WO2014192669A1 - 脱硝装置の制御装置、脱硝装置、及び脱硝装置の制御方法 - Google Patents
脱硝装置の制御装置、脱硝装置、及び脱硝装置の制御方法 Download PDFInfo
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- WO2014192669A1 WO2014192669A1 PCT/JP2014/063776 JP2014063776W WO2014192669A1 WO 2014192669 A1 WO2014192669 A1 WO 2014192669A1 JP 2014063776 W JP2014063776 W JP 2014063776W WO 2014192669 A1 WO2014192669 A1 WO 2014192669A1
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- exhaust gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D41/0047—Controlling exhaust gas recirculation [EGR]
- F02D41/005—Controlling exhaust gas recirculation [EGR] according to engine operating conditions
- F02D41/0055—Special engine operating conditions, e.g. for regeneration of exhaust gas treatment apparatus
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/06—Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
- F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
- F02M26/19—Means for improving the mixing of air and recirculated exhaust gases, e.g. venturis or multiple openings to the intake system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/34—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with compressors, turbines or the like in the recirculation passage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/35—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with means for cleaning or treating the recirculated gases, e.g. catalysts, condensate traps, particle filters or heaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/04—Engine intake system parameters
- F02D2200/0406—Intake manifold pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/34—Control of exhaust back pressure, e.g. for turbocharged engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1448—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an exhaust gas pressure
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- 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
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/40—Engine management systems
Definitions
- the present invention relates to a denitration device control device, a denitration device, and a denitration device control method.
- exhaust gas from an internal combustion engine such as a diesel engine contains NOx, SOx, and harmful substances such as soot and substances that give a load to the environment. Therefore, various methods that do not discharge such harmful substances have been proposed.
- EGR exhaust gas recirculation
- Patent Document 1 describes an apparatus for recirculating and cooling exhaust gas from an automobile diesel engine.
- the device described in Patent Document 1 includes a compressor driven by an exhaust turbine, and a downstream side of the exhaust turbine and an upstream side of the supercharger are connected by an exhaust gas recirculation path.
- the exhaust gas recirculation path is connected to an air suction pipe before the compressor, and the exhaust gas and air are mixed in the suction pipe and then supplied to the compressor.
- a compressor for a large engine provided in a ship or the like does not have an air suction pipe as described in Patent Document 1, and mixing means for mixing exhaust gas and air and introducing the mixture to the compressor Is provided immediately before the compressor.
- exhaust gas is supplied to the mixing means using a blower that is not provided in the engine described in Patent Document 1. For this reason, in a supercharger for a large engine, if the pressure of the exhaust gas is high, the exhaust gas may be discharged out of the system from the air suction port connected to the mixing means.
- the present invention has been made in view of such circumstances, and is capable of preventing the exhaust gas to be sent to the internal combustion engine from leaking out of the system, the control device for the denitration device, the denitration device, and the denitration device
- An object is to provide a method for controlling an apparatus.
- the following means are employed in the denitration apparatus control apparatus, denitration apparatus, and denitration apparatus control method of the present invention.
- a control apparatus for a denitration apparatus includes an exhaust turbine that is rotationally driven by exhaust gas discharged from an internal combustion engine, one of the air sucked from an intake port and the exhaust gas when the exhaust turbine is rotationally driven.
- a compressor that compresses a portion and sends it to the internal combustion engine; a mixing means that mixes the air and the exhaust gas and guides the air to the suction port; and an air inlet that is connected to the mixing means and guides the air to the mixing means And a blower for sending the exhaust gas to the mixing means, a control apparatus for a denitration apparatus, a pressure measuring means for measuring the pressure of the gas guided to the compressor, and a pressure measurement by the pressure measuring means
- a rotation speed control means for controlling the rotation speed of the blower so that the value is less than the atmospheric pressure.
- the denitration device compresses the exhaust turbine that is rotationally driven by the exhaust gas discharged from the internal combustion engine, and the air and exhaust gas that is sucked from the suction port when the exhaust turbine is rotationally driven, and sends the compressed air to the internal combustion engine.
- a compressor is provided. That is, a supercharger is formed by the exhaust turbine and the compressor.
- the compressor is connected to mixing means for mixing air and exhaust gas and introducing the mixture to the suction port, and air introduction means for introducing air to the mixing means.
- the denitration apparatus also includes a blower that sends exhaust gas to the mixing means.
- the control device of the denitration device measures the pressure of the gas guided to the compressor by the pressure measuring means.
- the gas measured by the pressure measuring means is exhaust gas, air, or a mixture of exhaust gas and air.
- the rotation speed of the blower is controlled by the rotation speed control means so that the pressure measurement value by the pressure measurement means is less than the atmospheric pressure.
- this configuration can prevent the exhaust gas to be sent to the internal combustion engine from leaking out of the system.
- the rotation speed control means sets the pressure measurement value as an upper limit according to any one of the scavenging pressure, the rotation speed of the compressor, the load of the internal combustion engine, and the rotation speed of the internal combustion engine.
- the number of rotations of the blower is controlled so as to be less than the value.
- the exhaust gas to be sent to the internal combustion engine can be prevented from leaking out of the system, and the exhaust gas can be set to an appropriate amount according to the operation of the internal combustion engine.
- the denitration device is provided in a ship, and the upper limit value has a tolerance according to a load fluctuation of the internal combustion engine assumed in the operation of the ship.
- This configuration can more reliably prevent the exhaust gas to be sent to the internal combustion engine from leaking out of the system.
- the rotational speed control means corrects the rotational speed of the blower calculated according to the oxygen concentration supplied to the internal combustion engine so that the measured pressure value is less than atmospheric pressure.
- the rotational speed of the blower is controlled based on the oxygen concentration supplied to the internal combustion engine, the exhaust gas to be sent to the internal combustion engine is moved out of the system while suppressing a decrease in the performance of the internal combustion engine. Leakage can be prevented.
- a denitration apparatus compresses an exhaust turbine that is rotationally driven by exhaust gas discharged from an internal combustion engine, air sucked from an intake port by the exhaust turbine being rotationally driven, and a part of the exhaust gas.
- a compressor for sending to the internal combustion engine, a mixing means for mixing the air and the exhaust gas and introducing the air to the suction port, an air introduction means connected to the mixing means and for introducing the air to the mixing means,
- the blower for sending the exhaust gas to the mixing means, the pressure measuring means for measuring the pressure of the gas guided to the compressor, and the rotation of the blower so that the pressure measurement value by the pressure measuring means is less than atmospheric pressure.
- a control device having a rotation speed control means for controlling the number.
- the control method of the denitration apparatus includes: an exhaust turbine that is rotationally driven by exhaust gas discharged from an internal combustion engine; and the air sucked from an intake port and the exhaust gas that are rotationally driven by the exhaust turbine.
- a compressor for sending to the internal combustion engine, a mixing means for mixing the air and the exhaust gas and introducing it to the suction port, an air introduction means for connecting the air to the mixing means, and for introducing the air to the mixing means, and the exhaust gas Is a control method of a denitration apparatus including a blower that sends the gas to the mixing means, the first step of measuring the pressure of the gas guided to the compressor by the pressure measurement means, and the pressure measurement value by the pressure measurement means is large.
- a second step of controlling the rotational speed of the blower so as to be less than the atmospheric pressure.
- FIG. 1 is a schematic configuration diagram of a denitration apparatus according to an embodiment of the present invention. It is a block diagram of the supercharger which concerns on embodiment of this invention. It is a functional block diagram of the blower rotation speed control part which concerns on embodiment of this invention.
- FIG. 1 is a schematic configuration diagram of a denitration apparatus 10 according to the present embodiment.
- the denitration device 10 according to the present embodiment is, for example, a marine denitration device, and is provided in an internal combustion engine (diesel engine 12 in the present embodiment).
- the denitration apparatus 10 includes a supercharger 14 and an EGR blower 16.
- the supercharger 14 includes an exhaust turbine 18 and a compressor 20.
- the exhaust turbine 18 is rotationally driven by exhaust gas discharged from the diesel engine 12.
- the compressor 20 compresses a part of the air and exhaust gas (hereinafter referred to as “EGR gas”) sucked from the suction port when the exhaust turbine 18 is rotationally driven, and sends the compressed air to the diesel engine 12.
- the compressor 20 is provided at the other end of the rotary shaft 22 provided with the exhaust turbine 18 at one end.
- the compressor 20 also has a return gas casing 24 (also see FIG. 2) that is a mixing means that mixes air and EGR gas and guides them to the suction port of the compressor 20, and air to the return gas casing 24.
- a silencer 26 (see also FIG. 2), which is an air introducing means for guiding, is connected.
- the mixture of air and EGR gas sent from the compressor 20 is cooled by the air cooler 28 and supplied to the diesel engine 12.
- the exhaust gas that has circulated through the exhaust turbine 18 circulates to the compressor 20 via the recirculation path 30.
- the exhaust gas flowing through the recirculation path 30 is a part of the exhaust gas flowing through the exhaust turbine 18 and is hereinafter referred to as “EGR gas”.
- EGR gas Exhaust gas that does not flow through the recirculation path 30 is discharged from the chimney to the outside of the system.
- the recirculation path 30 includes an EGR valve 32, an EGR scrubber 34, and an EGR blower 16 in order from the upstream side.
- the EGR valve 32 adjusts the flow rate of the EGR gas that is circulated to the recirculation path 30.
- the EGR scrubber 34 includes a water treatment device 35, and removes soot and the like contained in the EGR gas by washing the EGR gas with water.
- the EGR blower 16 sends EGR gas to the compressor 20.
- the denitration apparatus 10 is provided with a pressure sensor 38 for measuring the pressure of the gas guided to the compressor 20.
- the gas measured by the pressure sensor 38 is EGR gas, air, or a mixture of exhaust gas and air.
- the denitration device 10 is controlled by a denitration device controller 40.
- the denitration device control device 40 includes a blower rotation speed control unit 42 that controls the rotation speed of the EGR blower 16 so that the pressure measurement value by the pressure sensor 38 is less than the atmospheric pressure.
- FIG. 2 is a configuration diagram of the supercharger 14.
- the exhaust turbine 18 includes a turbine casing 50, a turbine disk 52 that is rotated by exhaust gas supplied from the diesel engine 12, and turbine blades 54 that are provided in the circumferential direction of the turbine disk 52.
- the turbine casing 50 is provided so as to cover the turbine disk 52 and the turbine blades 54.
- the turbine casing 50 passes through a turbine casing inlet 50 a through which exhaust gas is guided from an exhaust gas collecting pipe (not shown) of the diesel engine 12, an exhaust gas passage 50 b that guides exhaust gas from the diesel engine 12 to the turbine blades 54, and the turbine blades 54.
- a turbine casing outlet 50c for guiding the exhaust gas to the outside of the exhaust turbine 18.
- the turbine disk 52 has a disk shape, and a plurality of turbine blades 54 extending radially outward from the center of rotation are provided along the circumferential direction.
- the turbine blades 54 are covered with a turbine casing 50 so as to surround the outside in the radial direction. Exhaust gas is guided to the turbine blade 54 from the exhaust gas passage 50b.
- the turbine disk 52 and the rotating shaft 22 are rotationally driven by the exhaust gas guided to the turbine blades 54.
- the exhaust gas that rotationally drives the turbine disk 52 and the rotary shaft 22 flows out from the turbine blades 54 to the turbine casing outlet 50c.
- the compressor 20 includes a compressor casing 56 and an impeller 58 that compresses air by being driven to rotate.
- the compressor casing 56 is provided so as to cover the impeller 58.
- the compressor casing 56 includes a compressor casing inlet 56a which is a suction port for taking in air and EGR gas from the outside through the silencer 26 and the return gas casing 24, and a spiral chamber 56b into which the air compressed by the impeller 58 is guided.
- the impeller 58 has a compressor casing outlet 56c for discharging the compressed air.
- the impeller 58 has a substantially disk shape, and a plurality of wings (not shown) extending from the center toward the radially outer side are provided on one surface thereof.
- the impeller 58 is covered by the spiral chamber 56b so as to surround the radially outer side. Air and EGR gas sucked from the compressor casing inlet 56a are guided to the impeller 58.
- the impeller 58 is rotationally driven when the exhaust turbine 18 provided on the rotary shaft 22 is rotationally driven.
- the air and EGR gas sucked from the compressor casing inlet 56 a are compressed by the rotationally driven impeller 58, and the compressed air and EGR gas are sent out radially outward of the impeller 58.
- the air and EGR gas compressed by the impeller 58 pass through the spiral chamber 56b and are led out from the compressor casing outlet 56c.
- the compressor casing 56 is provided so as to sandwich the return gas casing 24 between the compressor casing 56 and the silencer 26.
- the return gas casing 24 has an opening 24a connected to an EGR return pipe (not shown) for guiding EGR gas, which is a part of the exhaust gas of the diesel engine 12, at a part of the outer wall thereof.
- the return gas casing 24 is provided with a substantially cylindrical mixing member 62 therein.
- the mixing member 62 has a substantially cylindrical shape, and its diameter is substantially equal to the diameter of the compressor casing inlet 56a.
- the mixing member 62 has one axial end connected to the compressor casing inlet 56a and the other end connected to the silencer 26, so that the air introduced from the silencer 26 into the mixing member 62 is compressed by the compressor. It can pass to the casing inlet 56a.
- the mixing member 62 is formed by forming a perforated plate having a plurality of holes 64 on its side wall into a cylindrical shape. For example, each of the plurality of holes 64 provided in the mixing member 62 has a substantially circular shape.
- Rotating shaft 22 having one end protruding toward exhaust turbine 18 and the other end protruding toward compressor 20 passes through bearing stand 66. Further, a turbine casing 50 and a compressor casing 56 are connected to the bearing stand 66. The turbine casing 50, the bearing stand 66, and the compressor casing 56 are integrally fastened by a plurality of bolts (not shown).
- the bearing stand 66 is provided with a journal bearing (not shown) and a thrust bearing (not shown). These journal bearings are provided in the vicinity on the exhaust turbine 18 side and in the vicinity on the compressor 20 side. With these journal bearings, the rotary shaft 22 can rotate around the axis and is supported by a bearing base 66.
- exhaust gas acts on the turbine blades 54 by the thrust bearings disposed on both sides of a thrust collar (not shown) provided so as to protrude toward the outer periphery in the radial direction of the rotating shaft 22, so that the rotating shaft 22 is axially moved. And the rotation about the rotation shaft 22 is made possible.
- the exhaust gas is guided from the exhaust gas collecting pipe of the diesel engine 12 to the turbine casing inlet 50 a of the turbine casing 50.
- the exhaust gas guided to the turbine casing inlet 50a is guided to the turbine blade 54 through the exhaust gas passage 50b.
- the turbine disk 52 and the rotary shaft 22 are rotationally driven by the exhaust gas guided to the turbine blades 54.
- the exhaust gas that rotationally drives the turbine disk 52 and the rotary shaft 22 flows out from the turbine blades 54 to the turbine casing outlet 50c.
- the impeller 58 is rotationally driven when the rotary shaft 22 is rotationally driven by exhaust gas.
- the impeller 58 is driven to rotate, air is sucked into the silencer 26 from the outer periphery of the silencer 26.
- a part of the exhaust gas of the diesel engine 12 is introduced into the return gas casing 24 as EGR gas from the introduction port 24 a of the return gas casing 24 provided between the silencer 26 and the compressor casing 56. .
- the air sucked through the silencer 26 is guided to the inside of the substantially cylindrical mixing member 62 provided inside the return gas casing 24 by the impeller 58 being rotationally driven. Further, the EGR gas introduced into the return gas casing 24 from the introduction port 24 a of the return gas casing 24 is guided into the mixing member 62 through a plurality of holes 64 provided in the mixing member 62. As a result, the EGR gas can be uniformly mixed with the air passing through the inside of the mixing member 62.
- the air and the EGR gas uniformly mixed in the mixing member 62 are mixed and sucked into the compressor casing 56 from the compressor casing inlet 56a.
- the air-fuel mixture sucked into the compressor casing 56 is compressed by an impeller 58 that is driven to rotate.
- the air-fuel mixture compressed by the impeller 58 is discharged from the compressor casing outlet 56c through the spiral chamber 56b.
- the air-fuel mixture compressed by the supercharger 14 is supplied to the diesel engine 12. Thereby, the air-fuel mixture in which air and EGR gas are sufficiently mixed by the supercharger 14 is supplied to the diesel engine 12.
- the pressure sensor 38 is provided in the vicinity of the end face of the air inlet of the silencer 26. Since the pressure sensor 38 is provided in the vicinity of the end face of the silencer 26 where the exhaust gas may leak out, the control by the blower rotation speed control unit 42, which will be described in detail later, as compared with the case where the pressure sensor 38 is provided elsewhere Good responsiveness.
- the pressure sensor 38 is not limited to this, and may be provided in the vicinity of the end face of the EGR gas inlet of the return gas casing 24 (pressure sensor 38_A) or the outer periphery of the return gas casing 24 (pressure sensor 38_B).
- the blower rotation speed control unit 42 controls the rotation speed of the EGR blower 16 so that a pressure measurement value by the pressure sensor 38 (hereinafter referred to as “compressor suction pressure P suc ”) becomes less than atmospheric pressure.
- the blower rotation speed control unit 42 sets the compressor suction pressure P suc to less than atmospheric pressure, whereby the pressure of the exhaust gas sent to the compressor 20 becomes negative with respect to the atmospheric pressure.
- the pressure of the exhaust gas sent to the compressor 20 becomes negative with respect to the atmospheric pressure, the exhaust gas does not leak out of the system from the silencer 26.
- the blower rotation speed control unit 42 includes, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), and a computer-readable recording medium.
- a CPU Central Processing Unit
- RAM Random Access Memory
- a series of processes for realizing various functions is recorded on a recording medium or the like in the form of a program as an example, and the CPU reads the program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized.
- FIG. 3 is a functional block diagram of the blower rotation speed control unit 42.
- the opening degree of the EGR valve 32 is constant (for example, fully open).
- the blower rotation speed control unit 42 corrects the rotation speed of the EGR blower 16 calculated according to the oxygen concentration supplied to the diesel engine 12 so that the compressor suction pressure P suc is less than atmospheric pressure. To do. Thereby, since the rotation speed of the EGR blower 16 is controlled based on the oxygen concentration supplied to the diesel engine 12, the blower rotation speed control unit 42 controls the diesel engine 12 while suppressing a decrease in the performance of the diesel engine 12. It is possible to prevent the EGR gas to be delivered from leaking out of the system.
- the blower rotation speed control unit 42 rotates the EGR blower 16 so that the compressor suction pressure P suc is equal to or less than the upper limit value corresponding to the scavenging pressure P s or the supercharger rotation speed N t. Control the number.
- the supercharger rotational speed Nt is the rotational speed of the compressor 20.
- the target O 2 concentration calculation unit 70 sets a target value of O 2 concentration to be supplied to the diesel engine 12 (hereinafter referred to as “target O 2 concentration”) based on the load of the diesel engine 12 (hereinafter referred to as “engine load”). And the target O 2 concentration is output to the subtraction unit 72A.
- the target O 2 concentration calculation unit 70 includes, as an example, a map showing the relationship between the engine load and the target O 2 concentration, and calculates the target O 2 concentration based on the map.
- the subtraction unit 72A calculates a difference value between the current O 2 concentration and the target O 2 concentration (current O 2 concentration ⁇ target O 2 concentration), and outputs the difference value to the frequency correction amount calculation unit 74A.
- the frequency correction amount calculation unit 74A calculates a frequency correction amount A, which is a frequency correction amount indicating the rotation speed of the EGR blower 16, by multiplying the difference value by the conversion coefficient ⁇ as shown in the equation (1). Then, the frequency correction amount A is output to the comparison unit 76.
- the conversion coefficient ⁇ is a positive value.
- Frequency correction amount A ⁇ ⁇ (current O 2 concentration ⁇ target O 2 concentration) (1)
- Upper limit calculation unit 78A is the upper limit value of the compressor suction pressure P suc based on the scavenging pressure P s (hereinafter referred to as "suction pressure upper limit value P A".) Is calculated, the suction pressure upper limit value P A to subtraction unit 72B1 Output.
- Upper limit calculation unit 78A includes a map showing the relation between the scavenging pressure P s and the compressor suction pressure P suc, calculates the suction pressure upper limit value P A on the basis of the map.
- the upper limit calculator 78B calculates an upper limit value of the compressor suction pressure P suc (hereinafter referred to as “suction pressure upper limit value P B ”) based on the supercharger rotation speed N t and subtracts the suction pressure upper limit value P B. To the unit 72B2.
- Upper limit calculation unit 78B includes a map showing the relationship between the supercharger speed N t and the compressor suction pressure P suc, calculates the suction pressure upper limit value P B on the basis of the map.
- Suction pressure upper limit value P A and the suction pressure upper limit value P B is the upper limit for the compressor suction pressure P suc and below atmospheric pressure.
- the suction pressure upper limit value P A and the suction pressure upper limit value P B is assumed to have a tolerance in accordance with the load fluctuation of the diesel engine 12 is assumed in the operation of the ship.
- the load of the diesel engine 12 provided in the ship may fluctuate rapidly depending on weather conditions and the like.
- the blower speed control unit 42 By providing the margin to the suction pressure upper limit value P A and the suction pressure upper limit value P B, the blower speed control unit 42, the load of the diesel engine 12 is rapidly increased, when the exhaust pressure is increased with this However, it is possible to more reliably prevent the exhaust gas to be sent to the diesel engine 12 from leaking out of the system.
- the suction pressure of the compressor 20 because should a negative pressure relative to atmospheric pressure, the compressor suction pressure P suc, suction pressure upper limit value P A, and the suction pressure upper limit value P B is a negative value
- Subtraction unit 72B1 includes suction pressure upper limit value P A and the difference value between the compressor suction pressure P suc - calculates (suction pressure upper limit value P A compressor suction pressure P suc), outputs the difference value to the frequency correction amount calculation unit 74B1 To do.
- the frequency correction amount calculation unit 74B1 calculates the frequency correction amount B1 of the EGR blower 16 by multiplying the difference value by the conversion coefficient ⁇ 1 as shown in the equation (2), and the frequency correction amount B1 is compared with the comparison unit 80. Output to.
- the conversion coefficient ⁇ 1 is a positive value.
- Frequency correction amount B1 ⁇ 1 ⁇ (suction pressure upper limit value P A ⁇ compressor suction pressure P suc ) (2)
- Subtraction unit 72B2 includes suction pressure upper limit value P B and the difference value between the compressor suction pressure P suc - calculates (suction pressure upper limit value P B compressor suction pressure P suc), outputs the difference value to the frequency correction amount calculation unit 74B2 To do.
- the frequency correction amount calculation unit 74B2 calculates the frequency correction amount B2 of the EGR blower 16 by multiplying the difference value by the conversion coefficient ⁇ 2 as shown in the equation (3), and the frequency correction amount B2 is compared with the comparison unit 80. Output to.
- the conversion coefficient ⁇ 2 is a positive value.
- Frequency correction amount B2 ⁇ 2 ⁇ (suction pressure upper limit value P B ⁇ compressor suction pressure P suc ) (3)
- the comparison unit 80 compares the frequency correction amount B1 and the frequency correction amount B2 to select which one is lower, and outputs the selected frequency correction amount B to the comparison unit 76.
- the comparison unit 76 When the frequency correction amount B is 0 (zero) or a negative value (B ⁇ 0), the comparison unit 76 outputs the frequency correction amount B to the addition unit 82, and the frequency correction amount B is a positive value. (B> 0), the frequency correction amount A is output to the adder 82.
- the addition unit 82 adds the frequency correction amount A or the frequency correction amount B to the current frequency of the EGR blower 16 and outputs the result to the EGR blower 16 as a frequency command value of the EGR blower 16.
- the blower rotation speed control unit 42 outputs to the EGR blower 16 a frequency command value obtained by adding a frequency correction amount B that is a negative value to the current frequency of the EGR blower 16, so that the EGR blower 16 Lower the frequency of the current.
- the EGR gas guided to the return gas casing 24 has a negative pressure, and the EGR gas is prevented from leaking out of the system.
- the blower rotation speed control unit 42 does not need to correct the frequency of the EGR blower 16, and therefore outputs the frequency correction amount B that is 0 to the addition unit 82 for correction.
- the frequency command value is output to the EGR blower 16 without performing it.
- the blower rotation speed control unit 42 adds the frequency correction amount A that is a positive value to the current frequency of the EGR blower 16.
- the frequency of the EGR blower 16 is increased from the current level.
- the amount of EGR gas guided to the return gas casing 24 increases, and the amount of exhaust gas mixture increases.
- the denitration apparatus 10 includes the exhaust turbine 18 that is rotationally driven by the exhaust gas discharged from the diesel engine 12, the air and EGR gas that are sucked from the intake port when the exhaust turbine 18 is rotationally driven. Is connected to a compressor 20 that compresses the gas and sends it to the diesel engine 12, a return gas casing 24 that mixes air and EGR gas and guides it to the suction port, and a return gas casing 24. A silencer 26 for guiding, and an EGR blower 16 for sending a part of the exhaust gas as EGR gas to the return gas casing 24 are provided.
- the denitration device control device 40 measures the pressure of the gas guided to the compressor 20 and controls the rotation speed of the EGR blower 16 so that the compressor suction pressure P suc becomes less than atmospheric pressure. Therefore, the denitration device control device 40 according to the present embodiment can prevent the EGR gas to be sent to the diesel engine 12 from leaking out of the system.
- the blower rotation speed control unit 42 sets the rotation speed of the EGR blower 16 so that the compressor suction pressure P suc is equal to or less than the upper limit value corresponding to the scavenging pressure P s and the turbocharger rotation speed N t.
- the blower rotation speed control unit 42 may control the rotation speed of the EGR blower 16 so as to be equal to or less than an upper limit value corresponding to the engine load and the engine rotation speed.
- blower rotation speed control unit 42 is configured so that the compressor suction pressure P suc corresponds to at least one of the scavenging pressure P s , the supercharger rotation speed N t , the engine load, and the engine rotation speed.
- the number of revolutions of the EGR blower 16 may be controlled so as to be equal to or less than the upper limit.
- the said embodiment demonstrated the form which controls the rotation speed of the EGR blower 16 so that compressor suction pressure Psuc may become less than atmospheric pressure
- this invention is not limited to this. It is only necessary to control the compressor suction pressure P suc to be less than atmospheric pressure.
- the denitration device control device 40 may use an EGR valve instead of the EGR blower 16 so that the compressor suction pressure P suc is less than atmospheric pressure. It is good also as a form which controls the opening degree of the EGR valve 32 with the form which controls the opening degree of 32, and the EGR blower 16.
Abstract
Description
このため、大型機関用の過給機では、排ガスの圧力が高いと、混合手段に接続されている空気の吸込み口から系外へ排ガスが排出される可能性がある。
そこで、脱硝装置の制御装置は、圧縮機に導かれる気体の圧力を圧力測定手段によって測定する。なお、圧力測定手段によって測定される気体は、排ガス、空気、又は排ガスと空気の混合気である。
そして、圧力測定手段による圧力測定値が大気圧未満となるように、回転数制御手段によってブロアの回転数が制御される。圧力測定手段による圧力測定値を大気圧未満とすることによって、圧縮機へ送出される排ガスの圧力が大気圧に対して負圧となる。圧縮機へ送出される排ガスの圧力が、大気圧に対して負圧となると空気導入手段から排ガスが系外へ漏れだすことはない。
本実施形態に係る脱硝装置10は、一例として、舶用の脱硝装置であり、内燃機関(本実施形態ではディーゼル機関12)に備えられる。
なお、圧縮機20から送出される空気とEGRガスの混合気は、空気冷却器28によって冷却されてディーゼル機関12に供給される。
タービンケーシング50は、タービンディスク52とタービン翼54とを覆うように設けられている。タービンケーシング50は、ディーゼル機関12の排ガス集合管(図示せず)から排ガスが導かれるタービンケーシング入口50aと、ディーゼル機関12の排ガスをタービン翼54へ導く排ガス通路50bと、タービン翼54を通過した排ガスを排気タービン18外へ導くタービンケーシング出口50cとを有している。
圧縮機ケーシング56は、インペラ58を覆うように設けられている。圧縮機ケーシング56は、サイレンサ26及び戻りガス用ケーシング24を介して外部からの空気及びEGRガスを取り入れる吸込み口である圧縮機ケーシング入口56aと、インペラ58が圧縮した空気が導かれる渦巻き室56bと、インペラ58が圧縮した空気を排出する圧縮機ケーシング出口56cとを有している。
ディーゼル機関12の排ガス集合管からタービンケーシング50のタービンケーシング入口50aへ排ガスが導かれる。タービンケーシング入口50aに導かれた排ガスは、排ガス通路50bを経てタービン翼54へ導かれる。タービン翼54に導かれた排ガスによってタービンディスク52及び回転軸22が回転駆動される。タービンディスク52及び回転軸22を回転駆動した排ガスは、タービン翼54からタービンケーシング出口50cに流出する。
ブロア回転数制御部42は、圧力センサ38による圧力測定値(以下「コンプレッサ吸込圧力Psuc」という。)が大気圧未満となるように、EGRブロア16の回転数を制御する。ブロア回転数制御部42は、コンプレッサ吸込圧力Psucを大気圧未満とすることによって、圧縮機20へ送出される排ガスの圧力が大気圧に対して負圧となる。圧縮機20へ送出される排ガスの圧力が、大気圧に対して負圧となるとサイレンサ26から排ガスが系外へ漏れだすことはない。
これにより、ブロア回転数制御部42は、ディーゼル機関12へ供給される酸素濃度を基準にEGRブロア16の回転数が制御するので、ディーゼル機関12の性能の低下を抑制しつつ、ディーゼル機関12に送出されるべきEGRガスが系外へ漏れ出すことを防ぐことができる。
これにより、ブロア回転数制御部42は、ディーゼル機関12に送出されるべきEGRガスが系外へ漏れ出すことを防ぐと共に、EGRガスをディーゼル機関12の動作に応じた適正な量とすることができる。
減算部72Aは、現状のO2濃度と目標O2濃度の差分値(現状O2濃度-目標O2濃度)を算出し、差分値を周波数補正量算出部74Aへ出力する。
周波数補正量算出部74Aは、(1)式に示されるように上記差分値に換算係数αを乗算することで、EGRブロア16の回転数を示す周波数の補正量である周波数補正量Aを算出し、周波数補正量Aを比較部76へ出力する。換算係数αは正の値である。
周波数補正量A=α×(現状O2濃度-目標O2濃度) ・・・(1)
上限値算出部78Bは、過給機回転数Ntに基づいたコンプレッサ吸込圧力Psucの上限値(以下「吸込圧力上限値PB」という。)を算出し、吸込圧力上限値PBを減算部72B2へ出力する。上限値算出部78Bは、一例として、過給機回転数Ntとコンプレッサ吸込圧力Psucとの関係を示したマップを備え、該マップに基づいて吸込圧力上限値PBを算出する。
吸込圧力上限値PA及び吸込圧力上限値PBは、コンプレッサ吸込圧力Psucを大気圧未満とするための上限値である。
船舶に備えられるディーゼル機関12の負荷は、気象条件等に応じて急激に変動する場合がある。吸込圧力上限値PA及び吸込圧力上限値PBに裕度を持たせることによって、ブロア回転数制御部42は、ディーゼル機関12の負荷が急激に増加し、これに伴い排気圧力が上昇した場合でも、ディーゼル機関12に送出されるべき排ガスが系外へ漏れ出すことをより確実に防ぐことができる。
周波数補正量B1=β1×(吸込圧力上限値PA-コンプレッサ吸込圧力Psuc) ・・・(2)
周波数補正量B2=β2×(吸込圧力上限値PB-コンプレッサ吸込圧力Psuc) ・・・(3)
このため、ブロア回転数制御部42は、EGRブロア16の現状の周波数に対して、負の値である周波数補正量Bを加算した周波数指令値をEGRブロア16へ出力することで、EGRブロア16の周波数を現状より下げる。これにより、戻りガス用ケーシング24へ導かれるEGRガスが負圧となり、EGRガスが系外へ漏れ出ることが防止される。
このため、ブロア回転数制御部42は、周波数補正量Aと共に周波数補正量Bが正の値の場合、EGRブロア16の現状の周波数に対して、正の値である周波数補正量Aを加算した周波数指令値をEGRブロア16へ出力することで、EGRブロア16の周波数を現状より上げる。これにより、戻りガス用ケーシング24へ導かれるEGRガスの量が多くなり、排ガス混合量が増加する。
従って、本実施形態に係る脱硝装置制御装置40は、ディーゼル機関12に送出されるべきEGRガスが系外へ漏れ出すことを防ぐことができる。
12 ディーゼル機関
16 EGRブロア
18 排気タービン
20 圧縮機
24 戻りガス用ケーシング
26 サイレンサ
38 圧力センサ
40 脱硝装置制御装置
42 ブロア回転数制御部
Claims (6)
- 内燃機関が排出する排ガスにより回転駆動される排気タービンと、
前記排気タービンが回転駆動することにより吸込み口から吸引した空気及び前記排ガスの一部を圧縮し、前記内燃機関に送出する圧縮機と、
前記空気と前記排ガスを混合して前記吸込み口へ導く混合手段と、
前記混合手段に接続され、前記空気を前記混合手段へ導く空気導入手段と、
前記排ガスを前記混合手段へ送出するブロアと、
を備える脱硝装置の制御装置であって、
前記圧縮機に導かれる気体の圧力を測定する圧力測定手段と、
前記圧力測定手段による圧力測定値が大気圧未満となるように、前記ブロアの回転数を制御する回転数制御手段と、
を備える脱硝装置の制御装置。 - 前記回転数制御手段は、前記圧力測定値が掃気圧力、前記圧縮機の回転数、前記内燃機関の負荷、及び前記内燃機関の回転数の何れか一つに応じた上限値以下となるように、前記ブロアの回転数を制御する請求項1記載の脱硝装置の制御装置。
- 前記脱硝装置は、船舶に備えられ、
前記上限値は、前記船舶の運航で想定される前記内燃機関の負荷変動に応じた裕度を有する請求項2記載の脱硝装置の制御装置。 - 前記回転数制御手段は、前記内燃機関へ供給される酸素濃度に応じて算出された前記ブロアの回転数を、前記圧力測定値が大気圧未満となるように補正する請求項1から請求項3の何れか1項記載の脱硝装置の制御装置。
- 内燃機関が排出する排ガスにより回転駆動される排気タービンと、
前記排気タービンが回転駆動することにより吸込み口から吸引した空気及び前記排ガスの一部を圧縮し、前記内燃機関に送出する圧縮機と、
前記空気と前記排ガスを混合して前記吸込み口へ導く混合手段と、
前記混合手段に接続され、前記空気を前記混合手段へ導く空気導入手段と、
前記排ガスを前記混合手段へ送出するブロアと、
前記圧縮機に導かれる気体の圧力を測定する圧力測定手段、及び前記圧力測定手段による圧力測定値が大気圧未満となるように、前記ブロアの回転数を制御する回転数制御手段を有する制御装置と、
を備える脱硝装置。 - 内燃機関が排出する排ガスにより回転駆動される排気タービン、前記排気タービンが回転駆動することにより吸込み口から吸引した空気及び前記排ガスを圧縮し、前記内燃機関に送出する圧縮機、前記空気と前記排ガスとを混合して前記吸込み口へ導く混合手段、前記混合手段に接続され、前記空気を前記混合手段へ導く空気導入手段、及び前記排ガスを前記混合手段へ送出するブロアを備える脱硝装置の制御方法であって、
前記圧縮機に導かれる気体の圧力を圧力測定手段によって測定する第1工程と、
前記圧力測定手段による圧力測定値が大気圧未満となるように、前記ブロアの回転数を制御する第2工程と、
を含む脱硝装置の制御方法。
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