CN100443705C - A turbocharged internal combustion engine - Google Patents
A turbocharged internal combustion engine Download PDFInfo
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- CN100443705C CN100443705C CNB2005800024645A CN200580002464A CN100443705C CN 100443705 C CN100443705 C CN 100443705C CN B2005800024645 A CNB2005800024645 A CN B2005800024645A CN 200580002464 A CN200580002464 A CN 200580002464A CN 100443705 C CN100443705 C CN 100443705C
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- turbosupercharger
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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
Abstract
A turbocharged internal combustion engine comprising: a turbocharger (15) actuators for opening and closing the exhaust valves (a, b) and an electronic controller which controls operation of the actuators to thereby control opening and closing of the exhaust valves (a, b). The exhaust valves comprise a first exhaust valve (a) connected to a first exhaust duct (14) and a second exhaust valve (16) connected to a second exhaust duct (16). The first exhaust duct (14) is connected to the turbocharger (15) so that exhaust gases passing through the first exhaust duct (14) drive the turbocharger (15). The second exhaust duct (16) bypasses the turbocharger (15) and the combusted gases flowing through the second exhaust duci are exhausted without passing through the turbocharger (15). The electronic controller by controlling the opening and closing of the first (a) and second (b) exhaust valves controls what proportion of the combusted gases leaving the combustion chamber flow through each of the first (14) and second (16) exhaust ducts.
Description
Technical field
The present invention relates to a kind of turbocharging internal-combustion engines.
Background technique
Turbocharging internal-combustion engines is known.Yet, thereby the rotating speed of effectively controlling turbosupercharger in the motor is a problem to imposing on that boosting of air inlet control always.Need wastegate or complicated valve gear.And, owing to must satisfy strict emission standard at all motors, therefore it is debatable using high pressure turbocharger, thereby this is because restriction that this turbosupercharger is forced flowing and the unacceptable delay that the cooling of exhaust is tending towards causing the catalytic converter igniting.Traditionally, in having the motor of two turbocharging, control subtly by each turbosupercharger relatively boosting of providing of another turbosupercharger be a problem.
Summary of the invention
The invention provides a kind of turbocharging internal-combustion engines, comprising:
The firing chamber of variable volume;
Inlet valve means, it is controlled the mobile of air that enters described firing chamber;
Fuel delivery means, be used for fuel be delivered to air and and air mixing;
Exhaust valve device is used to control flowing of waste gas (combusted gas) from described firing chamber;
Compressor set is used for pressurized air before the permission air enters described firing chamber;
Actuator devices is used to open and close described exhaust valve device; And
Electronic controller, it controls the operation of described actuator devices, thereby controls the opening and closing of described exhaust valve device, wherein:
Described exhaust valve device comprises: at least one first exhaust valve that is connected to downtake pipe; And at least one second exhaust valve, be connected to described downtake pipe and separate also independently second exhaust pipe;
Described compressor set comprises first turbosupercharger, and described downtake pipe is connected to this first turbosupercharger, rotates thereby make by described first turbosupercharger of the exhaust gas drive of described downtake pipe;
Described second exhaust pipe is walked around described first turbosupercharger, thereby the waste gas that flows through described second exhaust pipe is not discharged by described first turbosupercharger; And
Thereby described electronic controller is controlled the opening and closing of described first exhaust valve and second exhaust valve by the operation of controlling described actuator devices, and it can operate to leave in the waste gas of described firing chamber with control has the exhaust-gas flow of much ratios respectively by described downtake pipe and described second exhaust pipe.
By using actuator by electronic controller controls, can control the operation of exhaust valve by this way, that is, make controller can control volume and flow, thereby control the operation of first turbosupercharger subtly by the waste gas of first turbosupercharger.
Description of drawings
Referring now to accompanying drawing the preferred embodiments of the present invention are described, wherein:
Fig. 1 schematically shows first embodiment according to internal-combustion engine of the present invention, and this internal-combustion engine has single type supercharging system; And
Fig. 2 represents second embodiment according to turbocharging internal-combustion engines of the present invention, and this internal-combustion engine has the two-step supercharging system;
Fig. 3 represents the 3rd embodiment according to turbocharging internal-combustion engines of the present invention, and this internal-combustion engine has turbosupercharger and mechanical supercharger (supercharger);
Fig. 4 represents the 4th embodiment according to turbocharging internal-combustion engines of the present invention, and this internal-combustion engine has motor compressor and turbosupercharger;
Fig. 5 represents the 5th embodiment according to turbocharging internal-combustion engines of the present invention, and this internal-combustion engine has the starting valve that allows to improve start-up function; And
Fig. 6 represents the 6th embodiment according to turbocharging internal-combustion engines of the present invention, and this internal-combustion engine has the basin that is used for pressurized gas.
Embodiment
In Fig. 1, can see four cylinder engine with four cylinders 10,11,12 and 13.Each cylinder all has intake valve " i " and two exhaust valves " a " and " b ".Exhaust valve " a " and " b " are at least respectively by the hydraulic actuator operation that is connected to described valve.All by the control of electronic controller (not shown), this electronic controller is the part of engine management system normally for each hydraulic actuator.In same cylinder, each exhaust valve " a " is independent of exhaust valve " b " and opens and closes.
Stream passes through exhaust valve " a " and the downtake pipe 14 that arrives from the exhaust-gas flow of cylinder 10,11,12 and 13.This outlet pipe 14 continues transported to waste gas the turbine 15a level of turbosupercharger 15.
Exhaust valve " b " all is connected to second exhaust pipe 16, and waste gas can flow to starter catalytic converter 17 from cylinder 10,11,12 and 13 through exhaust valve " b " by this second exhaust pipe.
From turbosupercharger 15 outputs, this outlet pipe 18 is engaged to outlet pipe 16 at joint 19 places to the waste gas that expands in turbine 15a by outlet pipe 18.At joint 19 places, stream mixes with the waste gas that flows through outlet pipe 16 from the waste gas of turbosupercharger 15, and mixed flow then enters atmosphere through second catalytic converter 21 then.
The fresh air (charge air) that charges into is inhaled among the compressor section 15b of turbosupercharger 15, continued transported to the intake valve " i " of cylinder 10,11,12 and 13 then by gas-entered passageway 19, charge into air and in the process of cylinder moving, passing through interstage cooler.
Electronic controller can utilize its control to actuator to control the opening and closing of exhaust valve " a " and " b ", thereby the exhaust flow of control flows much ratios in whole waste gas of each cylinder is to outlet pipe 14, and the exhaust-gas flow of much ratios is by outlet pipe 16.Like this, the operation of controller may command turbosupercharger 15.Needs bigger boost the time, will from whole waste gas that cylinder 10,11,12 and 13 is discharged, carry by turbosupercharger 15 by the waste gas of larger proportion, vice versa.When engine start, the major part from the waste gas that cylinder 10,11,12 and 13 is discharged (if not discharging whole waste gas) will be by outlet pipe 16, guaranteeing starter catalytic converter 17 than preignition, and so discharging when reducing engine start.
Figure 2 illustrates second modification according to motor of the present invention.This motor has four cylinders 100,101,102 and 103, and each cylinder all has intake valve " i ", exhaust valve " a " and exhaust valve " b ".Exhaust valve " a " and " b " are at least by the hydraulic actuator operation under the control of electronic controller (not shown).In same cylinder, each exhaust valve " a " can be independent of exhaust valve " b " to be operated.
Cylinder 100,101,102 and 103 exhaust valve " a " all are connected to downtake pipe 104, and this downtake pipe is guided waste gas into the turbine part 105a of high pressure turbocharger 105.Cylinder 100,101,102 and 103 exhaust valve " b " all are connected to outlet pipe 106, and waste gas is walked around high pressure turbocharger 105 by this outlet pipe and flowed to the turbine part 107a of low pressure turbocharger 107.
The expansion waste gas of discharging the turbine part 105a of turbosupercharger 105 flows to joint 109 by outlet pipe 108, and at these joint 109 places, expansion waste gas is imported in the exhaust flow that passes through along outlet pipe 106.Directly from exhaust valve " b " so the mixed flow of the waste gas that passes through and the waste gas of discharging from turbosupercharger 105 is transfused to the turbine 107a of low pressure turbocharger 107.
The waste gas of discharging from the turbine 107a of turbosupercharger 107 enters atmosphere by exhaust passage 110 through catalytic converter 111.
The air that charges into that is inhaled among the compressor section 107b of turbosupercharger 107 is discharged from by suction tude 112, with through interstage cooler 113.Pressurized air just can pass through the compressor section 105b of high pressure turbocharger 105 then in case be cooled in interstage cooler 113, perhaps can walk around turbosupercharger 105 fully and pass through along bypass channel 114.
The pressurized air that is provided to turbosupercharger 105 is supplied under first pressure, is pressurized to the second higher pressure by turbosupercharger 105 then.The forced air that leaves compressor 105b passes through pipeline 115, thereby mixes again with the air that flows through bypass channel 114.Mixed air stream passes through interstage cooler 116 and suction tude 117 and the intake valve that arrives " i " then.
In bypass channel 114, be provided with by-pass valve 118.By-pass valve 118 is by described electronic controller controls.The operation of by-pass valve 118 will make electronic controller control by high pressure turbocharger 105 making how many air inlets.
The opening and closing of electronic controller controls exhaust valve " a " and " b " (by control) to the actuator that is connected to exhaust valve, thereby control is passed through outlet pipe 104 from the exhaust-gas flow of much ratios in the whole exhaust flows in cylinder 100,101,102 and 103, and the exhaust-gas flow of much ratios is by outlet pipe 106.Like this, electronic controller may command turbosupercharger 105 and 107 operation.
In some cases, preferably make all or most at least exhaust flow walk around turbosupercharger 105 fully.In this case, exhaust valve " a " keeps complete (or almost) to cut out, and exhaust valve " b " opens and closes in each circulation individually.In this case, electronic controller also will be opened by-pass valve 118 fully, can not pass through turbosupercharger 105 thereby charge into air.For example, turbosupercharger 105 is walked around in expectation fully when the starting of motor.Because turbosupercharger 105 is a high pressure turbocharger, so will form bigger restriction to exhaust flow from cylinder.This restriction and therefore producing the firing time that will increase catalyzer 111 to the cooling of waste gas.On the other hand, low pressure turbocharger 107 will apply much smaller restriction to waste gas, and therefore under starting state, waste gas preferably only flows through turbosupercharger 107.
The system of describing among Fig. 2 need not uneconomic wastegate with regard to its essence.In the layout of Fig. 2, all waste gas all passes through turbosupercharger 107.
By changing exhaust valve " a " and " b " thus control valve timing pass through the air-flow of outlet pipe 104, can be easily the boost level of the air inlet that is supplied to intake valve " i " be controlled by electronic controller.And controller can be controlled by control by-pass valve 118 and boost.
When engine speed was higher, if to not carrying out suitable control by the exhaust flow of outlet pipe 104 and by the electronic controller that the inlet stream of bypass channel 114 is controlled, then turbosupercharger 105 may provide excessive boosting.Usually under the situation of full load under steady state and high-engine rotating speed, high pressure turbocharger 105 can be bypassed substantially, so that most of air inlet will flow in bypass channel 114, and most of exhaust flow will be by outlet pipe 106.
Fig. 3 schematically shows according to three cylinder compression-ignition engines 300 of the present invention, and it has forced induction system, and this forced induction system comprises the low pressure stage with turbosupercharger 301 and has the high pressure stage of mechanical supercharger 302.There is shown three cylinders 303,304 and 305, wherein each cylinder all has exhaust valve " a ", and this exhaust valve is to controlling via passage 309 to the blast air of the turbine of low pressure turbocharger 301.Each cylinder also has the exhaust valve of controlling to the blast air of bypass channel 303 " b ".Bypass channel 303 allows exhaust to walk around low pressure turbocharger 301 and flows directly into atmosphere.
The motor of Fig. 3 adopts the air that charges into that is drawn in the compressor section of low pressure turbocharger 301 via air filter 304 to carry out work.The air that pressurizeed flows to by-pass valve 306 via passage 305 then, perhaps flows to the compressor section of high-pressure machinery pressurized machine 302.Then, the air that charges into that pressurizeed in high-pressure machinery pressurized machine 302 flows out by passage 307.By-pass valve 306 can be controlled by engine management system, thereby the air quantity that charges into of the pressurization of the compressor that flows into mechanical supercharger 302 is controlled.Alternatively, can adopt simple mechanical pre-loaded valve, it is opened under pressure with restriction as to the input of the compressor of mechanical supercharger 302 and the pressure of mobile ventilation (scavenge air) limiting.The forced air of bypass scavenge air and discharge mechanical supercharger 302 mixed before they flow through interstage cooler 308, delivered into cylinder 303,304,305 by intake valve " i " then.
Engine management system is controlled exhaust valve in each cylinder " a " and opening of " b ", thereby control flows is to the amount of the pressurization exhaust of the turbine of low pressure turbocharger 301.Part exhaust can flow to the turbine of turbosupercharger 301, and a part can flow directly into atmosphere via bypass channel 303.
Can be susceptible to normally Roots's blowing-type mechanical supercharger of mechanical supercharger 302.It can be the clutch mechanical supercharger, thereby under the control of electronic controller, only turns round under some engine operating status.
The 4th modification of motor has been shown among Fig. 4.The motor 400 that illustrates has three cylinders, and each cylinder all is a type shown in Figure 1.And each cylinder all has four cylinder head valves.Each cylinder all has the exhaust valve " a " that is connected to downtake pipe 401, and each cylinder all has the exhaust valve " b " that is connected to the second exhaust pipe 402 that separates with downtake pipe 401.
In the motor of Fig. 4, suck fresh air and pass through motor compressor 405 its compression via filter 404., and do not turn round in other cases with under low engine speed and/or by electronic controller controls motor compressor 405 in running during starts.Under other situation, by-pass valve 406 is opened, and walks around low pressure motor compressor 405 to allow charging into air.
Discharge low pressure compressor 405 or the air by by-pass valve 406 continues to flow to high pressure turbocharger 407 then, thereby in this turbosupercharger, be compressed, output to interstage cooler 409 by pipeline 408 afterwards, then via the cylinder of intake valve " i " to motor.
Waste gas can be discharged from cylinder 410,411,412 via exhaust valve " a " or by exhaust valve " b ".These valves are subjected to the control by the actuator of engine management system control.The operation of this engine management system control valve " a " and " b ", thus the exhaust air flow of controlling much ratios is passed through outlet pipe 401, and the exhaust air flow of much ratios is by outlet pipe 402.Flow through the turbine of the blast air of outlet pipe 401, and the exhaust that flows through outlet pipe 402 is walked around turbosupercharger 407 and is flowed directly into atmosphere to high pressure turbocharger 407.
The modification of the turbo charge system of the motor of Fig. 5 presentation graphs 2 has advantageously been improved the starting (except that during starts, motor will as mentioned above like that turn round) of this turbo charge system with auxiliary engine.The supplementary features of described motor are starting valve 520.This valve is controlled by engine management system.During engine start, starting valve 520 cuts out.And controller can change the operation of exhaust valve.By cut-off valve 520 and change the operation of exhaust valve, controller can make motor turn round like this, that is, make gas be compressed in each firing chamber, discharges via exhaust valve " a " then.The gas that is discharged from provides power for high pressure turbocharger 502, and makes it begin rotation.The gas of discharging from the turbine of turbosupercharger 502 is transferred back the firing chamber via exhaust valve " b " then.The gas that is transferred back and then pressurized by exhaust valve " a " discharging, thereby circulates once more.This makes motor work as pneumatic pump, thus fuel is injected the firing chamber and pilot engine before the starting high pressure turbocharger 502 so that its fast rotational.This is very favorable, particularly because the air of recirculation can be than the fresh air temperature height that charges into.Provide such equipment just to need not mechanical supercharger or motor compressor, described mechanical supercharger or motor compressor select to be used for assisting the starting of the compression ignition engine that does not have quick starting operator scheme shown in Figure 5 usually.
Although being depicted as, the layout that is used for quick starting operation system of Fig. 5 is applied to motor shown in Figure 2, but can enter the firing chamber being used for further compression via exhaust valve " b " recirculation by making the gas that leaves turbosupercharger, thereby can become provide the quick starting pattern the engine arrangement of other accompanying drawing.
Fig. 6 shows another example according to motor of the present invention.In this modification, each cylinder all has a kind of additional exhaust valves " c ".Except (can utilizing valve " c " during this) during engine braking and the engine start, exhaust valve " a " and " b " operate in a manner described.Additional exhaust valves " c " is connected to the basin 604 that is used for store compressed gas by passage 601,602,603.During engine braking, valve " c " is controlled so as to and allows pressurized gas to flow to basin 604 from cylinder.Like this, when needed (for example when engine start) just can open valve " c ", so that previously stored pressurized gas is supplied to cylinder, thereby it is expanded and the driven plunger to-and-fro motion in cylinder.
Have only when basin is not pressurized to its limit, just operated valve " c " flows to basin 604 to allow pressurized gas.Have only when the pressure in the basin 604 is enough, valve " c " just allows gas to flow to cylinder from basin 604.
In Fig. 2 and embodiment shown in Figure 5, can substitute low pressure turbocharger by electric boosted turbosupercharger, this electric boosted turbosupercharger is assisted by electric power when hanging down engine speed or when starting, but in other cases, provides power by the exhaust from motor.Output power when electric boosted turbosupercharger is used in the high-engine rotating speed.
Can operate above-mentioned motor by spark ignition or ignition by compression.The present invention is applicable to the conventional engine with any amount cylinder, but also applicable to the internal-combustion engine except conventional engine (for example, rotary engine).
Above-mentioned exhaust valve " a " and " b " can be the lifting valves by the hydraulic actuator operation.Yet, can operate the lifting valve by the actuator (for example, electromagnetic actuators) of any other suitable form.In fact, can substitute the lifting valve by the suitable valve gear of actuator control by sleeve valve or any other.
Above-mentioned intake valve " i " itself can preferably be controlled by the actuator under electronic controller controls, but this not necessarily, but can adopt any type of air door operation, for example traditional cam and tappet operation.
Above-mentioned turbosupercharger can be the turbosupercharger of fixed geometry or the turbosupercharger of geometry-variable.
Claims (16)
1, a kind of turbocharging internal-combustion engines comprises:
The firing chamber of variable volume;
Inlet valve means, it is controlled the mobile of air that enters described firing chamber;
Fuel delivery means, be used for fuel be delivered to air and and air mixing;
Exhaust valve device is used to control flowing from the waste gas of described firing chamber;
Compressor set is used for pressurized air before the permission air enters described firing chamber;
Actuator devices is used to open and close described exhaust valve device; And
Electronic controller, it controls the operation of described actuator devices, thereby controls the opening and closing of described exhaust valve device, wherein:
Described exhaust valve device comprises: at least one first exhaust valve that is connected to downtake pipe; And at least one second exhaust valve, be connected to described downtake pipe and separate also independently second exhaust pipe;
Described compressor set comprises first turbosupercharger, and described downtake pipe is connected to this first turbosupercharger, rotates thereby make by described first turbosupercharger of the exhaust gas drive of described downtake pipe;
Described second exhaust pipe is walked around described first turbosupercharger, thereby the waste gas that flows through described second exhaust pipe is not discharged by described first turbosupercharger; And
Thereby described electronic controller is controlled the opening and closing of described first exhaust valve and second exhaust valve by the operation of controlling described actuator devices, and it can operate to leave in the waste gas of described firing chamber with control has the exhaust-gas flow of much ratios respectively by described downtake pipe and described second exhaust pipe;
Described compressor set also comprises second turbosupercharger;
Described first turbosupercharger is a high-voltage booster, it can receive the pressurized air that is in first pressure from described second turbosupercharger, this second turbosupercharger is a low pressure turbocharger, and described first turbosupercharger arrives the second higher pressure with air compression; And
Leave the waste gas of this first turbosupercharger after expanding and mix with the waste gas that flows in described second exhaust pipe in the turbine of described first turbosupercharger, mixed then exhaust flow drives described second turbosupercharger and rotates.
2, turbocharging internal-combustion engines according to claim 1 is characterized in that, the exhaust-gas flow of leaving described second turbosupercharger flows into atmosphere then by catalytic converter.
3, turbocharging internal-combustion engines according to claim 1 and 2, it is characterized in that, also comprise first interstage cooler, the air that compresses in described second low pressure turbocharger passed through this first interstage cooler before arriving described first high pressure turbocharger.
4, turbocharging internal-combustion engines according to claim 1 and 2, it is characterized in that, also comprise: the air inlet bypass channel flows to described inlet valve means thereby can be walked around described first turbosupercharger by this bypass channel by the air of described second turbosupercharger compression; And the by-pass valve device, be used for compressed-air actuated the flowing by described bypass channel controlled.
5, a kind of turbocharging internal-combustion engines comprises:
The firing chamber of variable volume;
Inlet valve means, it is controlled the mobile of air that enters described firing chamber;
Fuel delivery means, be used for fuel be delivered to air and and air mixing;
Exhaust valve device is used to control flowing from the waste gas of described firing chamber;
Compressor set is used for pressurized air before the permission air enters described firing chamber;
Actuator devices is used to open and close described exhaust valve device; And
Electronic controller, it controls the operation of described actuator devices, thereby controls the opening and closing of described exhaust valve device, wherein:
Described exhaust valve device comprises: at least one first exhaust valve that is connected to downtake pipe; And at least one second exhaust valve, be connected to described downtake pipe and separate also independently second exhaust pipe;
Described compressor set comprises first turbosupercharger, and described downtake pipe is connected to this first turbosupercharger, rotates thereby make by described first turbosupercharger of the exhaust gas drive of described downtake pipe;
Described second exhaust pipe is walked around described first turbosupercharger, thereby the waste gas that flows through described second exhaust pipe is not discharged by described first turbosupercharger;
Thereby described electronic controller is controlled the opening and closing of described first exhaust valve and second exhaust valve by the operation of controlling described actuator devices, and it can operate to leave in the waste gas of described firing chamber with control has the exhaust-gas flow of much ratios respectively by described downtake pipe and described second exhaust pipe;
Described compressor set also comprises mechanical supercharger;
Described first turbosupercharger is a low pressure turbocharger, and it is compressed to first pressure with air inlet;
Described mechanical supercharger is the high-pressure machinery pressurized machine, and its pressurized air with described first turbosupercharger output is compressed to second pressure higher than described first pressure;
Described compressor set also comprises bypass channel, can be walked around described mechanical supercharger by this bypass channel by the pressurized air of described first turbosupercharger compression; And
The by-pass valve device is set, so that compressed-air actuated the flowing by described bypass channel controlled.
6, turbocharging internal-combustion engines according to claim 5 is characterized in that, described by-pass valve device is the electrically-controlled valve by described electronic controller controls.
7, a kind of turbocharging internal-combustion engines comprises:
The firing chamber of variable volume;
Inlet valve means, it is controlled the mobile of air that enters described firing chamber;
Fuel delivery means, be used for fuel be delivered to air and and air mixing;
Exhaust valve device is used to control flowing from the waste gas of described firing chamber;
Compressor set is used for pressurized air before the permission air enters described firing chamber;
Actuator devices is used to open and close described exhaust valve device; And
Electronic controller, it controls the operation of described actuator devices, thereby controls the opening and closing of described exhaust valve device, wherein:
Described exhaust valve device comprises: at least one first exhaust valve that is connected to downtake pipe; And at least one second exhaust valve, be connected to described downtake pipe and separate also independently second exhaust pipe;
Described compressor set comprises first turbosupercharger, and described downtake pipe is connected to this first turbosupercharger, rotates thereby make by described first turbosupercharger of the exhaust gas drive of described downtake pipe;
Described second exhaust pipe is walked around described first turbosupercharger, thereby the waste gas that flows through described second exhaust pipe is not discharged by described first turbosupercharger; And
Thereby described electronic controller is controlled the opening and closing of described first exhaust valve and second exhaust valve by the operation of controlling described actuator devices, and it can operate to leave in the waste gas of described firing chamber with control has the exhaust-gas flow of much ratios respectively by described downtake pipe and described second exhaust pipe;
Described compressor set also comprises motor compressor, and described first turbosupercharger is high pressure turbocharger, its receive the air that compressed by described motor compressor and with described air pressurized to higher level;
Described compressor set also comprises: bypass channel, and air can be walked around described motor compressor by this bypass channel, thereby directly flows to described turbosupercharger;
Automatically controlled by-pass valve is set, and it is controlled the mobile of air by described bypass channel; And
Described controller is controlled the operation of described by-pass valve and described motor compressor, thereby described motor compressor is only turned round under engine start and/or low engine speed, and in other cases, air inlet is walked around described motor compressor fully and is only compressed by described turbosupercharger.
8, a kind of turbocharging internal-combustion engines comprises:
The firing chamber of variable volume;
Inlet valve means, it is controlled the mobile of air that enters described firing chamber;
Fuel delivery means, be used for fuel be delivered to air and and air mixing;
Exhaust valve device is used to control flowing from the waste gas of described firing chamber;
Compressor set is used for pressurized air before the permission air enters described firing chamber;
Actuator devices is used to open and close described exhaust valve device; And
Electronic controller, it controls the operation of described actuator devices, thereby controls the opening and closing of described exhaust valve device, wherein:
Described exhaust valve device comprises: at least one first exhaust valve that is connected to downtake pipe; And at least one second exhaust valve, be connected to described downtake pipe and separate also independently second exhaust pipe;
Described compressor set comprises first turbosupercharger, and described downtake pipe is connected to this first turbosupercharger, rotates thereby make by described first turbosupercharger of the exhaust gas drive of described downtake pipe;
Described second exhaust pipe is walked around described first turbosupercharger, thereby the waste gas that flows through described second exhaust pipe is not discharged by described first turbosupercharger;
Thereby described electronic controller is controlled the opening and closing of described first exhaust valve and second exhaust valve by the operation of controlling described actuator devices, and it can operate to leave in the waste gas of described firing chamber with control has the exhaust-gas flow of much ratios respectively by described downtake pipe and second exhaust pipe;
Described compressor set comprises second low pressure turbocharger, it is with air compression to the first pressure, and described first turbosupercharger is a high pressure turbocharger, and it will be arrived second pressure higher than described first pressure by the air compression that described low pressure turbocharger compresses;
Described downtake pipe continues transported to described first high pressure turbocharger with exhaust, rotate to drive described high pressure turbocharger, and described second exhaust pipe continues transported to described second low pressure turbocharger with exhaust, and walk around described first high pressure turbocharger, thereby driving described second low pressure turbocharger rotates; And
Described controller is controlled the operation of described actuator devices, thereby the exhaust-gas flow that is controlled at stream much ratios in the waste gas of described firing chamber is by described downtake pipe, the exhaust-gas flow of much ratios is by described second exhaust pipe, thereby described controller is controlled the operation of described first high pressure turbocharger and described second low pressure turbocharger.
9, turbocharging internal-combustion engines according to claim 8 is characterized in that, the expansion exhaust of leaving described first high pressure turbocharger is transported in the described second exhaust pipe, to be continued transported to described second low pressure turbocharger.
10, according to Claim 8 or 9 described turbocharging internal-combustion engines, it is characterized in that described compressor set also comprises: bypass channel, air can be walked around described first high pressure turbocharger by this bypass channel; And by-pass valve, it is controlled the mobile of air by described bypass channel.
11, turbocharging internal-combustion engines according to claim 10 is characterized in that, described by-pass valve is by described electronic controller controls.
12, according to claim 5,6,7,8 or 9 described turbocharging internal-combustion engines, it is characterized in that described compressor set also comprises interstage cooler, be used for this air inlet of cooling before the compressor air inlet is transported to described firing chamber.
13, according to claim 1,2,5,6,7,8 or 9 described turbocharging internal-combustion engines, it is characterized in that, also comprise the starting valve by described electronic controller controls, it can prevent that exhaust from flowing through described second exhaust pipe during engine start, and wherein:
The exhaust of leaving described turbosupercharger by described downtake pipe supply is transported in the described second exhaust pipe of described starting valve upstream; And
The described electronic controller of operation during starts at motor, to close described starting valve, and open and close described exhaust valve device, make the pressurized gas that leaves described firing chamber be continued transported to described first turbosupercharger that is connected to this downtake pipe via described downtake pipe, to drive described first turbosupercharger, make pressurized gas be back to described firing chamber then, in this firing chamber, to be compressed once more via described second exhaust pipe.
14, according to claim 1,2,5,6,7,8 or 9 described turbocharging internal-combustion engines, it is characterized in that, also comprise: basin; The basin passage, it leads to described basin from described firing chamber; And cylinder head basin valve gear, be used to control waste gas from described firing chamber flowing to described basin, and control institute's waste gas of storing is from described basin mobile to described firing chamber, thereby the waste gas that compresses can be continued transported to described basin in described firing chamber within it, and turn back to described cylinder after being used in this cylinder, to expand with storage.
15, according to claim 1,2,5,6,7,8 or 9 described turbocharging internal-combustion engines, it is characterized in that, injection device can enough inject fuel described firing chamber early in upstroke, thereby make fuel and air mixing to produce uniform mixture, light this mixture by uniform supercharging ignition by compression then, and wherein alternatively, described injection device can inject fuel after a while with in the ignition by compression of described firing chamber in described upstroke.
16, turbocharging internal-combustion engines according to claim 15, it is characterized in that, under the partial load working order of motor, described controller in the upstroke manipulate of piston to close described exhaust valve device, thereby waste gas is captured in the described firing chamber, captive waste gas and fuel and air form mixture, thereby with uniform supercharging compression ignition operation motor the time, play the effect that postpones fire fuel and air mixture.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0400808.2 | 2004-01-14 | ||
| GBGB0400808.2A GB0400808D0 (en) | 2004-01-14 | 2004-01-14 | A turbocharged internal combustion engine |
| GB0400794.4 | 2004-01-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1910355A CN1910355A (en) | 2007-02-07 |
| CN100443705C true CN100443705C (en) | 2008-12-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800024645A Expired - Fee Related CN100443705C (en) | 2004-01-14 | 2005-01-14 | A turbocharged internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN100443705C (en) |
| GB (1) | GB0400808D0 (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4341706B2 (en) * | 2007-07-18 | 2009-10-07 | トヨタ自動車株式会社 | Control device for internal combustion engine |
| WO2010101728A2 (en) * | 2009-03-03 | 2010-09-10 | Borgwarner Inc. | Turbocharger |
| JP5433534B2 (en) | 2009-09-08 | 2014-03-05 | 株式会社豊田自動織機 | Internal combustion engine with a supercharger |
| EP2503125B1 (en) * | 2011-03-25 | 2014-11-19 | Ford Global Technologies, LLC | Internal combustion engine equipped with two turbochargers and method to operate such an engine |
| FR3015577B1 (en) * | 2013-12-19 | 2018-02-02 | Valeo Systemes De Controle Moteur | ASSEMBLY COMPRISING A THERMAL MOTOR AND A CONFIGURED ELECTRIC COMPRESSOR FOR HEATING GASES OF ADMISSION |
| CN104500265B (en) * | 2014-12-30 | 2016-04-27 | 清华大学 | The supercharging residual neat recovering system of internal-combustion engine |
| KR101826571B1 (en) * | 2016-08-30 | 2018-02-07 | 현대자동차 주식회사 | Engine system |
| US10570834B2 (en) * | 2016-10-27 | 2020-02-25 | Cummins Inc. | Supercharging for improved engine braking and transient performance |
| US10202913B2 (en) * | 2017-02-06 | 2019-02-12 | Ford Global Technologies, Llc | Method and system for boosted engine system |
| US10746090B2 (en) * | 2018-08-27 | 2020-08-18 | The Boeing Company | High altitude internal combustion engine/turbocharger exhaust combustor |
| IT201900006696A1 (en) * | 2019-05-09 | 2020-11-09 | Ferrari Spa | FOUR-WHEEL DRIVE HYBRID VEHICLE INCLUDING AN INTERNAL COMBUSTION THERMAL ENGINE EQUIPPED WITH AN ELECTRIFIED TURBINE AND CORRESPONDING CONTROL METHOD |
| GB2584683B (en) * | 2019-06-11 | 2021-06-09 | Perkins Engines Co Ltd | Two stage turbocharger with cooling arrangement |
| CN115126596A (en) * | 2022-06-23 | 2022-09-30 | 宁波吉利罗佑发动机零部件有限公司 | Turbocharging device and vehicle |
Citations (3)
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|---|---|---|---|---|
| US6029452A (en) * | 1995-11-15 | 2000-02-29 | Turbodyne Systems, Inc. | Charge air systems for four-cycle internal combustion engines |
| US6415600B1 (en) * | 1998-07-10 | 2002-07-09 | Saab Automobile Ab | Catalytic converter system for i.c.-engine with divided flow and two converters |
| EP1306534A2 (en) * | 2001-10-24 | 2003-05-02 | Hitachi, Ltd. | Engine supercharging system |
-
2004
- 2004-01-14 GB GBGB0400808.2A patent/GB0400808D0/en not_active Ceased
-
2005
- 2005-01-14 CN CNB2005800024645A patent/CN100443705C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6029452A (en) * | 1995-11-15 | 2000-02-29 | Turbodyne Systems, Inc. | Charge air systems for four-cycle internal combustion engines |
| CN1439801A (en) * | 1997-09-29 | 2003-09-03 | 涡轮动力系统有限公司 | Two-stage pressurizing system for four-stroke IC engine |
| US6415600B1 (en) * | 1998-07-10 | 2002-07-09 | Saab Automobile Ab | Catalytic converter system for i.c.-engine with divided flow and two converters |
| EP1306534A2 (en) * | 2001-10-24 | 2003-05-02 | Hitachi, Ltd. | Engine supercharging system |
Also Published As
| Publication number | Publication date |
|---|---|
| GB0400808D0 (en) | 2004-02-18 |
| CN1910355A (en) | 2007-02-07 |
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