WO2008020550A1 - 6-cycle engine with regenerator - Google Patents
6-cycle engine with regenerator Download PDFInfo
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- WO2008020550A1 WO2008020550A1 PCT/JP2007/065334 JP2007065334W WO2008020550A1 WO 2008020550 A1 WO2008020550 A1 WO 2008020550A1 JP 2007065334 W JP2007065334 W JP 2007065334W WO 2008020550 A1 WO2008020550 A1 WO 2008020550A1
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- Prior art keywords
- engine
- regenerator
- cycle
- exhaust
- pressure
- Prior art date
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- 230000001172 regenerating effect Effects 0.000 claims abstract description 84
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B75/021—Engines characterised by their cycles, e.g. six-stroke having six or more strokes per cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/10—Engines with prolonged expansion in exhaust turbines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
- F01L1/38—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle for engines with other than four-stroke cycle, e.g. with two-stroke cycle
-
- 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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/26—Multi-cylinder engines other than those provided for in, or of interest apart from, groups F02B25/02 - F02B25/24
-
- 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
- F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
- F02B63/04—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for electric generators
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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
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
-
- 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
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
- F02M35/10222—Exhaust gas recirculation [EGR]; Positive crankcase ventilation [PCV]; Additional air admission, lubricant or fuel vapour admission
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
-
- 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
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
- F02B2031/006—Modifying induction systems for imparting a rotation to the charge in the cylinder having multiple air intake valves
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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
- F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional 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
- F02M26/13—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
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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
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/23—Layout, e.g. schematics
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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
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/1015—Air intakes; Induction systems characterised by the engine type
- F02M35/10203—Rotary, e.g. "Wankel", engines; Engines with cylinders in star arrangement; Radial piston engines; W-engines
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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
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/104—Intake manifolds
- F02M35/108—Intake manifolds with primary and secondary intake passages
- F02M35/1085—Intake manifolds with primary and secondary intake passages the combustion chamber having multiple intake valves
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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
Definitions
- the present invention relates to a combined cycle internal combustion engine that improves fuel efficiency by using a positive displacement internal combustion engine combined with a regenerator as a 6-cycle engine, and its use.
- regenerator such a device that converts the pressure energy remaining in the exhaust gas into motive power
- regenerative pressure the pressure at the exhaust port that serves as the inlet pressure of the regenerator
- Pescara Cycle As a gas turbine engine that uses a reciprocating piston engine as a combustion engine in a positive displacement type as a combustion chamber, a free piston type gas turbine called a Pescara Cycle is known.
- the amount of gas can be changed by continuously changing the vane angle of the nozzle of the exhaust turbine, changing the opening area of the turbine nozzle, and changing the gas passage area.
- Corresponding systems are known (see, for example, Patent Document 4).
- Variable nozzle number Bin is disclosed in the application on which the priority of this application is based.
- a series noble vehicle that travels by converting the output of the internal combustion engine into electric power and driving the vehicle driving motor with the electric power.
- Paralleleno and hybrid vehicles are known, in which a vehicle is driven via a transmission with the output from an internal combustion engine, and a motor is directly connected to the output shaft of the engine and the motor is driven by electric power from a battery! / (For example, see Patent Document 5).
- Patent Document 1 Japanese Patent No. 3739725
- Patent Document 2 Japanese Utility Model Publication 2-96435
- Patent Document 3 Japanese Patent No. 2819676
- Patent Document 4 Japanese Patent Laid-Open No. 2001-12252 FIG.
- Patent Document 5 Patent 2857666
- Patent Document 6 Japanese Unexamined Patent Application Publication No. 2006-22890
- the expansion ratio of the combustion gas is determined by the compression ratio.
- the intake air is adiabatically compressed during the compression stroke, burned in a state where the temperature has risen, and expanded by the compression ratio in the explosion / expansion stroke for power, so the exhaust valve opens when the pressure is still significantly higher than the outside air pressure.
- the exhaust gas energy has been released to the atmosphere.
- the inventive concept of an internal combustion engine intended to utilize this pressure energy and having an expansion ratio larger than the compression ratio is the concept of the Atkinson cycle and has been known for a long time.
- the mirror cycle is an attempt to apply it to a normal 4-cycle engine by changing the timing of the intake valve.
- these engines have lower output if the displacement is the same, and the friction due to reciprocating motion does not change. There was a problem of increasing the ratio.
- abnormal combustion means that when the air-fuel mixture in the combustion chamber rises in temperature locally, the air-fuel mixture self-ignites and burns at once due to the temperature rise caused by the pressure increase prior to the propagation of the flame from the spark plug. This phenomenon is called knocking. If abnormal combustion occurs, it will burn at a time earlier than the intended combustion time, causing the pressure in the combustion chamber near the top dead center of the piston to rise abnormally, causing an unpleasant knocking noise and Damage to parts such as the head and the head can cause a significant decrease in engine durability. However, when trying to regenerate the exhaust energy, the amount of energy that can be regenerated is reduced by the amount of energy thrown away into the cooling water.
- a gas turbine engine has an advantage that it is compact in terms of output. Partial power There is a disadvantage that it takes time from start-up when fuel efficiency is bad to full opening.
- the “free piston gas turbine” is known, and the part of the positive displacement engine that forms the combustion chamber takes the form of a two-cycle engine, so the regenerative pressure is reduced to the scavenging pressure.
- the exhaust valve is opened, the exhaust gas freely expands to the scavenging pressure, and some pressure energy is released.
- the supercharged air is sent in excess of the amount required for combustion in the cylinder, it was inevitably impossible to use a premixed engine, and it was limited to a direct injection engine. Since it does not have a crankshaft, it has the disadvantages of poor controllability of the number of cycles per hour corresponding to the engine speed and poor response to load fluctuations.
- exhaust gas recirculation (EGR) system is used to actively send exhaust gas to the intake air of the engine.
- EGR exhaust gas recirculation
- the oxygen concentration in the intake decreases and the amount of fuel that can be burned decreases and the output decreases, whereas the scavenging contains fresh air and passes through the catalyst.
- exhaust gas to be exhausted still has excessive oxygen.
- the cylinder arrangement of a multi-cylinder 6-cycle engine can generally be the same as the cylinder arrangement used in a 2-cycle engine.
- a 6-cycle engine with a number of cylinders that is a multiple of 3 cannot be used as an engine for passenger cars or the like because it is not an equidistant engine with a 2-cycle cylinder arrangement.
- 6-cylinder engines with a small number of explosions per revolution are often desired to have about 6 cylinders! /, But are often used in vehicles, etc./ This is a problem because there are only arrangements where primary vibrations occur.
- the direct injection engine includes a compression ignition engine and a spark ignition engine provided with a fuel injection valve in a cylinder.
- the regenerative pressure that maximizes the theoretical efficiency of the entire positive displacement engine with regenerator is called the ideal regenerative pressure.
- the concept of a hybrid vehicle shall be understood to include both electric and hydraulic vehicles.
- a hydraulic pump is used for the generator, a pressure accumulator is used for the battery, When it is written as a power line, it is a high-pressure oil passage, and when it is written that power is converted into electric power, it means that the fluid is pressurized and pumped. The same applies to the claims.
- a first problem solving means of the present invention is an internal combustion engine characterized in that a positive displacement engine and an engine that extracts the output from the exhaust thereof by a regenerator are a six-cycle engine with a regenerator.
- the combustion chamber and the exhaust valve are cooled by scavenging by the stroke of (5) scavenging introduction and (6) scavenging exhaust, Even if the regenerative pressure is increased, there is an advantage that the exhaust valve will not be melted and the regenerator will be made easier.
- the gas in the combustion chamber that may flow backward when the intake valve is opened at the start of the intake stroke is scavenging, and even if the regenerative pressure increases, the temperature is low and no backfire occurs even if the intake is touched.
- the 6-cycle engine can cool the combustion chamber from the inside, so that abnormal combustion is unlikely to occur even when "insulated”. For this reason, the combustion energy previously discarded in the cooling water can be converted into power by the regenerator, which has the advantage of improving the regenerative efficiency.
- a second problem solving means of the present invention comprises a scavenging port independent of an intake port,
- the internal combustion engine according to the first problem solving means is characterized by having a system for circulating the exhaust gas from the regenerator mainly to the scavenging port.
- the second problem solving means has an effect of promoting the reduction action of the catalyst by lowering the oxygen concentration of the exhaust gas passing through the catalyst without lowering the oxygen concentration in the intake air.
- a direct injection 6-cycle engine there is a method in which both scavenging and intake ports are shared and fresh air is supplied, but in that case, a fixed equipment type such as a flushing facility is used to remove nitrogen oxides in the exhaust.
- a catalytic system can be used for the exhaust purification system, which has the advantage of being miniaturized.
- a third problem-solving means of the present invention is an internal combustion engine according to the first problem-solving means characterized in that the exhaust manifold between the 6-cycle engine and the regenerator is covered with a heat insulating material and insulated. It is an institution.
- the third problem solving means has an advantage that the regenerative output is improved without wastefully throwing away the energy of the exhaust gas supplied to the regenerator.
- the exhaust turbine is actively cooled to prevent the exhaust turbine journal from being damaged by heat, and the exhaust manifold is also cooled by directly touching the outside air. It was.
- the exhaust temperature is low due to the presence of scavenging air, so the exhaust manifold hold positively and guiding more exhaust energy to the regenerator increases the overall efficiency of the engine.
- the force S tends to take time force S to increase the temperature of the catalyst compared to a 4-cycle engine, which also has the effect of shortening this.
- One way to raise the temperature of the exhaust catalyst is to keep EGR gas around the catalyst and keep it warm. In order to improve efficiency, the exhaust port to the regenerator should be further insulated.
- a fourth problem solving means of the present invention includes a mechanism for changing the amount of exhaust gas passing through the regenerator, and by changing the regenerative pressure by the mechanism, the output of the six-cycle engine and the regenerator are
- the internal combustion engine according to the first problem solving means is characterized in that the output ratio of the engine can be controlled.
- an internal combustion engine is provided that is suitable for supplying power by changing the power distribution ratio with respect to two loads. For example, apart from the driving force for driving, the driving force of the machine part that harvests and thresh agricultural products is required regardless of the driving speed. It is suitable as a power source for moving objects such as agricultural machinery and pleasure boats that need to drive relatively large generators apart from propulsion!
- the 6-cycle engine consumes its own kinetic energy to discharge the gas in the cylinder. Also, if the regenerative pressure is increased, the amount of gas remaining in the combustion chamber increases during the scavenging exhaust stroke, and the amount of intake gas decreases during the next (1) intake stroke, resulting in a decrease in the output torque of the 6-cycle engine. Due to these two effects, the output of the 6-cycle engine decreases as the regenerative pressure increases, whereas the output of the regenerator simply increases as the regenerative pressure increases.
- This problem-solving means controls the ratio of the output from the 6-cycle engine and the regenerator by controlling the regenerative pressure using this principle.
- This problem solving means has an effect of preventing the output from the regenerator from becoming too large by controlling the regenerative pressure to be substantially constant regardless of the load of the 6-cycle engine.
- a 6-cycle engine with a regenerator introduces more intake air and increases fuel when the load increases, so the maximum pressure increases.
- the ideal regenerative pressure also rises, and the expansion ratio inside the regenerator also rises to cope with it, so the output from the regenerator increases more than the output increase of the entire engine.
- the expansion ratio in the regenerator does not change, and the output of the regenerator is only proportional to the exhaust gas amount of the entire engine, so the output of the regenerator can be suppressed. .
- the generator that absorbs the output of the regenerator can be downsized, and the load capacity of the controller, the capacitor that stores the power, and the motor that uses the generated power is also small. This is an advantage that the whole system becomes compact.
- the overall efficiency of the engine including the regenerator at full load, is slightly lower, but the output of the 6-cycle engine alone at full load is higher than when the ideal regenerative pressure is used, and the exchange of scavenging and intake gas Higher efficiency increases the maximum output of the entire engine, and has the advantage of being thermally comfortable.
- a fifth problem solving means of the present invention is that a supercharger is provided at an intake port of a 6-cycle engine, and a gas turbine as a regenerator is provided at an exhaust port, and a main output is taken out from the gas turbine.
- An internal combustion engine according to the first problem-solving means is provided at an intake port of a 6-cycle engine, and a gas turbine as a regenerator is provided at an exhaust port, and a main output is taken out from the gas turbine.
- the 6-cycle gas turbine has a high power shaft speed and is a prime mover that is compact and easy to control.
- the generator can be made compact because the speed of cutting the magnetic flux of the generator is high because the rotational speed of the output shaft is high, and the generator voltage can be made high.
- the 6-cycle gas turbine has a regenerative pressure higher than the supercharging pressure, it is not necessary to increase the amount of scavenging more than the free piston type gas turbine, and the exhaust expands freely during the thermal cycle. There is nothing to do, so the thermal efficiency is high.
- the 6-cycle gas turbine can be used not only for diesel engines but also for premixed engines because it can mix air into the intake port and fresh air and circulating gas into the scavenging port. There is. Since a 6-cycle engine with a crankshaft is used for the positive displacement engine, it is possible to use an internal combustion engine type control system that uses a crankshaft, which makes it easy to control engine speed and load fluctuations. have.
- the positive displacement engine generates inertial vibration due to the reciprocating motion of the piston.
- a drive shaft such as a screw with the body
- the output shaft is fixed to the hull and so on, and the vibration propagates to the hull, causing passengers to feel uncomfortable.
- the output of a 6-cycle engine which is a positive displacement engine
- the output of a 6-cycle engine is used to drive auxiliary equipment such as a turbocharger and a generator. Vibration does not propagate to the hull. Due to the presence of the regenerator, the exhaust noise is quiet and the fuel efficiency is good.
- a drive shaft such as a screw can be turned directly from a turbine with little vibration, or once converted into electric power by a generator and used by the motor. As a result, it is possible to achieve both fuel efficiency and merchandise as a power source for passenger ships and hybrid vehicles.
- the cooling system can be simplified due to the internal cooling with quieter exhaust noise and better fuel efficiency than conventional positive displacement generators. It can also be used as a power source for houses and villas and as a portable generator with good fuel efficiency. It is also excellent as a power source for air compressors of IMPa or less when using a compact turbine compressor.
- 6-cycle gas turbines for generators are from the 30kW class if they are small, and more than 10MW for power plants by installing many 6-cycle engines that are positive displacement engines if they are large. Up to class, it can replace conventional internal combustion engines.
- a large power plant such as a power plant is used because the efficiency of a normal gas turbine can be increased, and a combined cycle that rotates a steam turbine with the thermal energy remaining in the exhaust gas can be used, so that the overall efficiency can be increased.
- the small lOOkW class it is difficult to increase the efficiency of the gas turbine itself due to the relationship between gas leaks and heat conduction ports, and it is too small to use a combined cycle that uses exhaust heat.
- the 6-cycle gas turbine is a compact combined cycle that converts the pressure energy remaining in the exhaust of a positive displacement engine into power using a regenerator, and is more efficient than a 4-cycle diesel engine. Therefore, there is a merit of using even a small one.
- an exhaust heat regenerative system that rotates the steam turbine with the thermal energy remaining in the exhaust gas can be added to improve the fuel efficiency of conventional gas turbines for thermal power generation. That's what you can do with force S.
- a sixth problem solving means of the present invention includes a positive displacement compressor as a supercharger and a motor generator capable of restarting a 6-cycle engine on an output shaft of a 6-cycle engine, and an exhaust gas turbine.
- the internal combustion engine according to the sixth problem solving means includes a positive displacement compressor that rotates in proportion to the rotational speed of the six-cycle engine as a supercharger!
- the boost pressure is constant because it is proportional to the number, and exhaust gas that is approximately proportional to the engine speed is sent to the regenerator.
- a pressure proportional to the square of the rotational speed is generated, and in order to obtain a stable supercharging pressure against changes in the engine speed, a plurality of superchargers are operated in combination.
- the force S that needs to be used by appropriately selecting the turbine S, and in the case of a positive displacement compressor, the boost pressure can be kept almost constant just by setting the rotation speed in proportion to the engine. There are benefits that can be reduced.
- the output of the six-cycle engine part is used to drive the supercharger and to supply high-pressure exhaust gas to the regenerator.
- the 6-cycle engine can be regarded as a high-pressure gas generator, and the output S of the entire engine can be controlled by controlling the rotation speed.
- the regenerative pressure is changed mainly by changing the total nozzle area of the exhaust turbine by a control computer, and a more accurate engine rotational speed is provided on the output shaft. This is done by changing the load by controlling the absorption torque of the motor generator.
- the internal combustion engine according to the means for solving problems of the present invention basically does not have an output control dedicated means such as a throttle valve except for a case where delicate intake air control such as an idling state is required. Since the output can be controlled, it is simple, and there is an advantage that there is no bombing loss due to the throttle valve and the efficiency is high.
- a 6-cycle gas turbine that extracts most of the output from the regenerator, or when it is used for power generation including the output of a 6-cycle engine, it becomes a compact and efficient engine that can easily control the output from the outside. .
- Exhaust noise is quiet due to the presence of the regenerator, which is particularly useful as a power generation unit for hybrid vehicles.
- an internal combustion engine according to the first to sixth problem-solving means is characterized in that a combustion chamber is provided in an exhaust manifold between a six-cycle engine and a regenerator. It is an institution.
- the first effect of the seventh problem solving means is that the unburned components of the exhaust gas are removed and the state of oxygen concentration, temperature, etc. can be controlled.
- exhaust gas tends to be excessive oxygen due to the presence of a scavenging stroke. Therefore, the combustion itself is operated in a somewhat fuel-rich state, so (4) unburned gas remains in the exhaust stroke.
- the exhaust in the exhaust stroke (4) and the exhaust in the (6) scavenging exhaust stroke are alternately discharged, so it is difficult to reliably mix the unburned components at the exhaust port and pass through the regenerator. It burns with the catalyst. This increases the load of the catalyst, leading to an abnormal increase in catalyst temperature and worsening of fuel consumption.
- the problem solving means can reliably burn the unburned gas in front of the regenerator in the combustion chamber installed in the exhaust port.
- means for composing the combustion chamber with a catalyst is also effective.
- the oxygen concentration can be lowered if the exhaust gas becomes excessively oxygen.
- the state of the catalyst can be managed more precisely, such as temporarily changing the exhaust to a reducing atmosphere without changing the operating state of the 6-site engine.
- it can be used to shorten the temperature raising time of the catalyst during warm-up.
- the second effect of the problem solving means is that the output of the regenerator can be increased.
- the output of the regenerator can also be improved by reliably burning the unburned gas. Furthermore, by supplying fuel to the combustion chamber with the fuel injection device, the exhaust gas temperature can be increased to the limit temperature of the turbine, and the output of the regenerator can be increased.
- the regenerative pressure is high, so the combustion energy in this combustion chamber can be converted into power efficiently by the regenerator, so the decrease in efficiency is Few.
- a similar known example for this purpose is the example of an afterburner used in jet engines such as fighter aircraft.
- the oxygen concentration remaining in the exhaust of a 6-cycle engine with a regenerator is not as high as the exhaust of a jet engine, so there is no significant increase in power output, but this effect is maximized by scavenging and making fresh. can do.
- An eighth problem-solving means of the present invention is equipped with an internal combustion engine according to the first problem-solving means.
- a regenerative body is equipped with a power transmission mechanism that transmits the output from the 6-cycle engine to the drive wheels, a motor that drives the vehicle, and a power transmission mechanism that transmits the driving force of the motor to the drive wheels.
- the moving body is characterized in that a generator is provided on the output shaft of the machine.
- the moving object according to the eighth problem solving means has an advantage that the output from the regenerator of the six-cycle engine can be efficiently used as traveling energy. Recently, the number of hybrid vehicles has been increasing. Therefore, if this power is applied to the driving motor originally possessed by the hybrid vehicle, there are fewer components required. In that case, it is possible to temporarily store the generated power in the battery. As described above, the moving body according to the means for solving the problem can incorporate a system as a hybrid vehicle with higher fuel efficiency by only increasing the size of some parts such as a battery. In other words, if this problem solution is applied to the conventional vehicle, the compact prime mover with high fuel efficiency can be obtained.
- a ninth problem-solving means of the present invention is a series-type hybrid moving body on which the internal combustion engine of claim 6 is mounted.
- the moving object according to the ninth problem solving means is simple in its engine itself, has good startability, and is efficient even when the engine speed is changed, so that the battery capacity is small, and the entire hybrid system is lightly configured. There is an advantage that you can. Due to the characteristics of the series and ibritt, the fuel efficiency improvement effect is particularly great when applied to city buses, small trucks for delivery, taxis, etc., which have a slow average speed and a large number of accelerations / decelerations.
- a tenth problem solving means of the present invention is the internal combustion engine according to claim 1, wherein the six-cycle engine is a W-type six-cylinder having 60 degrees on both sides.
- the 6-cycle engine with a regenerator by the tenth problem solving means is a 180 degree equidistant explosion engine having the number of cylinders of 6 cylinders and no inertial primary vibration.
- It can be mounted horizontally or vertically with respect to the vehicle body, and is particularly useful as an engine for moving vehicles such as passenger cars with a displacement of 2 liters or more and small and medium trucks.
- An eleventh problem solving means of the present invention includes the internal combustion engine of claim 1 or the internal combustion engine of claim 10 in which the six-cycle engine is a 90 degree V-type four-cylinder engine, and the rotation shaft of the internal combustion engine travels along direction It is the front-wheel drive vehicle arrange
- the vehicle according to the eleventh problem solving means has an advantage of being able to provide a hybrid vehicle compatible with a front-wheel drive vehicle equipped with a conventional premixed 4-cycle engine.
- a combination of a diesel engine and a hybrid system which could not be installed in the past, can also be achieved by increasing the supercharging pressure and making the 6-cycle engine part compact.
- the solution to this problem is a 90-degree V-type 4-cylinder 6-cycle engine with 270 degree equidistant explosions and an internal combustion engine with claim 10 with 180 degree equidistant explosions, which are equidistant explosion engines suitable for passenger cars. This problem has been solved by utilizing the fact that the engine width is short with little vibration.
- the front and rear length of the engine can be slightly increased S, and a method of extending the front part of the vehicle can be used, so it can be compatible with conventional front-wheel drive vehicles.
- This extension of the front part does not become a fatal defect because it leads to securing a space for mounting hybrid-related parts by increasing the engine room.
- this problem solving means is capable of hybridizing a small-sized passenger car with a large number of vehicles around the world, and among them, a 2-liter class or more engine-side-mounted FF vehicle that is the mainstream. In addition, it can be dieselized, which has a great effect on reducing global oil consumption.
- FIG. 1 (A) is a schematic diagram of a 6-cycle engine with a regenerator of the present invention, and (B) is a P—V of a 4-cycle gasoline engine and a 6-cycle engine with a regenerator. It is a conceptual diagram of a diagram. (Embodiment 1) [FIG. 2] A schematic view of an embodiment of an EGR system for an engine of the present invention. (Example 2)
- FIG. 3 is a schematic diagram of an embodiment of an EGR system for a supercharged engine according to the present invention.
- Example 3 A schematic view of an EGR system of an engine equipped with a multistage regenerator of the present invention. (Example 4)
- FIG. 5 is a PV diagram of a 6-cycle engine part of a 6-cycle diesel engine with a regenerator according to the fourth problem solving means. (Example 5)
- FIG. 6 A schematic diagram of the PV diagram of the entire organization.
- Figure (A) shows the overall view
- Figure (B) shows an enlarged view near the origin. (Example 5)
- FIG. 7 is a schematic diagram of the engine of the first embodiment according to a fourth problem solving means.
- FIG. 8 A schematic diagram of the engine of the second embodiment according to the fourth problem solving means. (Example 6)
- FIG. 9 is a schematic diagram of a 6-cycle gas turbine according to the present invention. (Example 7)
- FIG. 10 (a) is a side view of an engine provided with a combustion chamber in an exhaust manifold according to the present invention, and (b) is an enlarged view of the combustion chamber portion. (Example 8)
- FIG. 11 A four-side view of a power section of a front-wheel drive vehicle according to the present invention. (Example 9)
- FIG. 12 is a control system diagram of the power section. (Example 9)
- FIG. 1 (A) is a schematic view seen from above of a four-cylinder six-cycle engine with a regenerator according to the first problem solving means.
- An exhaust turbine 100 which is a regenerator, is attached to the exhaust manifold 80 of a 6-stroke engine 1 that is not supercharged, and the pressure remaining in the exhaust is converted into rotational energy. The air is discharged from the second hold 80b to the atmosphere.
- Fig. 1 (B) is a graph showing the volume and pressure change of the combustion chamber during the compression stroke and explosion / expansion stroke of the unsupercharged four-cycle engine and the engine according to the first problem solving means.
- PV diagram The dotted line is a PV diagram for a premixed 4-cycle engine with a compression ratio of 9.5.
- the height of point A1 indicates the intake pressure, which is atmospheric pressure, and the volume on the horizontal axis indicates the volume in the cylinder when the piston is at bottom dead center.
- the change in volume and pressure during adiabatic compression when the piston is rising is represented by a curve that rises to the left from point A1 to point A2.
- the solid line is a PV diagram when the compression ratio of a 6-cycle engine with a regenerator of the same displacement is 12.2, including the compression stroke, explosion, expansion stroke, and expansion stroke in the regenerator. Yes.
- the difference between the compression ratio and the 4 cycle is the gas temperature force at the end of the intake stroke. This is due to the lower price of the 6-cycle engine.
- the compression process starts from B1. At this time, the capacity of the 6-cycle engine with a high compression ratio is smaller at the top dead center, so the volume at the start of compression is also smaller.
- B2 is reached when adiabatic compression is performed during the compression stroke and the piston reaches the top dead center position. It ignites and burns here, and the pressure rises to B3.
- the exhaust valve opens at B4 and is fed from the 6-cycle engine to the regenerator while maintaining the pressure at that time.
- the pressure of B4 at this time is called the regenerative pressure, and an ideal Atkinson cycle is realized when taking a PV diagram like the solid line in this figure, and the theoretical efficiency of the entire engine is maximized.
- the regenerative pressure is called “ideal regenerative pressure”.
- the exhaust gas is then adiabatically expanded to a pressure of B5 in the regenerator and released at atmospheric pressure.
- the 6-cycle engine after B4, the exhaust, scavenging introduction, scavenging exhaust, and intake strokes are completed and one cycle is completed.
- FIG. 2 is a schematic diagram of the EGR system of the engine as the second problem solving means.
- the diagram of the 6-cycle engine is a view of one combustion chamber portion of the cylinder head 20 of the multi-cylinder engine of this embodiment as viewed from the cylinder side.
- the umbrella portion of the poppet type intake valve 22, the scavenging valve 42 and the exhaust valve 32, and the nozzle portion of the direct injection injector 18 are visible.
- the reason for the small number of exhaust valves is that the timing of opening the scavenging exhaust valve is narrow, from D8 to D6, as explained in Fig. 5 below, so that it opens and closes quickly.
- a gas passage 111 for circulating the exhaust gas is provided in the scavenging port of the engine, and a cooler 112 is provided in the passage.
- the second valve 43 controls the amount of scavenging, and the scavenging valve controls the amount of fresh air mixed with the scavenging. Normally, when supercharging the engine, it is necessary to provide separate supercharged air for scavenging and intake.
- FIG. 3 shows an EGR system for an engine with a supercharger that is a second embodiment of the second problem solving means.
- the turbocharger 200 is provided only at the intake port of the engine and is higher than the pressure of the scavenging port, which is the exhaust gas pressure. Since the scavenging pressure is low, it is compressed in the scavenging exhaust stroke in the 6-cycle engine, and then pushed out to the exhaust port. Scavenging is low in pressure The force that reduces the gas weight relative to the intake air When the gas is supercharged, the temperature rises due to adiabatic compression, whereas scavenging still cools the inside of the combustion chamber at a lower temperature with fresh air. I can do it. There is an advantage that a turbocharger dedicated to scavenging is not required.
- FIG. 4 is a schematic diagram of an EGR system of an embodiment of an engine with a supercharger which is a third embodiment according to the second problem solving means.
- a plurality of regenerators 100 and 100B are provided in series, and a gas passage 111 for circulating exhaust gas between the two regenerators is provided, and a cooler 112 is provided in the passage. Cooling the exhaust gas expanded to atmospheric pressure in the regenerator as shown in Fig. 2 and Fig. 3 and supercharging it again is the best method in terms of thermal cycle efficiency.
- the supercharger dedicated to scavenging can be omitted, and the effect of being able to reduce the cooler is effective since the cooling gas is effective because the circulating gas pressure is high.
- the scavenging pressure is not necessarily the same as the boost pressure of the intake air. However, in this embodiment, the intake air pressure is reduced so that fresh air can be introduced into the scavenging when the scavenging valve 43B is opened. Is higher.
- Fig. 5 is a PV diagram of a 6-cycle engine that is supercharged at 4 atm of a 6-cycle diesel engine equipped with a turbocharger and a regenerator according to the fourth means for solving problems.
- 6 explain the change in output of the cycle engine alone.
- the solid line is the PV diagram of the 6-cycle engine alone when using the ideal regenerative pressure
- the dotted line is the PV diagram when the regenerative pressure is lower than the ideal regenerative pressure.
- the compression stroke starts from D1, which is the supercharging pressure, and is adiabatically compressed in the compression stroke, and reaches D2 when the piston reaches the top dead center position.
- the area force surrounded by Dl, D8, D2, D3, D3b, and D4 shows the energy converted from the combustion gas to the engine rotational force in the compression stroke and explosion / expansion stroke of the 6-cycle engine.
- the energy in the area enclosed by D4, D6, D7, and D1 is taken out from the rotational force of the engine to push out the exhaust.
- the energy in the area surrounded by the solid line connecting Dl, D8, D6, and D7 is brought out.
- the dotted line shows the case where the regenerative pressure is half that of the ideal regenerative pressure.
- the piston pushes out scavenging with regenerative pressure to top dead center and reaches D6b.
- the piston begins to descend from here, and the intake valve is opened at D7b.
- the intake stroke is completed at D1
- the intake valve is closed, and one cycle is completed.
- the energy output in one cycle of the six-stroke engine at this time is D5, D8b, D2, D3, D3b, D4, D5. Subtracting twice the area enclosed by the solid and dotted lines connecting D8b, D6b, and D7b.
- the output of the single 6-cycle engine with a half of the regenerative pressure has increased by 35%.
- the output of a single 6-cycle engine can be further increased because more fuel with higher exchange efficiency with fresh air can be supplied.
- Fig. 6 is a PV diagram of the entire engine including the turbocharger and regenerator of the same 6-cycle diesel engine with a turbocharger regenerator.
- (B) is an enlarged view near the origin.
- the fresh air introduced to the turbocharger at atmospheric pressure G1 is supercharged and becomes the pressure of G2.
- the 6-site engine inhales the supercharged fresh air as D1 pressure, and the exhaust valve opens at D4 through the process explained in Fig. 5.
- three PV diagrams are shown as the subsequent changes: a solid line, a dotted line, and a two-dot chain line.
- the solid line represents the ideal regenerative pressure and corresponds to the solid line graph in Fig. 5.
- Exhaust pushed out from the 6th cycle with the pressure of D4 becomes the inlet pressure G3 of the regenerator as it is, and continues adiabatic expansion inside the regenerator, and is discharged outside at atmospheric pressure G4.
- the dotted line corresponds to the dotted line in FIG.
- the gas in the combustion chamber which was D4 when the exhaust valve was opened, freely expands to the regenerative pressure G3b.
- G3b point is on the right side of the solid line. .
- Exhaust pushed out from the 6th cycle at the pressure of D5 becomes the inlet pressure G3b of the regenerator as it is, and continues adiabatic expansion inside the regenerator, and is discharged outside at atmospheric pressure G4b.
- the energy that can be output in one cycle is represented by the area enclosed by the lines of Gl, Dl, D2, D3, D3b, D4, D5, G3b, and G4b.
- the energy that can be regenerated by the regenerator (the area on the left side of the dotted line connecting G3b and G4b) is less than the ideal regenerative pressure (the area on the left side of the solid line connecting G3 and G4)!
- the difference in total efficiency is about 2% because the output of the cycle engine is larger, and the cycle can be used industrially. This is because the free-expanded pressure energy is not simply released, but is simply converted into gas thermal energy, so that it is possible to regenerate much of it later with a regenerator.
- the two-dot chain line is a PV diagram when the regenerative pressure is the same as the supercharging pressure.
- the decrease in the overall efficiency due to the change in the regenerative pressure is a quadratic function with respect to the deviation from the maximum efficiency pressure, and when the exhaust is freely expanded so far, the decrease in the overall efficiency reaches 11%.
- the load in a cruise operation such as a vehicle with high driving performance is considerably lower than the full load, it is not possible to set such a pressure as the set pressure of the regenerator at full load. In general, industrial use is not denied. If it can be used at a regenerative pressure that is close to the ideal regenerative pressure in the high-frequency range and cruise driving range, the usage frequency is low! is there.
- the regenerative pressure cannot be set to a value slightly higher than the cylinder internal pressure when the exhaust valve of the 6-cycle engine is open! However, the exhaust valve will not melt! / Limited to the range.
- the output of the 6-cycle engine may be 0, such as when idling, but it is attached to the turbine If the entire engine is used at a very low load, such as when it is desired to continue to supply power to the auxiliary equipment, such a pressure setting may be positively considered.
- FIG. 7 is a schematic diagram showing a first example of the fourth problem solving means.
- a 6-cycle engine 1 exhaust manifold 80 is equipped with a scroll-type positive displacement expander 100 as a regenerator 100, and its output is transmitted to the 6-cycle engine 1 as power via a transmission 180 and a power transmission belt 181. is doing.
- the dotted circle drawn on the regenerator 100 indicates the exhaust manifold 80 b on the lower side, and exhaust gas from the expander is discharged.
- transmission 180 has the smallest ratio, the engine takes ideal regenerative pressure.
- the intake gas volume of the regenerator increases compared to the capacity of the 6-cycle engine pushing out the exhaust gas, and the exhaust expands freely when the exhaust valve of the 6-cycle engine opens, ideally The regenerative pressure is lower than the regenerative pressure.
- the gas expansion ratio in the expander is a fixed value. Therefore, it is better not to change the regenerative pressure, the efficiency of the regenerator, and the exhaust noise This is desirable. Therefore, the transmission ratio is increased at full load, and the regenerative pressure is lower than the ideal regenerative pressure, as shown by the dotted line in Fig. 6, and the transmission ratio is reduced at the partial time to control regeneration at the ideal regenerative pressure. .
- FIG. 8 is a schematic diagram showing a second embodiment according to the fourth problem solving means.
- the exhaust manifold 80 of the six-cycle engine 1 has a turbine-type regenerator 100 that drives a generator 151 and an auxiliary machine 150 arranged coaxially.
- the regenerative pressure can be controlled by controlling the total nozzle area using a variable vane turbine or a variable number of nozzles turbine.
- the regenerative pressure can always be operated near the ideal regenerative pressure if the total area of the nose is controlled to an appropriate size according to the exhaust gas volume of the 6-cycle engine.
- a wastegate valve 35 is provided in the exhaust portion of the six-cycle engine, and the exhaust is released to the atmosphere as necessary.
- the efficiency when this valve is actuated deteriorates.
- the output of a 6-cycle engine can be instantaneously increased to the maximum. Even if the inlet pressure of the regenerator is temporarily reduced, the rotational speed of the turbine can be maintained by temporarily reducing the load torque of the generator, which is the load, for a short time.
- the speed of the 6-cycle engine can be quickly increased with respect to the accelerator to increase the output of the entire engine! / In some cases, it can be used as a system with little time lag. This is advantageous when used as a prime mover for a moving body in which a load such as a vehicle fluctuates greatly.
- the 6-cycle engine 1 includes a supercharger 200 driven by a motor 250, and the supercharging pressure can be controlled from the outside, and the output of the entire engine is also controlled by the supercharging pressure. I'm doing it.
- the gas turbine When regenerating with a two-stage gas turbine with a regenerative pressure of 1 stage, the gas turbine needs to handle a flow velocity higher than the sonic speed in order to increase the cycle efficiency.
- the nozzle shape of the turbine needs to be a divergent nozzle that expands again after the area of the cross section is reduced once to form a throat. At this time, if the gas falls into an excessive expansion or underexpansion at the throat, the efficiency deteriorates rapidly. Therefore, the pressure ratio between the inlet and outlet of the turbine must be used as the design value.
- the turbine since the turbine handles supersonic speeds, the turbine is controlled to have a constant regenerative pressure that is lower than the ideal regenerative pressure at full load. There is an effect that the engine efficiency can always be kept high while simplifying the regeneration system.
- FIG. 9 is a schematic diagram of a 6-cycle gas turbine according to the fifth problem solving means.
- the output of the 6-cycle engine 1 is used to drive the turbocharger 200, which is a turbine compressor, via the speed increaser 280 and to drive the auxiliary machine 150 via the auxiliary machine drive belt 154.
- Most engine output is output by the regenerative turbine 100 and converted to electric power by the generator 151.
- FIG. 10 is a side view of an in-line multi-cylinder six-cycle engine having an exhaust manifold 80 according to the third problem solving means and a combustion chamber according to the seventh problem solving means.
- Combustion chamber 7 0 is located in the exhaust manifold assembly connected from the exhaust port 31 of each cylinder of the 6-cycle engine 1.
- the exhaust manifold 80 having a combustion chamber inside is covered with a heat insulating material 71 including the outer periphery of the exhaust turbine, and the inside of the exhaust manifold is also coated with heat insulation.
- a regenerator 100 is connected downstream of the combustion chamber, and an exhaust catalyst 63 is placed in an exhaust manifold 80b downstream of the regenerator.
- a combustion chamber wall 72 having gas holes 73 open, and the exhaust gas after combustion and the scavenging exhaust gas are mixed with the exhaust gas alternately entering to burn the incombustible gas. Therefore, the internal volume of the combustion chamber wall 72 needs to be at least equivalent to the volume of exhaust gas for one cycle of one cylinder.
- a fuel injection port of a fuel supply machine 75 which supplies fuel to the combustion chamber when necessary. When fuel is supplied, it quickly gasifies at the temperature of the combustion chamber, and mixes with oxygen remaining in the exhaust gas and burns. The reason why the fuel supply device is located below the combustion chamber is to prevent thermal damage.
- FIG. 11 is a four-sided view of a power plant mounted on a horizontal engine series hybrid type FF vehicle using the ninth and eleventh problem solving means.
- the 6-cycle engine part is an engine that adopts the third, sixth and seventh problem solving means.
- (A) is a front view of the power plant as viewed from the front of the vehicle,
- (B) is a side view,
- (C) is a top view, and
- (D) is a rear view.
- 6-cycle engine 1 is a 90-degree V-type four-cylinder engine that is independently equipped with scavenging and intake ports, and is equipped with a scroll-type positive displacement compressor 210 directly connected to the crankshaft as a supercharger. An amount of intake air proportional to the engine speed is supplied to the intake port of the 6-cycle engine at a stable pressure.
- the compression ratio of the positive displacement compressor 210 is 2 to 3, and the 6-cycle engine itself becomes compact accordingly. The actual supercharging pressure becomes higher as the temperature rises due to the effect of adiabatic compression.
- V-type four-cylinder six-cycle engine 1 is placed slightly backward.
- a combustion chamber equipped with a fuel supply machine 75 is provided at the gathered portion of the insulated exhaust manifold where the exhaust port force of each cylinder has also increased, and a variable nozzle number turbine 100 as a regenerator is provided above it.
- the output shaft is equipped with a generator 151 for conversion into electric power.
- the exhaust is then directed to the front exhaust catalyst, directed downwards in front of the engine, and then rearward along the underside of the vehicle body Has been led by
- This embodiment includes an EGR system corresponding to the third embodiment.
- the circulating exhaust gas flows from the upstream side of the catalyst so as to keep the temperature around the catalyst, and then it is cooled by the EGR system cooler 112, which is drawn with a dashed line in Fig. Guided to scavenging port of engine 1!
- the output shaft of the 6-cycle engine is directly connected to a power generation combined use motor 155 as an auxiliary machine. Electricity is generated from the surplus output of the 6-cycle engine, and the power generated by the generator 151 is supplied to the battery. It is stored and used to drive the motor 550 for driving the vehicle.
- the engine output is mainly output from the turbine 100, and the 6-cycle engine only drives the turbocharger 200 as an auxiliary machine and the generator motor. is there.
- the vehicle travels by driving the front wheels with drive shafts 522 and 522b by changing the output from the motor to an appropriate rotational speed with the transmission 520.
- the motor 550 and the transmission 520 are indicated by a one-dot chain line.
- FIG. 12 is a control system diagram of this embodiment.
- the 6-cycle engine section is shown as a single bank for ease of component power.
- the vehicle drive motor 550 is driven by the motor controller 560 in accordance with the accelerator sensor 24 to accelerate and decelerate the vehicle.
- the control computer 610 is provided with means for sensing the amount of charge of the battery 580 and a function of operating a rotary actuator 360 that rotates an open / close valve that changes the number of nozzles of the variable nozzle number turbine.
- the control computer 610 determines the amount of power generation based on the detected value of the battery charge, determines the number of revolutions of the six-cycle engine, changes the regenerative pressure mainly by controlling the exhaust pressure of the exhaust turbine, and rotates the six-cycle engine. Control the number.
- the regenerative pressure decreases according to the principle explained in Examples 5 and 6, and the output of the 6-cycle engine increases, so the rotational speed of the 6-cycle engine increases and the output of the entire engine increases.
- More precise engine output control is performed by the control computer controlling the motor controller 560, changing the load of the 6-cycle engine according to the amount of power generated by the power generation motor 155, and adjusting the rotational speed.
- the control computer 610 stops the fuel supply when power generation is no longer necessary, increases the load on the motor 155, and stops the engine. The engine is also restarted by the power generation combined motor 155.
- control computer 610 includes means for sensing the signal of the catalyst from the exhaust sensor 68, an activator 91 for opening and closing the second valve and the scavenging valve at the scavenging port, and a scavenging valve actuator.
- Means for operating the eta 94 are provided. If the exhaust temperature is determined to be high by the detection value of the exhaust sensor, the actuator 91 opens the second valve to increase the amount of scavenging. If it is determined that the oxygen concentration is high, the scavenging valve will be closed. At this time, the fuel supply from the direct injection injector of the 6-cycle engine can be increased. If the second valve is already fully opened and the 6-cycle engine itself is in a thermally limited state, the oxygen concentration is lowered by supplying fuel from the fuel supply device 75 to the combustion chamber of the exhaust port.
- FIG. 13 shows a power system diagram of a moving body according to the eighth problem solving means.
- 1 is a 6-cycle engine with an in-line 4-cylinder regenerator equipped with a supercharger 200.
- a gas turbine is used as the regenerator 100.
- the output of the regenerator is converted into electric power by the generator 151, and the motor controller 560 converts the voltage and frequency to an alternating current appropriate for driving the vehicle drive motor 550.
- the speed is changed to an appropriate speed at 520 and transmitted to the right and left horseshoe wheels 525 and 525b via the drive and shafts 522 and 522b.
- the output shaft of the 6-cycle engine 1 is shared with the motor 550, and the output is transmitted to the drive wheels through the transmission 520 together with the output of the motor.
- the six-cycle engine 1 includes a supercharger 200 driven by a motor 250, and controls the rotation speed of the supercharger by a motor controller in accordance with a driver's instruction. The output is controlled. A part of the output of the regenerator drives an auxiliary machine 150 such as an air conditioner compressor through an auxiliary reduction gear 152 and an auxiliary clutch 153.
- This moving body The embodiment is a vehicle and includes a battery 580. The battery must have at least energy to accelerate the turbocharger 200! /, So it is all right! /, So the size of the battery for the hybrid vehicle is not necessarily required.
- the power stored in the 580 can be compensated for, so if there is an output step in the engine for any reason or the temporary shortage of driving force while the boost pressure rises can be compensated .
- the power generator 15 attached to the regenerator 100 is controlled by the motor controller 560 so that the turbine as a regenerator is always efficient. It can be kept at an appropriate rotational speed.
- the hybrid vehicle can be made by increasing the battery 580.
- the auxiliary machine is driven by the regenerator! /, So the necessity of the belt 154 for driving the auxiliary machine shown in FIG. 9 is eliminated, and the overall length of the engine 1 can be reduced accordingly. There is an advantage that a space for the hybrid vehicle drive motor 550 can be secured.
- the same purpose can be achieved by providing another motor for driving the auxiliary machine instead of the speed reducer 152 of this embodiment and driving the motor with the electric power generated by the generator 151.
- the motor 550 and the transmission 520 of this embodiment By replacing the motor 550 and the transmission 520 of this embodiment with a hybrid system having characteristics of both a series type and a parallel type described in Patent Document 6, an engine stoppage during running can be realized, It is possible to further improve the practical fuel consumption.
- FIG. 14 is a cylinder direction and a crankpin arrangement diagram of a W-type 6-cycle 6-cylinder engine.
- Dotted lines a, b, and c indicate the cylinder center lines in the three cylinder blocks arranged in the W shape, and 51 indicates a piston that slides in the cylinder.
- 50al, 50bl, and 50c1 indicated by solid lines are crank pin arrangements of a set of W banks, and pistons 51al, 51bl, and 51cl indicated by solid lines are drawn at positions corresponding to the pin positions.
- the crank pins 50a2, 50b2, and 50c2 and the pistons 51a2, 51b2, and 51c2 shown by dotted lines indicate the position of another W thread and W-knock.
- the crank pin arrangement for the two pistons of one cylinder block is 180 degrees phase, and the primary balance including the couple is balanced, 180 degrees etc. It becomes a six-cycle engine with a two-stage explosion.
- the number of bearings of the crank is determined by taking into account the three bearing forces placed on both sides of one set of three crankpins in the W bank, and the rigidity and strength of the crank.
- the W-type 6-cylinder 6-cycle engine of the present embodiment is a replaceable engine that does not change the length in the vehicle body width direction as compared with the engine of the embodiment of the power unit of the FF vehicle in FIG.
- regenerator-equipped 6-cycle engine [0101] The application of the regenerator-equipped 6-cycle engine according to the present invention exists for all applications that require an internal combustion engine with excellent fuel efficiency.
- the present invention is for simply and efficiently regenerating the energy remaining in the exhaust of a positive displacement engine, and contributes to an improvement in fuel consumption.
- the advantage is that the exhaust noise can be kept low.
- a 6-cycle engine with a regenerator is a system that does not decrease in efficiency even when supercharged at a relatively high pressure, and has a large merit of downsizing by supercharging.
- this principle can be used as an engine that drives two output shafts.
- the 6-cycle gas turbine is highly controllable and can be used as a gas turbine.
- a power plant including a generator can be configured particularly compactly for power generation.
- a power plant including a generator can be configured particularly compactly for power generation.
- it can be used as an engine mounted on moving bodies such as ships, high-speed buses, large trucks and vehicles from the power plant.
- the 6-cycle engine can be cooled from the inside as a small generator, the cooling system can be simplified and the entire power generation system can be made compact. This means that it can be used as a power source for hybrid vehicles that are on the rise.
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2007800307126A CN101506492B (zh) | 2006-08-18 | 2007-08-06 | 带再生器的6冲程内燃机 |
US12/377,861 US8186334B2 (en) | 2006-08-18 | 2007-08-06 | 6-cycle engine with regenerator |
EP07792007A EP2053214A1 (en) | 2006-08-18 | 2007-08-06 | 6-cycle engine with regenerator |
BRPI0715700-2A2A BRPI0715700A2 (pt) | 2006-08-18 | 2007-08-06 | motor de seis ciclos e motor de combustço interna tipo combinado, motor de seis ciclos com regenerador e corpo màvel |
JP2008529844A JP4298788B2 (ja) | 2006-08-18 | 2007-08-06 | 回生機付6サイクル機関 |
CA002658790A CA2658790A1 (en) | 2006-08-18 | 2007-08-06 | Six-cycle engine with regenerator |
MX2009001586A MX2009001586A (es) | 2006-08-18 | 2007-08-06 | Motor de seis ciclos con regenerador. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-248694 | 2006-08-18 | ||
JP2006248694A JP2006348947A (ja) | 2006-08-18 | 2006-08-18 | 排気圧回生機付内燃機関 |
Publications (1)
Publication Number | Publication Date |
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WO2008020550A1 true WO2008020550A1 (en) | 2008-02-21 |
Family
ID=37645029
Family Applications (4)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/056492 WO2008020498A1 (en) | 2006-08-18 | 2007-03-27 | Six-cycle engine having increased opportunity of valve opening |
PCT/JP2007/064035 WO2008020519A1 (en) | 2006-08-18 | 2007-07-16 | Exhaust catalyst control for six-cycle engine |
PCT/JP2007/065334 WO2008020550A1 (en) | 2006-08-18 | 2007-08-06 | 6-cycle engine with regenerator |
PCT/JP2007/066006 WO2008020619A1 (en) | 2006-08-18 | 2007-08-17 | Turbine with variable number of nozzles |
Family Applications Before (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/056492 WO2008020498A1 (en) | 2006-08-18 | 2007-03-27 | Six-cycle engine having increased opportunity of valve opening |
PCT/JP2007/064035 WO2008020519A1 (en) | 2006-08-18 | 2007-07-16 | Exhaust catalyst control for six-cycle engine |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/066006 WO2008020619A1 (en) | 2006-08-18 | 2007-08-17 | Turbine with variable number of nozzles |
Country Status (10)
Country | Link |
---|---|
US (3) | US20100083921A1 (ja) |
EP (2) | EP2053215A1 (ja) |
JP (5) | JP2006348947A (ja) |
KR (2) | KR20090042287A (ja) |
CN (3) | CN101506497A (ja) |
BR (1) | BRPI0715700A2 (ja) |
CA (2) | CA2658788A1 (ja) |
MX (2) | MX2009001352A (ja) |
RU (2) | RU2009101965A (ja) |
WO (4) | WO2008020498A1 (ja) |
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- 2007-07-16 MX MX2009001352A patent/MX2009001352A/es unknown
- 2007-07-16 WO PCT/JP2007/064035 patent/WO2008020519A1/ja active Application Filing
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013111648A1 (ja) * | 2012-01-27 | 2013-08-01 | ヤマハ発動機株式会社 | 掃気行程を有する6サイクルエンジン |
JPWO2013111648A1 (ja) * | 2012-01-27 | 2015-05-11 | ヤマハ発動機株式会社 | 掃気行程を有する6サイクルエンジン |
US9284883B2 (en) | 2012-01-27 | 2016-03-15 | Yamaha Hatsudoki Kabushiki Kaisha | Six-stroke cycle engine having scavenging stroke |
NL2028576B1 (en) | 2021-06-29 | 2023-01-09 | Daf Trucks Nv | Internal combustion engine arranged for conducting a six-stroke internal combustion process. |
Also Published As
Publication number | Publication date |
---|---|
JPWO2008020619A1 (ja) | 2010-01-07 |
CN101506492B (zh) | 2012-01-11 |
RU2009101964A (ru) | 2010-09-27 |
CA2658790A1 (en) | 2008-02-21 |
US20100278628A1 (en) | 2010-11-04 |
JP4314595B2 (ja) | 2009-08-19 |
JP4255035B2 (ja) | 2009-04-15 |
RU2009101965A (ru) | 2010-09-27 |
KR20090045286A (ko) | 2009-05-07 |
WO2008020519A1 (en) | 2008-02-21 |
CN102269058A (zh) | 2011-12-07 |
JPWO2008020519A1 (ja) | 2010-01-07 |
WO2008020498A1 (en) | 2008-02-21 |
CN101506497A (zh) | 2009-08-12 |
US8821105B2 (en) | 2014-09-02 |
MX2009001586A (es) | 2009-02-25 |
US8186334B2 (en) | 2012-05-29 |
JP2006348947A (ja) | 2006-12-28 |
EP2053214A1 (en) | 2009-04-29 |
KR20090042287A (ko) | 2009-04-29 |
US20100083921A1 (en) | 2010-04-08 |
MX2009001352A (es) | 2009-02-25 |
CA2658788A1 (en) | 2008-02-21 |
US20100050963A1 (en) | 2010-03-04 |
JPWO2008020550A1 (ja) | 2010-01-07 |
CN101506492A (zh) | 2009-08-12 |
EP2053215A1 (en) | 2009-04-29 |
WO2008020619A1 (en) | 2008-02-21 |
JPWO2008020498A1 (ja) | 2010-01-07 |
JP4277063B2 (ja) | 2009-06-10 |
JP4298788B2 (ja) | 2009-07-22 |
BRPI0715700A2 (pt) | 2013-08-06 |
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