CN103026024B - For the piston-engined egr of opposed type - Google Patents
For the piston-engined egr of opposed type Download PDFInfo
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- CN103026024B CN103026024B CN201180024717.4A CN201180024717A CN103026024B CN 103026024 B CN103026024 B CN 103026024B CN 201180024717 A CN201180024717 A CN 201180024717A CN 103026024 B CN103026024 B CN 103026024B
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- pressurized air
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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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/08—Engines with oppositely-moving reciprocating working pistons
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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
- F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/186—Other cylinders for use in engines with two or more pistons reciprocating within same cylinder
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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
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
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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
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/14—Direct injection into combustion chamber
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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)
- Exhaust-Gas Circulating Devices (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The open one of the present invention has one or more than one has mouthful cylinder (c) and uniflow scavenged two-stroke, opposed type piston engine (49), it comprises exhaust gas recirculatioon (EGR) structure (131), this exhaust gas recirculatioon (EGR) structure (131) provides the part produced by motor (49) exhaust, for mixing with pressurized air, to control the generation of NOx between main combustion period.
Description
Background technique
Related domain is internal-combustion engine.Particularly, related domain relates to the uniflow scavenging opposed type piston engine having mouth with exhaust gas recirculatioon.More particularly, related domain comprises and has one or more than one and have the cylinder of mouth (portedcylinder) and uniflow scavenged two-stroke opposed type piston engine, wherein exhaust gas recirculatioon (EGR) structure provides the part exhaust produced by motor for mixing with pressurized air, with the generation of the NOx during control combustion.
Just as seen in Figure 1, internal-combustion engine opposed type piston engine illustrates, this opposed type piston engine comprise mouth 12 that is that there is machining or that be formed in wherein and longitudinally arrange/(displaced) relief opening of skew and at least one cylinder 10 of suction port 14 and 16.Oil nozzle 17, at the center of cylinder longitudinal direction or near the center of cylinder longitudinal direction, is arranged on opening by the nozzle bore of lateral cylinder surface or this nozzle bore contiguous.Two pistons 20,22 are arranged in hole 12, and wherein its end surfaces 20e, 22e toward each other.For convenience's sake, piston 20 is called " exhaust " piston, because it is near relief opening 14, and the end of this cylinder that relief opening is formed in wherein is called " exhaust end ".Similarly, piston 22 is called " air inlet " piston, because it is near suction port 16, and the corresponding end of this cylinder is called " inlet end ".
The piston-engined operation of opposed type with one or more than one cylinder of such as cylinder 10 is understood completely.In this respect, and with reference to figure 2, respond the burning occurred between end surfaces 20e, 22e, opposed type piston moves away respective top dead center (TDC) position, and this top dead center position is their mutual hithermost positions in the cylinder.When moving from TDC, the mouth that piston keeps it relevant is closed until they arrive respective lower dead center (BDC) position, and in lower dead center, they leave farthest mutually.Piston can same phase shift, and relief opening and suction port 14,16 are are as one man opened and closed.Alternatively, piston in phase place can in advance another, in this case, air inlet and relief opening have the different opening and closing time.
In many opposed type piston structures, phase deviation is introduced in piston movement.Such as, as shown in Figure 1, the advanced inlet piston of exhaust pition and phase deviation makes this piston move near its BDC position with such order, namely, move at exhaust pition 20 when suction port 16 is still closed and opened by relief opening during BDC 14, so that combustion gas starts to flow out from relief opening.Piston continue mobile mutually leave time, relief opening 14 still when opening suction port 16 open, and the air inlet of pressurized air (" pressurized air ") is forced in cylinder 10, exhaust is expelled outside relief opening 14.When permission pressurized air is by suction port, the exhaust from cylinder is called " scavenging " by the movement of relief opening.Because the pressurized air entering cylinder flows (towards relief opening) along with the identical direction that goes out to flow of exhaust, this scavenging process is called " uniflow scavenging ".
When piston moves by its BDC position and be reverse, relief opening 14 is closed by exhaust pition 20 and scavenging stops.When inlet piston 22 continues to move away BDC, suction port 16 stays open state.At this piston towards TDC(Fig. 2) when continuing mobile, suction port 16 is closed and pressurized air in cylinder is compressed between end surfaces 20e and 22e.Usually, when suction port 16 is opened when pressurized air by this pressurized air during this suction port be turbulent flow to promote good scavenging, with, the fuel oil of air and injection mixing after inlet close.Usually, this fuel oil is the diesel oil be ejected into by high pressure nozzle in cylinder.With reference to figure 1, as an example, the air (or being called for short " turbulent flow ") 30 of turbulent flow has general spiral motion, and this spiral motion forms the vortex of the longitudinal axis circulation around cylinder in mouth.As what be clear that in fig. 2, when piston advances towards its respective tdc position in casing bore, fuel oil 40 is directly injected to by nozzle 17 and is formed in the pressurized air 30 of turbulent flow in cylinder port 12 between end surfaces 20e and 22e of piston.When piston 20 and 22 is close to its respective tdc position, form the pressurized air of turbulent flow and the mixture of fuel oil is compressed in the firing chamber 32 be formed between end surfaces 20e and 22e.When mixture reaches firing temperature, fuel oil is lighted a fire in a combustion chamber, and driven plunger towards its respective BDC position separately.
As shown in Figure 2, fuel oil is directly injected to (injection of direct side) in cylinder port by the side of cylinder and the turbulent motion mutual effect of the remnants of pressurized air in the motion of fuel oil and this casing bore.When motor operation level increases and ignition heat raises, produce the amount of the increase of nitrogen oxide (NOx).But effulent strict gradually requires to represent needs strict NOx reducing degree.A kind of technology is by exhaust gas recirculatioon (" EGR ") reducing NOx emissions thing.EGR has been included in each cylinder to be had in the 4 two-stroke engine structures of spark ignition and two-stroke compression ignition engine that single piston runs.But this egr is not be directly used in have in uniflow scavenged two-stroke opposed type piston engine, because need to produce the pressure difference delivered to by exhaust pump in the inflow air-flow of air in opposed type piston engine.Therefore, need to be suitable for the effective egr with the piston-engined structure of uniflow scavenged two-stroke opposed type and operation.
Summary of the invention
The solution of this problem utilizes to have the exhaust gas recirculatioon of the cylinder of mouth to reduce by one or more than one of motor to have the piston-engined NOx emission thing of uniflow scavenged two-stroke opposed type.This motor comprises and has the relief opening and at least one cylinder of suction port that piston controls, and provides the pressurized air passages of pressurized air at least one cylinder of this motor.
On the one hand, EGR is provided by EGR circuit, and this EGR circuit has the input of the relief opening being connected to this cylinder and is connected to the loop output of pressurized air passages.The pressure official post exhaust stream provided between exhaust and pressurized air passages crosses EGR circuit to pressurized air passages, and exhaust here and air mix and be supplied to this at least one suction port.
On the other hand, when scavenging stops, EGR has the exhaust of the residue in the cylinder of mouth to provide by preserving this.
Accompanying drawing explanation
Fig. 1 is the side-looking partial schematic sectional view of the piston-engined cylinder of opposed type of prior art, and wherein opposed piston near respective bottom dead center position, and is suitably marked with " prior art ".
Fig. 2 is the side-looking partial schematic sectional view of the cylinder of Fig. 1, and wherein opposed piston, near respective top dead center position, forms firing chamber at the end surfaces of this position piston, and is suitably marked with " prior art ".
Fig. 3 is the conceptual schematic view of opposed type piston internal combustion engines, has the situation (aspects) of the air manager system of EGR shown in it.
Fig. 4 be illustrate for Fig. 3 have mouth, the conceptual schematic view of preferred egr in uniflow scavenging internal-combustion engine.
Fig. 5 be for Fig. 3 have mouth, the schematic diagram of the preferred EGR of uniflow scavenging internal-combustion engine.
Fig. 6 be for do not have turbosupercharger have mouth, the schematic diagram of the piston-engined another kind of egr of uniflow scavenging opposed type.
Embodiment
The egr described in this manual appear at comprise have at least one cylinder have mouth, in the piston-engined illustrative context of uniflow scavenging opposed type, in this cylinder, be provided with the pair of pistons that its end surfaces is relative.The cylinder that " has mouth " comprises machining or one or more than one air inlet to be formed in its sidewall and relief opening.The basis being provided for the embodiment understanding various egr in the illustrated manner wanted in this illustrative context.
In figure 3, the internal-combustion engine 49 opposed type piston engine imbody with the cylinder 50 that at least one has mouth.Such as, this motor can have one have the cylinder of mouth, two have the cylinder of mouth, three cylinders having the cylinder of mouth or four or more to have mouth.Illustratively, to illustrate and in the example that describes, motor is that supposition has multiple opposed type reciprocating engine having the cylinder of mouth at these.In this respect, each cylinder 50 has mouth 52 and forms or be machined in relief opening and the suction port 54 and 56 of its corresponding end.This relief opening and each opening comprising one or more than one circumference array of suction port 54 and 56, wherein adjacent opening separates (in some describe by solid bridge, each opening is called " mouth ", but the structure of the circumference array of this mouth is different from the mouth structure shown in Fig. 3).Exhaust and inlet piston 60 and 62 are slidably disposed in mouth 52, and wherein its end surfaces 61 and 63 toward each other.Exhaust pition 60 is connected to bent axle 71, and inlet piston is connected to bent axle 72.
When the piston 60 and 62 of cylinder 50 is near tdc position or its, in the mouth 52 between the end surfaces 61 and 63 of piston, form firing chamber.Be directly injected in firing chamber by least one fuel nozzle 100 fuel oil in the opening of the sidewall of cylinder 50 by being arranged on.
Also with reference to figure 3, motor 49 comprises the air manager system 51 of the conveying of pressurized air that administrative institute provides and the exhaust that motor 49 produces.Representational air manager system structure comprises pressurized air subtense angle and exhaust gas subsystem.In air manager system 51, pressurized air subtense angle comprise receive air inlet and air inlet is processed into the pressurized air source of pressurized air,---being transported at least one suction port of motor and at least one air-cooler in this pressurized air passages by this air passageways pressurized air---this cooler that is connected to the pressurized air passages of this pressurized air source connect into receive and and before the suction port being supplied to motor or multiple suction port charge air cooling (or comprising the gaseous mixture of pressurized air).Such cooler can comprise the device of air to liquid and/or air-air, or other cooling units.Thereafter, this cooler is called charger-air cooler.Pressurized air subtense angle also comprises the pressurized machine of the suction port pressurized air in pressurized air passages being pumped into motor.Exhaust gas subsystem comprises the exhaust passage emitted exhaust products from engine exhaust port being transported to outlet pipe.
With reference to figure 3, preferred pressurized air subtense angle comprises can by electric motor, or by being connected to the pressurized machine/mechanical supercharger 110 of the gear of bent axle, chain or belt device drives.Such as, but not limited to, in Fig. 4,5 and 6, pressurized machine 110 is connected to the bent axle 72 driven by it by belt linkage.This pressurized machine 110 can be single speed or many speed variators, or full variable speed device.Preferably, but not necessarily, air manager system 51 comprises the turbosupercharger 120 of the compressor having turbo machine 121 and rotate on common shaft 123.Turbo machine 121 is connected to exhaust gas subsystem and compressor 122 is connected to pressurized air subtense angle.Turbo machine 121 can be the device of fixed geometry or geometry-variable.Turbosupercharger 120 is from leaving relief opening 54 and flowing directly to extracting energy in the exhaust exhaust passage 124 from relief opening 54 or gas exhaust manifold 125.In this respect, turbo machine 121 is rotated by the exhaust by it.Turbo machine 121 rotary compression machine 122, makes compressor produce pressurized air by compress inlet air.The pressurized air exported by compressor 122 flows through conduit 126 to charger-air cooler 127, therefrom pressurized air by mechanical supercharger/pressurized machine (supercharger) 110 pumping to suction port.Intake manifold 130 is exported to from mechanical supercharger by charger-air cooler 129 by the air that mechanical supercharger 110 compresses.Suction port 56 is received by the pressurized air of mechanical supercharger 110 pumping by intake manifold 130.Preferably but not necessarily, in many boxer formula piston engine, intake manifold 130 is made up of the collection chamber be communicated with the suction port 56 of all cylinders 50.
exhaust management: desired modifications or employing are for there being the air administrative structure of the internal-combustion engine of the cylinder type of mouth, so that the NOx emission thing of also reason firing chamber generation.Wish to utilize have the exhaust gas recirculation of the cylinder of mouth to control this effulent by opposed type is piston-engined specifically.The exhaust of recirculation mixes to reduce peak combustion temperatures with pressurized air, this reduces NOx emission thing.This process is called exhaust gas recirculatioon (" EGR ").Egr can utilize the exhaust in the air-flow of the new charge being transported to recirculation line 131 introducing that the valve in Fig. 3 controls in the EGR channel of cylinder outside.Alternatively, or additionally, when scavenging stops, EGR process can utilize the remaining exhaust be retained in cylinder 50.When outside EGR, exhaust is pumped in the inflow air-flow of air.The pressure source be communicated with EGR channel is formed and makes exhaust flow through EGR channel to enter pressure difference in pressurized air subtense angle.In some cases, when from guarantee the source of the high pressure in the position being fed to the inlet stream of pressurized air than its (exhaust stream) obtain by be recycled exhaust time, there is virtual pump.In other cases, the active pump of such as pressurized machine 110 is used for the exhaust pump be recycled to deliver to mechanical supercharger just in the pressurized air of pumping to suction port.In these areas, utilize the variable that mechanical supercharger provides additional, run for the EGR controlled in opposed type piston engine.In some cases, the exhaust of recirculation utilizes one or more than one cooler for recycled exhaust gas to cool, and this cooler for recycled exhaust gas comprises the device of air to liquid and/or air-air.In other cases, the exhaust of recirculation is cooled separately by one or more than one charger-air cooler, or combines with one or more than one cooler for recycled exhaust gas and cool.
first EGR circuit structure: in some cases, the internal-combustion engine shown in Fig. 3 comprises the first EGR circuit structure.With reference to figure 4, for uniflow scavenged, have mouth, the exhaust of any exhaust source that the first EGR circuit structured loop of opposed type piston applications leaves since one or more than one cylinder.Such as, but do not get rid of other exhaust source, the first EGR circuit structure comprises the EGR mouth 55 of the longitudinal medial being arranged on relief opening 54; That is, EGR mouth 55 is arranged between relief opening 54 and longitudinal mid point of cylinder 50.This EGR mouth structure according to any concrete structure need comprise one or more than one mouthful of opening.Response burning, when moving towards BDC, exhaust pition 60 moves by EGR mouth 55, and countercylinder mouth pressure opens EGR mouth, and this cylinder port pressure guarantees the pressure higher than intake manifold 130.This pressure difference enters the conduit 133 controlled by one-way valve 134 from the exhaust of an EGR mouth 55 pumping part by collection chamber or manifold (not shown), then enter in intake manifold 130, here, so it mixes with pressurized air and recirculation enters in cylinder port.Preferably, but not necessarily, before the import to charger-air cooler 129, exhaust enters in the pressurized air exported by mechanical supercharger 110.When EGR mouth is opened air-distributor pressure, (" EGR opens ") wishes that the ratio of the pressure of cylinder to air-distributor pressure is no more than threshold value---exceed it and blocked flow may occur in one-way valve 134.This pressure ratio is by the size of EGR mouth and it is relative to the impact of the position (decentre is nearer, and pressure is higher) of the longitudinal center of cylinder and the state (supercharging, turbo machine back pressure etc.) of gas handling system.
Also with reference to figure 4, in the modification of the first EGR circuit structure, in conduit 131, the exhaust of flowing is mixed by mixer 135 with the pressurized air exported by pressurized machine 110, and mixer 135 can be configured to, such as, and Venturi tube.Exhaust is imported in mixer 135 by valve 136.The pressurized air of the compression exported by mechanical supercharger 110 is supplied to the Mixed design of mixer 135.The input that the mixing of the pressurized air of the pressurization produced by mixer 135 and exhaust is supplied to charger-air cooler 129 (or, alternatively, be supplied to the input of charger-air cooler 127).Valve 136 is by the signal operation exported by control unit of engine (ECU) 149.
In some respects, the fluctuation reducing exhaust stream is wished.Under these circumstances and with reference to figure 4, trap 145 is arranged in series in the first loop between EGR mouth 55 and the input of valve 136.At some in other, before exhaust mixes with pressurized air, wish coolant exhaust, under these circumstances, cooler for recycled exhaust gas 146 is arranged in series in the first loop between one-way valve 134 and the input of valve 136.Alternatively, loop structure can be 134,136,146.When using both EGR trap 145 and cooler 146, preferred but optional, cooler for recycled exhaust gas 146 is arranged in series to be exported between the input of valve 136 at EGR trap 145.
second EGR circuit structure: in some respects, the internal-combustion engine 49 shown in Fig. 3 can comprise another kind of EGR circuit structure.With reference to figure 3 and 4, the second egr comprises conduit 131 and valve 138, to shunt from gas exhaust manifold 54 input that a part is vented to charger-air cooler, makes this part exhaust cooled.In order to contribute to the mixing of best exhaust/pressurized air, wishing interpolation device, flowing together with pressurized air by the exhaust of this device and mixing.When exhaust is introduced in pressurized air in the position away from intake manifold 56 by hope, this part exhaust is divided to the input of charger-air cooler 127.This loop makes exhaust stand the cooling impact of two charger-air coolers (127 and 129).If should obtain less cooling, then valve 138 can be configured to three-way valve (as Fig. 4 clearly finding), and this part exhaust can be diverted to the input of mechanical supercharger 110 around cooler 127.This makes this part exhaust only stand the cooling of charger-air cooler 129 alternatively.If needed, only the special cooler for recycled exhaust gas of coolant exhaust can comprise in the second loop.Such as, cooler for recycled exhaust gas can be connected with valve 138, or connects with the delivery outlet of valve 138 and the input of mechanical supercharger 110 and be arranged in conduit 131.In some respects, valve 138 is configured to single three-dimensional device.Alternatively, valve 138 is configured to a pair valve, and each valve is in the respective branch be connected with the Y of conduit 131, and one of them valve controls to the supply of the exhaust of the input of cooler 127, and another controls to the supply of the exhaust of the input of mechanical supercharger 110.
utilize the EGR of residue exhaust: in the internal-combustion engine of direct current or loop scavenging, sometimes wish to collect after scavenging stops or remaining air displacement in holding cylinder.This remaining exhaust can be used for regulating the original state (condition) for burning to the point being conducive to reducing NOx emission thing.According to the structure of turbomachinery, when low and medium speed and load, uniflow scavenged motor can have incomplete scavenging.Because the remaining exhaust of cylinder interior is hot, the temperature obtained of the supercharging that air is new raises greatly, and therefore this method is best suited for and reduces NOx under part engine load state.
The amount that each Zhou Xunhuan flows to the pressurized air of cylinder can be used for changing the remaining air displacement stayed in the cylinder.In this respect, regulate in any given operation cycle the amount flowing to pressurized air in cylinder can be used for " adjustments " retain the amount of the exhaust for generation of burning next time in the cylinder.Retaining the one side of exhaust EGR seen in fig. 4, the by-pass conduit loop 148 comprising valve 139 is arranged in parallel with pressurized machine 110.Valve 139 runs to control by mechanical supercharger 110 pumping to the amount of the pressurized air of motor.The amount arranging the pressurized air of pumping can control the amount of the exhaust of scavenging, and therefore controls the amount being retained in the exhaust in any cylinder after scavenging.In this respect, if wish high mainfold presure (as what be instructed to for high engine load), valve 139 is cut out completely and pressurized air is supplied to motor by with two-forty.When valve 139 is opened gradually, turned back to the import of mechanical supercharger by the amount of the increase of the pressurized air of mechanical supercharger 110 pumping, this has an opportunity to reduce the amount of the pressurized air being supplied to motor.Therefore, pressurized air/fuel oil ratio reduces and is retained in the amount increase of the exhaust in any cylinder.Be the minimizing of NOx in the benefit realized by this respect retaining exhaust EGR and imposed on the minimizing of pumping load of motor by mechanical supercharger 110.
The increase of (felt) pressure (" back pressure ") felt by the exhaust flowing to turbo machine also can be used for changing the amount that the residue stayed in the cylinder is vented.In this respect, the amount of back pressure in regulating any given operation to circulate can be used for amount that residue that " adjustments " occur for burning next time is vented.Therefore, in the another aspect of the exhaust EGR retained, see Fig. 4, vario valve 140 is arranged in series with exhaust output.Valve 140 (felt) back pressure directly affecting and produce in the upstream of valve is set, and therefore, after affecting scavenging, be retained in the amount of the exhaust in any cylinder.In the diagram, valve 140 is arranged in series with the output of turbo machine 121.In this case, any back pressure obtained from the arranging of valve is distributed on all cylinders of motor.In optional, the valve 140a of equivalence can be arranged in series between the input and the gas exhaust manifold of exhaust output collecting one or more than one cylinder of turbo machine 121.In another is optional, the valve 140a of equivalence can be arranged in series with gas exhaust manifold or each relief opening of multiple cylinder.
turbo machine by-pass structure: referring again to Fig. 4, the by-pass conduit loop 143 comprising valve 144 is arranged in parallel with turbo machine 121.Valve 144 runs the amount controlling the exhaust flowing to turbo machine 121 from motor.The valve 144 arranging bypass turbine 121 enables exhaust be discharged in outlet pipe 128 and need operating turbine machine 121 and compressor 122.When such as from during the part engine load of cold start-up in engine warms, exhaust is remained on higher temperature levels and improves reprocessing conversion efficiency (such as, for specific filter cleaner and catalysis device) by this.And, under part engine load state, the operation that valve 144 bypass turbine 121 reduces turbosupercharger is set at motor run duration, and allow more exhaust to be driven (such as on mechanical supercharger 110, via valve 138), also provide exhaust to outlet pipe 128 at a higher temperature, to increase reprocessing conversion efficiency simultaneously.The turbo machine with geometry-variable structure is comprised, with the pressure in the exhaust manifolds 124 of control valve 144 upstream for changing the another kind of structure flowing to the amount of the exhaust of turbo machine 121 from motor.The turbo machine of geometry-variable (VGT) is utilized to replace the turbo machine of fixed geometry not to be to cancel the needs to the such as turbine bypass valve of valve 144.VGT only has limited mass flow scope, and within the scope of this, it works with satisfactory efficiency.Outside this scope, turbine bypass valve can be used for the suction pressure of Mass Control stream and motor 49.
preferred EGR embodiment: uniflow scavengedly there is the opposed type piston engine of mouth to be shown in Fig. 5 for having.In this preferred structure, be vented and flow through conduit 124 to turbo machine 121 from a relief opening of motor or multiple relief opening 54, it is changed (not shown) by reprocessing and flows to outside outlet pipe 128 therefrom, before being input to turbo machine 121, part exhaust to be shunted and from here by the input of valve 138 ' to charger-air cooler 127, at charger-air cooler 127, it mixes with the air-flow of the fresh air of introducing from conduit 124 via 131.In charger-air cooler 127, exhaust and air mix and are cooled, and the exhaust/air mixture of cooling is imported into mechanical supercharger 110.Mechanical supercharger 110 compression exhausts/air mixture, and this is transported to charger-air cooler 129 by the mixture compressed.Then the mixture of the compression of this cooling enters cylinder 50 via suction port 56.Optionally, comprise intake-air throttle valve 141 and turbine bypass valve 144, the exhaust for recirculation controls the highi degree of accuracy of the ratio of fresh air.
exhaust is arranged and is controlled: according to the requirement of concrete structure, the EGR shown in Figure 4 and 5 and turbo machine by-pass structure can uniflow scavenging type by the motor of mouth in realize individually, or to realize in any combination of two or more structures or its part.An example is egr, and the exhaust retaining the recirculation that uncooled exhaust in the cylinder and the cooled and fresh air being supplied to cylinder mix in the structure shown here after scavenging is combined or mixes.The relevant amount of the exhaust of the recirculation of this reservation can change accurately to control EGR flow rate and temperature.Intake-air throttle valve 141 can be arranged in the air-flow of the fresh air flowing to compressor 22, to control the ratio of exhaust to fresh air of recirculation more accurately.If realize (implemented) on each cylinder basis, then provide the single EGR of high speed and pressurized air/fuel oil adjustment (trim) to revise the change between current cylinder and cylinder caused by flowing dynamics and/or fabrication tolerance.
Performed by ECU for utilizing the EGR control procedure responding engine running state of the egr system of one or more structures shown in Figure 4 and 5 or its any combination, this engine operating state is by any one or more than one defined of the following valve of automatic operation: valve 136,138,139,140,140a and 144, intake manifold valve 141, if with mechanical supercharger 110---utilize many speed or variable speed device, and if turbosupercharger 120---utilize variable-geometry devices.Certainly, valve, throttle valve and the operation for the relevant elements of EGR can comprise one or more than one of electricity, pneumatic, machinery and the actuating operations of hydraulic pressure.In order to automatic operation fast, accurately, preferred valve is the high speed of the setting with continuous variable, computer-controlled device.Each valve has the first state and the second state, and in the first state, it is opened (arranging for some control by ECU149) to allow gas to flow through it, and in the second state, it is closed to stop gas to flow through it.
Preferably, EGR control procedure automatically operates the egr system comprising one or more structures, and these structures describe in this article according to one or more than one parameter relevant with the mixture of exhaust gas recirculation and exhaust gas recirculation and pressurized air and illustrate.Parameter value by one or more than one sensor combination, calculate and table look-up and determine, to manage/to control the ratio of the mixture parameter in the value of single parameter and EGR and one or more cylinder.
the EGR embodiment replaced: the egr of replacement is shown in having of Fig. 6 to be had mouthful cylinder and in uniflow scavenged two-stroke opposed type piston engine, wherein only has pressurized machine to provide scavenging pressure.Assuming that reprocessing conversion is realized by Emission Control Device, this Emission Control Device comprise reduction CO and hydrocarbon oxidation catalyst (DOC), reduce the diesel particulate filter (DPF) of soot exhaust thing and the optional catalytic reduction device for reducing NOx.All these devices need additional heat to run, and turbosupercharger does not exist the contention reduced the heat obtained from exhaust, also reduces the specific power of motor simultaneously.And DPF and DOC closely can be connected to now turbosupercharger and usually be arranged on gas exhaust manifold wherein.Further, the waste-heat rejection that the convection current cancelling turbosupercharger and its conduit reduction piston-engined size of opposed type needed and minimizing and turbocharger housing and conduit causes.Preferably, although not necessarily, the exhaust for recirculation is extracted from the outlet of DPF, does not have particulate and is cooled, and be pumped into the import of mechanical supercharger in DPF outlet.Although exhaust is colder after DPF, it can cool further with cooler for recycled exhaust gas.
For two-stroke, have mouth, another EGR embodiment piston-engined is shown in Figure 6 for dc sweeps opposed type.Preferably, motor does not comprise turbosupercharger.Exhaust flows through conduit 124 from gas exhaust manifold 125, by DOC150 and DPF151, then flows to the outside of outlet pipe 128 by valve 140.Part exhaust is by changing be diverted in the input of cooler for recycled exhaust gas 142 by arranging pressure that valve 140 determines.The exhaust of the cooling exported by EGR is measured (ismetered) by valve 147 in the air stream entering mechanical supercharger 110.Intake-air throttle valve 141 can be arranged in the air stream of the mechanical supercharger of the upstream of the output flowing to valve 147, more accurately to control the ratio of exhaust to air of recirculation by forming a small amount of vacuum.Because another kind of EGR circuit is drawn (drawn) by mechanical supercharger 110, therefore greatly reduce from the time required for charger-air cooler 129 emptied of exhaust gases, thus improve transient response.If mechanical supercharger 110 is from motor Direct driver, it will realize at a high speed and high stream together with motor.When the effulent that demand fulfillment is strict requires, when needing under high engine speed and load, the exhaust be pumped required for booster capacity realizes.The pressure that supercharger bypass valve 139 allows mechanical supercharger to produce changes continuously.
Although describe egr with reference to the opposed type piston engine structure of mouth that has with two bent axles, it should be understood that each side of these structures can be applied to the opposed type piston engine with one or more than one bent axle.And each side of these egr can be applied to the opposed type piston engine having the cylinder of mouth having and every side that is that be oppositely arranged and/or one or more than one bent axle is arranged.Therefore, the protection giving these structures is only limited by the appended claims.
Claims (8)
1. one kind has mouth, uniflow scavenged, opposed type piston engine (49), it comprises at least one cylinder (50), pair of pistons (60, 62) and the pressurized air passages of pressurized air is provided at least one suction port of described motor, described at least one cylinder (50) has relief opening and the suction port (54 of mouth (52) and piston control, 56), described pair of pistons (60, 62) be oppositely arranged in described mouth (52), each piston is connected to the piston-engined bent axle (71 of described opposed type, 72), wherein exhaust gas recycling loop, namely EGR circuit has loop input (124) of the relief opening (54) being connected to described cylinder and is connected to the loop output of described pressurized air passages, described pressurized air passages comprises at least one charger-air cooler (127, 129), and described loop exports the pressurized air input being connected at least one charger-air cooler (127), and described motor comprises the pump be communicated with described EGR circuit, be vented by described EGR circuit in described pressurized air passages with pumping.
2. according to claim 1 have mouth, uniflow scavenged, opposed type piston engine, wherein said pump is included in the mechanical supercharger (110) in described pressurized air passages, the pressurized air of the pressurized air input that described mechanical supercharger (110) has mechanical supercharger input and is connected to described at least one charger-air cooler (129) exports, and the valve be arranged in parallel with described mechanical supercharger (139) can be arranged to the first state and the second state, in described first state, the pressurized air that described mechanical supercharger input is connected to described mechanical supercharger by described valve exports, in described second state, the input of described mechanical supercharger to be exported with the pressurized air of described mechanical supercharger by described valve and separates.
3. according to claim 1 have mouth, uniflow scavenged, opposed type piston engine, also comprise and there is the turbosupercharger (120) that the pressurized air being connected to described pressurized air passages exported and be connected to the turbo machine input of described relief opening (54), and the back pressure valve (140a) of series connection between described turbo machine input and described relief opening, wherein said back pressure valve can be arranged to the state that back pressure is worked to described relief opening.
4. according to claim 3 have mouth, uniflow scavenged, opposed type piston engine, and wherein said turbosupercharger comprises the turbo machine (121) of geometry-variable.
5. according to claim 1 have mouth, uniflow scavenged, opposed type piston engine, also comprise turbosupercharger (120), described turbosupercharger (120) has the pressurized air being connected to described pressurized air passages and exports, is connected to the turbo machine input of described relief opening (54), is connected to the turbo machine output of exhaust output (128), and the back pressure valve (140) of series connection between described turbo machine exports and described exhaust exports, wherein said back pressure valve can be arranged to the state that back pressure is worked to described relief opening.
6. according to claim 5 have mouth, uniflow scavenged, opposed type piston engine, and wherein said turbosupercharger comprises the turbo machine (121) of geometry-variable.
7. according to claim 1 have mouth, uniflow scavenged, opposed type piston engine, also comprise the turbosupercharger (120) with the pressurized air output being connected to described pressurized air passages and the turbo machine (121) with the input being connected to described relief opening (54), and the turbine bypass valve (144) to be arranged in parallel with described turbo machine, wherein said turbine bypass valve can be arranged to the first state and the second state, in described first state, described turbo machine input is connected to turbo machine by described turbine bypass valve and exports, and in described second state, the input of described turbo machine to be exported with described turbo machine by described turbine bypass valve and separates.
8. according to claim 7 have mouth, uniflow scavenged, opposed type piston engine, and wherein said turbo machine (121) is the turbo machine of geometry-variable.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US39584510P | 2010-05-18 | 2010-05-18 | |
| US61/395,845 | 2010-05-18 | ||
| US40159810P | 2010-08-16 | 2010-08-16 | |
| US61/401,598 | 2010-08-16 | ||
| PCT/US2011/000864 WO2011146111A1 (en) | 2010-05-18 | 2011-05-16 | Egr construction for opposed-piston engines |
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| Publication Number | Publication Date |
|---|---|
| CN103026024A CN103026024A (en) | 2013-04-03 |
| CN103026024B true CN103026024B (en) | 2016-01-27 |
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| CN201180024717.4A Active CN103026024B (en) | 2010-05-18 | 2011-05-16 | For the piston-engined egr of opposed type |
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| EP (1) | EP2572089B1 (en) |
| JP (1) | JP6117695B2 (en) |
| CN (1) | CN103026024B (en) |
| WO (1) | WO2011146111A1 (en) |
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Also Published As
| Publication number | Publication date |
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| CN103026024A (en) | 2013-04-03 |
| EP2572089A1 (en) | 2013-03-27 |
| JP6117695B2 (en) | 2017-04-19 |
| JP2013529275A (en) | 2013-07-18 |
| EP2572089B1 (en) | 2015-03-18 |
| WO2011146111A1 (en) | 2011-11-24 |
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