Fuel injection system of an internal combustion engine

Abstract: A fuel injecting amount of an internal combustion engine is calculated utilizing equations determined from a physical model describing a behavior of fuel in the engine. The fuel injection system includes estimation means in which estimation values f andw and f andv of the adhering fuel amount and the vapor fuel amount respectively are calculated based on: a product λr·m of the detected fuel/air ratio and the detected air amount; a division Vf/ω of fuel evaporating amount by the engine speed; and a fuel injecting amount q. The fuel injecting amount is calculated in the system based on the division Vf/ω, the estimated values f andw and f andv, the product λr·m, and a summed up deviation from a target ratio. The coefficients of respective terms are determined by analyzing the physical model by modern control theory. A variation of the invention does not use an air/fuel sensor.

Description: BACKGROUND OF THE INVENTION The present invention relates to a fuel injection system of an internal combustion engine, in which the amount of fuel injected by a fuel injection valve, hereforth referred to as the fuel injecting amount, is determined based on a physical model describing a behavior of fuel coming into a cylinder of the engine. A fuel injection system is disclosed, which determines a fuel injecting amount of a fuel injection valve so that an air/fuel ratio of an air/fuel mixture supplied to an engine is adjusted to coincide with a target ratio, for example, in JP-A-No. 59-196930. The system uses identification that the linear approximation holds between a control input and a control output. The control input is regarded as a compensation value for compensating a basic fuel injecting amount obtained from the rotating speed of an engine and the amount of intake air. The control output is regarded as an actual measurement of the air/fuel ratio detected by an air/fuel ratio sensor. Using such identification provides a physical model for describing dynamic behavior of the engine, based on which a control law is designed. The system of this known type, based on the linear control theory, is thus constructed to determine the fuel injecting amount, utilizing the control law. Actually, however, the linear relationship does not hold between the control input and the control output. The physical model obtained from a simple linear approximation, thus, is allowed to describe the dynamic behavior of the engine accurately only in a very limited operating condition. For this reason, the conventional systems suppose several physical models in several regions of the engine operation in each of which the linear approximation can almost hold. Accordingly several control laws corresponding to the physical models must be designed in respective regions. In the aforementioned system, control laws have to be switched depending on the physical model in the respective region of the engine operation, resulting in cumbersome control. Switching the control law might cause the control at the boundary between the regions to be unstable. A system of this type uses an approximation by lower order physical model for improving responsiveness of the control by reducing calculating time. In this method, an approximation error or an error due to the difference among individual engines is absorbed by an integral operation. However, in the conventional method, the physical model is provided based on physically meaningless state variables on the assumption that the linear approximation can hold between the control output and control input. Hence approximating the physical model by lower order will deteriorate the control accuracy because of the increase in the amount of the integral term. Further, since the above system determines the fuel injecting amount in accordance with an actual measurement of an air/fuel ratio detected by an air/fuel ratio sensor as the control output, the control cannot be applied to an engine with no such sensor. EP-A-184 626 also discloses a method for controlling the fuel injection in an internal combustion engine, wherein the air-fuel ratio of the mixture supplied to each cylinder of the engine is maintained at a desired value by calculating from sensor data a deposition rate at which injected fuel deposites and forms a film mass on an intake manifold wall of the engine, and a vaporisation rate at which the film mass vaporizes from the manifold wall, calculating a current film mass quantity and calculating the desired fuel quantity taking into account the intake air flow and the desired air-fuel ratio in accordance with a linear equation. Since the calculation of the desired fuel quantity takes into account only the estimated film mass on the intake manifold wall and the fact that a part of the fuel forming the film mass is evaporated when fuel is injected into the intake manifold, the actual quantity of fuel supplied to the cylinder only consists of the injected fuel quantity and the evaporated part of the film mass. However, the disadvantage that the vapor fuel is not totally sucked into the cylinder but a vapor fuel quantity remains in the intake mainfold, is not considered. Furthermore, it is not considered that also a part of the injected fuel quantity evaporates forming a further vapor fuel quantity in the intake mainfold. Also the deposition weight is calculated as a function of the throttle position while the influence of the engine speed is not taken into consideration. EP-A-152 019 discloses a similar method for controlling the fuel injection in an internal combustion engine, wherein on the basis of the phenomenon that a part of fuel vapored from a liquid film adherent on a wall surface of a fuel intake manifold remains in the intake manifold in the form of vapor fuel, the quantity of liquid film and the quantity of vapor fuel are estimated by using control parameters such as air mass flowing through a throttle valve, a throttle opening, an engine speed, an air-fuel ratio, etc. The quantity of liquid film and the quantity of vapor fuel at a desired point of time are then predicted on the basis of the result of this estimation. Furthermore, the quantity of liquid film is estimated in the case where the data as to the air-fuel ratio obtained by an λ-sensor include an observation delay. However, the estimated value of vapor fuel remaining in the intake mainfold only relates to a part of fuel evaporating from the liquid film adherent on the wall surface. It is not considered that, when a quantity of fuel is injected into the intake manifold, also a certain amount of that fuel evaporates and remains in the intake manifold as vapor fuel. Furthermore, it is not taken into account that some of the vapor fuel evaporated from the liquid film as well as from the injected fuel quantity will again adhere on the wall surface of the intake manifold thereby increasing the film mass quantity. Thus, according to this prior art, the exact vapor fuel amount remaining in the intake pipe at a certain time as well as the fuel amount evaporated in one intake cycle are not taken into account so that the physical models of this prior art are not precise. For example, when the amount of evaporated fuel that stays in the intake pipe is large, the increased amount of fuel flowing into the cylinder due to the vapor fuel amount, is not considered and, thus, a precise control can not be obtained. SUMMARY OF THE INVENTION It is an object of the present invention to provide a fuel injection system of an internal combustion engine, which determines the fuel injecting amount with great accuracy without switching control laws. According to the present invention, as shown in Fig. 1, the fuel injection system of an internal combustion engine (M2) for determining a fuel injection amount q of a fuel injection valve (M4) is based on a physical model describing a relationship between an amount fw of fuel adhering to an inner wall of an intake pipe (M1), an amount fv of vapor fuel in the intake pipe (M1), the fuel injection amount q, a fuel amount fc coming into the cylinder (M3), and a fuel evaporating amount at every intake stroke Vf/ω , the system comprising: an operating state detection means (M5, M15) for determining a rotating speed ω of the engine (M2), an evaporating amount per unit time Vf of the fuel adhering to the inner wall of the intake pipe (M1) as a function of the measured engine temperature, and an amount m of air flowing in the intake pipe of the engine; a dividing means (M6, M16) for dividing the evaporating amount per unit time Vf by the engine speed ω ; an estimation means (M7, M17) for calculating estimation values fw and fv of the adhering fuel amount fw and the vapor fuel amount fv based on said division Vf/ω at the dividing means (M6, M16) and the fuel injection amount q according to said physical model; a fuel injection amount calculation means (M9, M19) for calculating the fuel injection amount q, based on the division Vf/ω , the estimation values fw and fv, and a product λr·m of the detected air amount m and a target fuel/air ratio λr; fc = α1·q + α2·fw + α3·fv fw(k+1) = (1-α2)·fw(k) + α4·q(k) - α5·Vf(k)/ω(k) fv(k+1) = (1-α3)·fv(k) + α6·q(k) + α5·Vf(k)/ω(k) λ(k)·m(k) = α2·fw(k) + α3·fv(k) + (1-α4-α6)·q(k) where subscript k denotes calculation at the k-th intake cycle time and k+1 denotes calculation at the (k+1)-th intake cycle time and coefficients α1 to α6 are predetermined values. The operating state detection means M5, M15 detects: the rotating speed ω of the engine M2, i.e., an engine speed; an evaporating amount Vf per unit time of the fuel adhering to the inner wall of the intake pipe M1; and an amount m of air coming into the cylinder M3. A known engine speed sensor can be used for detecting the engine speed ω. The evaporating amount Vf can be derived from a known function between a saturated vapor pressure Ps of the fuel in the intake pipe M1 and a pressure P in the intake pipe M1 (intake pipe pressure). The saturated vapor pressure Ps is hardly obtained by a sensor. So the following equation (1) is utilized for providing it. The pressure Ps is a function of a temperature T of the fuel. The temperature T can be represented by either the water temperature of a water jacket of the engine M2, or the temperature of a cylinder head adjacent to the intake port. Thus the temperature T (°K), either in the water jacket or in the cylinder head detected by a temperature sensor is used as the parameter in the equation (1): Ps = β1·T² - β2·T + β3 (1) where β1, β2, β3 are proper constants. First, the saturated vapor pressure Ps is obtained based on temperature signals from the sensor at the water jacket or at the cylinder head. Then a pressure P in the intake pipe is sensed by a known pressure sensor. The fuel evaporating amount Vf is detected by utilizing a predetermined data map or a predetermined equation based on the saturated vapor pressure Ps and the intake pipe pressure P. Alternatively, since the fuel evaporating amount Vf greatly changes dependent on the pressure Ps, it may be obtained with approximation from the following equation (1)' using only Ps as the parameter: Vf = β4·Ps (1)' where β4 is a constant. The air amount m coming into the cylinder M3 can be easily obtained, for example, from the following equation (2). When the engine speed ω is constant, the air amount m is approximated by a linear function of the pressure P, such as: m = {βx(ω)·P - βy(ω)}/Ti, (2) where βx(ω) and βy(ω) are coefficients depending on the engine speed ω. Accordingly the air amount m is detected based on the pressure P and the temperature Ti detected by the respective known sensors, and the engine speed ω detected by the aforementioned sensor, utilizing the above equation (2). Also, the air amount m may be detected by compensating a basic air amount m by the temperature Ti. The basic air amount m is obtained from a predetermined map using the pressure P and the engine speed ω as parameters. The air amount m coming into the cylinder M3 at an intake stroke still can be estimated based on the amount of the air coming into the intake pipe M1 detected by a known air flow meter attached upstream of a throttle valve. An example of the physical model as the basis of the above inventive construction will be described. A fuel amount fc coming into the cylinder M3 of the engine M2 is given by the following equation (3), using the fuel injecting amount q of the fuel injection valve M4, the adhering fuel amount fw and the vapor fuel amount fv. fc = α1·q + α2·fw + α3·fv (3) The above equation is given because the fuel amount fc is considered as the sum of a direct influx α1·q by the fuel injected from the fuel injection valve M4, an indirect influx α2·fw spilling from the intake pipe M1 to which the injected fuel adheres, and a vapor fuel influx α3·fv remaining in the intake pipe M1 due to evaporation of either the injected fuel or the fuel adhering to the inner wall. Since the fuel injecting amount q is determined by the control parameter of the fuel injection valve M4 (e.g., injection valve opening time), which is a known variable, the fuel amount fc can be estimated if the adhering fuel amount fw and the vapor fuel amount fv are obtained as hereforth explained. The adhering fuel amount fw decreases by α2 at every intake cycle caused by the flow into the cylinder M3 at the intake stroke as well as by evaporation in the intake pipe M1. Conversely it increases by α4 which is a part of the fuel injecting amount q injected from the fuel injection valve M4 synchronously with the intake cycle. The amount of the fuel evaporating at every intake stroke can be represented as α5·Vf/ω. Thus the adhering fuel amount fw is given by the following equations (4): fw(k+1) = (1-α2)·fw(k) + α4·q(k) - α5·Vf(k)/ω(k) (4) where k is a number of the intake cycle time. The vapor fuel amount fv decreases by α3 at every intake cycle caused by the flow into the cylinder M3 at the intake stroke. It increases by α6 due to the evaporation of a part of the fuel injecting amount q. It further increases by the evaporation of the adhering fuel. The vapor fuel amount fv is given by the following equation (5). fv(k+1) = (1-α3)·fv(k) + α6·q(k) + α5·Vf(k)/ω(k) (5) A fuel amount fc(k) admitted into the cylinder M3 of the engine M2 is represented by the following equation (6) using a fuel/air ratio λ(k) which can be detected from the concentration of the oxygen in the exhaust gas, and the air amount m(k) coming into the cylinder M3. fc(k) = λ(k)·m(k) (6) When the coefficients α1 through α6 of the respective equations are determined by the known method of system identification, a state equation (7) and an output equation (8) are obtained as shown below. Both equations use the adhering fuel amount and the vapor fuel amount as state variables, and are described in a discrete system taking the intake cycle of the engine as a sampling cycle. Those equations determine a physical model for describing behavior of fuel in the engine. The estimation means M7, M17 obtains estimations f andw and f andv of the state variables fw and fv, based on: the division Vf/ω from the dividing means M6, M16 and the fuel injecting amount q of the fuel injection valve M4. Here the calculation utilizes the first equation set in accordance with the aforementioned physical model. Since the adhering fuel amount fw and the vapor fuel amount fv cannot be detected directly by a sensor like the engine speed ω, nor detected even indirectly by calculations from detected results of sensors like the fuel evaporating amount Vf or the air amount m, they are estimated by the estimation means M7, M17. The estimation means M7, M17 may have a construction of known observers like minimal order observer, identity observer, dead beat observer, linear function observer, or adaptive observer. The design methods of the observers are explained in detail in "Introduction to Dynamic System--Theory, Models and Applications" by David G. Luenberger, John Wiley & Sons Inc., New York (1979). The fuel injecting amount calculation means M9, M19 calculates the fuel injecting amount q of the fuel injection valve M4 based on the division Vf/ω from the dividing means M6, M16 the estimations f andw and f andv from the estimation means M7, M17, and the product λr·m of the target fuel/air ratio λr and the air amount m, i.e., target fuel amount coming into the cylinder M3, utilizing the second equation determined from the physical model. The fuel injecting amount calculation means M9, M19 is so constructed to calculate the control variable of the servo system compensated for the non-linearity. The control variable is a sum of the products as follows: the products of the state variables f andw and f andv estimated by the estimation means M7, M17 and coefficients predetermined by the physical model; the product of the target fuel amount λrm and coefficients predetermined by the physical model; and the product of the division Vf/ω(k) calculated by the dividing means M6, M16 and coefficients predetermined by the physical model. In the above constructed fuel injection system of the invention, the estimation means M7, M17 estimates the state variables f andw and f andv based on the division Vf/ω calculated by the dividing means M6, M16 and the fuel injecting amount q of the fuel injection valve M4, utilizing the first equation determined from the physical model. The fuel injecting amount calculation means M9, M19 calculates the fuel injecting amount q of the fuel injection valve M4 based on the division Vf/ω from the dividing means M6, M16 the estimations f andw and f andv from the estimation means M7, M17, and the product λr·m of the target fuel/air ratio λr and the air amount m detected by the operating state detection means M5, M15, utilizing the second equation determined from the physical model. The fuel injection system of the present invention calculates the fuel injecting amount in accordance with the control law determined from the physical model which describes the fuel behavior in the engine as shown by the equations (7) and (8), utilizing the adhering fuel amount and the vapor fuel amount as state variables. The fuel injecting amount of the engine, thus, is subjected to a feedback control. The fuel injection system of an internal combustion engine of this invention sets a control law in accordance with a physical model describing the fuel behavior in the engine, and is compensated for the non-linearity in accordance with the division calculated by the dividing means M6, M16. Therefore the system allows a single control law to cover the control of the fuel injecting amount with great accuracy under wide-ranging operating conditions of the engine. Accordingly its construction is further simplified and can be expressed in lower order, thereby improving the responsiveness of the control. BRIEF EXPLANATION OF THE DRAWINGS Fig. 1A is a block diagram representing a construction of the present invention. Fig. 1B is a block diagram representing a construction of another feature of the present invention. Fig. 2 is a schematic diagram illustrating an internal combustion engine and its peripheral equipment according to a first embodiment of the present invention. Fig. 3 is a block diagram representing a control system of the present invention. Fig. 4 is a flowchart describing a series of operations for the control of the present invention. Fig. 5 is a flowchart describing a modification of the fuel injection control according to the first embodiment of the present invention. Fig. 6 is a schematic diagram illustrating an internal combustion engine and its peripheral equipment according to a second embodiment of the present invention. Fig. 7 is a block diagram representing another control system of the present invention. Fig. 8 is a flowchart describing another series of operations for the control of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to the drawings. Shown in Fig. 2, an intake pipe 4 admits air through an air cleaner 6. The intake pipe 4 is provided with a throttle valve 8 for controlling the flow of the admitted air, a surge tank 10 for suppressing pulsation of the admitted air, a sensor 12 for detecting a pressure P in the intake pipe 4 (intake pipe pressure), and a sensor 13 for detecting an intake air temperature Ti. An exhaust pipe 14 is provided with an oxygen sensor 16 for detecting a fuel/air ratio of an air/fuel mixture coming into a cylinder 2a of an internal combustion engine 2 in accordance with the concentration of oxygen in the exhaust gas, and a three way catalytic converter 18 for treating the exhaust gas. Residual HC of the fuel and the combustion residues such as CO and NOx in the exhaust gas are converted into harmless gases in the three way catalytic converter 18. The engine 2 is provided with sensors for detecting operating states thereof such as an engine speed sensor 22 for detecting the engine speed ω in accordance with the rotation of a distributor 20, a crank angle sensor 24 for detecting a fuel injecting timing t to the engine 2 in accordance with the rotation of the distributor 20, a water temperature sensor 26 installed on a water jacket of the engine 2 for detecting a cooling water temperature T, and the aforementioned sensors 12, 13, and 16. The distributor 20 is so constructed to apply high voltage from an igniter 28 to spark plugs 29 at a predetermined ignition timing. Signals detected by the respective sensors are fed to an electronic control circuit 30 constructed as an arithmetic logic circuit including a microcomputer to be used for driving a fuel injection valve 32 to control the amount of the fuel injected therefrom. The electronic control circuit 30 comprises a CPU 40, a ROM 42, a RAM 44, an input port 46, and an output port 48. The CPU 40 performs arithmetic operations for the fuel injection control in accordance with a predetermined control program. The control program and initial data used for the operation by the CPU 40 are stored in the ROM 42. The data used for the operation are temporarily stored in the RAM 44. The detected signals from the respective sensors are received through the input port 46. A driving signal to the fuel injection valve 32 responding to the result operated by the CPU 40 is supplied through the output port 48. The electronic control circuit 30 is constructed to perform feedback control of a fuel injecting amount q of the fuel injection valve 32 so that the fuel/air ratio λ of the mixture coming into the cylinder 2a of the engine 2 is adjusted to the target fuel/air ratio λr set in accordance with the respective operating state of the engine 2. A control system used for the feedback control will be described with reference to a block diagram of Fig. 3, which does not show any hardware structure. Actually it is realized as a discrete system by executing a series of programs shown in the flowchart of Fig. 4. The control system of this embodiment is designed based on a physical model represented by the equations (7) and (8). Referring to Fig. 3, in the control system of this embodiment, the temperature T detected by the sensor 26 is input to a first calculator P1. Then a saturated vapor pressure Ps is calculated based on the input temperature T, utilizing the equation (1). Further a fuel evaporating amount Vf is calculated based on the pressure Ps, utilizing the equation (1)′. The fuel evaporating amount Vf is input to a divider P2 to be divided by the engine speed ω detected by the sensor 22. The division Vf/ω is input to a multiplier P3 to be multiplied by a predetermined coefficient f5. The engine speed ω detected by the sensor 22 is input to a second calculator P4 along with the pressure P detected by the sensor 12, and the temperature Ti detected by the sensor 13. The second calculator P4 calculates an air amount m coming into the cylinder 2a based on the engine speed ω, the pressure P, and the temperature Ti, utilizing equation (2). The calculated result is output to both a first multiplier P5 and a second multiplier P6. At the first multiplier P5, a fuel/air ratio λ of the mixture coming into the cylinder 2a detected by the oxygen sensor 16 is multiplied by the air amount m calculated by the second calculator P4, resulting in the actual fuel amount λ·m coming into the cylinder 2a. At the second multiplier P6, a target fuel/air ratio λr determined in accordance with the load imposed on the engine 2 is multiplied by the air amount m calculated by the second calculator P4, resulting in a calculated required fuel amount λr·m (target fuel amount) to come into the cylinder 2a. The target fuel amount λr·m calculated by the multiplier P6 is input to a multiplier P7 to be multiplied by a predetermined coefficient f4. The products of the first and the second multipliers P5 and P6 are input to a difference operating portion P8 where the difference of the products m·(λ - λr) is calculated. The difference is summed up at a summing portion P10, which is further multiplied by a predetermined coefficient f3 at a multiplier P9. The actual fuel amount λ·m calculated by the first multiplier P5 and the division Vf/ω calculated by the divider P2 are output to an observer P11. The observer P11 is so constructed to estimate the adhering fuel amount fw and the vapor fuel amount fv based on the actual fuel amount λ·m, division Vf/ω from the divider P2, the fuel injecting amount q of the fuel injection valve 32, and the adhering fuel amount f andw and the vapor fuel amount f andv which are estimated in the previous execution of the same routine, utilizing a predetermined equation. The obtained estimations f andw and f andv are multiplied by coefficients f1 and f2 at multipliers P12 and P13, respectively. The products obtained from the multipliers P12 and P13, along with the products from other multipliers P3, P7 and P9 , are added by adders P14 through P17. Accordingly the fuel injecting amount q of the fuel injection valve 32 is determined. A design method for the aforementioned control system in Fig. 3 will be explained. A design method for the control system of this type is described in detail, as for example, in the above-cited reference. Therefore the method is described only briefly herein. This embodiment uses the Smith-Davison design method. The control system of this embodiment is designed based on the aforementioned physical model represented by the equations (7) and (8). This physical model with non-linearity is linearly approximated. If the following equations are provided: y (k) =λ(k)·m(k) - (1-α4-α6)·q(k) (9) x (k) = [fw(k) fv(k)] T (10) Θ = [α2 α3] (14) the equations (7) and (8) are represented by the following equations. x (k+1) = Φ · x (k) + Γ ·q(k) + Π ·Vf(k)/ω(k) (15) y (k) = Θ · x (k) (16) Suppose a disturbance W(k) is added to the right side of the equation (15), the equations (15) and (16) will be as shown by the following equations (15)' and (16)'. Variables at this time are represented by subscript a. x a(k+1) = Φ · x a(k) + Γ ·qa(k) + Π ·Vf(k)/ω(k) + E ·W(k) (15)' y a(k) = Θ · x a(k) (16)' Suppose y (k) = y r (target value), the equations (15) and (16) are represented by the following equations (15)'' and (16)''. x r = Φ · x r + Γ ·qr + Π ·Vf(k)/ω(k) (15)'' y r = Θ · x r (16)'' From the above equations (15)', (15)'' and (16)', (16)'', the equations (17) and (18) are obtained. x a(k+1) - x r = Φ ·( x a(k)- x r) + Γ ·(qa(k)-qr) + E ·W(k) (17) y a(k) - y r = Θ ·( x a(k)- x r) (18) Suppose ΔW(k) = W(k) - W(k-1) = 0 , on the assumption that the disturbance W changes in a stepwise fashion in the equation (17), the equations (17)′ and (18)′ are obtained from the equations (17) and (18). Δ( x a(k+1) - x r) = Φ ·Δ( x a(k)- x r) + Γ ·Δ(qa(k)-qr) (17)′ Δ( y a(k) - y r) = Θ ·Δ( x a(k) - x r) (18)′ Therefore, the above equations (17)′ and (18)′ entail a state equation which is linearly approximated and extended to a servo system as shown by the following equation (19). The above equation (19) is rewritten to the following equation (20). δ X (k+1) = P a·δ X (k) + G a·δ u (k) (20) A quadratic criterion function in the discrete system can be represented as follows. With weighted parameter matrices Q and R selected, the input δ u (k) for minimizing the quadratic criterion function J is obtained from the next equation (22). δ u (k) = F·δ X (k) (22) The optimal feedback gain F in the equation (19), thus, is determined by: F = -( R + G a T · M · G a)⁻¹· G a T · M · P a (23) where M is a regular symmetric matrix satisfying a discrete Ricacci equation shown by M = P a T · M · P a + Q - ( P a T · M · G a)·( R + G a T · M · G a)⁻¹·( G a T ·M · P a) (24) Hence Δ(qa(k) - qr) is given by: where F is [F1 F2]. With the above equation (25) integrated, qa(k) - qr is given by When control is performed according to equation (26) under the condition of equations (15)'' and (16)'', i.e., y (k) = y r , the following equation (27) is given. qr = F1· x r - F1· x a(0) + y a(0) (27) Then substituting the equation (27) into the equation (15)'' provides the following equation. x r = [ Φ + Γ ·F1]· x r + Γ ·(-F1· x a(0) + qa(0)) + Π ·Vf(k)/ω(k) (28) Suppose x a(k+1) = x (k) (k → ∞ ) , the following equations are obtained. x r(k) = [ I - Φ - Γ ·F1]⁻¹· Γ ·(-F1· x a(0) + qa(0)) + [ I - Φ - Γ ·F1]⁻¹· Π ·Vf(k)/ω(k) (29) y r(k) = Θ ·[I - Φ - Γ ·F1]⁻¹· Γ ·(-F1· x a(0) + qa(0)) + Θ ·[ I - Φ - Γ ·F1]⁻¹· Π ·Vf(k)/ω(k) (30) Therefore the following equation is provided. -F1· x a(0) + qa(0) = [ Θ ·[ I - Φ - Γ ·F1]⁻¹· Γ ]⁻¹· y r - [ Θ ·[ I - Φ - Γ ·F1]⁻¹· Γ ]⁻¹ · Θ ·[ I - Φ - Γ ·F1]⁻¹· Π ·Vf(k)/ω(k) (31) In the equation (31), substituting the following equations (32) and (33) into the equation (26) provides the equation (34). F3 = [ Θ ·[ I - Φ - Γ ·F1]⁻¹· Γ ]⁻¹ (32) F4 = -[ Θ ·[ I - Φ - Γ ·F1]⁻¹· Γ ]⁻¹· Θ ·[I - Φ - Γ ·F1]⁻¹ (33) Substituting the equations (9) and (10) into the equation (34) provides Accordingly the control system shown in Fig. 3 is designed. The equation (36) corresponds to the second equation for calculating the fuel injecting amount. The observer P11 is so constructed to estimate the adhering fuel amount fw and the vapor fuel amount fv in the equation (36) since they cannot be directly measured. Gopinath design method or the like is known for the design method of the observer of this type, which is described in detail by the cited "Basic System Theory". Here the minimal order observer is adopted. If the following equation (37) is provided, the aforementioned equation (15) is rewritten to the equation (38) as below. x (k+1) = Φ · x (k) + Δ u (k) (38) The generalized system of the observer for the physical model represented by the above equations (38) and (16) is determined as the following equation (39). Therefore the observer P11 of this first embodiment can be designed as the following equation (40), by which the adhering fuel amount fw and the vapor fuel amount fv are estimated. The fuel injection control executed by the electronic control circuit 30 will be described referring to a flowchart of Fig. 4. The variables used in the current processing will be hereinafter represented by subscript (k). The process for fuel injection control begins with the start of the engine 2, and is repeatedly carried out during the operation of the engine 2. When the process is initiated, step 100 is executed where the variables of both the adhering fuel amount estimation f andwo and the vapor fuel amount estimation f andvo, and the fuel injecting amount q are initialized. At step 110, the integral value Smλ of the difference between the actual fuel amount λm and the target fuel amount λrm is set at 0. At step 120, the fuel/air ratio λ(k), the pressure P(k), the intake air temperature Ti(k), the engine speed ω(k), and the fuel temperature T(k) are calculated based on the output signals from the respective sensors. At step 130, the target fuel/air ratio λr responding to the load imposed on the engine 2 is calculated based on the pressure P(k) and the engine speed ω(k) obtained at step 120. At this step 130, the target fuel/air ratio λr is so set that an air excess rate of the air fuel mixture becomes 1, i.e., λr is set at the stoichiometric air/fuel ratio. In case of engine operation with heavy load, the target fuel/air ratio λr is set to the richer side so as to increase the output of the engine by increasing the fuel amount more than usual. In case of engine operation with light load, it is set to the leaner side so as to reduce the fuel consumption by decreasing the fuel amount less than usual. After the target fuel/air ratio λr(k) is set at step 130, the control proceeds to step 140. The process at this step 140 is executed as the second calculator P4 in which the air amount m(k) coming into the cylinder 2a is calculated based on the pressure P(k), the intake air temperature Ti(k), and the engine speed ω(k) which are obtained at step 120, utilizing either the equation (2) or a predetermined data map representing such relation of equation (2). The control further proceeds to step 150 where the process is executed as the first calculator P1 and the divider P2. At this step 150, the fuel evaporating amount Vf obtained based on the fuel temperature T(k) is divided by the engine speed ω(k) to calculate the evaporating amount Vfw(k), i.e., Vf(k)/ω(k), between cycle to cycle of the intake stroke. In this embodiment, the saturated vapor pressure Ps(k) is obtained from the equation (1) or a predetermined data map, and the pressure Ps(k) is used for calculating the evaporating fuel amount Vf based on the equation (1)′. Since the evaporating fuel amount Vf also changes dependent on the pressure P, it may be calculated based on the saturated vapor pressure Ps(k) obtained from the equation (1) and the pressure P(k) obtained at step 120. The process at following step 160 is executed as the first multiplier P5 where the fuel/air ratio λ(k) obtained at step 120 is multiplied by the air amount m(k) obtained at step 150 to calculate the actual fuel amount λm(k) that has come into the cylinder 2a at the previous intake stroke. Then the control proceeds to step 170 where the process is executed as the observer P11. At step 170, the estimations of the adhering fuel amount f andw(k) and the vapor fuel amount f andv(k) are provided based on the actual fuel amount λm(k) at step 160, the fuel injecting amount q obtained in the previous execution of the same routine, the evaporating amount Vfw(k) at step 150, and estimations of the adhering fuel amount f andwo and the vapor fuel amount f andvo obtained in the previous execution of the same routine, utilizing the equation (40). The process at step 180 is executed as the second multiplier P6. At this step 180, the target fuel amount λrm(k) coming into the cylinder 2a is calculated by multiplying the target fuel/air ratio λr(k) set at step 130 by the air amount m(k) obtained at step 140. The control further proceeds to step 190 where the fuel injecting amount q is calculated based on the integral value Smλ of the difference between the actual fuel amount λm and the target fuel amount λrm, estimations f andw(k) and f andv(k) obtained at step 170, the target fuel amount λrm(k) at step 180, and the evaporating amount Vfw(k) at step 150, utilizing equation (36). At step 200, the fuel injection control is executed by opening the fuel injection valve 32 during the period corresponding to the fuel injecting amount q(k) obtained at step 190 at the fuel injection timing determined based on the detection signal from the crank angle sensor 24. When the fuel supply to the engine 2 is terminated after the execution of the fuel injection control at step 200, the control proceeds to step 210 where the process is executed as the summing portion P10. At step 210, the difference between the actual fuel injection amount λm(k) obtained at step 160 and the target fuel injection amount λrm(k) at step 180 are added to the integral value Smλ(k) obtained in the previous execution of the same routine to obtain an integral value Smλ(k). The control proceeds to step 220 where the estimations f andw(k) and f andv(k) obtained at step 170 are set as the values f andwo and f andvo used for providing estimations of the adhering fuel amount f andw and the vapor fuel amount f andv at next processing. The program then returns to step 120 again. In the fuel injection system of this embodiment, the control law is set based on the physical model describing the behavior of fuel in the engine 2. Accordingly the behavior which varies responsive to the temperature of the intake pipe of the engine 2, i.e., warming-up state of the engine 2, can be compensated for its non-linearity by Vfw (Vf/ω), resulting in the fuel injection control covered by a single control law. This will eliminate cumbersome processing such as switching from one control law to another in accordance with the operating state of the engine, thereby simplifying the control system. Since the system utilizes the physical model enabled to describe the behavior of fuel with high accuracy, it can perform the control without being influenced by disturbances in spite of the control law with lower order, thus improving the control accuracy. The state variables estimated at the observer are the adhering fuel amount and the vapor fuel amount. Therefore, an abnormality of the system can be detected by determining whether they are estimated accurately by the observer. In the above embodiment, the control system is designed based on the physical model represented by equations (7) and (8) on the assumption that all the fuel evaporating from the inner wall of the intake pipe is to be the vapor fuel. However, some part of the fuel evaporating at the intake stroke of the engine (1/4 of the total evaporating amount α5·Vf/w between an intake cycle to the next intake cycle in a 4-cycle engine) may not remain inside the intake pipe as the vapor fuel. Instead, it may directly flow into the cylinder of the engine. For the case, the equations (5) and (6) are rewritten to the following equations (50) and (51). fv(k+1) = (1-α3)·fv(k) + α6·q(k) + 3·α5·Vf(k)/4·ω(k) (50) fc(k) = λ(k)·m(k) + α5·Vf(k)/4·ω(k) (51) The physical model is modified as the following equations (52) and (53): where α7 = α5·3/4 and α8 = α5/4 . The control system can also be designed by this physical model. In this case, the control system can be designed in the same manner as the above embodiment by the following equations. y (k) = λ(k)·m(k) - (1-α4-α6)·q(k) - α8·Vf(k)/ω(k) (54) x (k) = [fw(k) fv(k)] T (55) Θ = [α2 α3] (59) Since the equations (52), (53) can be represented as the aforementioned equations (15), (16), the state equation which is linearly approximated and extended to the servo system shown by the equation (19) is obtained in the same manner as the above embodiment. Then the equation (34) is derived from solving the Ricacci equation. Substituting the equations (54) and (55) into the equation (34) provides the following equation (60). Then the control system can be designed, which is the same as the above embodiment shown in Fig. 3. The observer P11 shown in Fig. 3 is also designed based on the equation (40) in the same manner as the above embodiment. In the above embodiment, estimations f andw and f andv of the adhering fuel amount fw and the vapor fuel amount fv obtained by the observer P11 are used as it is for the control. However in case of the engine operation with light load, at low engine speed, and at a high cooling water temperature of 80°C or more, the adhering fuel amount fw might be estimated as negative due to an increase in the evaporating amount Vf/ω calculated at every intake stroke. In practice, since the adhering fuel amount fw can not become negative, such estimation would disturb the stable control. The processes executed by steps 171 and 172 shown in Fig. 5 are required for solving the aforementioned problem. At those steps, after the amount fw is estimated at step 170 shown in Fig. 4, it is determined whether the estimated value f andw is negative. If the value is determined to be negative, it is set at 0. A second embodiment will be described, which corresponds to the second feature of the present invention shown in Fig. 1B. The schematic diagram illustrating the internal combustion engine 2 and its peripheral equipments applied to this embodiment are shown in Fig. 6. The construction of them, however, is different from that of the first embodiment shown in Fig. 2 only in that the oxygen sensor (air/fuel ratio sensor) of the exhaust pipe 14 is excluded. Accordingly this embodiment is different from the first one in that the fuel/air ratio λ is not used in the control to be described hereinafter. The control system of the second embodiment is represented by the block diagram of Fig. 7. As shown in Fig. 7, the control system is not provided with the first multiplier P5, adder P8, summing portion P10, multiplier P9, and adder P14 shown in Fig. 3. The observer P31 is constructed to calculate estimations f andw and f andv without using the·fuel/air ratio λ. Since the other parts of the construction are the same as those of the first embodiment, the numerals designating the identical parts will be added by 20. The design method of the control system of Fig. 7 will be described. If the following equations are provided: x (k) = [fw(k) fv(k)] T (70) w (k) = [Vf(k)/ω(k)] (74) y (k) = [λ(k)·m(k)] (75) u (k) = [q(k)] (76) Λ = [1-α4-α6] (77) Θ = [α2 α3] (78) the equations (7) and (8) are represented by the following equations, respectively. x (k+1) = Φ · x (k) + Γ · u (k) + E · w (k) (79) y (k) = Θ · x (k) + Λ · u (k) (80) In case of steady state with y (k) = y r (target value), supposing u (k) = u r and x (k) = x r entails that the equations (79) and (80) are represented by the following equations (79)′ and (80)′. x r = Φ · x r + Γ · u r + E · w (k) (79)′ y r = Θ · x r + Λ · u r (80) ′ From the above equations (79), (79)′, and (80), (80)′, the following equations are derived. x (k+1) - x r = Φ ·( x (k) - x r) + Γ ·( u (k) - u r) (81) y (k) - y r = Θ ·( x (k) - x r) + Λ ·( u (k) - u r) (82) If the following equations are provided: X(k) = x (k) - x r (83) U(k) = u (k) - u r (84) Y(k) = y (k) - y r - Λ ·( u (k) - u r) (85) the equations (81) and (82) become as follows. X(k+1) = Φ ·X(k) + Γ ·U(k) (86) Y(k) = Θ ·X(k) (87) In the above equations (86) and (87), supposing X(k) → 0 entails Y(k) = 0. Also supposing u (k) → u r entails y (k) → y r. The next step is to design the optimal regulator of the above equation (86) can be designed. That is, the optimal regulation is obtained as shown in the following equation (88), by solving discrete Ricacci equation. U(k) = F ·X(k) (88) The equation (88) is transformed into the following equation (89) utilizing the equations (83) and (84). u (k) = F · x (k) - F · x r + u r (89) If x r and u r in equations (79)′ and (80)′ are given by the following equation (90), the above equation (79) is determined to provide u (k). In this embodiment, the above equation (90) is rewritten as the following equation (91) from the equations (70) through (78). Thus, the values x r and u r (i.e., fwr, fvr and qr) are obtained as follows. fwr = β11·Vf(k)/ω(k) + β12·{λr·m(k) - (1-α4-α6)· u (k)} (92) fvr = β21·Vf(k)/ω(k) + β22·{λr·m(k) - (1-α4-α6)· u (k)} (93) qr = β21·Vf(k)/ω(k) + β23·{λr·m(k) - (1-α4-α6)· u (k)} (94) where β11 through β23 are constants. The following equation (95) is obtained from the equation (89) using coefficients f1, f2, f4, and f5. u (k) = f1·fw(k) + f2·fv(k) + f4·m(k)λr + f5·Vf(k)/ω(k) (95) In this way, the control system shown in Fig. 7 can be designed. The equation (95) corresponds to the second equation in the fuel injecting amount calculation means M19 for obtaining the fuel injecting amount. The observer P31 is so constructed to estimate the adhering fuel amount fw and the vapor fuel amount fv utilized in the equation (95) since they cannot be directly measured. Gopinath design method or the like is known for the design method of the observer of this type. This embodiment cannot use the conventional observer because the air/fuel ratio λ of the mixture which is actually supplied to the engine 2 cannot be measured. However, the equation (7) which describes the behaviour of fuel in the engine 2 provides the amounts fw and fv without the actual value of λ. The reason is as follows. The second and third terms of the right side of the equation (7) can be calculated because q(k) is derived from the electronic control circuit 30 as the control parameter, Vf(k) is detected by the saturated vapor pressure Ps from the cooling water temperature T from the sensor 26, and the intake pipe pressure P from the sensor 12, and further the engine speed ω(k) is detected by the engine speed sensor 22. If the following equations (96) and (97) are provided, the equation (98) is obtained as below. δw(k) = fw(k) - f w(k) (96) δv(k) = fv(k) - f v(k) (97) The equation (98) is stable because 1 - α2 < 1 and 1 - α3 < 1 . Therefore, δw(k) and δv(k) → 0, i.e., f andw(k) → fw(k), and f andv(k) → fv(k). If appropriate initial values are provided for fw(k) and fv(k), they can be estimated by utilizing the equation (7). In this embodiment, the observer P31 is so constructed to estimate the adhering fuel amount fw and the vapor fuel amount fv by utilizing the equation (7). Even if the disturbance brings such conditions as fw(k) ≠ f andw, and fv(k) ≠ f andv, the equation (95) will provide u(k) (i.e., fuel injecting amount q(k)) with no problem, since the f andw(k) and f andv(k) follow fw(k) and fv(k), The fuel injection control executed by the electronic control circuit 30 in this second embodiment will be described referring to a flowchart of Fig. 8. Hereinafter, the variables used for the current processing will be represented by subscript (k). The process for fuel injection control begins with the start of the engine 2, and is repeatedly carried out during the operation of the engine 2. When the process is initiated, step 300 is executed where the variables of the adhering fuel amount estimation f andwo and the vapor fuel amount estimation f andvo, and the fuel injecting amount q are initialized. At step 310, intake pipe pressure P(k), intake air temperature Ti(k), engine speed ω(k), and cooling water temperature T(k) are obtained based on the output signals from the respective sensors. Then the control proceeds to step 320 where a target fuel/air ratio λr responding to the load imposed on the engine 2 is calculated based on the P(k) and ω(k) obtained at step 310. At this step 320, the target fuel/air ratio λr is so set that an air excess rate of the air fuel mixture becomes 1, i.e., at the stoichiometric air/fuel ratio. In case of the engine operation with heavy load, the target fuel/air ratio λr is set to the richer side to increase the output of the engine by increasing the fuel amount more than usual. Conversely in case of the engine operation with light load, it is set to the leaner side to reduce the fuel consumption by decreasing the fuel amount less than usual. After the target fuel/air ratio λr(k) is set at step 320, the control proceeds to step 330. The process at step 330 is executed as the second calculator P24 in which an air amount m(k) coming into the cylinder 2a is calculated based on P(k), Ti(k), and ω(k) obtained at step 320, utilizing either the equation (2) or a predetermined data map. The process at the following step 340 is executed as the first calculator P21 and the divider P22. At this step 340, the fuel evaporating amount Vf obtained based on T(k) and P(k) at step 310 is divided by the engine speed ω(k) to calculate the evaporating amount Vfw(k), i.e., Vf(k)/ω(k) between an intake cycle to the next intake cycle. The process at step 350 is executed as the observer P31 in which estimations of the adhering fuel amount f andw(k) and the vapor fuel amount f andv(k) are provided based on the evaporating amount Vfw(k) at step 340, the fuel injecting amount q obtained in the previous execution of the same routine, and estimations f andwo, f andvo obtained in the previous execution of the same routine, utilizing the following equation (99) which is derived from the equation (7). The process at steps 360 is executed as the multiplier P26. There, the target fuel amount λrm(k) coming into the cylinder 2a is calculated by multiplying the target fuel/air ratio λr/(k) set at step 320 by the air amount m(k) at step 330. The control proceeds to step 370 where the fuel injecting amount q(k) is calculated based on the estimations f andw(k), f andv(k) obtained at step 350, the target fuel amount λrm(k) at step 360, and the evaporating amount Vfw(k) at step 340, utilizing the equation (95). At step 380, the fuel injection is executed by opening the fuel injection valve 32 during the period corresponding to the fuel injecting amount q(k) determined at step 370 at the fuel injection timing determined based on the detection signal from the crank angle sensor 24. When the fuel supply to the engine 2 is terminated after the execution of the fuel injection at step 380, the control proceeds to step 390. At step 390, the estimations f andw(k) and f andv(k) obtained at step 350 are set as the values of the adhering fuel amount f andwo and the vapor fuel amount f andvo used for providing estimations f andw and f andv at next processing. Then the program returns to step 310 again. In the fuel injection system of this embodiment, the control law is set based on the physical model describing the behavior of fuel in the engine 2. The behavior which varies responsive to the temperature of the intake pipe in the engine 2, i.e., warming-up state of the engine, can be compensated for its non-linearity by Vfw, i.e., Vf/ω. Accordingly the fuel injection control is covered by a single control law. This will eliminate the cumbersome processing such as switching from one control law to another in accordance with the operating state of the engine, thereby simplifying the control system. The fuel/air ratio can be adjusted to the target ratio without using a sensor for detecting the fuel/air ratio λ of the mixture actually supplied to the engine 2, thereby simplifying the construction of the device. The state variables estimated at the observer are the adhering fuel amount and the vapor fuel amount. Therefore, an abnormality of the system can be detected by determining whether they are estimated accurately by the observer. The control system of this embodiment is designed based on the physical model represented by the equations (7) and (8) on the assumption that all the fuel evaporating from the inner wall of the intake pipe would be the vapor fuel. However, some part of the evaporating fuel at the intake stroke of the engine (1/4 of the total evaporating amount α5·Vf/ω between an intake cycle to the next intake cycle in a 4-cycle engine) may not remain inside the intake pipe as the vapor fuel. Instead it may directly flow into the cylinder of the engine. Thus the equations (5) and (6) are rewritten to the equations (100) and (101) as follows. fv(k+1) = (1-α3)·fv(k) + α6·q(k) + 3·α5·Vf(k)/4·ω(k) (100) fc(k) = λ(k)·m(k) + α5·Vf(k)/4·ω(k) (101) The physical model is modified as the following equations (102) and (103): where α7 = α5·3/4 and α8 = α5/4 . The control system can be designed from this physical model. In this embodiment, the observer P31 is designed by using the equation (7). A known observer may be available in which the state variables are estimated on the assumption that the fuel/air ratio λ is controlled to coincide with the target fuel/air ratio λr. In case a minimal order observer is designed from the equation (7), the following equation is given. This observer cannot be directly applied to the device which does not detect the fuel/air ratio λ. However, the adhering fuel amount fw and the vapor fuel amount fv can be estimated by making the second term of the equation (104) as B andλrm(k) on the assumption that the fuel/air ratio λ is adjusted to the target ratio λr by the fuel injection control.

Claims: A fuel injection system of an internal combustion engine (M2) for determining a fuel injection amount q of a fuel injection valve (M4) based on a physical model describing a relationship between an amount fw of fuel adhering to an inner wall of an intake pipe (M1), an amount fv of vapor fuel in the intake pipe (M1), the fuel injection amount q, a fuel amount fc coming into the cylinder (M3), and a fuel evaporating amount at every intake stroke Vf/ω , the system comprising: an operating state detection means (M5, M15) for determining a rotating speed ω of the engine (M2), an evaporating amount per unit time Vf of the fuel adhering to the inner wall of the intake pipe (M1) as a function of the measured engine temperature, and an amount m of air flowing in the intake pipe of the engine; a dividing means (M6, M16) for dividing the evaporating amount per unit time Vf by the engine speed ω ; an estimation means (M7, M17) for calculating estimation values fw and fv of the adhering fuel amount fw and the vapor fuel amount fv based on said division Vf/ω at the dividing means (M6, M16) and the fuel injection amount q according to said physical model; a fuel injection amount calculation means (M9, M19) for calculating the fuel injection amount q, based on the division Vf/ω , the estimation values fw and fv, and a product λr·m of the detected air amount m and a target fuel/air ratio λr; wherein said physical model is described by the following equations: fc = α1·q + α2·fw + α3·fv fw(k+1) = (1-α2)·fw(k) + α4·q(k) - α5·Vf(k)/ω(k) fv(k+1) = (1-α3)·fv(k) + α6·q(k) + α5·Vf(k)/ω(k) λ(k)·m(k) = α2·fw(k) + α3·fv(k) + (1-α4-α6)·q(k) where subscript k denotes calculation at the k-th intake cycle time and k+1 denotes calculation at the (k+1)-th intake cycle time and coefficients α1 to α6 are predetermined values. The fuel injection system according to claim 1, being characterized in that the evaporating amount per unit time Vf is determined from a temperature T of the engine (M2) by the operating state detection means (M5, M15), utilizing the following equations: Vf = β4·Ps, and Ps = β1·T² - β2·T + β3, where Ps is a saturated vapor pressure of the fuel and β1, β2, β3, and β4 are constants. The fuel injection system according to claim 1, being characterized in that the evaporating amount per unit time Vf is determined from a saturated vapor pressure Ps of the fuel and a pressure P of the intake air by the operating state detection means (M5, M15), the saturated vapor pressure Ps being determined from a temperature T of the engine (M2) utilizing the following equation: Ps = β1·T² - β2·T + β3, where β1, β2, and β3 are constants. The fuel injection system according to claim 1, being characterized in that the estimation means (M7, M17) sets the value of the adhering fuel amount fw to zero when the calculated estimation value of the adhering fuel amount fw is negative. The fuel injection system according to claim 1, being characterized in that the operating state detection means (M5) further indirectly detects a fuel/air ratio λ of a mixture coming into the cylinder (M3); the estimation means (M7) calculates said estimated values fw and fv further based on a product λ·m of the detected fuel/air ratio λ and the detected air amount m; the system further comprises a summing means (M8) for summing up a difference m·(λ - λr) between the product λ·m and a product λr·m of a preset fuel/air ratio λr and the air amount m; and said fuel injection amount calculation means (M9) calculates the fuel injection amount q further based on the difference summed up by the summing means (M8). The fuel injection system according to claims 1 or 2, being characterized in that said fuel injecting amount calculation means calculates the fuel injecting amount q utilizing a second equation determined from said physical model, the second equation being a linear equation as follows: q(k) = f1· f w(k) + f2· f v(k) + f4·m(k)·λr + f5·Vf(k)/ω(k) where coefficients f1, f2, f4, and f5 are determined from said physical model. The fuel injection system according to claim 6, being characterized in that said second equation is an optimal regulator determined from a linear equation that is derived from said physical model, the linear equation being as follows: X(k+1) = Φ ·X(k) + Γ ·U(k) (86) where matrices Φ , Γ are determined from the physical model. The fuel amount injection system according to claim 5, being characterized in that said estimation means (M7) estimates said estimated values fw and fv utilizing a first equation determined from said physical model, the first equation being as follows: where matrices A, B, and J are determined from the physical model. The fuel amount injection system according to claim 5, being characterized in that the fuel injecting amount calculation means calculates the fuel amount q according to a second equation, where the second equation is a linear equation as follows: where coefficients f1, f2, f3, f4, and f5 are determined from the physical model. The fuel injection system according to claim 9, being characterized in that said second equation is an optimal regulator determined from a linear equation that is derived from said physical model, the linear equation being as follows: δ X (k+1) = P a·δ X (k) + G a·δ u (k) (20) where matrices P a, G a are determined from the physical model.

Inventors: OHATA AKIRA, OHATA, AKIRA
Applicants: TOYOTA MOTOR CO LTD, TOYOTA JIDOSHA KABUSHIKI KAISHA
Application year: 1988
Main classification: F02D41
IPC codes: F02B75, F02D41