Abstract:
In effecting individual cylinder fuel injection control in an electronically controlled diesel engine, wherein rpm variations with every explosion cylinder are detected and compared with one another, and a fuel injection quantity control actuator is controlled with every cylinder so as to make the rpm variations of respective cylinders uniform, so that engine vibrations due to a dispersion in fuel injection quantity between the cylinders can be reduced, the individual cylinder correction quantity of the fuel injection quantity control actuator is determined in accordance with a deviation in the rpm variation obtained from a difference between a mean rpm variation and rpm variations of respective cylinders, the upper and lower limit guard values of the individual cylinder correction quantity, the values being variable in association with a range, which the fuel injection quantity control actuator can follow up, is determined in accordance with engine temperature or fuel temperature, and the fuel injection quantity control actuator is controlled with every cylinder in accordance with the individual cylinder correction quantity having imposed thereon restrictions by the upper and lower limit guard values, so as to prevent the divergence of the individual cylinder correction quantity.

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     This invention relates to a method of controlling individual cylinder fuel injection quantities in an electronically controlled diesel engine and a device therefor, and particularly to improvements in a method of controlling individual cylinder fuel injection quantities in an electronically controlled diesel engine and a device therefor, suitable for use in an electronically controlled diesel engine in a motor vehicle, wherein rpm variations with every explosion cylinder are detected and compared with one another, and a fuel injection quantity control actuator is controlled with every cylinder so as to make the rpm variations of respective cylinders uniform, so that engine vibrations due to a dispersion in fuel injection quantity between the cylinders can be reduced. 
     2. Description of the Prior Art 
     In general, the vibrations of a diesel engine during idling are by far higher than those of a gasoline engine. The diesel engine resiliently supported by an engine mounting mechanism resonates with the engine vibrations, resulting in not only worsening the comfortableness of a vehicle, but also adversely affecting components around the engine. This is mainly caused by the vibrations of the primary/secondary low frequencies attributed to periodical dispersions of the fuel fed under pressure to the respective cylinders at a cycle only half the turn of the diesel engine when the diesel engine is of four cycle type for example. More specifically, in a diesel engine, if a dispersion occurs in the fuel injection quantity between the cylinders, then, as shown in FIG. 1, the rpm variations ΔNE between the explosion cylinders (in the case of the engine of four cylinders, 180°CA (crank angle)) are not equal to one another, whereby surging S of deviations about a crank occurs at a cycle of every four explosions, which surge gives an uncomfortable feeling to an occupant of a vehicle. In the drawing, designated at TDC is a top dead center. 
     For this, it is conceivable that an engine body, a fuel injection pump and an injection nozzle are manufactured with very high accuracies, so that a dispersion in fuel quantities fed to respective cylinders can be reduced. However, to achieve this, great difficulties in production engineering are encountered, and a fuel injection pump and the like become very expensive. On the other hand, it is also conceivable that an engine mounting mechanism is improved so as to reduce the vibrations of the engine. However, the mounting mechanism becomes complicated and expensive, and further, the vibrations of the diesel engine itself are not reduced thereby, thus not enabling to offer the fundamental solution of the problem. 
     To obviate the above-described problem, it is conceivable that an NE raw wave form is obtained by a gear 20 secured to a drive shaft 14 of a fuel injection pump 12 and an engine rotation sensor 22 mounted to a pump housing 12A as shown in FIG. 2 for example, an engine speed NEi(i=1 to 4) through a rotation of 45°CA immediately before the cylinder to be corrected is calculated from the time duration ΔT needed for the rotation through 45°CA, i.e. the rotation through 22.5°PA (pump angle) (45°CA of the engine) of the drive shaft 14 for example, which is detected by a fall of an NE pulse having formed the NE raw wave form as shown in FIG. 3, an rpm variation DNE p  (p=1 to 4) with every explosion cylinder is detected from the engine speed NEi as shown in FIG. 4, the resultant value is compared with a mean value (hereinafter referred to as a &#34;mean rpm variation&#34;) ##EQU1## of the rpm variations of all of the cylinders, when the rpm variation of the cylinder is smaller than the mean rpm variation WNDLT, the fuel injection quantity of the cylinder is regarded to be small, a fuel injection quantity (hereinafter referred to as an &#34;everytime correction quantity&#34;) Δq to be increased is learned in accordance with a difference (hereinafter referred to as an &#34;rpm variations difference&#34;) DDNE p  (p=1 to 4), as shown in FIG. 5 for example, and reflected at the time of a subsequent fuel injection of the cylinder. On the contrary, when the rpm variation of the cylinder is larger than the mean rpm variation WNDLT, to decrease the fuel injection quantity of the cylinder. A fuel injection control actuator, such for example as a spill actuator for controlling a spill ring in a distribution type fuel injection pump is controlled with every cylinder until the rpm variations of the respective cylinders become uniform as illustrated in FIG. 6 for example, whereby the fuel injection quantity is increased or decreased with every cylinder, so that the dispersion in fuel injection quantity between the cylinders can be obviated, thereby enabling to reduce the engine vibrations. 
     Referring to FIG. 6, ΔQ p  (p=1 to 4) is an individual cylinder correction quantity as being an integrated value of the everytime correction quantities Δq, K 5  is a coefficient of correction for preventing hunting when the engine speed is within a range between 1000 rpm and 1500 rpm during neutral position, wherein the higher the engine speed is, the lower the individual cylinder correction quantity is made, Q fin  is an injection quantity calculated from a mean engine speed NE, an accelerator opening Accp and the like, and Vsp is an output from a spill position sensor for detecting a displacement of the spill actuator. 
     However, since the upper and lower guard limit values of the individual cylinder correction quantity ΔQp have heretofore been set at constant values, but not determined by the temperature, in some cases, the movement of the spill ring has not reached the individual cylinder correction quantity ΔQp by the injection time as shown in FIG. 7, because the follow-up action of the spill ring becomes slow at the time of low temperature where the fuel viscosity becomes high, such for example as at the fuel temperature of -20° C. or less. Then, since the individual cylinder correction quantity ΔQp is not satisfactorily corrected, such a vicious circle arises that a deviation of the rpm variation DDNEp ( =WNDLT-DNEp ) is not decreased and an everytime correction quantity Δq of the succeeding time corresponding to the deviation of rpm variation DDNEp is further integrated to the individual cylinder correction quantity ΔQp, is diverged to the upper and lower limit values, exceeding a range, which the spill ring can follow up, as shown in FIG. 8 (an example of the coolant temperature of -20° C. or less), the individual cylinder correction quantity ΔQp and the spill ring movement do not correspond to each other so that the individual cylinder injection quantity correction cannot be made in time, and the correction of the succeeding cylinder is interfered with, thus presenting such a disadvantage that the individual cylinder correction cannot be made satisfactorily. 
     SUMMARY OF THE INVENTION 
     The present invention has been developed to obviate the above-described disadvantages of the prior art and has as its object the provision of a method of controlling individual cylinder fuel injection quantities in a electronically controlled diesel engine, wherein the individual cylinder correction quantity can be constantly set within a range, which the fuel injection quantity control actuator can follow up, and consequently, the correction of the cylinder of the preceding time does not interfere with the correction of the cylinder of the succeeding time due to the divergence of the correction quantity, whereby the injection quantity corrections with every cylinder are reliably performed, so that the level of vibrations can be reduced to the minimum, and the device therefor. 
     To this end, the present invention contemplates that, in a method of controlling individual cylinder fuel injection quantities in an electronically controlled diesel engine, wherein rpm variations with every explosion cylinder are detected and compared with one another, and a fuel injection quantity control actuator is controlled with every cylinder so as to make the rpm variations of respective cylinders uniform, so that engine vibrations due to a dispersion in fuel injection quantity between the cylinders can be reduced, as the technical gist thereof is illustrated in FIG. 9, the method comprises the steps of: 
     determining a deviation in the rpm variation from a difference between a mean rpm variation and rpm variations of the respective cylinders; 
     determining an individual cylinder correction quantity of the fuel injection quantity control actuator in accordance with the deviation in the rpm variation; 
     detecting engine temperature or fuel temperature; 
     determining the upper and lower limit guard values of the individual cylinder correction quantity, the values being variable in association with a range, which the fuel injection quantity control actuator can follow up, in accordance with the engine temperature or the fuel temperature; 
     imposing restrictions on the individual cylinder correction quantity by the upper and lower guard values; and 
     controlling the fuel injection quantity control actuator with every cylinder in accordance with the individual cylinder correction quantity having imposed thereon the restrictions. 
     To the above end, the present invention contemplates that, in a device for controlling individual cylinder fuel injection quantities in an electronically controlled diesel engine, the device comprises: 
     a fuel injection pump including a spill ring and a spill actuator, for controlling fuel injection quantities; 
     injection nozzles for injecting fuel discharged from the fuel injection pump into combustion chambers; 
     an accelerator sensor for detecting an accelerator opening; 
     an engine rotation sensor for detecting an engine speed; 
     a temperature sensor for detecting an engine temperature or a fuel temperature; and 
     a control unit for determining a target injection quantity at least from the accelerator opening and the engine speed, controlling the spill actuator so that the fuel of the target injection quantity can be discharged from the fuel injection pump, determining the individual cylinder correction quantity of the spill actuator in accordance with the deviation in the rpm variation obtained from a difference between the mean rpm variation and the rpm variations of the respective cylinders so as to eliminate a dispersion in the rpm variation, determining the upper and lower limit guard values of the individual cylinder correction quantity, the values being variable in association with a range, which the spill actuator can follow up, in accordance with the engine temperature or the fuel temperature, and controlling the spill actuator with every cylinder in accordance with the individual cylinder correction quantity having imposed thereon restrictions by the upper and lower limit guard values. 
     A specific form of the present invention is of such an arrangement that the engine temperature is regarded as the coolant temperature, whereby necessity of another separate temperature sensor is eliminated, thus avoiding the cost increase. 
     Another specific form of the present invention is of such an arrangement that the fuel temperature is regarded as the fuel temperature in the fuel injection pump, so that the fuel viscosity in the pump can be more accurately predicted. 
     A further specific form of the present invention is of such an arrangement that absolute values of the upper and lower limit guard values are reduced when the engine temperature or the fuel temperature is low, so that the interference between the corrections of the cylinders can be reliably prevented when the temperature is lower than the normal temperature. 
     A still further specific form of the present invention is of such an arrangement that the upper and lower limit guard values are set at plus or minus 2 mm 3  /st under normal temperature and at plus or minus 1 mm 3  /st under low temperature. 
     According to the present invention, the upper and lower limit guard values of the individual cylinder correction quantity are made variable in association with the range, which the fuel injection quantity control actuator can follow up, in accordance with the engine temperature or the fuel temperature, so that the individual cylinder correction quantity can be constantly held within the range, which the fuel injection quantity control actuator can follow up. In consequence, even when the fuel viscosity is high immediately after the starting under a very low temperature, the divergence of the correction quantity can be prevented from occurring, the correction of the cylinder of the preceding time does not interfere with the correction of the cylinder of the succeeding time, and the injection quantity corrections are reliably performed with every cylinder, so that the level of vibrations can be reduced to the minimum. Moreover, the quality levels for the dispersion of the individual cylinder injection quantity of the fuel injection pump and for the dispersion of the valve opening pressure of the injection nozzles can be lowered, thus enabling to reduce the costs. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The exact nature of this invention, as well as other objects and advantages thereof, will be readily apparent from consideration of the following specification relating to the accompanying drawings, in which like reference characters designate the same or similar parts throughout the figures thereof and wherein: 
     FIG. 1 is a graphic chart showing the relationship between the rpm variation and surging of deviations about the crank in the conventional electronically controlled diesel engine; 
     FIG. 2 is a sectional view showing the arrangement of the engine rotation sensor used in the conventional electronically controlled diesel engine; 
     FIG. 3 is a graphic chart showing the conventional method of determining the engine speed through 45°CA; 
     FIGS. 4 and 5 are graphic charts showing the conventional method of determining everytime correction quantities; 
     FIGS. 6 through 8 are graphic charts showing examples of signal wave forms in various portions in the prior art; 
     FIG. 9 is a flow chart showing the technical gist of the method of controlling individual cylinder fuel injection quantities in the electronicaly controlled diesel engine according to the present invention; 
     FIG. 10 is a sectional view, partially including a block diagram, showing the general arrangement of an embodiment of the electronically controlled diesel engine in a motor vehicle, to which the present invention is applied; 
     FIG. 11 is a block diagram showing the arrangement of the electronic control unit used in the embodiment; 
     FIG. 12 is a flow chart showing the interrupt routine for determining the everytime correction quantities and the indicidual cylinder correction quantities; 
     FIG. 13 is a graphic chart showing an example of a map for determining the coefficient of correction as used in the routine; 
     FIG. 14 is a graphic chart showing an example of the relationship between the coolant temperature and the upper and lower limit guard values of the individual cylinder correction quantity as used in the routine; and 
     FIG. 15 is a graphic chart showing an example of the relationship between the coolant temperature, the individual cylinder correction quantities and the upper and lower limit guard values in the embodiment. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Detailed description will hereunder be given of embodiments of the electronically controlled diesel engine in a motor vehicle, to which is applied the method of controlling individual cylinder fuel injection quantities according to the present invention, with reference to the drawings. 
     As shown in FIG. 10, the embodiment of the present invention comprises: 
     a distribution type fuel injection pump 12 including a drive shaft 14 rotatable in association with the rotation of a crankshaft of a diesel engine 10, a feed pump 16 (FIG. 10 shows a state of the feed pump unfolded through 90°) solidly secured to the drive shaft 14, for feeding the fuel under pressure, a fuel pressure regulating valve 18 for regulating fuel feeding pressure, an engine rotation sensor 22 formed of an electromagnetic pickup for example, for detecting the rotating condition of a diesel engine 10 from a rotary displacement of a gear 20 solidly secured to the drive shaft 14, a roller ring 25 for driving a pump plunger 24 in cooperation with a face cam 23, a timer piston 26 (FIG. 10 shows a state of the timer piston unfolded through 90°) for controlling the rotational position of the roller ring 25, a timing controlling valve 28 for controlling the position of the timer piston 26 to control the fuel injection timing, a timer position sensor 30 formed of a variable inductance sensor for example, for detecting a position of the timer piston 26, a spill ring 32 for controlling the fuel spill timing from the pump plunger 24, a spill actuator 34 for controlling the position of the spill ring 32 to control the fuel injection quantity, a spill position sensor 36 formed of a variable inductance sensor for example, for detecting a position Vsp of the spill ring 32 from a displacement of a plunger 34A of the spill actuator 34, a fuel cutting solenoid (hereinafter referred to as an &#34;FCV&#34;) 38 for cutting the fuel during stop of the engine in operation, and a delivery valve 42 for preventing the counterflow and after-dripping of fuel; 
     injection nozzles 44 for injecting the fuel discharged from the delivery valve 42 of the fuel injection pump 12 into combustion chambers of the diesel engine 10; 
     an intake air pressure sensor 48 for detecting the pressure of intake air taken in through an intake pipe 46; 
     an intake air temperature sensor 50 for detecting the temperature of the intake air; 
     a coolant temperature sensor 52 provided on a cylinder block of the engine 10, for detecting engine coolant temperature; 
     an accelerator sensor 56 for detecting a depressing angle (hereinafter referred to as an &#34;accelerator opening&#34;) Accp of an accelerator pedal 54 operated by a driver; and 
     an electronic control unit (hereinafter referred to as an &#34;ECU&#34;) 58 for determining a target injection timing and a target injection quantity from the accelerator opening Accp detected from an output of the accelerator sensor 56, the engine speed NE obtained from an output of the engine rotation sensor 22, the engine coolant temperature detected by the coolant temperature sensor 52 and so on, and for controlling the timing controlling valve 28, the spill actuator 34 and the like, so that the fuel of the target injection quantity can be injected from the fuel injection pump 12 at the target injection timing. 
     As detailedly shown in FIG. 11, the ECU 58 comprises: 
     a central processing unit (hereinafter referred to as a &#34;CPU&#34;) 58A formed of a microprocessor for example, for performing various operations and processings; 
     a clock 58B for generating various clock signals; 
     a random access memory (hereinafter referred to an a &#34;RAM&#34;) 58C for temporarily storing operational data and the like in the CPU 58A; 
     a read only memory (hereinafter referred to as a &#34;ROM&#34;) 58D for storing control programs, various data and the like; 
     a multiplexer (hereinafter referred to as an &#34;MPX&#34;) 58N for successively taking in an output from the coolant temperature sensor 52, which is inputted through a buffer 58E, an output from the intake air temperature sensor 50, which is inputted through a buffer 58F, an output from the intake air pressure sensor 48, which is inputted through a buffer 58G, an output from the accelerator sensor 56, which is inputted through a buffer 58H, the output Vsp from the spill position sensor 36, which is driven in response to a sensor driving frequency signal outputted from a sensor driving circuit 58J, and inputted through a sensor signal detecting circuit 58K, an output from the timer position sensor 30, which is driven in response to a sensor driving frequency signal outputted from a sensor driving circuit 58L, and inputted through a sensor signal detecting circuit 58M and so on; 
     an analogue-digital converter (hereinafter referred to as an &#34;A/D converter&#34;) 58P for converting analogue signals outputted from the MPX 58N into digital signals; 
     an input-output port (hereinafter referred to as an &#34;I/0 port&#34;) 58Q for taking an output from the A/D converter 58P into the CPU 58A; 
     a waveform shaping circuit 58R for waveform-shaping an output from the engine rotation sensor 22 and directly taking the same into the CPU 58A; 
     a driving circuit 58S for driving the timing controlling valve 28 in accordance with the result of operation of the CPU 58A; 
     a driving circuit 58T for driving the FCV 38 in accordance with the result of operation of the CPU 58A; 
     a servo amplifter 58V and a driving dircuit 50W, for driving the spill actuator 34 in accordance with a deviation between a spill position signal Vsp outputted from the spill position sensor 36 and an output from the CPU 58A, which is converted into an analogue signal by a digital-analogue converter (hereinafter referred to as a &#34;D/A converter&#34;) 58U; and 
     a common bus 58X for connecting the above-mentioned components to one another. 
     Description will hereunder be given of action of the embodiment. 
     Calculation of the everytime correction quantities Δq and the individual cylinder correction quantities ΔQp in the embodiment is carried out by an input capture interrupt routine ICI passing with every 45°CA as shown in FIG. 12. 
     More specifically, simultaneously with a fall of an NE pulse outputted with every 45°CA from the engine rotation sensor 22, the routine proceeds to Step 110, and, as shown in FIG. 3, an engine speed NEi(i=1 to 4) with every 45°CA is calculated from a time duration ΔT from a fall of NE pulse of the last time to a fall of NE pulse of this time. A counter i is renewed in a sequence of 1 - 2 - 3 - 4 - 1 by falls of NE pulses, whereby this engine speed NEi is renewed in a sequence of NE 1  - NE 2  - NE 3  - NE 4  - NE 1  with every 180°CA and stored in the respective memories. 
     Subsequently, the routine proceeds to Step 112, where a mean engine speed NE through 180°CA is calculated as shown in the following equation. 
     
         NE=(NE.sub.1 +NE.sub.2 +NE.sub.3 +NE.sub.4)/4              (1) 
    
     Then, the routine proceeds to Step 114, where the counter i is renewed, and thereafter, in Step 116, a coefficient of correction K 5  corresponding to the engine speed NE, for preventing the hunting when the engine speed is relatively high, such as 1000 rpm-1500 rpm, is calculated from a map having the relationship indicated in FIG. 13, which is previously stored in the ROM 58D. 
     Subsequently, the routine proceeds to Step 118, where judgment is made as to whether the counted value of the counter i is 4 or not. When the result of judgment is positive, namely, it is immediately after the renewal in a sequence of 3 to 4 of the counter i, the routine proceeds to Step 120, where judgment is made as to whether the idling is in the stable state or not. When the result of judgment is positive, namely, there are established all of such conditions that it is neither the time of starting nor the time immediately after the starting, the accelerator angle Accp is 0%, the shift position is neutral or a drive range is selected and the vehicle speed is zero in the case of a vehicle provided with an automatic transmission, for example, the routine proceeds to Step 122, where judgment is made as to whether there are two or more cylinders, in which the engine speed NE 1  is the minimum value out of NE 1  -NE 4  for one and the same cylinder p, or not. When the result of judgment is positive, namely, it is judged that no misfire and the like occur and the rotation is in the stable conditions, the routine proceeds to Step 124, where rpm variations DNE p  (p=1 to 4) corresponding to the respective cylinders are calculated through the following equation, as shown in FIG. 4, and stored in the respective memories. 
     
         DNE.sub.p ←NE.sub.3 -NE.sub.1                         (2) 
    
     Herein, a counter p is associated with the respective cylinders, when the counter i is changed in a sequence of 4 to 1, the renewals in a sequence of 1 - 2 - 3 - 4 - 1 are made, and one turn is completed through 720°CA. 
     Subsequently, the routine proceeds to Step 126, where a mean rpm variation WNDLT is calculated through the following formula and stored. ##EQU2## 
     Then, the routine proceeds to Step 128, where a deviation DDNE p  between the mean rpm variation WNDLT and the rpm variation DNE p  of the respective cylinders is calculated through the following formula. 
     
         DDNE.sub.p ←WNDLT-DNE.sub.p                           (4) 
    
     Subsequently, the routine proceeds to Step 130, where everytime correction quantities Δq are calculated through the following equation in accordance with the calculated deviation DDNE p , from the relationship as shown in FIG. 5 for example. 
     
         Δq=f(DDNE.sub.p)                                     (5) 
    
     Then, the routine proceeds to Step 132, where the everytime correction quantity Δq obtained this time is integrated to the individual cylinder correction quantity ΔQ p  which is the integrated value up to the last time as is shown in the following formula and stored as the quantity of this time. 
     
         ΔQ.sub.p ←ΔQ.sub.p +Δq              (6) 
    
     Since the individual cylinder correction quantity ΔQ p  is associated with the respective cylinders, there are four quantities including ΔQ 1  to ΔQ 4 . 
     Upon completion of the Step 132, the routine proceeds to Step 134, where the upper limit guard value ΔQpmax of the individual cylinder correction quantity is calculated from the relationship shown in FIG. 14 for example, in accordance with the coolant temperature previously obtained from an output of the coolant temperature sensor 52 by a one second routine and the like for example. Subsequently, the routine proceeds to Step 136, where judgment is made as to whether the individual cylinder correction quantity ΔQp calculated in the Step 132 is larger than the upper limit guard value ΔQpmax thereof or not. When the result of judgment is positive, the routine proceeds to Step 138, where the upper limit guard value ΔQpmax is made to be the individual cylinder correction quantity ΔQp, thereby completing this interrupt routine ICI. 
     On the other hand, when the result of judgment in the Step 136 is negative, the routine proceeds to Step 140, where the lower limit guard value ΔQpmin is calculated in accordance with the coolant temperature THW. Then, the routine proceeds to Step 142, where judgment is made as to whether the individual cylinder correction quantity ΔQp is smaller than the lower limit guard value ΔQpmin thereof or not. When the result of judgment is positive, the routine proceeds to Step 144, where the lower limit guard value ΔQpmin is made to be the individual cylinder correction quantity ΔQp, thus completing this interrupt routine ICI. 
     When the result of judgment in the Step 142 is negative, the individual cylinder correction quantity ΔQp obtained in the Step 132 is adopted as it is, thereby completing this interrupt routine ICI. 
     On the other hand, when the result of judgment in the Step 118 is negative, the routine proceeds to Step 150, where judgment is made as to whether the counted value of the counter i is 2 or not. When the result of judgment is positive, namely, such a judgment is made that it is immediately after the counted value of the counter i is renewed in a sequence of 1 to 2, the routine proceeds to Step 152, where the counter p is renewed. Upon completion of the Step 152 or when the result of judgment in the Step 150 is negative, the routine proceeds to Step 154, where a product obtained by multiplying the individual cylinder correction quantity ΔQ p+1  by the coefficient of correction K 5  is added to an injection quantity Qfin obtained from the mean engine speed NE and the accelerator opening Accp by the publicly known injection quantity calculating routine as shown in the following formula, thereby determining the final injection quantity Qfin&#39;. 
     
         Qfin&#39;←Qfin+K.sub.5 X Q.sub.p+1                        (7) 
    
     Upon completion of the Step 154 or when the result of judgment in the Step 120 or 122 is negative, this interrupt routine ICI is completed. 
     FIG. 15 shows the example of the relationship between the coolant temperature THSW, the individual cylinder correction quantities ΔQp and the upper and lower limit guard values ΔQpmax and ΔQpmin in this embodiment. As apparent from the drawing, under the normal temperature, even if the individual cylinder correction quantity ΔQp moves to the upper and lower limit guard values at its normal temperature, to plus or minus 2 mm 3  /st for example, the spill ring can substantially follow up, so that no interference is made with the correction control of the succeeding cylinder. On the other hand, at the time of the low temperature, where the coolant temperature THW is -20° C. or less, the upper and lower limit guard values ΔQpmax and ΔQpmin are reduced to plus or minus 1 mm 3  /st for example, also no interference is made with the correction control of the succeeding cylinder. In consequence, irrespective of the coolant temperature, the correction control with every cylinder can be reliably performed. 
     In this embodiment, the upper and lower limit guard values ΔQpmax and ΔQpmin of the individual cylinder correction quantity are made variable in accordance with the coolant temperature, whereby necessity of a separate temperature sensor is eliminated and no cost increase is caused. In addition, the temperature used as an index when the upper and lower limit guard values ΔQpmax and ΔQpmin are varied, need not necessarily be limited to the coolant temperature, and it is possible to use the oil temperature or the fuel temperature detected by a thermister or the like provided in the fuel injection pump or the fuel return passage. When the fuel temperature in the pump is detected, the viscosity of the fuel in the pump can be more accurately predicted. 
     In the above embodiment, the present invention has been applied to the electronically controlled diesel engine in a motor vehicle, provided with the spill ring as being the fuel injection quantity control actuator, however, it is apparent that the scope of the present invention need not necessarily be limited to this, and the present invention is applicable to the diesel engine for general use provided with the fuel injection quantity control actuator of any other type.