WO2016175194A1 - Dispositif de récupération d'énergie excédentaire de compresseur d'alimentation pour moteur à combustion interne - Google Patents

Dispositif de récupération d'énergie excédentaire de compresseur d'alimentation pour moteur à combustion interne Download PDF

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Publication number
WO2016175194A1
WO2016175194A1 PCT/JP2016/063013 JP2016063013W WO2016175194A1 WO 2016175194 A1 WO2016175194 A1 WO 2016175194A1 JP 2016063013 W JP2016063013 W JP 2016063013W WO 2016175194 A1 WO2016175194 A1 WO 2016175194A1
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WIPO (PCT)
Prior art keywords
hydraulic
hydraulic pump
internal combustion
combustion engine
hydraulic pressure
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PCT/JP2016/063013
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English (en)
Japanese (ja)
Inventor
信之 坂入
和徳 大田
貴士 谷口
服部　泰典
Original Assignee
三井造船株式会社
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.)
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Application filed by 三井造船株式会社 filed Critical 三井造船株式会社
Priority to KR1020177031285A priority Critical patent/KR101859893B1/ko
Priority to CN201680025870.1A priority patent/CN107532502B/zh
Publication of WO2016175194A1 publication Critical patent/WO2016175194A1/fr

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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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D23/00—Controlling engines characterised by their being supercharged
    • 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

Definitions

  • the present invention relates to a supercharger surplus power recovery device for an internal combustion engine equipped with a supercharger.
  • a turbocharger is used to rotationally drive the turbine by the exhaust gas of the engine, and the supply air density is increased by a compressor rotated by the turbine. The output is improved.
  • a generator is connected to a supercharger and the generator is rotated by the supercharger to generate power (for example, Patent Document 1 and 2).
  • surplus exhaust energy of the engine is directly converted into electric energy, which is used for inboard equipment of a ship equipped with this encin.
  • the applicant of the present invention as a unique technique, effectively uses almost all of the surplus exhaust energy of the engine, and connects the hydraulic pump to the supercharger of the internal combustion engine and rotates the hydraulic pump by the supercharger.
  • Many supercharger surplus power recovery devices for internal combustion engines have been developed for generating hydraulic pressure and recovering surplus exhaust energy using the generated hydraulic pressure (see, for example, Patent Documents 3 and 4).
  • a hydraulic pump is connected to a crankshaft of an internal combustion engine, and the hydraulic pump and a hydraulic pump connected to a supercharger are connected by an oil passage, so that excess exhaust energy is obtained.
  • the hydraulic pump connected to the crankshaft of the internal combustion engine is driven to rotate as a hydraulic motor by the hydraulic pump on the supercharger side, and the surplus power of the supercharger is used to bias the internal combustion engine. It is used, and about 3-4% of the engine output can be recovered. As a result, it is possible to significantly utilize the surplus exhaust energy of the internal combustion engine.
  • this electronically controlled internal combustion engine appropriately adjusts the in-cylinder pressure of the engine by appropriately changing the opening and closing timing of the exhaust valve and the fuel injection valve by an electronic controller, and the internal combustion engine according to the operating conditions and environment.
  • the engine performance can be improved.
  • the hydraulic pressure supplied for operating the exhaust valve and the fuel injection valve varies depending on the engine load, and the amount of hydraulic oil consumed also varies depending on the engine load. Therefore, the hydraulic pressure is controlled by the variable mechanism of the variable displacement hydraulic pump. I have control.
  • this variable displacement hydraulic pump is a system in which the hydraulic pump 103 is driven by shaft power transmitted from the crankshaft of the internal combustion engine 100 via a transmission, or a motor-driven hydraulic pressure (not shown). Driven by a pump.
  • the latter electric motor uses electric power generated by the generator rotated by the power of the auxiliary internal combustion engine described above or different from the above, and accordingly, the fuel consumption of the entire internal combustion engine is correspondingly increased.
  • the hydraulic power necessary for operating the exhaust valve and the fuel injection valve corresponds to approximately 2% of the engine output.
  • the turbocharger surplus power recovery device of the conventional internal combustion engine recovers surplus power of exhaust gas as hydraulic power by rotating the hydraulic pump with the power of the supercharger, and the crankshaft of the engine
  • the hydraulic motor attached to the engine is driven to rotate by this hydraulic power, and the crankshaft is energized to reduce the fuel consumption of the engine.
  • the surplus power recovery device 101 of the supercharger, the exhaust valve, the fuel injection valve, and the like are hydraulically controlled. Therefore, it is necessary to equip both the hydraulic device (hereinafter also referred to as an engine operating device) 102 for the system configuration with a hydraulic pump, valves, safety devices, piping, and the like for the system configuration, resulting in an increase in cost. .
  • the present invention has been made to solve such problems, and in an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, a system for a supercharger surplus power recovery device for the internal combustion engine
  • the overall power transmission efficiency can be drastically improved, and the redundant arrangement of hydraulic equipment can be eliminated, which can greatly reduce the cost and facilitate the design. It is an object to provide a surplus machine power recovery device.
  • a supercharger surplus power recovery device for an internal combustion engine includes an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas path of the internal combustion engine. And a turbocharger that is rotationally driven by the exhaust gas of the internal combustion engine and supplies supercharged air to the internal combustion engine, and is connected to the supercharger and is rotationally driven by the supercharger to generate hydraulic pressure.
  • a first hydraulic pump that is operated, a hydraulic mechanism that supplies hydraulic pressure to an operating device of the internal combustion engine to operate the internal combustion engine, and a power source that is connected to a power source that generates rotational power and is driven to rotate by the power source.
  • a second hydraulic pump that supplies hydraulic pressure to the operating device, a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and a hydraulic mechanism that is disposed from the second hydraulic pump to the operating device.
  • First oil to supply hydraulic pressure In the supercharger excess power recovery apparatus for an internal combustion engine having bets, in that a second oil passage for supplying hydraulic pressure from the first hydraulic pump is disposed in the hydraulic mechanism to the operating device.
  • the supercharger surplus power recovery device for an internal combustion engine is provided in an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas passage of the internal combustion engine.
  • a turbocharger that is rotationally driven by the exhaust gas of the internal combustion engine and supplies the supercharged air to the internal combustion engine;
  • a turbine that is disposed in parallel with the supercharger in the exhaust gas path and is rotationally driven by the exhaust gas;
  • a first hydraulic pump connected to a turbine and driven to rotate by the turbine to generate hydraulic pressure, a hydraulic mechanism for supplying hydraulic pressure to an operating device of the internal combustion engine to operate the internal combustion engine, and a power source for generating rotational power
  • a second hydraulic pump that is rotationally driven by the power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism, a controller that controls operations of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and hydraulic pressure Machine
  • the supercharger surplus power recovery device for an internal combustion engine provided with a first oil passage for supplying hydraulic pressure from the second
  • the operating device for operating the above-mentioned engine means devices such as an exhaust valve and a fuel injection valve necessary for operating the internal combustion engine, and a power source that generates rotational power is, for example, An internal combustion engine, an electric motor, etc. are said.
  • a power source that generates rotational power is, for example, An internal combustion engine, an electric motor, etc. are said.
  • the operating device for operating the above-described engine and the power source for generating rotational power are merely examples, and the present invention is not limited to these.
  • the supercharger surplus power recovery device for an internal combustion engine of the present invention is connected to a supercharger or a turbine and is driven to rotate by the supercharger or the turbine to generate hydraulic pressure.
  • the hydraulic pressure can be directly supplied to the operating device of the internal combustion engine via the second oil passage without using a power source.
  • a conventional supercharger surplus power recovery device for an internal combustion engine in which an operating device for operating an engine is electronically controlled, it is connected to the supercharger and is rotationally driven by this supercharger or turbine to be hydraulically operated.
  • the hydraulic pump connected to the crankshaft of the internal combustion engine is rotationally driven, and then the internal combustion engine and a power source such as an electric motor that is rotationally driven by the electric power generated by the internal combustion engine are operated.
  • the hydraulic pump necessary to supply hydraulic pressure to the equipment is driven to rotate.
  • the second hydraulic pump that is rotationally driven by the power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism must supply a large amount of hydraulic pressure required for operation to the operating device depending on the load of the internal combustion engine. . For this reason, the required capacity or number of second hydraulic pumps must be determined according to the maximum discharge amount.
  • the first hydraulic pump Can supply hydraulic pressure to the operating device via the second oil passage.
  • the required capacity or number of second hydraulic pumps can be reduced by the amount of hydraulic pressure supplied from the first hydraulic pump, and cost reduction can be achieved. Further, the power loss that increases in accordance with the discharge amount can be reduced as the required capacity or the number of second hydraulic pumps decreases.
  • the conventional supercharger surplus power recovery device for the internal combustion engine can be eliminated. That is, the hydraulic pump connected to the crankshaft of the internal combustion engine can be eliminated, and the power loss generated by this hydraulic pump can be completely eliminated.
  • the controller supplies the hydraulic pressure generated by the first hydraulic pump to the operating device via the second oil passage when the internal combustion engine is at a high load.
  • the controller supplies the hydraulic pressure generated by the first hydraulic pump when the internal combustion engine is at a high load directly to the operating device via the second oil passage, so that the excess exhaust energy of the internal combustion engine at the time of the high load is increased. Without power loss, it can be used effectively as the hydraulic pressure required for operating equipment.
  • the hydraulic pressure can still be supplied from the first hydraulic pump to the operating device.
  • the second hydraulic pump can be driven to rotate by the hydraulic pressure generated by the first hydraulic pump via the third oil passage, thereby energizing the rotation of the power source.
  • the power source when the power source is an internal combustion engine, fuel efficiency can be improved directly, and when the power source is an electric motor, it is operated as a generator to generate electric power. Significant improvement in fuel consumption can be achieved.
  • the controller supplies a part of the hydraulic pressure generated by the first hydraulic pump to the operating device via the second oil passage at the time of high load, and the first hydraulic pump It is desirable to supply the remainder of the hydraulic pressure generated by the second hydraulic pump via the third oil passage.
  • the first hydraulic pump can generate a hydraulic pressure that is approximately twice that required for the operating equipment. Accordingly, the controller supplies a part of the hydraulic pressure generated by the first hydraulic pump at the time of high load to the operating device via the second oil passage, and the third hydraulic oil generates the remaining hydraulic pressure generated by the first hydraulic pump.
  • the second hydraulic pump By supplying the second hydraulic pump via the passage, the surplus exhaust energy of the internal combustion engine at the time of high load can be effectively utilized as the hydraulic pressure required for the operating equipment without power loss, and the first hydraulic pressure
  • the rotation of the power source connected to the second hydraulic pump can be energized by the hydraulic pressure generated by the pump.
  • the power source when the power source is an internal combustion engine, fuel efficiency can be improved directly, and when the power source is an electric motor, it is operated as a generator to generate electric power. Significant improvement in fuel consumption can be achieved.
  • the second hydraulic pump is a variable displacement hydraulic pump, and the hydraulic mechanism allows the supply of hydraulic pressure from the second hydraulic pump to the operating device and the first hydraulic pump.
  • a non-return function that prevents backflow of hydraulic pressure from the downstream side of the oil passage to the second hydraulic pump and a control of the controller forcibly allow backflow of hydraulic pressure from the downstream side of the first oil passage to the second hydraulic pump.
  • the first oil passage is provided with a first check valve mechanism having a check release function, and the second oil passage is formed by connecting the operating device side to the downstream side of the first check valve mechanism of the first oil passage.
  • the third oil passage is preferably formed by connecting the second hydraulic pump side to the downstream side of the first check valve mechanism of the first oil passage.
  • the controller turns off the check release function of the first check valve mechanism, so that the second hydraulic pump can supply hydraulic pressure to the operating device of the internal combustion engine, and the first The hydraulic pressure generated by one pump can be supplied to the operating device of the internal combustion engine.
  • the controller since the second hydraulic pump is a variable displacement hydraulic pump, the controller turns on the check release function of the first check valve mechanism, so that the hydraulic pressure generated by the first hydraulic pump is supplied to the second pump.
  • the rotation of the second hydraulic pump including the variable displacement hydraulic pump that is, the rotation of the power source to which the second hydraulic pump is connected can be energized.
  • the hydraulic mechanism can be simplified by the above-described configuration.
  • the hydraulic pump can be rotated forward by the backflow of the hydraulic pressure from the normal discharge port by the variable mechanism.
  • the supercharger surplus power recovery device for the internal combustion engine it is desirable to further include a fourth oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the first hydraulic pump.
  • the controller supplies the hydraulic pressure generated by the second hydraulic pump to the first hydraulic pump via the fourth oil passage when the internal combustion engine is under a low load, thereby supplying the first hydraulic pressure. It is desirable to increase the supercharging capability of the supercharger by energizing the rotation of the pump.
  • the controller supplies the hydraulic pressure generated by the second hydraulic pump to the first hydraulic pump via the fourth oil passage when the internal combustion engine is under a low load, thereby energizing the rotation of the first hydraulic pump and the supercharger
  • the supercharger surplus power recovery apparatus for an internal combustion engine further includes a third oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the first hydraulic pump to the second hydraulic pump, and the first hydraulic pump has a variable capacity.
  • the hydraulic mechanism includes a non-return function that allows the supply of hydraulic pressure from the first hydraulic pump to the second hydraulic pump and prevents backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump;
  • the third oil passage is provided with a second check valve mechanism having a check release function forcibly allowing a backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump under the control of the controller.
  • the oil passage is preferably composed of the third oil passage.
  • the hydraulic mechanism further includes a third oil passage that supplies hydraulic pressure from the first hydraulic pump to the second hydraulic pump, and the first hydraulic pump is a variable displacement hydraulic pump,
  • the second hydraulic pump is forcibly controlled by a non-return function that allows the hydraulic pressure to be supplied from the first hydraulic pump to the second hydraulic pump and prevents the backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump and the controller.
  • a third check valve mechanism having a check release function for allowing a backflow of hydraulic pressure from the first hydraulic pump to the first hydraulic pump is provided in the third oil passage, and the fourth oil passage is constituted by the third oil passage.
  • the hydraulic mechanism can be simplified by the above-described configuration.
  • the hydraulic pump in a variable displacement hydraulic pump, the hydraulic pump can be rotated forward by a reverse flow of hydraulic pressure from a normal discharge port by the variable mechanism.
  • the hydraulic mechanism includes a drain mechanism that drains the hydraulic pressure generated by the first hydraulic pump under the control of the controller and returns the hydraulic pressure to the first hydraulic pump.
  • the hydraulic mechanism includes the drain mechanism that drains the hydraulic pressure generated by the first hydraulic pump under the control of the controller and returns the hydraulic pressure to the first hydraulic pump, thereby supplying the hydraulic pressure from the first hydraulic pump to the operating device.
  • the supply of hydraulic pressure from the first hydraulic pump to the second hydraulic pump and the supply of hydraulic pressure from the second hydraulic pump to the first hydraulic pump can be prevented from being performed.
  • the supercharger surplus power recovery device for an internal combustion engine includes an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas of the internal combustion engine provided in an exhaust gas passage of the internal combustion engine.
  • a supercharger that is rotationally driven by gas and supplies supercharged air to the internal combustion engine; a first hydraulic pump that is connected to the supercharger and is rotationally driven by the supercharger to generate hydraulic pressure; and the internal combustion engine
  • a hydraulic mechanism that supplies hydraulic pressure to the operating equipment of the engine and operates the internal combustion engine; and a power source that is connected to a power source that generates rotational power and is rotated by the power source to supply hydraulic pressure to the operating equipment via the hydraulic mechanism.
  • Two hydraulic pumps a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and a first oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the operating device.
  • a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and a first oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the operating device.
  • Of internal combustion engines equipped with In excess power recovery device comprises a second oil passage for supplying hydraulic pressure to the working device from the first hydraulic pump is disposed in the hydraulic mechanism.
  • the supercharger surplus power recovery device for an internal combustion engine includes an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas passage of the internal combustion engine.
  • a turbocharger that is rotationally driven by the exhaust gas of the engine and that supplies supercharged air to the internal combustion engine, a turbine that is disposed in parallel with the supercharger in the exhaust gas path and is rotationally driven by the exhaust gas, and a turbine
  • a first hydraulic pump that is connected and rotated by a turbine to generate hydraulic pressure, a hydraulic mechanism that supplies hydraulic pressure to an operating device of the internal combustion engine to operate the internal combustion engine, and a power source that generates rotational power.
  • a second hydraulic pump that is rotationally driven by the power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism; a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump; Arrangement In the supercharger surplus power recovery device for an internal combustion engine, which is provided with a first oil passage that supplies hydraulic pressure from the second hydraulic pump to the operating device, the hydraulic pressure is provided from the first hydraulic pump to the operating device. A second oil passage is provided.
  • the power transmission efficiency of the entire system of the supercharger surplus power recovery device of the internal combustion engine can be dramatically improved, and hydraulic devices It is possible to eliminate the redundant deployment, and thereby it is possible to greatly reduce the cost and facilitate the design.
  • FIG. 2 is a circuit diagram showing a flow of a hydraulic circuit when the internal combustion engine of FIG. 1 is under a low load.
  • FIG. 2 is a circuit diagram showing a flow of a hydraulic circuit at a medium load of the internal combustion engine of FIG. 1.
  • FIG. 2 is a circuit diagram showing a flow of a hydraulic circuit when the internal combustion engine of FIG.
  • FIG. 2 is a block diagram showing a supercharger surplus power recovery device for an internal combustion engine different from FIG. 1.
  • FIG. 6 is a partial block diagram showing a supercharger surplus power recovery device for an internal combustion engine, which is further different from FIGS. 1 and 5. It is a block diagram which shows the supercharger surplus power recovery apparatus of the conventional internal combustion engine.
  • Reference numeral 1 in FIG. 1 shows, as an example, a low-speed diesel engine (power source, internal combustion engine) for propulsion mounted on a ship, and this engine 1 is required to operate the engine, for example, an exhaust valve,
  • An operating device such as a fuel injection valve is an electronically controlled engine that is electronically controlled via hydraulic pressure, and a supercharger 5 that supplies supercharged air that is rotationally driven by the exhaust gas to the engine 1. It has.
  • the supercharger 5 includes a compressor 6 and a turbine 7, and the compressor 6 and the turbine 7 are connected by a rotating shaft 8.
  • the turbine 7 is rotationally driven by the exhaust gas of the engine 1, and the compressor 6 is rotated by the turbine 7. Thereby, the air supply density of the engine 1 is increased, and the output of the engine is improved.
  • the supercharger 5 is not necessarily limited to a single stage.
  • the engine 1 is not limited to a marine engine, and the type is not limited to a low-speed diesel engine. Includes gas engines fueled by natural gas, city gas, etc., and all other types of electronic control engines.
  • a transmission 9 is connected to the rotating shaft 8 of the supercharger 5, and a variable displacement first hydraulic pump 10 is connected to the transmission 9.
  • a transmission 3 is connected to one end of the crankshaft 2 of the engine 1, and a variable displacement second hydraulic pump 11 is connected to the transmission 3.
  • the second hydraulic pump 11 can be directly connected to the crankshaft 2 of the engine 1 without providing the transmission 3.
  • the number of the first hydraulic pump 10 and the number of the second hydraulic pumps 11 described above is one in FIG. 1, but is merely an example, and a plurality of units may be provided.
  • the first hydraulic pump 10 and the second hydraulic pump 11 are incorporated in the hydraulic mechanism 20.
  • one discharge port 11a of the second hydraulic pump 11 is connected to the oil passage 21, and the engine described above is passed through the check valve 31, the oil passage 22, the check valve 32, and the oil passage 23 in this order.
  • the hydraulic pressure is supplied by being connected to the control circuit of the one operating device.
  • a first oil passage is formed by the oil passages 21, 22, and 23.
  • the other discharge port 11 b of the second hydraulic pump 11 is connected to one discharge port 10 b of the first hydraulic pump 10 via an oil passage 24.
  • the other discharge port 10a of the first hydraulic pump 10 is connected to the oil passage 26, and the check valve 36, the oil passage 27, the oil passage 22, and the oil passage 23 are connected in this order to the operating device 51 of the engine 1 described above. Connected to the control circuit, it can supply hydraulic pressure. Further, the oil passage 27 is also connected to one discharge port 11 a of the second hydraulic pump 11 through the oil passage 22, the check valve 31, and the oil passage 21 in this order.
  • discharge ports 10a and 10b of the first hydraulic pump 10 and the discharge ports 11a and 11b of the second hydraulic pump 11 are both discharge ports.
  • one of the two is a hydraulic discharge port and the other is a hydraulic intake depending on the operating state.
  • the oil passages 26, 27, 22, and 23 form a second oil passage
  • the oil passages 26, 27, 22, and 21 form a third oil passage
  • the oil passages 21, 22, 27, and 26 form a fourth oil passage, respectively.
  • the check valve 31 is integrated with the electromagnetic switching valve 41 to form the first check valve mechanism 30.
  • the first check valve mechanism 30 is a check that forcibly allows a backflow of hydraulic pressure from the oil passage 22 to the oil passage 21, that is, the second hydraulic pump 11, by switching the electromagnetic switching valve 41 under the control of the controller 50. Has a release function.
  • the check valve 31 allows the hydraulic pressure to be supplied from the second hydraulic pump 11 to the control circuit of the operating device 51 through the oil passage 21 and from the oil passage 22 to the first. 2 A normal check function for preventing the backflow of hydraulic pressure to the hydraulic pump 11 is activated.
  • the check valve 31 is forcibly opened to allow the backflow of hydraulic pressure from the oil passage 22 to the second hydraulic pump 11.
  • an accumulator 45 is disposed between the second hydraulic pump 11 and the check valve 31 to absorb hydraulic pressure fluctuations caused by ocean waves, exhaust valve driving, fuel injection, and the like.
  • the check valve 36 and the electromagnetic switching valve 42 form a second check valve mechanism 35.
  • the second check valve mechanism 35 is a check that forcibly allows the backflow of hydraulic pressure from the oil passage 27 to the oil passage 26, that is, the first hydraulic pump 10 by switching the electromagnetic switching valve 42 under the control of the controller 50. Has a release function.
  • the check valve 31 When the check release function is OFF, the check valve 31 allows the hydraulic pressure to be supplied from the first hydraulic pump 10 to the control circuit of the operating device 51 and the check valve 31 through the oil passage 26. Oil passage 2 A normal check function that prevents the backflow of hydraulic pressure from 7 to the oil passage 26, that is, the first hydraulic pump 10, works. On the other hand, when the check release function is ON, as described above, the check valve 31 is forcibly opened to return the hydraulic pressure from the oil passage 27 to the oil passage 26, that is, the first hydraulic pump 10. Is acceptable.
  • An electromagnetic opening / closing valve 44 is disposed between the oil passage 26 and the oil passage 24, and when the electromagnetic opening / closing valve 44 is opened, the oil pressure of the oil passage 26 is drained to the oil passage 24 to increase the oil pressure of the oil passage 26. Can be opened.
  • the oil path 26, the electromagnetic on-off valve 44, and the oil path 24 constitute a drain mechanism.
  • the controller 50 detects, for example, the intake air suction temperature, the supply air pressure downstream of the supercharger 5 and the like by means of sensors, and, based on the detected supply air pressure, intake temperature, etc., as described later.
  • the operations of the hydraulic pump 10, the second hydraulic pump 11, the electromagnetic switching valves 41 and 42, the electromagnetic on-off valve 44, and the like are electrically controlled.
  • the controller 50 may control the operations of the first hydraulic pump 10, the second hydraulic pump 11, the electromagnetic switching valves 41 and 42, the electromagnetic opening / closing valve 44, and the like using parameters other than the above-described supply pressure and suction temperature. is there.
  • the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG. 2 to turn off the check release function of the first check valve mechanism 30 and 2
  • the electromagnetic switching valve 42 of the check valve mechanism 35 is operated to turn off the check release function of the second check valve mechanism 35. Further, the electromagnetic opening / closing valve 44 is closed.
  • the check valve 31 prohibits the backflow of hydraulic pressure from the oil passage 22 to the oil passage 21, and the check valve 36 prohibits the backflow of hydraulic pressure from the oil passage 27 to the oil passage 26.
  • the controller 50 rotates the electric motor 52 to generate a hydraulic pressure necessary for starting by the hydraulic pump 53 and supplies the hydraulic pressure to the control circuit of the operating device 51.
  • the check valve 32 also prevents backflow of hydraulic pressure from the oil passage 23 to the oil passage 22.
  • the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 to turn on the first check valve mechanism 30. While turning off the check release function, the electromagnetic switching valve 42 of the second check valve mechanism 35 is operated to turn on the check release function of the second check valve mechanism 35. For this reason, the check valve 36 is forcibly opened to allow the backflow of hydraulic pressure from the oil passage 27 to the oil passage 26.
  • the hydraulic pressure generated by the second hydraulic pump 11 is supplied to the control circuit of the operating device 51 via the oil passage 21, the check valve 31, the oil passage 22, the check valve 32, and the oil passage 23 in this order.
  • the hydraulic pressure generated by the second hydraulic pump 11 flows through the oil passage 21, the check valve 31, the oil passage 22, the oil passage 27, the forcibly opened check valve 36, and the oil passage 26 in this order.
  • the rotation of the supercharger 5 connected to the first hydraulic pump 10 is energized by the hydraulic pressure generated by the second hydraulic pump 11 so that the supercharging at the time of low load, which tends to be insufficient, is properly performed.
  • the variable displacement first hydraulic pump 10 can rotate the supercharger 5 in the forward direction also by the backflow of the hydraulic pressure from the discharge port 10a by the variable mechanism.
  • the controller 50 reads the intake air intake temperature detected by the sensor, the supply air pressure in the supply passage on the downstream side of the supercharger 5, and the like. Further, the necessary power for energizing the supercharger 5 is set in the controller 50 for each engine load. The controller 50 controls the power for energizing the supercharger 5 by appropriately changing the capacity of the variable displacement type first hydraulic pump 10 based on the supply pressure, the suction temperature, and the like.
  • the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG.
  • the non-return release function 30 is turned off and the electromagnetic on-off valve 44 is opened.
  • the hydraulic pressure generated by the first hydraulic pump is drained from the oil passage 26 to the oil passage 24 through the electromagnetic on-off valve 44 and released, so that the pressure is low and the check is not performed. It does not flow through the valve 36 to the high pressure oil passage 27.
  • the first hydraulic pump 10 that is rotationally driven by the supercharger 5 is in a so-called no-load operation, but a constant pressure of hydraulic pressure is discharged to cool the system.
  • the hydraulic pressure generated by the second hydraulic pump 11 is supplied to the control circuit of the operating device 51 through the oil passage 21, the check valve 31, the oil passage 22, the check valve 32, and the oil passage 23.
  • the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG. 3 to release the check of the first check valve mechanism 30. Since the function is OFF, the oil pressure in the oil passage 27 does not flow to the oil passage 26 through the check valve 36 due to the normal check function of the check valve 36.
  • the first hydraulic pump 10 when the internal combustion engine is at a medium load, for example, during a load of 35 to 50%, the first hydraulic pump 10 is in a no-load operation and the hydraulic pressure is supplied to the operating device 51 only by the second hydraulic pump 11. The If it is necessary to disconnect the hydraulic pressure between the first hydraulic pump 10 on the supercharger 5 side and the second hydraulic pump 11 on the engine 1 side, for example, in the case of an emergency stop, the same as described above Operation is performed.
  • the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG.
  • the check release function of the mechanism 30 is turned on, and the electromagnetic switching valve 42 of the second check valve mechanism 35 is operated to turn off the check release function of the second check valve mechanism 35. Further, the electromagnetic on-off valve 44 is closed.
  • the check valve 31 of the first check valve mechanism 30 is forcibly opened to allow a backflow of hydraulic pressure from the oil passage 22 to the oil passage 21, that is, the second hydraulic pump 11.
  • the check valve 36 of the second check valve mechanism 35 also allows the flow of hydraulic pressure from the oil passage 26 to the oil passage 27 by a normal check function.
  • the hydraulic pressure generated by the first hydraulic pump 10 is supplied to the control circuit of the operating device 51 through the oil passage 26, the check valve 36, the oil passage 27, the check valve 32, and the oil passage 23 in this order. Is done. For example, when the load is 50% or more, all of the hydraulic pressure required by the operating device 51 can be supplied from the first hydraulic pump 10.
  • the first hydraulic pump 10 can generate a hydraulic pressure that is, for example, about twice that required for the operating device 51. For this reason, the hydraulic pressure generated by the first hydraulic pump 10 passes through the oil passage 26, the check valve 36, the oil passage 27, the oil passage 22, the check valve 31, and the oil passage 21 in this order. 11 is also supplied to the discharge port 11a to urge the rotation of the second hydraulic pump 11.
  • the controller 50 adjusts the hydraulic power recovered from the supercharger 5 by appropriately changing the capacity of the first hydraulic pump 10 based on the maximum power recoverable from the supercharger 5 set in advance.
  • the second hydraulic pump 11 may be connected not to the engine but to an electric motor (power source) 54 that generates rotational power in the same manner as the engine.
  • an electric motor for example, an induction motor is used.
  • the number of revolutions of the induction motor is determined by the frequency of the power system, and always rotates at a constant speed. For this reason, the rotation speed control of the electric motor 54 by the above-described hydraulic mechanism 20 or the like is not particularly required.
  • the above-described surplus hydraulic pressure supplied from the first hydraulic pump 10 generates electric power by operating the motor 54 as a generator, and this electric power is supplied to the power system. Since electric power required in a ship or the like is usually generated by a generator that is rotationally driven by an engine, the fuel efficiency of the engine can be improved as a result. In addition, since the operation of the supercharger surplus power recovery device for the internal combustion engine at the time of low load, medium load, and high load of the engine is the same as that of the engine 1 described above, the description thereof is omitted.
  • a power turbine 55 is disposed in the exhaust gas passage 4 of the engine in parallel with the supercharger 5 via a flow rate adjusting valve 56, and the first hydraulic pump 10 is connected to the power turbine 55.
  • the operation of the supercharger surplus power recovery device for the internal combustion engine at the time of medium load and high load of the engine in this case is the same as that of the engine 1 described above.
  • the rotation of the supercharger 5 cannot be directly urged through the first hydraulic pump 10 by the hydraulic pressure generated by the second hydraulic pump 11 when the engine is under a low load.
  • Others are the same as in the case of the supercharger 5 described above, and the description is omitted.
  • the first hydraulic pump described above is not necessarily a variable displacement type, and may be a fixed displacement type. If it is a fixed capacity type, a large space can be saved. However, when the first hydraulic pump is of a fixed displacement type, the pump cannot be rotated forward by the backflow of the hydraulic pressure from the discharge port. It cannot be added.
  • the supercharger surplus power recovery device of the internal combustion engine is connected to the supercharger 5 or the power turbine 55, and is rotated by the supercharger 5 or the power turbine 55 to generate hydraulic pressure.
  • the hydraulic pump 10 can directly supply hydraulic pressure to the operating device 51 of the engine 1 without going through the engine 1 or the electric motor 52 which is a power source.
  • the conventional second hydraulic pump that is rotationally driven by this power source and supplies hydraulic pressure to the operating equipment via the hydraulic mechanism supplies the hydraulic pressure required for operation to the operating equipment when the internal combustion engine is under a high load. Must be supplied in large quantities. For this reason, the required capacity or number of second hydraulic pumps is determined according to the maximum discharge amount.
  • the first hydraulic pressure The pump 10 directly supplies hydraulic pressure to the operating device 51 via the second oil passage.
  • the required capacity or the number of the second hydraulic pumps 11 can be reduced by the amount of hydraulic pressure supplied from the first hydraulic pump 10, and the cost can be reduced. Further, the power loss that increases in accordance with the discharge amount can be reduced as the required capacity or the number of the second hydraulic pumps 11 decreases.
  • the first hydraulic pump 10 can generate a hydraulic pressure that is, for example, about twice that required for the operating device.
  • the controller 50 supplies a part of the hydraulic pressure generated by the first hydraulic pump 10 to the operating device 51 at the time of high load, and the first hydraulic pump 10 generates it. Since the remaining hydraulic pressure is supplied to the second hydraulic pump 11, it is possible to effectively use the excess exhaust energy of the engine 1 at the time of high load as the hydraulic pressure required for the operating device 51 without power loss due to the hydraulic pump.
  • the rotation of the power source to which the second hydraulic pump 11 is connected can be urged by the hydraulic pressure generated by the first hydraulic pump 10.
  • the power source is the engine 1
  • fuel efficiency is improved directly
  • the power source is the electric motor 52
  • this is operated as a generator to generate electric power.
  • the fuel consumption of the entire internal combustion engine can be improved.
  • a load up to 35% is a low load
  • a load 35 to 50% is a medium load
  • a load 50% or more is a high load.
  • it is different depending on the type and usage form of the internal combustion engine, and is not limited thereto.
  • the supercharger surplus power recovery device for an internal combustion engine according to the present invention is not necessarily mounted on the above-described ship if the operating device for operating the engine is an electronic control through a hydraulic pressure and has a supercharger. It is not limited to the low-speed diesel engines for propulsion that are used, but can be widely used for all kinds of internal combustion engines and for all types of internal combustion engines.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention a pour objet d'améliorer considérablement l'efficacité de transmission de puissance et d'éviter d'avoir à installer des dispositifs hydrauliques redondants. La présente invention est équipée: d'un moteur à combustion interne (1) pour lequel des dispositifs d'actionnement (51) qui permettent l'actionnement du moteur sont commandées électroniquement au moyen d'une pression hydraulique; d'un compresseur d'alimentation (5); d'une première pompe hydraulique (10) qui est entraînée en rotation par le compresseur d'alimentation, ce qui permet de générer une pression hydraulique; d'un mécanisme hydraulique (20); d'une seconde pompe hydraulique (11) qui est entraînée en rotation par la source d'alimentation (1) et qui fournit une pression hydraulique aux dispositifs d'actionnement; d'un dispositif de commande (50) permettant de commander le fonctionnement de la première pompe hydraulique, de la seconde pompe hydraulique et du mécanisme hydraulique; de premiers passages d'huile (21, 22, 23) permettant de fournir une pression hydraulique à partir de la seconde pompe hydraulique aux dispositifs d'actionnement; et de deuxièmes passages d'huile (26, 27, 22, 23) permettant de fournir une pression hydraulique à partir de la première pompe hydraulique aux dispositifs d'actionnement. En outre, la présente invention est équipée de troisièmes passages d'huile (26, 27, 22, 21) permettant de fournir une pression hydraulique à partir de la première pompe hydraulique à la seconde pompe hydraulique et de quatrièmes passages d'huile (21, 22, 27, 26) permettant de fournir une pression hydraulique à partir de la seconde pompe hydraulique à la première pompe hydraulique.
PCT/JP2016/063013 2015-04-30 2016-04-26 Dispositif de récupération d'énergie excédentaire de compresseur d'alimentation pour moteur à combustion interne WO2016175194A1 (fr)

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KR1020177031285A KR101859893B1 (ko) 2015-04-30 2016-04-26 내연 기관의 과급기 잉여 동력 회수 장치
CN201680025870.1A CN107532502B (zh) 2015-04-30 2016-04-26 内燃机的增压器剩余动力回收装置

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JP2015092862A JP6012810B1 (ja) 2015-04-30 2015-04-30 内燃機関の過給機余剰動力回収装置
JP2015-092862 2015-04-30

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JP6409162B1 (ja) * 2017-10-02 2018-10-24 株式会社三井Ｅ＆Ｓマシナリー 内燃機関の過給機余剰動力回収装置及び船舶

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KR200488841Y1 (ko) * 2018-02-07 2019-03-26 (주)준마플랜트 집진기
KR20200140504A (ko) * 2019-06-07 2020-12-16 가부시키가이샤 미쯔이 이앤에스 머시너리 내연기관의 과급기 잉여동력 회수장치 및 선박

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JP6383925B1 (ja) * 2017-06-21 2018-09-05 株式会社三井Ｅ＆Ｓマシナリー 内燃機関の過給機余剰動力回収装置及び船舶
WO2018235887A1 (fr) * 2017-06-21 2018-12-27 株式会社三井Ｅ＆Ｓマシナリー Dispositif de récupération d'énergie excédentaire de compresseur de suralimentation pour moteur à combustion interne, et navire
JP2019007376A (ja) * 2017-06-21 2019-01-17 株式会社三井Ｅ＆Ｓマシナリー 内燃機関の過給機余剰動力回収装置及び船舶
KR20190025747A (ko) * 2017-06-21 2019-03-11 가부시키가이샤 미쯔이 이앤에스 머시너리 내연 기관의 과급기 잉여 동력 회수 장치 및 선박
KR102018587B1 (ko) * 2017-06-21 2019-11-04 가부시키가이샤 미쯔이 이앤에스 머시너리 내연 기관의 과급기 잉여 동력 회수 장치 및 선박
JP6409162B1 (ja) * 2017-10-02 2018-10-24 株式会社三井Ｅ＆Ｓマシナリー 内燃機関の過給機余剰動力回収装置及び船舶
WO2019069816A1 (fr) * 2017-10-02 2019-04-11 株式会社三井Ｅ＆Ｓマシナリー Dispositif de récupération de puissance en excès de turbocompresseur pour moteur à combustion interne, et navire
KR20190042016A (ko) * 2017-10-02 2019-04-23 가부시키가이샤 미쯔이 이앤에스 머시너리 내연 기관의 과급기 잉여 동력 회수 장치 및 선박
KR102012289B1 (ko) 2017-10-02 2019-08-20 가부시키가이샤 미쯔이 이앤에스 머시너리 내연 기관의 과급기 잉여 동력 회수 장치 및 선박

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CN107532502A (zh) 2018-01-02
CN107532502B (zh) 2020-01-21
JP6012810B1 (ja) 2016-10-25
JP2016211386A (ja) 2016-12-15
KR20170124622A (ko) 2017-11-10

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