CN100507249C - Engine - Google Patents
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- CN100507249C CN100507249C CN 200680001586 CN200680001586A CN100507249C CN 100507249 C CN100507249 C CN 100507249C CN 200680001586 CN200680001586 CN 200680001586 CN 200680001586 A CN200680001586 A CN 200680001586A CN 100507249 C CN100507249 C CN 100507249C
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- 238000002347 injection Methods 0.000 claims abstract description 105
- 239000007924 injection Substances 0.000 claims abstract description 105
- 230000007246 mechanism Effects 0.000 claims abstract description 36
- 239000007921 spray Substances 0.000 claims description 32
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- 239000002826 coolant Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 239000003381 stabilizer Substances 0.000 description 2
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Classifications
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- Y02T10/144—
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- Y02T10/44—
Abstract
An engine includes an in-cylinder injector injecting fuel into a cylinder, a port injector injecting fuel into an intake manifold, and a valve-opening-characteristic changing mechanism changing at least lift or opening duration of an intake valve. When the engine is in a predetermined operating region and the valve-opening-characteristic changing mechanism decreases the lift or the opening duration of the intake valve, the ratio of fuel injected by the in-cylinder injector is increased according to an amount of the decrease of the lift or the opening duration and accordingly a decrease in tumble ratio is compensated for by the injection flow.
Description
Technical field
The present invention relates to motor, and relate to particularly having and fuel sprayed into the in-cylinder injection device of cylinder and fuel sprayed into the tuned port injection device of intake manifold or suction port and have the motor of opening of valves characteristic changing mechanism.
Background technique
Generally speaking, known a kind of so-called pair of spraying motor has the tuned port injection device that fuel is sprayed into the in-cylinder injection device of cylinder and fuel is sprayed into intake manifold or suction port, and the running state according to motor is used these spargers in turn, with for example realize when motor during in the underrun zone stratified-charge combustion and when the homogeneous charge combustion of motor when high load running is regional, perhaps with the predetermined fuel injection ratio use simultaneously these spargers with raising such as fuel economy and output characteristics.
Further, also from the open known a kind of pair of spraying motor of No.11-351041 of Japan Patent for example, it belongs to the above-mentioned type and has pressurized machine such as turbosupercharger.
Change according to boost pressure from the fuel quantity of in-cylinder injection device injection with from the ratio between the fuel quantity of tuned port injection device injection at the open disclosed motor of No.11-351041 of Japan Patent with pressurized machine.Particularly, when the equilibrium mode following time of motor in high supercharge pressure region, the ratio of the fuel quantity that sprays from the tuned port injection device increases, and the fuel quantity ratio that sprays from the in-cylinder injection device reduces.Equal or when being higher than predetermined value when the front end temperature of in-cylinder injection device increases to, the ratio of the fuel quantity that sprays from the in-cylinder injection device is higher than when motor used ratio during at equilibrium mode.In this way, in the firing chamber, produce homogeneous air-fuel mixture, thereby improved combustion efficiency and prevented that sediments is accumulated in the in-cylinder injection device.
For lean-combustion engine with pressurized machine and opening of valves characteristic changing mechanism, in order to improve fuel economy and to reduce toxic emission (especially for example reducing NOx), consideration realizes output torque control in the rare zone corresponding to middle low speed and intermediate/low load region, and this can realize by for example following manner: according to the aperture control air inflow of closure; By at WOT and do not have control valve lift under the state of pumping loss or opening of valves endurance of suction valve and close timing and control air inflow; Control air inflow by the pressure that the supercharging of control pressurized machine produces.The suction air that the above-mentioned air inflow control that expectation is undertaken by control valve stroke of suction valve or opening of valves endurance in the WOT state will be rolled stream (that is, height roll stream than) greatly is provided in the firing chamber with the expansion lean flammability limit.
Yet, as from shown in Figure 3 roll stream than and the valve stroke of suction valve or the relation of opening of valves between the endurance as seen, roll stream than roughly reducing with the valve stroke of suction valve or the ratio that is reduced to of opening of valves endurance.Thereby, if the valve stroke of suction valve or opening of valves endurance reduce, can not realize fully that then the required stream that rolls of lean-burn compares.Then, owing to roll stream,, to be set at the control air fuel ratio denseer inevitably as shown in the relation between suction valve lift among Fig. 4 or opening of valves endurance and the required air fuel ratio than reducing.As a result, the problem that fuel economy deteriorates and toxic emission (especially NOx) worsen takes place.
Summary of the invention
The object of the invention provides a kind of motor that is used for addressing the above problem, can prevent owing to rolling stream than reducing to cause deterioration of lean burn, thus the raising fuel economy, and NOx can be reduced.Notice that Japanese publication No.11-351041 does not put down in writing such purpose.
According to one embodiment of present invention, motor comprises: the in-cylinder injection device that fuel is sprayed into cylinder; Fuel is sprayed into the tuned port injection device of intake manifold; Can change the lift of suction valve and open in the endurance at least one opening of valves characteristic changing mechanism; With the fuel injection control unit, when motor in the predetermined work zone, and when opening of valves characteristic changing mechanism reduced the lift of suction valve and opens in the endurance at least one, the fuel injection control unit was according to lift and open the ratio that the decrease of at least one in the endurance increases the fuel that is sprayed by the in-cylinder injection device.Herein, motor can be the lean-combustion engine that pressurized machine is installed.
Before boost pressure reached predetermined pressure, the fuel ratio that the in-cylinder injection device sprays can increase according to the size of boost pressure.
When boost pressure surpasses predetermined pressure, can fix the ratio of the fuel that sprays by the in-cylinder injection device.
Motor can also comprise that degree of overlapping changes the unit, when motor in the predetermined work zone, and when opening of valves characteristic changing mechanism reduced the lift of suction valve and opens in the endurance at least one, degree of overlapping changed the unit increases degree of overlapping by the On/Off timing that changes outlet valve amount.
Motor for the embodiment of the invention, no matter whether pressurized machine exists, when motor in predetermined work when zone, and when opening of valves characteristic changing mechanism reduced the lift of suction valve and opens in the endurance at least one, the fuel injection control unit was according to lift and open the ratio that the decrease of at least one in the endurance increases the fuel that is sprayed by the in-cylinder injection device.
Thereby the fuel quantity that sprays into cylinder is according to lift and open that the decrease of at least one increases in the endurance.Therefore the jet flow that increases be used for replenishing because the lift of suction valve and in the unlatching endurance stream that rolls that reduces to cause of at least one reduce, make fuel economy be improved, and NOx is reduced.Notice that motor of the present invention is not limited to lean-combustion engine.
, comprise under the situation of pressurized machine that before boost pressure reached predetermined pressure, the fuel ratio that the in-cylinder injection device sprays increased according to the size of boost pressure herein at motor.Thereby before reaching predetermined supercharge pressure, the fuel injection control unit increases the ratio of in-cylinder injection device burner oil according to the size of boost pressure.Thereby the fuel quantity that the in-cylinder injection device sprays before reaching predetermined supercharge pressure increases according to the size of boost pressure, and wherein said predetermined supercharge pressure can reach the required stream that rolls of lean-burn and compare.Thereby, when boost pressure is low, replenish and roll stream with the jet flow of increase, make lean-burn be maintained, fuel economy is improved, and NOx is reduced.
Further, when boost pressure surpasses predetermined pressure, the ratio of sparger burner oil in the stationary cylinder.Thereby, when boost pressure surpasses predetermined pressure, the fuel ratio that sparger sprays in the fuel injection control unit stationary cylinder.Thereby in the fuel quantity that fixedly sprays into cylinder, the boost pressure that surpasses predetermined pressure provides the enough stream that rolls, thereby finishes lean-burn with rarer air fuel ratio.
And, motor can also comprise that degree of overlapping changes the unit, when motor in the predetermined work zone, and when opening of valves characteristic changing mechanism reduced the lift of suction valve and opens in the endurance at least one, degree of overlapping changed mechanism and increases degree of overlapping by the On/Off timing that changes outlet valve.In this way, internal EGR can be used for further reducing NOx.In addition, can prevent because the change of the On/Off timing of suction valve and the influence of actual compression ratio.And the advantage that high compression ratio is provided is opened in the delay of outlet valve, thereby fuel economy can be further enhanced, and NOx can further be reduced.
Description of drawings
Fig. 1 shows the motor whole system structure of first and second embodiments according to the present invention.
Fig. 2 shows the block diagram of the electronic structure of the embodiment of the invention.
Fig. 3 is the figure that opening of valves endurance or valve stroke is shown and rolls the relation between the stream ratio.
Fig. 4 shows the figure of relation between opening of valves endurance or valve stroke and the required air fuel ratio (A/F).
Fig. 5 shows the figure that shines upon with exemplary engine working zone in embodiments of the present invention.
Fig. 6 is the figure that illustrates exemplary basic output torque control in the lean-burn zone of the lean-combustion engine that pressurized machine is installed in the embodiment of the invention.
Fig. 7 shows the flow chart according to the exemplary control processing process of first embodiment of the invention.
Fig. 8 is the figure that illustrates output torque control in the lean-burn zone of the lean-combustion engine that pressurized machine is installed in the present invention first and second embodiments.
Fig. 9 shows the flow chart according to the exemplary control processing process of second embodiment of the invention.
Figure 10 shows the valve timing diagram of second embodiment of the invention, wherein (A) and (C) corresponding to the respective valve timing in the zone (a) of Fig. 6 and zone (c), and (B) show at the On/Off timing advancement amount of control outlet valve EX with the valve timing under the situation of the amount that changes degree of overlapping.
Embodiment
Below, describe in detail with reference to the accompanying drawings and implement best mode of the present invention.
Fig. 1 summary illustrates a kind of system architecture, and this structure roughly illustrates the lean-combustion engine that pressurized machine is installed, and wherein this motor, and is applied in this system as pressurized machine according to the first and second aspects of the present invention with turbosupercharger.Motor 100 shown in Figure 1 (for example is configured to multicylinder engine, four cylinder engine, yet Fig. 1 only illustrates a cylinder), air-fuel mixture burns in each firing chamber 102 so that piston 103 to-and-fro motion obtain power from the bent axle (not shown) thus.Notice that motor can not have pressurized machine.
Each firing chamber 102 of motor 100 is communicated with suction port 104 and relief opening 105.Intake manifold 106 is connected to suction port 104.Gas exhaust manifold 107 is connected to relief opening 105.In the cylinder head of motor 100, be provided for the suction valve IN and the outlet valve EX that is used for On/Off relief opening 105 of On/Off suction port 104 at each firing chamber 102.Motor 100 also has spark plug 109, and its quantity is corresponding to the quantity of cylinder.Spark plug 109 is arranged in the cylinder head, in the face of the inboard of relevant firing chamber 102.
In motor 100 of the present invention, be provided with fuel is sprayed the tuned port injection device 110p that is fed to suction port 104 and directly fuel sprayed the in-cylinder injection device 110c that is fed to firing chamber 102.The in-cylinder injection device 110c quantity that motor 100 has is corresponding to the quantity of cylinder.Each in-cylinder injection device 110c can directly spray into relevant firing chamber 102 with the fuel such as gasoline, and is connected to the fuel tank (these parts do not illustrate) that holds such as the liquid fuel of gasoline by fuel-supply pipe.In addition, above-mentioned tuned port injection device 110p can spray into the fuel such as gasoline relevant suction port 104, and is connected to aforementioned fuel tank by the fuel-supply pipe (not shown).Each firing chamber 102 is provided with an in-cylinder injection device 110c at least.
Herein, in motor 100 of the present invention, suction valve IN is by suction valve mechanism 112 On/Off, suction valve mechanism 112 has variable lift mechanisms and vario valve timing mechanism, these mechanisms allow the opening of valves characteristic changing, and wherein the opening of valves characteristic comprises valve stroke or opening of valves endurance and the On/Off timing of suction valve IN.Outlet valve EX is by exhaust valve mechanism 114 On/Off, and exhaust valve mechanism 114 has the vario valve timing mechanism, and this vario valve timing mechanism allows to comprise at least the opening of valves characteristic changing of On/Off timing.Herein, suction valve mechanism 112 can be realized that this known opening of valves characteristics control equipment is configured to comprise for example disclosed centre (intermediary) driving mechanism in the open No.2001-263015 of Japan Patent by known opening of valves characteristics control equipment.In addition, exhaust valve mechanism 114 also is known.Thereby, below they are not described in detail, but provide simple description.
For valve stroke or opening of valves endurance and On/Off timing, change valve stroke or opening of valves endurance by variable lift mechanisms, and change the On/Off timing by the vario valve timing mechanism.
Suction valve IN is promoted by the middle driving mechanism and the rocking arm of intake cam via the opening of valves characteristics control equipment.The Control Shaft position of driving mechanism in the middle of the control, with the driving endurance of control intake cam, and control valve lift and from opening timing to the angular range of closing timing (that is the opening of valves endurance of suction valve IN).Further, intake cam is attached to admission cam shaft, and the phase variable of admission cam shaft is to change the On/Off timing of suction valve IN.Notice that as long as adopt the intake cam of lateral symmetry, valve stroke and the relation of opening of valves endurance are exactly to reduce with valve stroke the opening of valves endurance and reduce.Thereby, in the following description, use a factor in these factors in some cases.
Similarly, outlet valve EX is promoted via rocking arm by exhaust cam.Exhaust cam is attached to exhaust cam shaft, and the phase variable of exhaust cam shaft is to change the On/Off timing of outlet valve EX.Herein, by changing the On/Off timing that admission cam shaft and exhaust cam shaft phase place separately change above-mentioned suction valve IN and outlet valve EX.Thereby, change the On/Off timing according to these camshafts phase place separately with respect to the advance angle or the delay angle of reference position, and that maintaining valve is opened the endurance is constant.
The piston 103 of motor 100 is configured to so-called dark bowl type, and recess 103a is formed on its top.In motor 100, suck at air under the state of each firing chamber 102, can directly spray to the recess 103a of the piston 103 each firing chamber 102 from each in-cylinder injection device 110c such as the fuel of gasoline.Thereby, in motor 100, be different from rare air-fuel mixture on every side, produce dense air-fuel mixture layer near the spark plug 109.Thereby, can realize stable state combustion with quite rare air-fuel mixture.
Further, pressure stabilizer 124 is arranged on the gas-entered passageway 122, is connected to intake manifold 106.On the upstream side of pressure stabilizer 124, the closure 126 of regulating air inflow is set.Closure 126 is so-called electronic control throttles and is driven by throttle motor 128.The inlet of gas-entered passageway 122 is provided with air-strainer 132.In the downstream side of filter cleaner, be provided for detecting the Air flow meter 134 of air inflow.Be provided for cooling off the interstage cooler 130 that sucks air in the downstream side of compressor 120C.In addition, in the downstream side of the compressor 120C of gas-entered passageway 122 boost pressure (air inlet pressure) sensor 136 is set.
The downstream side of the turbine 120T of turbosupercharger 120 connects outlet pipe 140.On the passage of outlet pipe 140, the NOx catalyzer 144 that is provided for the three-way catalyst 142 of for example preheating and is used to handle the NOx under the lean-burn state.Utilize these catalyst-assemblies, be purified from the exhaust of each firing chamber 102.In the present embodiment, all-range air-fuel ratio sensor 146 is arranged on the downstream part of turbine 120T and then to detect the air fuel ratio of exhaust.In addition, on the downstream side of three-way catalyst 142, first lambda sensor 147 is set.And, on the downstream side of NOx catalyzer 144, second lambda sensor 148 is set.These all-range air-fuel ratio sensors 146 and first and second lambda sensors 147,148 that are used to detect discharge characteristic and state are generically and collectively referred to as exhaust sensor 149.
ECU 200 uses for example various mappings that are stored in the storage device, reference value, setting value, and checkout value based on information and for example sensor, the control engine operating parameter, fuel quantity that described engine operating parameter such as sparger 110c and 110p are sprayed and the fuel injection ratio between sparger 110c and the 110p, the ignition timing of spark plug 109, the degree that throttle motor 128 is opened closure, boost pressure by 121 generations of variable-nozzle work actuator, valve stroke or opening of valves endurance and the On/Off timing of the suction valve IN that suction valve mechanism 112 realizes, the On/Off timing of the outlet valve EX that realizes with exhaust valve mechanism 114.Especially, in the storage device of ECU200, the mapping in the running state zone of the expression motor of being stored 100 is as mapping shown in Figure 5, wherein the longitudinal axis is represented accelerator pedal travel (the required load that the accelerator pedal degree that is detected by accelerator pedal sensors 152 is represented), and transverse axis is represented engine speed (engine rotary speed that is detected by crankshaft angle sensor 151).The optimum value that the desirable characteristics of set basis motor 100 is determined by experiment at aforementioned control in mapping, and these mappings are stored in the storage device of ECU 200.
With reference to the mapping of the zone of the engine operating state among Fig. 5, the example when motor 100 of the present invention output torque control when lean-burn is regional is described herein.For this motor 100, for carrying out control respectively according to the combustion zone of chemically correct fuel (hereinafter being called " theory ") with according to the combustion zone of rare air fuel ratio, wherein, in combustion zone according to chemically correct fuel, accelerator pedal is to bigger degree, promptly this zone is high load and high-engine rpm or high engine speed zone, and this combustion zone is expressed as theoretical zone " 1 " in Fig. 5; Corresponding to all the other intermediate/low load region and middle low-speed region, the lean-burn zone is represented by the rare zone " 2 " among Fig. 5 according to the combustion zone of rare air fuel ratio.For rare zone " 2 ", basically fuel sprays producing homogeneous and rare air-fuel mixture firing chamber 102 from tuned port injection device 110p, and at following three regional (a) and (b) and (c) carries out aforementioned output torque control respectively: superlow loading and ultralow velocity band (a); Low-load and low-speed region (b); Shoulder load and intermediate speed zone (c).
For these zones, for example as shown in FIG. 6, the engine operating parameter of setting is (A) closure opening degree for example, hereinafter referred to as throttle opening, (B) valve stroke of suction valve IN or opening of valves endurance (representing with " IN opens the endurance " among Fig. 6), the advancement amount of (C) the On/Off timing of suction valve IN (in Fig. 6, being expressed as " IN VVT ") and (D) boost pressure.Particularly, for zone (a), according to the increase (that is, the increase of required output torque) of accelerator depression degree, throttle opening substantial linear ground increases with the control air inflow.At this moment, the valve stroke of suction valve IN or opening of valves endurance remain big lift or long unlatching endurance.Shown in the valve timing at Fig. 6 top, open timing and roughly be right after afterwards, and close timing afterwards at lower dead centre (BDC) and be delayed significantly at upper dead center (TDC).The advancement amount of On/Off timing diminishes, and promptly with respect to normal amount delay is arranged.Thereby, improved the fuel economy in the Atkinson circulation.Because when motor exhaust energy deficiency when this zone (a) moves, supercharger pressure is roughly zero.
For zone (b), when accelerator depression degree increases, closure roughly keeps standard-sized sheet, and the valve stroke of suction valve IN or opening of valves endurance increase along with accelerator depression degree and reduce, and On/Off timing (IN VVT) changes (shift to an earlier date), makes valve be right after upper dead center after unlatching and slightly be later than lower dead centre and closes to control air inflow.Further, for zone (c), increase along with accelerator depression degree and the state of a control of retaining zone (b) when increasing at the pressure of pressurized machine, with the control air inflow.
About motor 100 of the present invention, according to above-mentioned basic output torque control, by using the jet flow of in-cylinder injection device 110c effectively, prevented owing to the lift of suction valve IN or open the endurance reduce cause rolling stream than the reduction that reduces the lean flammability limit that is caused, make and improved fuel economy and reduced toxic emission, especially NOx.
Then, referring now to the control of the flow chart description first embodiment of the invention of Fig. 7 and Fig. 8.Fig. 7 shows the processing procedure that is used to control fuel injection ratio variation between tuned port injection device 110p and the in-cylinder injection device 110c by ECU 200 execution of present embodiment.Repeat this processing procedure in each predetermined set crank angle.
At first, at S701, ECU 200 is according to based on the accelerator depression degree (required load) of the checkout value that is included in accelerator pedal position sensor 152 in the sensor and crankshaft angle sensor 151 and the operation area that revolution Ne (rotating speed) determines motor.Further, in step S702 subsequently, according to the relevant detection value of closure enable possition sensor 154, Control Shaft position transducer 155, intake cam position transducer 156 and exhaust sensor 149, determine such as the lift of throttle opening, suction valve IN or open the advancement amount of On/Off timing of endurance, suction valve IN and the corresponding currency of the engine operating parameter of control air fuel ratio (hereinafter referred to as " control A/F ").Program then proceeds to S703 to judge that engine condition is now whether in tuned port injection device 110p and the in-cylinder injection device 110c zone with certain fuel injection ratio burner oil.This judgement is according to the lift of suction valve IN for example or opens the endurance and whether be equal to or less than the predetermined lift of judging usefulness or open the endurance and carry out.
When the judged result among the S703 is negative (="No"), promptly when valve stroke or opening of valves endurance greater than the predetermined lift of judging usefulness or when opening the endurance, program proceeds to S704.Then, according to above-mentioned basic controlling, tuned port injection device 110p sprays 100% fuel.In other words, in-cylinder injection device 110c stops burner oil,, send the instruction with in-cylinder injection ratio α=0% burner oil, and this processing procedure finishes that is.Notice that carry out fuel injection control by another process, this control comprises corresponding to the amount of fuel injected of running state and fuel injection timing.
When the judged result in S703 is when affirming (="Yes"), promptly, during the endurance, handle proceeding to S705 less than the predetermined valve lift of judging usefulness or opening of valves when valve stroke or opening of valves endurance to determine the fuel injection ratio alpha (%) of in-cylinder injection device.Particularly, according to lift or the unlatching endurance of suction valve IN, determine cylinder fuel injection ratio α (seeing that (B) IN in Fig. 8 zone (b) opens endurance, (E) fuel injection ratio).Thereby according to reducing of lift or unlatching endurance, cylinder fuel injection ratio α increases, thereby the fuel quantity that the in-cylinder injection device sprays increases.Thereby the jet flow of increase has compensated owing to the lift of suction valve or has opened the stream that rolls that the endurance reduces to cause and reduced.Thereby it is higher that lean flammability limit keeps, and will not control A/F and be set at dense.The total amount of supposing the burner oil that engine operating state is required is 100%, and the fuel ratio that the in-cylinder injection device sprays is α, the fuel ratio that tuned port injection device 110p sprays be (100-α) (%).Thereby when having determined the fuel ratio that the in-cylinder injection device sprays, the fuel ratio that the tuned port injection device sprays is also unique to be determined.Thereby, in the following description, the fuel ratio α that only uses the in-cylinder injection device to spray.
Subsequently, in the present embodiment, in S705, according to the lift of suction valve IN or open after the fuel ratio α that the endurance determines that the in-cylinder injection device sprays, in S706 subsequently, determine actual supercharge pressure Dp as the boost pressure currency according to the checkout value of pressurized sensor 136.Then in S707, whether judge this actual supercharge pressure Dp greater than setting boost pressure Ds, wherein boost pressure Ds is predetermined, and according to this boost pressure Ds can obtain lean-burn required roll stream than (seeing the zone (c) among Fig. 8).When being judged as actual supercharge pressure Dp when preestablishing boost pressure Ds, promptly when judged result was sure (="Yes"), program proceeded to S708.Then, according to the size of this actual supercharge pressure Dp, the fuel ratio α that the in-cylinder injection device sprays increases.In other words, actual supercharge pressure Dp reach preestablish boost pressure Ds before, the fuel ratio α that the in-cylinder injection device sprays increases according to the size of this actual supercharge pressure Dp.In this way, by increasing the fuel ratio α that the in-cylinder injection device sprays, and thereby increase fuel quantity that the in-cylinder injection device sprays rolling the deficiency of stream by the jet flow compensation that increases, thereby solved the problem of boost pressure deficiency.As a result, it is higher that lean flammability limit keeps, and will not control A/F and be set at dense.
When being judged as actual supercharge pressure Dp at S707, promptly when judged result is negative (="No"), this means that this boost pressure allows to roll stream than the supply inhaled air with enough greater than predefined boost pressure Ds.Then, program proceeds to S709, and does not pass through S708.At S709, as shown in Figure 8, the zone (c) actual supercharge pressure Dp reach preestablish boost pressure Ds before, increase the fuel ratio α that the in-cylinder injection device sprays control (actual supercharge pressure Dp reach preestablish boost pressure Ds after, the fuel ratio that in-cylinder injection device 110c sprays is fixed), and roll the stream ratio when actual supercharge pressure Dp surpasses the height that boost pressure self is realized when preestablishing boost pressure Ds, they provide rarer air fuel ratio.Thereby control A/F is corrected near rare.Thereby lean-burn is kept, and fuel economy is improved, and NOx has further reduced.
Refer again to the flow chart of Fig. 8 and Fig. 9, describe the control in the second embodiment of the invention.Fig. 9 is the processing procedure that fuel injection ratio changes and degree of overlapping changes between that the ECU 200 by embodiment carries out, control tuned port injection device 110p and the in-cylinder injection device 110c.This processing procedure also repeats in each predetermined setting crank shaft angle.
In a second embodiment, especially for the zone (b) among above-mentioned first embodiment, also the advancement amount of the On/Off of outlet valve EC (below be also referred to as EX VVT advancement amount) is carried out control shown in Figure 10 and change, further improved fuel economy thus and further reduced NOx with control degree of overlapping (being also referred to as the O/L amount).Herein, (A) among Figure 10 and (C) correspond respectively among above-mentioned Fig. 6 zone (a) and the zone (c) the valve timing.(B) among Figure 10 is illustrated in the On/Off timing advancement amount of control outlet valve EX with the valve timing under the situation that changes degree of overlapping.
As mentioned above,, the lift of suction valve IN, the advancement amount of opening endurance and On/Off timing (INVVT) are controlled with the control air inflow, controlled output torque thus for zone (b).Herein, suction valve IN closes timing not only to the control air inflow, and to the control actual compression ratio with to roll stream be important Control Parameter than also.Can control the amount of the internal EGR that is used for further reducing NOx by the amount that increases the valve overlap degree.In order to increase the degree of overlapping of valve, can shift to an earlier date the On/Off timing (IN VVT) of suction valve IN, On/Off timing (EX VVT) that also can the delayed exhaust valve.Yet, if the On/Off timing (IN VVT) of suction valve in advance is to increase degree of overlapping, then the increase of actual compression ratio has surpassed required compression ratio in the aforementioned Atkinson circulation, this has caused can not carrying out lean combustion owing to following influence, and described influence postpones or be used for the ignition timing delay control that internal EGR is proofreaied and correct from the ignition timing for fear of pinking.On the contrary, the On/Off timing of delayed exhaust valve EX (EX VVT) is less to the actual compression ratio influence to increase degree of overlapping, and can only postpone at the ignition timing of internal EGR calibration setup, and this is favourable to lean-burn.And the effect that high compression ratio is provided is opened in the delay of outlet valve EX, thereby fuel economy is further enhanced and NOx is further reduced.
Then, in a second embodiment, at first in S901, the accelerator depression degree and the revolution Ne that detect according to the checkout value from accelerator pedal position sensor 152 and crankshaft angle sensor 151 determine engine working area.Further, in S902 subsequently, according to the respective detection value of closure enable possition sensor 154, Control Shaft position transducer 155, intake cam position transducer 156 and exhaust sensor 149, the corresponding currency of these running parameters is defined as the lift of throttle opening, suction valve IN or opens On/Off timing advancement amount and the control A/F of endurance, suction valve IN.Then, processing proceeds to S903, wherein according to about the lift of suction valve IN or open the endurance and whether be equal to or less than the predetermined lift of judging usefulness or the judgement of opening the endurance, come the judgment task zone whether in tuned port injection device 110p and in-cylinder injection device 110c fuel injection region with certain fuel injection ratio burner oil.
Described as mentioned in conjunction with basic controlling, when the judged result among the S903 is negative (="No"), promptly when lift or open the endurance greater than the predetermined lift of judging usefulness or when opening the endurance, processing proceeds to S904, sends the instruction that accounts for 100% fuel injection ratio burner oil with tuned port injection device 110p.In other words, send of the instruction of in-cylinder injection device with 0% fuel injection ratio (being α=0%) burner oil.Then, at S905, determine allowing degree of overlapping (O/L) is the On/Off timing advancement amount of zero outlet valve EX, and finishes this processing process.
On the contrary, if the judgement in S903 be sure (="Yes") and thereby lift or open the endurance less than the predetermined lift of judging usefulness or open the endurance, then program proceeds to S906 with according to the lift of suction valve IN or open the endurance and determine the fuel injection ratio alpha (%) (seeing the zone (b) among Fig. 8) of in-cylinder injection device.Then, in the present embodiment, in S907, in order to obtain to determine On/Off timing (EX VVT) advancement amount of outlet valve EX according to the lift of suction valve IN or the amount of the degree of overlapping (O/L) of unlatching endurance.Ignition timing is corrected to for the timing that is fit to the corresponding internal EGR amount of the amount of this degree of overlapping (O/L).Further, in S907, the fuel injection timing of in-cylinder injection device 110c is set the timing of closing that is later than outlet valve EX for.Thereby, after outlet valve EX closes, improved height and rolled the stream ratio from the jet flow of in-cylinder injection device 110c.
Further, in following S908,, determine actual supercharge pressure Dp as the currency of boost pressure according to the checkout value of pressurized sensor 136.In S909, judge this actual supercharge pressure Dp whether greater than setting boost pressure Ds, wherein this setting boost pressure Ds is predetermined, and by this setting boost pressure can obtain lean-burn required roll stream than (seeing the zone (c) among Fig. 8).When being judged as actual supercharge pressure Dp when preestablishing boost pressure Ds less than this, be certainly when (="Yes") promptly when judging, program proceeds to S910, increases the fuel injection ratio alpha of in-cylinder injection device 110c according to the size of actual supercharge pressure Dp.This process finishes subsequently.In other words, actual supercharge pressure Dp reach preestablish boost pressure Ds before, the fuel injection ratio alpha of in-cylinder injection device 110c increases according to the size of actual supercharge pressure Dp.In this way, the fuel injection ratio alpha of in-cylinder injection device increases, and the fuel quantity that the in-cylinder injection device sprays also thereby increase has solved the problem of boost pressure deficiency.Therefore the jet flow that increases has compensated the deficiency of rolling stream.As a result, it is higher that lean flammability limit keeps, and will not control A/F and be set at dense.
On the contrary, when being judged as actual supercharge pressure Dp when preestablishing boost pressure Ds in S909, promptly when judging whether fixed (="No"), boost pressure allows to roll stream than the supply inhaled air with enough.Then, program proceeds to S911, and without above-mentioned S910.At S911, as shown in Figure 8, in zone (c), the fuel injection ratio alpha of sparger makes its increase reach up to actual supercharge pressure Dp and preestablishes boost pressure Ds (after actual supercharge pressure Dp reaches predefined boost pressure Ds in the control cylinder, the fuel injection ratio alpha of in-cylinder injection device 110c is fixed), and, realize that by boost pressure self height rolls the stream ratio, thereby air fuel ratio can be further thinning when actual supercharge pressure Dp surpasses when preestablishing boost pressure Ds.Thereby, for the purpose of the amount that reduces above-mentioned degree of overlapping (O/L), proofread and correct the advancement amount of the On/Off timing (EX VVT) of outlet valve EX, make that ignition timing is suitable timing for the internal EGR amount corresponding with the amount of this degree of overlapping (O/L).Further, also according to the correction of closing timing, proofread and correct the fuel injection timing of in-cylinder injection device 110c to outlet valve EX.Then, in S912, as in the above-described embodiments, will control A/F and further proofread and correct rarelyr.In this way, rarer burning is maintained, and fuel economy obtains increasing, and NOx further is reduced.
Although the present invention is described in detail and illustrates, can be expressly understood that this description is a n-lustrative and exemplary, not restrictive.Scope of the present invention is only by appended claim restriction.
Claims (4)
1. motor comprises:
The in-cylinder injection device, it sprays into cylinder with fuel;
The tuned port injection device, it sprays into intake manifold with fuel;
Opening of valves characteristic changing mechanism, it changes the lift of suction valve and opens in the endurance at least one; With
The fuel injection control unit, when described motor in the predetermined work zone, and described opening of valves characteristic changing mechanism reduces the described lift of described suction valve and in the described unlatching endurance at least one the time, described fuel injection control unit according to described lift and in the described unlatching endurance the described amount that reduces of at least one increase the ratio of the fuel that sprays by described in-cylinder injection device.
2. motor according to claim 1 also comprises pressurized machine, wherein,
Before boost pressure reached predetermined pressure, described fuel injection control unit increased the described ratio of the fuel that is sprayed by described in-cylinder injection device according to the size of described boost pressure.
3. motor according to claim 2, wherein,
When described boost pressure surpassed described predetermined pressure, the described ratio of the fuel that is sprayed by described in-cylinder injection device was fixed in described fuel injection control unit.
4. motor according to claim 1, comprise that also degree of overlapping changes the unit, when described motor in the predetermined work zone, and when described opening of valves characteristic changing mechanism reduced the described lift of described suction valve and in the described unlatching endurance at least one, described degree of overlapping changed the unit increases degree of overlapping by the On/Off timing that changes outlet valve amount.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP069470/2005 | 2005-03-11 | ||
| JP2005069470 | 2005-03-11 | ||
| JP316541/2005 | 2005-10-31 |
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| CN101091049A CN101091049A (en) | 2007-12-19 |
| CN100507249C true CN100507249C (en) | 2009-07-01 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US9371796B2 (en) * | 2011-01-07 | 2016-06-21 | Nissan Motor Co., Ltd. | Combustion control device and method for diesel engine |
| JP6090573B2 (en) * | 2013-06-27 | 2017-03-08 | 三菱自動車工業株式会社 | Engine control device |
| KR101542979B1 (en) * | 2013-12-26 | 2015-08-10 | 현대자동차 주식회사 | Engine Control Apparatus having Turbocharger and Method Thereof |
| DE102017201866A1 (en) * | 2017-02-07 | 2018-08-09 | Robert Bosch Gmbh | Method and arrangement for controlling a mechanism for adjusting a valve lift curve |
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