CN1364216A - Method for operating multi-cylinder internal combustion engine - Google Patents
Method for operating multi-cylinder internal combustion engine Download PDFInfo
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- CN1364216A CN1364216A CN01800487A CN01800487A CN1364216A CN 1364216 A CN1364216 A CN 1364216A CN 01800487 A CN01800487 A CN 01800487A CN 01800487 A CN01800487 A CN 01800487A CN 1364216 A CN1364216 A CN 1364216A
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 139
- 238000000034 method Methods 0.000 title claims abstract description 70
- 238000002347 injection Methods 0.000 claims abstract description 101
- 239000007924 injection Substances 0.000 claims abstract description 101
- 239000000446 fuel Substances 0.000 claims abstract description 56
- 230000006835 compression Effects 0.000 claims abstract description 8
- 238000007906 compression Methods 0.000 claims abstract description 8
- 238000010304 firing Methods 0.000 claims description 39
- 239000007921 spray Substances 0.000 claims description 35
- 230000001105 regulatory effect Effects 0.000 claims description 27
- 238000005507 spraying Methods 0.000 claims description 21
- 230000001915 proofreading effect Effects 0.000 claims description 7
- 230000000694 effects Effects 0.000 abstract description 2
- 230000006698 induction Effects 0.000 abstract 1
- 239000000203 mixture Substances 0.000 description 32
- 230000003068 static effect Effects 0.000 description 8
- 102000043859 Dynamin Human genes 0.000 description 3
- 108700021058 Dynamin Proteins 0.000 description 3
- 238000009841 combustion method Methods 0.000 description 3
- YWXYYJSYQOXTPL-SLPGGIOYSA-N isosorbide mononitrate Chemical compound [O-][N+](=O)O[C@@H]1CO[C@@H]2[C@@H](O)CO[C@@H]21 YWXYYJSYQOXTPL-SLPGGIOYSA-N 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 238000001914 filtration Methods 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/008—Controlling each cylinder individually
- F02D41/0085—Balancing of cylinder outputs, e.g. speed, torque or air-fuel ratio
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
- F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
- F02D41/3023—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the stratified charge spark-ignited mode
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
The invention relates to a method for operating a multi-cylinder internal combustion engine (1), especially a direct injection internal combustion engine. According to the invention, fuel is injected into a combustion chamber (4) via a high-pressure injection valve (9) in a first operational mode during a compression phase and in a second operational mode during an induction phase. In addition, the engine is switched over between the operational modes, and the torques of the individual cylinders of the internal combustion engine are equated, whereby the cylinder equalization is effected in the first operational mode by means of a controller. In order to be able to effect the cylinder equalization in a simple, quick and effective manner and while using few calculations, the invention provides that the injection correction factors (r_ik) for correcting cylinder-specific torque errors (M_f_ik) in a number of operating points (k) are determined and stored, statistical flow rate errors (q_stat) and dynamic flow rate errors (q_dyn) of the high-pressure injection valve (9) are determined, and the quantity of fuel to be injected into the combustion chamber (4) is corrected for according to the determined flow rate errors (q_stat, q_dyn) of the high-pressure injection valve (9).
Description
Prior art
The present invention relates to a kind of method of moving multi-cylinder engine, particularly a kind of direct-injection internal combustion engine of described multi-cylinder engine, wherein, fuel under first method of operation in a compression stage and in a charging stage, spraying in this firing chamber under second method of operation through a high-pressure injection valve, wherein, between these methods of operation, change, and consistent the adjusting carried out in the torque of each cylinder of internal-combustion engine, under first method of operation, the consistent adjusting by means of a regulator of cylinder carried out.In addition, the invention still further relates to a kind of internal-combustion engine, particularly a kind of direct-injection internal combustion engine, it has a firing chamber, fuel can under first method of operation in a compression stage and in a charging stage, spraying into this firing chamber under second method of operation through a high-pressure injection valve, this internal-combustion engine has a control gear that is used to carry out method of operation conversion, also has one and be used for carrying out at least the consistent regulator of regulating of cylinder under first method of operation.At last, the invention still further relates to a kind of control gear, this device is used for described internal-combustion engine.
This system that direct fuel injection is gone in the combustion chambers of internal combustion engines generally is known.Be divided into first method of operation and second method of operation at this.First method of operation is a kind of so-called stratified combustion mode, and second method of operation is a kind of so-called homogeneous combustion mode.Stratified mixture combustion is specially adapted to little load, and homogeneous combustion is applicable to the big load of internal-combustion engine.
When stratified mixture combustion, fuel sprays into the firing chamber under the compression stage of internal-combustion engine mode is that at time of ignition, a fuel cloud is near next-door neighbour's spark plug.This injection can realize in a different manner.Therefore, the fuel cloud that sprays into is positioned near the spark plug when spraying into and after firm the spraying into, and by this plug ignition.Also can utilize a kind of charge movement that the fuel cloud that sprays into is carried to spark plug, and then light.In these two kinds of combustion methods, all there is not uniform fuel distribution, but stratified charge.
The advantage of stratified mixture combustion is and can realizes less engine load with very little fuel quantity.But, bigger load can not be realized by stratified mixture combustion.
In being applicable to the homogeneous combustion of this bigger load, fuel sprays in the stage at air-intake of combustion engine, therefore meeting eddy generation, thus be easy in the firing chamber, realize fuel distribution.Thus, the homogeneous combustion operation method is roughly corresponding with the operation method that a kind of fuel of internal-combustion engine sprays in the suction tude in due form.As requested, also can under less load, adopt homogeneous combustion.
In stratified mixture combustion, air throttle is opened in leading to the suction tude of firing chamber greatly, and burning is basically only by waiting that the fuel quantity that is sprayed into controls and/or regulate.When homogeneous combustion, air throttle is opened or closed according to required torque, and the fuel quantity of injection is controlled and/or regulated according to amount of air drawn.
In addition, in these two kinds of methods of operation, that is, in stratified mixture combustion and homogeneous combustion, the fuel quantity that sprays into also will be controlled and/or be adjusted to fuel saving according to some Operational Limitss, reduce the optimum value of exhaust or the like.This control and/or the control gear of regulating by internal-combustion engine carry out, and are different in these two kinds of methods of operation.
In direct-injection internal combustion engine, fuel is sprayed in the firing chamber of internal-combustion engine by a high-pressure injection valve usually.Since machining tolerance and wearing and tearing, the cracking pressure difference of high-pressure injection valve.Because on the high-pressure injection valve, provide identical jet pressure by a shared high pressure accumulator, so, the fuel quantity difference that in each firing chamber, sprays into, this can cause the operation of internal-combustion engine not steady, cause toxic emission to increase, also can cause the increase of fuel consumption.
In order to compensate by the high-pressure injection valve that is used for the fuel injection owing to the change to through-flow characteristic of processing and wearing and tearing difference causes, DE19828279 discloses a kind of consistent mean of calculating of cylinder that is used for multi-cylinder engine.At this, the torque of each cylinder of internal-combustion engine comes consistent the adjusting by the fuel quantity that change sprays in the firing chamber.Each cylinder torque output as far as possible uniformly produces positive influences to calmness running, discharging and the consumption of internal-combustion engine.
Suggestion records this pre-control characteristic curve for pre-control characteristic curve of each cylinder configuration during internal combustion engine operation in DE19828279A1.When stratified mixture combustion, undertaken by a regulator that cylinder is consistent to be regulated, control characteristic curve in advance and be used to unload the consistent regulator of regulating of cylinder and improve dynamics.When homogeneous combustion, adopt an injection correction factor that provides by pre-control characteristic curve to proofread and correct discharge time.The output parameter of regulator is constant in time when homogeneous combustion, that is, regulator is invalid, and cylinder is consistent regulates controlled carrying out.
Yet in DE19828279A1, consistent only adjusting of the controlled cylinder during homogeneous combustion carried out at the quiescent flow error, and in other words, it only is used in big discharge time.The dynamic flow error is not considered.The torque error of (, when internal-combustion engine must produce big torque and load operation) each cylinder in the time of can proofreading and correct long-time injection by this method.And under the situation of short discharge time when idling for internal combustion engine (for example), to not compensation sufficiently of torque error, this causes the not steady and uneven running of internal-combustion engine.
Task of the present invention is to improve that cylinder is consistent to be regulated, make it not only at long discharge time but also under the situation of short discharge time, not only under first method of operation of internal-combustion engine but also can proofread and correct the torque error of each cylinder under second method of operation at internal-combustion engine.
In order to finish task of the present invention, described at the first bruss prior art the present invention advises based on this specification :-on a plurality of operating points, measure and proofread and correct the required injection correction factor of each cylinder torque error,
And it is stored ,-spray the quiescent flow sum of errors dynamic flow that correction factors are obtained the high-pressure injection valve by these
The amount error ,-combustion of waiting to spray into the firing chamber proofreaied and correct according to the flow error of the high-pressure injection valve of being obtained
The material amount.
Advantage of the present invention
At first, the present invention measures the injection correction factor of each cylinder of internal-combustion engine on a plurality of operating points.In addition, operating point becomes the branch definition by the air-fuel mixture amount of cylinder air inlet with mixed gas.After measuring the injection correction factor, they are stored.
The main cause of the torque error of each cylinder is the error of high-pressure injection valve, especially flow error.Therefore, flow error reflects the torque error of each cylinder more exactly.The present invention has utilized this point, is obtained the flow error of high-pressure injection valve under the stratified mixture combustion method of operation of the routine of internal-combustion engine and/or the homogeneous combustion method of operation by stored injection correction factor.Then, treat the fuel quantity that sprays into the firing chamber according to the flow error of the high-pressure injection valve of being obtained and proofread and correct, thus the torque of mating each cylinder.
Static error is defined as the static flow error that produces under the situation that the high-pressure injection valve is opened fully.The error that dynamin error is defined as the static flow error that produces and dynamically produces in high-pressure injection opening of valves and pass closed procedure.Therefore particularly, the dynamic flow error of high-pressure injection valve is for the fuel quantity in the firing chamber that sprays into a cylinder through the high-pressure injection valve with produce decisive influence by the torque of this cylinder output.
Owing to from stored injection correction factor, not only obtain the quiescent flow error of the high-pressure injection valve of internal-combustion engine according to the present invention, and obtain its dynamic flow error, and it is considered in the correction of waiting to spray into the fuel quantity in the firing chamber, so, each operating point at internal-combustion engine, can guarantee that not only when stratified mixture combustion, and when homogeneous combustion internal-combustion engine steadily and equably moves.
Of the present invention one favourable form of implementation suggestion is only tried to achieve the injection correction factor under first method of operation (that is stratified mixture combustion).When stratified mixture combustion, the torque error of each cylinder is regulated by means of being used for the consistent regulator of regulating of cylinder fully.A fuel quantity and ratio have been provided from the torque of internal-combustion engine output.The regulating action of regulator is corresponding to spraying correction factor.Under the situation of stratified mixture combustion, can measure the injection correction factor with very high precision, and eliminate the torque difference of each cylinder of internal-combustion engine fully.
Another alternative embodiment suggestion of the present invention, the injection correction factor of each cylinder is not only tried to achieve under first method of operation, and tries to achieve under second method of operation (that is homogeneous combustion).Different is, carries out when stratified mixture combustion that cylinder is consistent to be regulated, and does not carry out when homogeneous combustion that cylinder is consistent to be regulated, and therefore, does not guarantee the ratio between fuel and the torque.Yet, can adopt a kind of method of adaptation to reduce torque error significantly, preferably this error is reduced to zero.Obtain required for this reason injection correction factor.Adaptive method by adopting this to proofread and correct the cylinder of two maximum deviations can reduce the torque difference, thereby and the fuel difference is reduced.
Though the precision of the injection correction factor that the injection correction factor score grate firing of obtaining when homogeneous combustion was obtained when burning is low, because the burning of λ=1, particularly aging along with internal combustion engine component, its reliability is higher.
Yet,, also can when homogeneous combustion, regulate torque error by means of regulator if adopt the independent λ value of a cylinder.Differently during with stratified mixture combustion be fuel quantity and be non-linear from the relation between the torque of internal-combustion engine output.
A preferred form of implementation suggestion of the present invention, obtain common static state and dynamic flow error according to the injection correction factor of in first method of operation, measuring and according to the injection correction factor of in second method of operation, measuring, and they are waited to spray into the basis of the fuel quantity in the firing chamber as correction.Common flow error can be obtained according to spraying correction factor by operation program arbitrarily.For example, carry out to spraying correction factor that what is called is averaged, weighting or filtering (Filterung).
In order to obtain common flow error, can handle arbitrarily spraying correction factor.For example, can from stratified mixture combustion and the quiescent flow error of in homogeneous combustion, obtaining obtain a common quiescent flow error.Equally can from stratified mixture combustion and the dynamic flow error of in homogeneous combustion, obtaining obtain a common dynamic flow error.A kind of mode of replacement is, not only considers static when asking common static state or dynamic flow error but also considers dynamic flow error.
The another kind of feasible method that constitutes common flow error is, if the flow error of obtaining in stratified mixture combustion or homogeneous combustion is consistent in first is similar to, then the static state that will obtain in stratified mixture combustion and dynamic flow error are as common flow error, if the flow error of obtaining in stratified mixture combustion or homogeneous combustion is inconsistent, then the static state that will obtain in homogeneous combustion and dynamic flow error are as common flow error.Though this causes the torque error of each cylinder of internal-combustion engine fully not to be corrected, for this, it is more reliable than the flow error of obtaining in stratified mixture combustion, is preferred therefore.
Another preferred form of implementation suggestion of the present invention will be used for the required regulating action of the torque error consistent regulator of regulating of cylinder, that be each cylinder of correction and be considered as the injection correction factor.Spray the evaluation of correction factor and storage by a kind of in DE19828279A1 disclosed method carry out.In DE19828279A1, this has been done more detailed description.
According to a preferred form of implementation of the present invention, proofread and correct the fuel quantity that sprays in the firing chamber by the discharge time that changes the high-pressure injection valve.To pass through the fuel quantity that corresponding high-pressure injection valve is sprayed into by means of two corrected value-static state of obtaining for each cylinder of internal-combustion engine and dynamic flow error-correction then.Change each discharge time by means of the quiescent flow error in the mode of multiplication,, change each discharge time in the mode of addition by means of the dynamic flow error.
Advantageously, the consistent injection correction factor of obtaining of regulating of cylinder that is used for is stored into a characterisitic family.This characterisitic family is preferably deposited in the control gear of internal-combustion engine, and it is with the revolution of internal-combustion engine on the one hand, is relevant with the torque of internal-combustion engine output on the other hand.During internal combustion engine operation, control gear can take out the injection correction factor that is deposited in, obtains the corresponding flow error of high-pressure injection valve, and correspondingly proofreaies and correct the fuel quantity of waiting to spray in the firing chamber.
According to of the present invention one preferred form of implementation, under the situation of long discharge time, will be used as the quiescent flow error with the corresponding injection correction factor of operating point.Spraying correction factor provides a value reliably for the quiescent flow error under the long situation of discharge time, (that is) influence, the error that causes owing to the opening and closing process is more little, and discharge time is just long more because the dynamin error of high-pressure injection valve.
According to another preferred form of implementation of the present invention, under the short situation of discharge time, will spray correction factor accordingly as the dynamic flow error with operating point.Discharge time is short more, that is, the time that the high-pressure injection valve opens or closes is short more, and dynamin error is big more to the influence of the flow error of high-pressure injection valve.
The invention enables the machining tolerance of high-pressure injection valve to strengthen.Because measure the performance of each single high-pressure injection valve in the method at each independent cylinder, and take in when regulating in that cylinder is consistent.In addition, according to the present invention, also to consider when regulating the dynamic flow error of high-pressure injection valve therefore, particularly under the short situation of discharge time, can realize the correction fully of each cylinder torque error in that cylinder is consistent.
Especially meaningfully, realize method of the present invention with the form of a control unit, this control unit is set for a control gear of internal-combustion engine, particularly direct-injection internal combustion engine.Store a program on this control unit, this program can be at a computing device of control gear, particularly move on a microprocessor, and is applicable to the method for the present invention of carrying out.In this case, the present invention realizes by a program that is stored on this control unit, therefore, describes the control unit that this has the program that is suitable for implementing the method in the mode identical with described method in the present invention.As control unit, can adopt particularly an electric storage medium, for example a ROM (read-only memory) (ROM), perhaps a flash memory.
As the another kind of solution that realizes the object of the invention, start the internal-combustion engine of described prior art based on this specification, the present invention's suggestion, control gear-on a plurality of operating points, obtain and the store required injection school of torque error of proofreading and correct each cylinder
Positive divisor ,-obtain a quiescent flow sum of errors one dynamic flow of high-pressure injection valve by spraying correction factor
The amount error ,-fuel quantity that sprays into the firing chamber proofreaied and correct according to the flow error of the high-pressure injection valve of obtaining.
At last,, start the control gear of the internal-combustion engine of described prior art, suggestion, this control gear-on a plurality of operating points, obtain and the store required injection school of torque error of proofreading and correct each cylinder based on this specification as a kind of scheme that realizes the object of the invention
Positive divisor ,-obtain a quiescent flow sum of errors one dynamic flow of high-pressure injection valve by spraying correction factor
The amount error ,-fuel that sprays into the firing chamber proofreaied and correct according to the flow error of the high-pressure injection valve of being obtained
Amount.
Preferably the consistent regulating action of regulating the regulator of usefulness of cylinder is considered as the injection correction factor.
Description of drawings
Below in conjunction with accompanying drawing the preferred embodiments of the present invention are described in detail.Wherein,
Fig. 1 is the sketch of a preferred implementing form of internal-combustion engine of the present invention;
Fig. 2 is another sketch of internal-combustion engine shown in Figure 1;
Fig. 3 is the control gear of a preferred implementing form of the present invention.
Figure 1 illustrates a direct spray type car combustion engine 1, piston 2 wherein can to-and-fro motion in a cylinder 3.Internal-combustion engine 1 has z cylinder 3.These cylinders 3 have a firing chamber 4 respectively, and each firing chamber is surrounded by a piston 2, a suction valve 5 and an outlet valve 6.A suction valve 5 and a suction tude 7 link, and an outlet valve 6 and an outlet pipe 8 link.Near suction valve 5 and outlet valve 6, a high-pressure injection valve 9 and a spark plug 10 extend in the firing chamber 4.Fuel can spray into firing chamber 4 by this high-pressure injection valve 9.Spark plug 10 can be lighted fuel in firing chamber 4.Under first method of operation (stratified mixture combustion), fuel is sprayed into firing chamber 4 in a compression stage.Under second method of operation (homogeneous combustion), fuel is sprayed into firing chamber 4 in a charging stage.Can the conversion operation mode at internal-combustion engine 1 run duration.
By the burning of fuel in firing chamber 4, piston 2 can be reciprocating in firing chamber 4.This to-and-fro motion is delivered on the bent axle 11 (Fig. 2), torque M _ ik of effect on this bent axle.
A sensor wheel 12 is set on the bent axle 11, measures the corner of this sensor wheel by means of a sensor 13.Another sensor 14 is set on cylinder 3, and this sensor is measured for example upper dead center of piston 2, as the border of a quartastroke engine two work cycle.Sensor 13 and 14 signal are transported to a control gear 15, and this control gear produces an ejection pulse signal t_ik on the operating point k of internal-combustion engine 1, be used to control a cylinder i (i=1 ... z) high-pressure injection valve 9.Operating point k is by the definition that becomes to assign to of the air-fuel mixture amount of cylinder charging and mixed gas.
Fig. 3 illustrates the part of control gear 15.In control gear 15, with disclosed method in DE19828279A1, the suitable regulator R_i (i=1 of each the cylinder i by being used for internal-combustion engine 1 ... z) or the PI-regulator produce to spray correction factor r_ik.Among the DE19828279A1 this has been done clearly to describe.The signal of the sensor 13,14 of cylinder i is fed to regulator R_i.
Spraying correction factor r_ik is the required factor of torque error M_f_ik that is used to proofread and correct internal-combustion engine 1 each cylinder i.Injection correction factor r_ik that is obtained and operating point are stored in the characterisitic family k_i (i=1 of independent cylinder relatively ... z) in.In order to determine operating point k, the revolution n_k and the torque M _ k of internal-combustion engine 1 flowed to characterisitic family k_i.
Not only when stratified mixture combustion, and when homogeneous combustion, also measure the injection correction factor r_ik of each cylinder i.When stratified mixture combustion, regulated the torque error M_f_ik of each cylinder i fully by means of a regulator R_i.Provided the ratio of the torque M _ k of fuel quantity and internal-combustion engine 1 output.The regulating action of regulator R_i is corresponding with injection correction factor r_ik.In stratified mixture combustion, can obtain with very high precision and spray correction factor r_ik, and can eliminate the torque differences M_f_ik of each cylinder i of internal-combustion engine 1 fully.
Different with stratified mixture combustion is, does not regulate in homogeneous combustion, so do not guarantee ratio between fuel and the torque M _ k.But can adopt the method for an adaptation to reduce torque error M_f_ik significantly, preferably be decreased to zero.Obtain required for this reason injection correction factor.Though the precision of the injection correction factor r_ik that obtains in homogeneous combustion is lower, owing to be the burning of λ=1, so have higher reliability.
Yet,, when λ equals about 0.85 homogeneous combustion, also can adjust torque error M_f_ik by means of regulator R_I if adopt the λ value of a single cylinder.Different with stratified mixture combustion is, fuel and be non-linear by the relation between the torque M _ k of internal-combustion engine 1 output.
Then, in functional block 17, obtain quiescent flow error q_stat and dynamic flow error q_dyn by spraying correction factor r_ik.When internal-combustion engine 1 stratified mixture combustion, consider that the injection correction factor r_ik that is produced by regulator R_i obtains flow error q_stat and q_dyn.During internal-combustion engine 1 homogeneous combustion, from characterisitic family k_i, take out the injection correction factor r_ik of each operating point k.Change between stratified mixture combustion (position " S ") and homogeneous combustion (position " H ") by means of switch 18.Switch 18 is by an operating unit 19 operations of control gear 15.Operating unit 19 is determined the actual operating of internal-combustion engine 1 according to the different roadability parameter 20 of internal-combustion engine 1.
In functional block 17, according to the present invention, under the situation of long discharge time t_ik, to be considered as quiescent flow error q_stat with the corresponding injection correction factor of operating point k r_ik, because the influence of dynamic flow error q_dyn is more little, discharge time t_ik is just long more, that is, the time that high-pressure injection valve 9 opens or cuts out is long more.Under the situation of short discharge time t_ik, to spray correction factor r_ik accordingly with operating point k and be considered as dynamic flow error q_dyn, because the influence of quiescent flow error q_stat is more little, discharge time t_ik is short more, that is, the time of the operation of high-pressure injection valve 9 is short more.
Then, in the processing unit 21 of control gear 15, obtain discharge time t_ik after the correction of definite cylinder i on the definite operating point k for one according to the injection correction factor r_ik of each cylinder i.Exactly,, proofread and correct each discharge time that is calculated,, proofread and correct each discharge time in the mode of addition by means of dynamic flow error q_dyn in the mode of multiplication by means of quiescent flow error q_stat.In addition, in processing unit 21, also can carry out filtering or unification to the discharge time t_ik that is obtained.
To sum up, at first obtain injection correction factor r_ik.At stratified mixture combustion with until during the homogeneous combustion of λ=0.85, torque error M_f_ik is adjusted to zero by means of regulator R_i.The regulating action of regulator R_I is corresponding to spraying correction factor r_ik.In stratified mixture combustion, between fuel quantity and torque M _ k of being exported, exist a ratio, in the homogeneous combustion of λ=0.85, be non-linear relation.Spraying correction factor r_ik is stored among the characterisitic family k_i of the single cylinder in the control gear 15.
When internal-combustion engine 1 operation, obtain quiescent flow error q_stat and dynamic flow error q_dyn according to injection correction factor r_ik in characterisitic family k_i for a definite operating point k storage.Proofread and correct the fuel quantity spray in the firing chamber 4 according to flow error q_stat, q_dyn, therefore, each cylinder i provides the torque M _ ik of consistent size, and has much irrelevant with error that each high-pressure injection valve 9 is had.This smooth running for internal-combustion engine 1, discharging and oil consumption all have positive influences.
The invention enables the machining tolerance of high-pressure injection valve 9 to strengthen.This is because also considered dynamic flow error q_dyn when proofreading and correct torque error M_f_ik, and obtains the characteristic of each high-pressure injection valve 9 of internal-combustion engine 1 at each cylinder, and takes in when regulating in that cylinder is consistent.
Claims (12)
1. move a multi-cylinder engine (1), the particularly method of a direct-injection internal combustion engine, wherein, fuel sprays into a firing chamber (4) in a charging stage by a high-pressure injection valve (9) at a compression stage and in second method of operation in first method of operation, and wherein, between the method for operation, change, and the torque of each cylinder of internal-combustion engine carried out consistent the adjusting, carry out by means of a regulator under first method of operation that described cylinder is consistent to be regulated, it is characterized in that :-on a plurality of operating points (k), obtain and store the torque error of proofreading and correct each cylinder (i)
(M_f_ik) required injection correction factor (r_ik) ,-obtain the quiescent flow error of high-pressure injection valve (9) by spraying correction factor (r_ik)
(q_stat) and dynamic flow error (q_dyn) ,-according to flow error (q_stat, the q_dyn) school of the high-pressure injection valve of being obtained (9)
Just spraying into the fuel quantity of firing chamber (4).
2. method as claimed in claim 1 is characterized in that: only obtain in first method of operation and spray correction factor (r_ik).
3. method as claimed in claim 1 is characterized in that: spray correction factor (r_ik) and not only try to achieve under first method of operation, and try to achieve under second method of operation.
4. method as claimed in claim 3, it is characterized in that: according to obtain common quiescent flow error (q_stat) and dynamic flow error (q_dyn) at the injection correction factor (r_ik) of trying to achieve under first method of operation with according to the injection correction factor (r_ik) of trying to achieve under second method of operation, they are used as the basis of proofreading and correct for the fuel quantity in firing chamber to be sprayed into (4).
5. as each method among the claim 1-4, it is characterized in that: torque error (M_f_ik) regulating action required, that be used for the consistent regulator of regulating of cylinder that will proofread and correct each cylinder (i) is considered as sprays correction factor (r_ik).
6. as each method among the claim 1-5, it is characterized in that: change discharge time and proofread and correct fuel quantity in the firing chamber to be sprayed into (4).
7. as each method among the claim 1-6, it is characterized in that: will spray correction factor (r_k) and be stored in the characterisitic family (k_i).
8. as each method among the claim 1-7, it is characterized in that: under the situation of long discharge time, will spray correction factor (r_ik) accordingly with operating point (k) and be considered as quiescent flow error (q_stat).
9. as each method among the claim 1-8, it is characterized in that: under the situation of short discharge time, will spray correction factor (r_ik) accordingly with operating point (k) and be considered as dynamic flow error (q_dyn).
10. the control unit that is used for the control gear (15) of internal-combustion engine (1), particularly direct-injection internal combustion engine, particularly ROM (read-only memory) (ROM) or flash memory, in this control unit, stored a program, this program can be at a computing device of described control gear (15), particularly move on the microprocessor, and be suitable for implementing a method as claimed in any preceding claim.
11. have the internal-combustion engine (1) of firing chamber (4), direct-injection internal combustion engine particularly, fuel can under first method of operation in a compression stage and in a charging stage, spraying into described firing chamber (4) under second method of operation through a high-pressure injection valve (9), this internal-combustion engine has one and be used for the control gear (15) changed between the described method of operation, and have a regulator, this regulator is used for carrying out at least that cylinder is consistent to be regulated under first method of operation, it is characterized in that: control gear (15)-obtain and store on a plurality of operating points (k) torque error of proofreading and correct each cylinder (i)
(M_f_ik) required injection correction factor (r_ik) ,-obtain the quiescent flow error of high-pressure injection valve (9) by spraying correction factor (r_ik)
(q_stat) and dynamic flow error (q_dyn) ,-according to flow error (q_stat, the q_dyn) school of the high-pressure injection valve of being obtained (9)
Wait for the fuel quantity that sprays in the firing chamber (4).
12. be used for an internal-combustion engine (1), the control gear of a direct-injection internal combustion engine (15) particularly, described internal-combustion engine has a firing chamber (4), fuel can under first method of operation in a compression stage and in a charging stage, spraying into this firing chamber under second method of operation by a high-pressure injection valve (9), this internal-combustion engine also has a regulator, be used under first method of operation, carrying out at least that cylinder is consistent to be regulated, described control gear (15) is used for changing between the method for operation, it is characterized in that: described control gear (15)-obtain and store on a plurality of operating points (k) is proofreaied and correct the torque error of each cylinder (i)
(M_f_ik) required injection correction factor (r_ik) ,-obtain the quiescent flow error of high-pressure injection valve (9) by spraying correction factor (r_ik)
(q_stat) and dynamic flow error (q_dyn) ,-according to flow error (q_stat, the q_dyn) school of the high-pressure injection valve of being obtained (9)
Wait for the fuel quantity that sprays in the firing chamber (4).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10012025.3 | 2000-03-11 | ||
| DE10012025A DE10012025A1 (en) | 2000-03-11 | 2000-03-11 | Method for operating a multi-cylinder internal combustion engine |
| PCT/DE2001/000346 WO2001069066A1 (en) | 2000-03-11 | 2001-01-30 | Method for operating a multi-cylinder internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1364216A true CN1364216A (en) | 2002-08-14 |
| CN1364216B CN1364216B (en) | 2010-06-09 |
Family
ID=7634442
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN018004873A Expired - Fee Related CN1364216B (en) | 2000-03-11 | 2001-01-30 | Method for operating multi-cylinder internal combustion engine |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP1179130B1 (en) |
| JP (1) | JP2003527527A (en) |
| CN (1) | CN1364216B (en) |
| AU (1) | AU3914501A (en) |
| BR (1) | BR0105031B1 (en) |
| DE (3) | DE10012025A1 (en) |
| MX (1) | MXPA01011465A (en) |
| RU (1) | RU2260141C2 (en) |
| WO (1) | WO2001069066A1 (en) |
Cited By (2)
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|---|---|---|---|---|
| CN103314201A (en) * | 2011-01-18 | 2013-09-18 | Ge延巴赫两合无限公司 | Method for operating an internal combustion engine having at least two cylinders |
| CN103375299A (en) * | 2012-04-26 | 2013-10-30 | 马自达汽车株式会社 | Multi-cylinder gasoline engine |
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| DE10235105B4 (en) * | 2002-08-01 | 2015-02-26 | Robert Bosch Gmbh | Method for operating an internal combustion engine, in particular of a motor vehicle |
| DE10317684B4 (en) | 2003-04-17 | 2015-02-12 | Robert Bosch Gmbh | Method and control device for operating an internal combustion engine |
| DE10323671A1 (en) * | 2003-05-16 | 2004-12-09 | Robert Bosch Gmbh | Method for operating an internal combustion engine |
| DE10339251B4 (en) * | 2003-08-26 | 2015-06-25 | Robert Bosch Gmbh | Method for operating an internal combustion engine |
| DE102004006294B3 (en) | 2004-02-09 | 2005-10-13 | Siemens Ag | Method for equalizing the injection quantity differences between the cylinders of an internal combustion engine |
| DE102004006554B3 (en) * | 2004-02-10 | 2005-06-30 | Siemens Ag | Cylinder equalization method for fuel injection in automobile engine using adaption of fuel injection parameters via learned adaption values |
| FR2910552B1 (en) * | 2006-12-21 | 2009-01-30 | Renault Sas | METHOD FOR CONTROLLING AN INTERNAL COMBUSTION ENGINE |
| JP2012026340A (en) | 2010-07-22 | 2012-02-09 | Denso Corp | Fuel injection control device for direct injection internal combustion engine |
| RU2519272C2 (en) * | 2012-01-10 | 2014-06-10 | Аркадий Фёдорович Щербаков | Method for ice injection parameter adjustment |
| JP5918702B2 (en) * | 2013-01-18 | 2016-05-18 | 日立オートモティブシステムズ株式会社 | Engine control device |
| US9593638B2 (en) * | 2014-09-18 | 2017-03-14 | Ford Global Technologies, Llc | Fuel injector characterization |
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| JP2920262B2 (en) * | 1991-06-14 | 1999-07-19 | トヨタ自動車株式会社 | Control device for multi-cylinder internal combustion engine |
| DE4122139C2 (en) * | 1991-07-04 | 2000-07-06 | Bosch Gmbh Robert | Method for cylinder equalization with regard to the fuel injection quantities in an internal combustion engine |
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| DE19650518C1 (en) * | 1996-12-05 | 1998-06-10 | Siemens Ag | Method for controlling a direct injection internal combustion engine |
| DE19720009C2 (en) * | 1997-05-13 | 2000-08-31 | Siemens Ag | Method for cylinder equalization with regard to the fuel injection quantity in an internal combustion engine |
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- 2000-03-11 DE DE10012025A patent/DE10012025A1/en not_active Withdrawn
-
2001
- 2001-01-30 DE DE50101962T patent/DE50101962D1/en not_active Expired - Lifetime
- 2001-01-30 JP JP2001567921A patent/JP2003527527A/en not_active Ceased
- 2001-01-30 AU AU39145/01A patent/AU3914501A/en not_active Abandoned
- 2001-01-30 MX MXPA01011465A patent/MXPA01011465A/en active IP Right Grant
- 2001-01-30 EP EP01913545A patent/EP1179130B1/en not_active Expired - Lifetime
- 2001-01-30 BR BRPI0105031-1A patent/BR0105031B1/en not_active IP Right Cessation
- 2001-01-30 CN CN018004873A patent/CN1364216B/en not_active Expired - Fee Related
- 2001-01-30 RU RU2001132751/06A patent/RU2260141C2/en not_active IP Right Cessation
- 2001-01-30 WO PCT/DE2001/000346 patent/WO2001069066A1/en active IP Right Grant
- 2001-01-30 DE DE10190969T patent/DE10190969D2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103314201A (en) * | 2011-01-18 | 2013-09-18 | Ge延巴赫两合无限公司 | Method for operating an internal combustion engine having at least two cylinders |
| CN103314201B (en) * | 2011-01-18 | 2016-12-14 | Ge延巴赫两合无限公司 | For the method running the internal combustion engine with at least two cylinder |
| CN103375299A (en) * | 2012-04-26 | 2013-10-30 | 马自达汽车株式会社 | Multi-cylinder gasoline engine |
| CN103375299B (en) * | 2012-04-26 | 2016-08-03 | 马自达汽车株式会社 | Many cylinders petrol engine |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2260141C2 (en) | 2005-09-10 |
| EP1179130A1 (en) | 2002-02-13 |
| WO2001069066A1 (en) | 2001-09-20 |
| CN1364216B (en) | 2010-06-09 |
| BR0105031A (en) | 2007-05-29 |
| DE10012025A1 (en) | 2001-10-18 |
| JP2003527527A (en) | 2003-09-16 |
| BR0105031B1 (en) | 2009-08-11 |
| EP1179130B1 (en) | 2004-04-14 |
| DE10190969D2 (en) | 2002-06-20 |
| AU3914501A (en) | 2001-09-24 |
| MXPA01011465A (en) | 2002-08-30 |
| DE50101962D1 (en) | 2004-05-19 |
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