合には、蒸気タービンおよびパワータービンのそれぞれの出力(負荷)を低下させるが、蒸気系の応答は遅いため、パワータービンの出力低下に遅れて蒸気タービンの出力低下が生じる。このときに、船内電力は最低必要電力を確保する必要があるため、パワータービンの出力目標値を、蒸気タービンの出力(負荷)状態、つまり蒸気タービンの出力低下状態に応じて上昇させるようにする。
このように、蒸気タービンの負荷状態を監視しながらパワータービンの出力目標値を補正するので、急激な船内電力負荷の低下に対してパワータービンの出力制御の方に偏よらずにパワータービンおよび蒸気タービンを連携した制御とすることができる。
パワータービン23と、蒸気タービン26と、発電機28とは、大きさ及び歯数が異なる互いに噛合する歯車を備える減速機24、27によって接続される。また、パワータービン23、蒸気タービン26、発電機28間の回転軸がクラッチ25を介して接続され、回転動力が伝達されたり遮断されたりする。
蒸気タービン26の後段に設けられる復水器29で蒸気は水に戻され、この水を冷却器31の熱やエンジン22の壁を冷却する熱で温めた後、排ガスエコノマイザーへ供給して蒸発させ蒸気を生成する。
前記エンジン負荷と該エンジン負荷から算出される蒸気タービン出力目標値と前記第2制御弁機構の操作量との関係が予め設定された蒸気タービン開度指令マップ109から、第2制御弁機構の操作量を抽出する蒸気タービンフィードフォワード制御手段110とを備えている。
図2の制御ロジックでは、ステップS1で開始されると、ステップS2でエンジン負荷毎に所望のパワータービン出力が得られる制御弁Bの開度マップを数値計算若しくは実測して用意する。図4は制御弁Bの制御弁開度マップ(パワータービン開度指令マップ)105を示す。
ステップS3では、発電出力指令計算器2(図2参照)によりエンジン負荷からパワータービン出力目標値を算出する。ステップS4でパワータービン実出力値を計測し、ステップS5でパワータービン出力目標値とパワータービン実出力値との偏差が減算器3(図2参照)によって計算され、ステップS6では制御偏差を基にPID制御器4(図2参照)でPID制御演算を行い、操作量O1を導出する。
すなわち、図3のフローチャートを次のように読み替える、ステップS1で開始されると、ステップS2でエンジン負荷毎に所望の蒸気タービンビン出力が得られる制御弁Eの開度マップを数値計算若しくは実測して用意する。図4に示す制御弁Bの制御弁開度マップ105に相当する制御弁Eの制御弁開度マップ(蒸気タービン開度指令マップ)109を用意する。
Claims (8)
- エンジンの排ガスを用いて駆動するパワータービンと、エンジンの排ガスエコノマイザーで発生した蒸気を用いて駆動する蒸気タービンとを備えるとともに、前記パワータービンと前記蒸気タービンとによって発電機を駆動し、前記該パワータービンの前段に配設され前記排ガスの流量を調整してパワータービンの出力を制御する1または複数の制御弁からなる第1制御弁機構と、前記蒸気タービンの前段に配設され蒸気タービンの出力を制御する1または複数の制御弁からなる第2制御弁機構とを備え、前記第1制御弁機構の操作量を制御するパワータービン制御手段と前記第2制御弁機構の操作量を制御する蒸気タービン制御手段とを有する排熱回収システムの制御装置において、
前記パワータービン制御手段は、エンジン負荷から算出されるパワータービン出力目標値と実際のパワータービン出力との偏差をPID制御器によって演算して前記第1制御弁機構の操作量を算出するパワータービンフィードバック制御手段と、
前記エンジン負荷と該エンジン負荷から算出されるパワータービン出力目標値と前記第1制御弁機構の操作量との関係が予め設定されたパワータービン開度指令マップから、前記第1制御弁機構の操作量を抽出するパワータービンフィードフォワード制御手段とを備え、
前記パワータービンフィードフォワード制御手段からの操作量と、前記パワータービンフィードバック制御手段からの操作量とを加算して前記第1制御弁機構の操作量として設定することを特徴とする排熱回収システムの制御装置。 - 前記第1制御弁機構の操作量が、前記パワータービンへの流入量を制御する流入制御弁の開度であることを特徴とする請求項1記載の排熱回収システムの制御装置。
- 前記第1制御弁機構の操作量が、前記パワータービンのバイパス量を制御するバイパス制御弁の開度であることを特徴とする請求項1記載の排熱回収システムの制御装置。
- 前記蒸気タービン制御手段は、エンジン負荷から算出される蒸気タービン出力目標値と実際の蒸気タービン出力との偏差をPID制御器によって演算して前記第2制御弁機構の操作量を算出する蒸気タービンフィードバック制御手段と、
前記エンジン負荷と該エンジン負荷から算出される蒸気タービン出力目標値と前記第2制御弁機構の操作量との関係が予め設定された蒸気タービン開度指令マップから、前記第2制御弁機構の操作量を抽出する蒸気タービンフィードフォワード制御手段とを備え、
前記蒸気タービンフィードフォワード制御手段からの操作量と、前記蒸気タービンフィードバック制御手段からの操作量とを加算して前記第2制御弁機構の操作量を設定することを特徴とする請求項1記載の排熱回収システムの制御装置。 - 前記第2制御弁機構の操作量が、前記蒸気タービンへの流入量を制御する流入制御弁の開度であることを特徴とする請求項4記載の排熱回収システムの制御装置。
- 前記第2制御弁機構の操作量が、前記蒸気タービンのバイパス量を制御するバイパス制御弁の開度であることを特徴とする請求項4記載の排熱回収システムの制御装置。
- 前記パワータービン出力目標値を、前記蒸気タービン負荷の変化に対応させて補正するパワータービン出力目標値補正手段を有し、該補正手段による補正後の補正パワータービン出力目標値に基づいて、前記パワータービンフィードバック制御手段および前記パワータービンフィードフォワード制御手段の制御がなされることを特徴とする請求項1記載の排熱回収システムの制御装置。
- 前記パワータービン出力目標値補正手段は、蒸気タービン負荷とエンジン負荷と補正パワータービン出力目標値との関係があらかじめ設定された補正パワータービン開度指令マップを基に、エンジン負荷と蒸気タービン負荷から補正パワータービン出力目標値を算出することを特徴とする請求項7記載の排熱回収システムの制御装置。
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Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03164526A (ja) * | 1989-12-19 | 1991-07-16 | Mitsubishi Heavy Ind Ltd | 複合内燃機関 |
JP3804693B2 (ja) | 1996-06-21 | 2006-08-02 | 大阪瓦斯株式会社 | 排熱回収システム |
JP2007001339A (ja) | 2005-06-21 | 2007-01-11 | Mitsubishi Heavy Ind Ltd | 船舶の推進装置における内燃機関廃熱回収プラント |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4027145A (en) * | 1973-08-15 | 1977-05-31 | John P. McDonald | Advanced control system for power generation |
US3894396A (en) * | 1973-10-10 | 1975-07-15 | Babcock & Wilcox Co | Control system for a power producing unit |
US4013877A (en) * | 1974-08-13 | 1977-03-22 | Westinghouse Electric Corporation | Combined cycle electric power plant with a steam turbine having an improved valve control system |
US4005581A (en) * | 1975-01-24 | 1977-02-01 | Westinghouse Electric Corporation | Method and apparatus for controlling a steam turbine |
DE4015104A1 (de) * | 1990-05-11 | 1990-11-29 | Tuttass Edmond | Kombinierte waermekraftanlage |
JP2695974B2 (ja) * | 1990-07-31 | 1998-01-14 | 株式会社東芝 | コージェネレーションプラントの出力制御装置 |
US5339632A (en) * | 1992-12-17 | 1994-08-23 | Mccrabb James | Method and apparatus for increasing the efficiency of internal combustion engines |
US6445980B1 (en) * | 1999-07-10 | 2002-09-03 | Mykrolis Corporation | System and method for a variable gain proportional-integral (PI) controller |
DE10392154T5 (de) * | 2002-03-04 | 2004-08-19 | Mitsubishi Heavy Industries, Ltd. | Turbinenanlage und Kombikraftwerk sowie Turbinenbetriebsverfahren |
EP1869293B1 (en) * | 2005-03-29 | 2013-05-08 | UTC Power Corporation | Cascaded organic rankine cycles for waste heat utilization |
JP2009146241A (ja) * | 2007-12-17 | 2009-07-02 | Fuji Koki Corp | 弁制御装置及び弁制御方法 |
JP5173776B2 (ja) * | 2008-12-15 | 2013-04-03 | 三菱重工業株式会社 | 排気エネルギー回収装置 |
-
2009
- 2009-12-24 CN CN201310118406.5A patent/CN103216314B/zh active Active
- 2009-12-24 CN CN2009801518636A patent/CN102265012B/zh active Active
- 2009-12-24 KR KR1020117013000A patent/KR101183505B1/ko active IP Right Grant
- 2009-12-24 WO PCT/JP2009/071486 patent/WO2010074173A1/ja active Application Filing
- 2009-12-24 JP JP2010544133A patent/JP5079102B2/ja not_active Expired - Fee Related
- 2009-12-24 EP EP09834971.5A patent/EP2372127A4/en not_active Withdrawn
- 2009-12-24 US US13/139,341 patent/US20110270451A1/en not_active Abandoned
-
2012
- 2012-06-25 JP JP2012142358A patent/JP5409848B2/ja active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03164526A (ja) * | 1989-12-19 | 1991-07-16 | Mitsubishi Heavy Ind Ltd | 複合内燃機関 |
JP3804693B2 (ja) | 1996-06-21 | 2006-08-02 | 大阪瓦斯株式会社 | 排熱回収システム |
JP2007001339A (ja) | 2005-06-21 | 2007-01-11 | Mitsubishi Heavy Ind Ltd | 船舶の推進装置における内燃機関廃熱回収プラント |
Non-Patent Citations (1)
Title |
---|
See also references of EP2372127A4 |
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Also Published As
Publication number | Publication date |
---|---|
EP2372127A1 (en) | 2011-10-05 |
JP5079102B2 (ja) | 2012-11-21 |
JP5409848B2 (ja) | 2014-02-05 |
KR101183505B1 (ko) | 2012-09-20 |
CN102265012A (zh) | 2011-11-30 |
CN103216314B (zh) | 2015-06-03 |
CN103216314A (zh) | 2013-07-24 |
JP2012211589A (ja) | 2012-11-01 |
KR20110084441A (ko) | 2011-07-22 |
EP2372127A4 (en) | 2014-08-13 |
US20110270451A1 (en) | 2011-11-03 |
JPWO2010074173A1 (ja) | 2012-06-28 |
CN102265012B (zh) | 2013-07-17 |
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