ENGINE SPEED CONTROLLING APPARATUS FOR INTERNAL COMBUSTION ENGINE

Abstract: An engine speed controlling apparatus for an internal com­ bustion engine (10) for controlling the engine speed of an internal combustion engine which has a means (16, 18) for governing the engine speed and in which a manipulated va­ riable of said governing beans and torque are in non-linear relationships. Although a real manipulated variable and the torque are in non-linear relationships, a virtual manipula­ ted variable in which an actual engine speed becomes a tar­ geted engine speed is calculated assuming those relation­ ships as being linear. The virtual manipulated variable is converted (by 38) to the real manipulated variable by using the actual non-linear relationships between the real mani­ pulated variable and the torque, and the governor is con­ trolled (by 40) on the basis of the converted real manipu­ lated variable.

Description: BACKGROUND OF THE INVENTION Field of the Invention: The present invention relates to an engine speed controlling apparatus for an internal combustion engine, and more particularly to an engine speed controlling apparatus for controlling the engine speed of an internal combustion engine mounted on an industrial vehicle such as a fork lift or an internal combustion engine used as a power source such as a generator. Description of the Related Art: In an internal combustion engine mounted on an industrial vehicle such as a fork lift or the like, since the cargo load acts in addition to the traveling load, it is necessary to prevent a change in the traveling load from hindering the loading and unloading operations and a change in the cargo load from hindering the traveling of the vehicle. In addition, an internal combustion engine used as a power source such as a generator is required to supply electric power on a stable basis. Various controlling apparatuses have hitherto been developed with a view to running such as internal combustion engine at a speed in the vicinity of a targeted engine speed. As one of such controlling apparatuses, a method is known in which the dynamics of the internal combustion engine and the load is approximated and expressed as a linear transmission function around a certain operating point of each factor, and compensation is effected through proportional plus integral plus differential (PID) action control (refer to "The Report of Experiments on the Speed Governing of Diesel Engine - Generator", Transactions of the Japan Society of Mechanical Engineers (Part 1) Vol. 43, No. 367, page 957, line 13 of the left column to line 1 of the right column). With the above-described conventional art, however, since the control system is designed by using characteristics of the internal combustion engine around certain operating points, there arises a need to design the control system for each operating point and effect control by changing over to an operation expression for control with respect to each operating point in conjunction with changes in the operating region of the internal combustion engine. Accordingly, this results in a problem such as an increased number of processes involved in designing the control system, and hunting which occurs in the engine speed at the time of making a changeover for control due to the discontinuity in expressions for control calculation. G. Marro: "Controlli automatici", 1989, Zanichelle, Bologna, Italy, discloses on pages 366 to 370 a control system in which the input-output relationship is non linear. A real manipulated variable is calculated from a feed back calculation, using a virtual manipulated variable. When an internal combustion engine is the subject of a control, the throttle opening and torque are not directly linked. They are indirectly linked by various parameters such as intake air pressure, amount of intake air, amount of fuel supply, ignition timing, and the like. Further, there are complicated dynamics (transfer functions G(S)) between these parameters. Accordingly such a control system becomes complicated. SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide an engine speed controlling apparatus for an internal combustion engine which makes it possible to favorably control the actual engine speed to a targeted engine speed regardless of the operating region of the internal combustion engine, thereby overcoming the above-described drawbacks in the conventional art. With this end, according to the present invention, there is provided an engine speed controlling apparatus for an internal combustion engine with the features according to claim 1. The present invention has been devised in the light of the following aspect. In other words, the variation in parameters's due to a change in an operating point of an internal combustion engine in relation between engine speed and a real manipulated variable linearly approximated about the operating point is ascribable to a change in the gradient of the actual torque acting within the internal combustion engine with respect to the real manipulated variable. In addition, this gradient changes due to a change in the torque or engine speed of the internal combustion engine, but this change is continuous. Accordingly, if a control calculation is made assuming that the gradient is fixed by disregarding the change in the gradient, i.e., assuming that the virtual manipulated variable and the torque are in linear relationships, and if compensation is then performed for the change in the gradient, it is possible to simplify control system design and secure excellent performance in stabilizing the engine speed over the entire run mng region of the internal combustion engine. In accordance with this aspect, in the present invention, assuming that the virtual manipulated variable and the torque are in linear relationships, the virtual manipulated variable is calculated by the calculating means in such a manner that actual engine speed detected by the detecting means becomes a targeted engine speed. Subsequently, the virtual manipulated variable is converted to the real manipulated variable by the converting means by using the actual non-linear relationships between the manipulated variable and the torque. The governing means for governing the engine speed of the internal combustion engine is controlled on the basis of this real manipulated variable. As described above, in accordance with the present invention, since it is assumed that the virtual manipulated variable and torque are in linear relationships, the dynamic relations between the virtual manipulated variable and the engine speed become identical over the entire operating region of the internal combustion engine. Hence, it is possible to obtain an advantage in that parameters of the control calculation are optimized at a certain operating point, and that the control system can therefore be simplified. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a block diagram in accordance with a first embodiment of the present invention; Fig. 2 is a block diagram illustrating the details of a virtual control amount-calculating circuit in accordance with the first embodiment; Fig. 3 is a block diagram of a second embodiment of the present invention; Fig. 4 is a block diagram illustrating the details of the virtual control amount-calculating circuit in accordance with the second embodiment; Fig. 5 is a diagram illustrating a table of a real manipulated variable and a virtual manipulated variable determined in correspondence with the engine speed or a targeted engine speed; Fig. 6 is a diagram explaining the conversion of a virtual manipulated variable to an real manipulated variable; Fig. 7 is a diagram explaining the magnitude of the virtual manipulated variable in cases where the real manipulated variable is restricted; Fig. 8 is a diagram illustrating relationships between the manipulated variable and torque; and Fig. 9 is a block diagram in accordance with a third embodiment of the present invention. DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring now to the accompanying drawings, a detailed description will be given of the preferred embodiments of the present invention. Fig. 1 illustrates a first embodiment in which a load system 12 for absorbing the output of an internal combustion engine 10 is connected to an output shaft of the engine 10. A disk 44 provided with a plurality of slits at equal intervals in a circumferential direction thereof is mounted on a rotating shaft (not shown) of the internal combustion engine 10. A detecting section 46 is constituted in such a manner as to sandwich the disk 44 with a light-emitting device and a light-receiving device. The detecting section 46 is connected to an input interface 24 via an engine speed detector 14. The internal combustion engine 10 is provided with an output governing means 16 for governing the output of the internal combustion engine by controlling the amount of air intake or the amount of fuel injected into a cylinder (in the case of a diesel engine). The output governing means 16 is driven by an actuator 18 such as a stepping motor or the like that is connected to an output interface 42. A lever opening detector 22 for detecting the opening of a lever is connected to a throttle lever 20 which sets the targeted engine speed of the internal combustion engine. The lever opening detector 22 is connected to an input interface 26. The interfaces 24, 26, 42 are connected to a control arithmetic unit 50 constituted by a microcomputer and the like. Alternatively, an arrangement may be provided in such a manner as to detect the throttle opening instead of the lever opening. The control arithmetic unit 50 is provided with an engine speed-calculating circuit 28 for calculating the actual engine speed N on the basis of a signal inputted from the input interface 24. An output terminal of the engine speed-calculating circuit 28 is connected to a deviation calculator 32 and a conversion relationship setter 36 for setting the relationship between a virtual manipulated variable and a real manipulated variable that correspond to the actual engine speed at the present time on the basis of a table shown in Fig. 5. Connected to the input interface 26 is a targeted engine speed-calculating circuit 30 for calculating targeted engine speed N R on the basis of a lever opening ϑ TH inputted via the input interface 26. This targeted engine speed-calculating circuit 30 is connected to the deviation calculator 32. The output terminal of the deviation calculator 32 is connected to a virtual-to-real converting circuit 38 for converting the virtual manipulated variable to the real manipulated variable via a virtual control amount-calculating circuit 34. The virtual-to-real converting circuit 38 is connected to a driving signal-calculating circuit 40 for calculating a driving signal on the basis of a real manipulated variable. The driving signal calculated by the driving signal-calculating circuit 40 is inputted to the actuator 18 via the output interface 42. As shown in Fig. 2, the aforementioned virtual control amount-calculating circuit 34 comprises a first transmitting element 34A for outputting a signal proportional to a deviation in which the actual engine speed N is subtracted from the targeted engine speed N R i.e., a deviation between the output of the targeted engine speed-calculating circuit 30 and the actual engine speed; a second transmitting element 34B for outputting a signal in which an amount proportional to this deviation is totalized at each timing, i.e., for each predetermined time; a third transmitting element 34C for determining a variation of the aforementioned deviation and outputting a signal provided with filtering processing for controlling excess fluctuations in the variation due to noise, a high-frequency engine speed variation and so forth; and an adder 34D for adding the signals from the first to third transmitting elements. A virtual manipulated variable signal is outputted from this adder 34D. A description will now be given of the operation of the first embodiment. The engine speed-calculating circuit 28 outputs the actual engine speed N of the internal combustion engine 10 on the basis of the output of the engine speed detector 14. The targeted engine speed-calculating circuit 30 outputs a signal corresponding to the targeted engine speed N R on the basis of the output of the lever opening detector 22. The deviation calculator 32 calculates a deviation between the targeted engine speed N R and the actual engine speed N. This deviation is subjected to PID processing by the virtual control amount-calculating circuit 34 and is converted to a virtual manipulated variable, and is inputted to the virtual-to-real converting circuit 38. A plurality of tables (see Fig. 5) which illustrate the relationships between the virtual manipulated variable and the real manipulated variable that correspond to each engine speed are stored in advance in the conversion relationship setter 36. Specifically, the conversion relationship setter 36 selects one of the tables illustrating the conversion relationship between the virtual manipulated variable and the real manipulated variable corresponding to the actual engine speed N at the present time outputted from the engine speed-calculating circuit 28, and sets the same in the virtual-to-real converting circuit 38. Here, as shown in Fig. 6, if the engine speed is assumed to be fixed, the real control amount-torque characteristics are non-linear, as indicated by a curve B. For this reason, assuming virtual control amount-torque characteristics to be linear as indicated by straight line A, by converting the real manipulated variable to the virtual manipulated variable on the basis of straight line A and curve B, the relationships between the virtual manipulated variable and the real manipulated variable corresponding to the engine speed that are shown in Fig. 5 are determined. That is, if it is assumed that the virtual manipulated variable is at point a , the torque in terms of the virtual control amount-torque characteristics (on the straight line A) is at point b, and the point in terms of characteristics of the real manipulated variable with the same torque as at point b versus torque is point c. The real manipulated variable corresponding to point c is point d. Accordingly, the real manipulated variable corresponding to the virtual manipulated variable at point a becomes the value of point d. Hence, if the relationships between the virtual manipulated variable and the real manipulated variable are determined by changing the engine speed, the table shown in Fig. 5 can be obtained. In the virtual-to-real converting circuit 38, the virtual manipulated variable calculated by the virtual control amount-calculating circuit 34 is converted to the real manipulated variable on the basis of the relationships between the virtual manipulated variable and the real manipulated variable corresponding to the actual engine speed at the present time which have been set by the conversion relationship setter 36. Then, in the driving signal-calculating circuit 40, a driving signal of the actuator corresponding to the real manipulated variable is determined, and the actuator 18 is controlled via the output interface 42, thereby controlling the output governing means 16. As a result, control is effected in such a manner that even if torque fluctuates due to variations in the load system 12, the actual engine speed becomes the targeted engine speed. In accordance with this embodiment, since the PID control of the virtual control amount-calculating circuit 34 is effected on the basis of the virtual manipulated variable which is in linear relationships with the torque, it becomes unnecessary to change over a control arithmetic expression based on a control amount, so that it is possible to obtain an advantage in that the control arithmetic expression is simplified and controllability is enhanced. Referring now to Fig. 3, a description will be given of a second embodiment of the present invention. In Fig. 3, components that are similar to those of Fig. 1 are denoted by the same reference numerals, and a description thereof will be omitted. As shown in Fig. 3, the targeted engine speed-calculating circuit 30 is connected to the conversion relationship setter 36 so as to set the conversion relationships between the virtual manipulated variable and the real manipulated variable on the basis of the targeted engine speed N R . In addition, a control arithmetic unit 52 for effecting observer plus state feedback control is used instead of the virtual control amount-calculating circuit 34 shown in Fig. 1. In this observer plus state feedback control, dynamics of both virtual manipulated variable and the engine speed are assumed to be a sum of a wasteful time and a secondary delay system (in the case of a gasoline engine), and this sum is expressed by a state equation of the following formula, and a feedback gain in each state is determined by solving Riccati's formula: x = Ax + bu As shown in Fig. 4, the control arithmetic unit 52 comprises a first transmitting element 52A for outputting a signal proportional to a deviation between the targeted engine speed and the actual engine speed; a second transmitting element 52B for outputting a signal in which an amount proportional to this deviation is totalized at each timing; a third transmitting element 52C for estimating an amount of state on the basis of the deviation and the virtual manipulated variable before a timing, i.e., before a unit timing; a fourth transmitting element 52D for outputting a signal proportional to the amount of state estimated by the third transmitting element 52C; a fifth transmitting element 52E for outputting the virtual manipulated variable before the timing; and an adder 52F for adding them. In this second embodiment, a plurality of tables illustrating the relationship between the virtual manipulated variable and the real manipulated variable determined in correspondence with a targeted engine speed, as shown in Fig. 5, are stored in the conversion relationship setter 36 in advance. An appropriate relationship between the virtual manipulated variable and the real manipulated variable corresponding to the targeted engine speed calculated by the targeted engine speed-calculating circuit 30 is selected and is set in the virtual-to-real converting circuit 38. Then, the virtual-to-real converting circuit 38 converts the virtual manipulated variable calculated by the control arithmetic unit 52 to the real manipulated variable, and the output governing means 16 is controlled in the same way as the first embodiment. In accordance with this embodiment, since complicated control such as observer plus state feedback control is effected by the control arithmetic unit, the simplification of values of control calculation by virtue of the virtual manipulated variable becomes more effective than in the case of the first embodiment. In addition, it is possible to obtain an advantage in that controllability is enhanced since the conversion relationships between the virtual manipulated variable and the real manipulated variable are determined in correspondence with the targeted engine speed. Referring now to Fig. 9, a description will be given of a third embodiment of the present invention. In this embodiment, the present invention is applied to controlling the rotation of an internal combustion engine used as a power source such as a generator. For this purpose, the throttle lever 20 for setting the targeted engine speed, the engine speed-calculating circuit 28, and the conversion relationship setter 36 for setting the conversion relationships between the virtual manipulated variable and the real manipulated variable are omitted, and a sole conversion relationship between the virtual manipulated variable and the real manipulated variable that correspond to a predetermined targeted engine speed is set in the virtual-to-real converting circuit 38. A virtual control amount-calculating circuit 54 effects calculation for PID processing referred to in the first embodiment or observer plus state feedback control referred to in the second embodiment. In accordance with this embodiment, a fixed targeted engine speed N R is set in advance, and the relationship between the virtual manipulated variable and the real manipulated variable that correspond to the targeted speed is stored in the virtual-to-real converting circuit 38. In this virtual-to-real converting circuit 38, the virtual manipulated variable calculated by the virtual control amount-calculating circuit 54 is converted to the real manipulated variable, and the output governing means 16 is controlled in the same way as the above-described embodiments. In accordance with this embodiment, the throttle lever for setting the target engine speed, the engine speed-calculating circuit for calculating the targeted engine speed, and the conversion relationship setter for setting the conversion relationships between the virtual manipulated variable and the real manipulated variable corresponding to the engine speed are omitted. Accordingly, advantages can be obtained in that the controlling apparatus is simplified, and that it is readily possible to realize an engine speed controlling apparatus for an internal combustion engine used as a power source for imparting fixed-speed rotation e.g. a generator. A description will now be given of a case where there are limitations to the variation during a fixed time of the output governing means in an internal combustion engine in the first to third embodiments (for instance, limitations due to the response characteristics of the stepping motor). In this case, inconsistency in a control calculation is eliminated by adding the following calculation. That is, as shown in Fig. 7, if a description is given of a case where the virtual manipulated variable before a certain timing is p, the virtual manipulated variable at the present time calculated by the virtual control amount-calculating circuit 34 or 52 is q, and the real manipulated variable corresponding to the respective cases are p' and q' and the variation from p' to q' is restricted by r', a virtual manipulated variable r corresponding to the real manipulated variable r' is determined, and this virtual manipulated variable r is used for calculation at a next timing as the virtual manipulated variable at the present time. It should be noted that although in the foregoing description an explanation has been given of an example in which the real manipulated variable and the like are calculated by using a table, the calculation may be made by means of an expression.

Claims: An engine speed controlling apparatus for an internal combustion engine (10) for controlling an engine speed (N) of an internal combustion engine which has a means (16) for governing engine speed and in which a real manipulated variable of said governing means and torque are in non-linear relationships, said apparatus comprising: detecting means (44, 46, 14) for detecting an actual engine speed; calculating means (32, 34, 52) for calculating a virtual manipulated variable of said governing means on the supposition that said virtual manipulated variable and torque are in linear relationships in such a manner that the actual engine speed (N) becomes a targeted engine speed (NR); converting means (36, 38) for converting the virtual manipulated variable to a real manipulated variable by using the non-linear relationships (B) between the real manipulated variable of said governing means and torque; and controlling means (18) for controlling said governing means on the basis of the so obtained real manipulating variable. An engine speed controlling apparatus for an internal combustion engine according to claim 1, wherein said calculating means (32, 34, 52) calculates the virtual manipulated variable which is in linear relationships with said torque. An engine speed controlling apparatus for an internal combustion engine according to claim 2, wherein said calculating means (32, 34) determines the virtual manipulated variable by a calculation for effecting proportional plus integral plus derivative action control on the basis of a deviation between the actual engine speed and the targeted engine speed. An engine speed controlling apparatus for an internal combustion engine according to claim 2, wherein said calculating means (32, 34) determines the virtual manipulated variable by a calculation for effecting observer plus state feedback control on the basis of a deviation between the actual engine speed (N) and the targeted engine speed (NR). An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 4, wherein said converting means (36, 38) comprises a setting circuit (36) for setting the relationships between the virtual manipulated variable and the real manipulated variable that correspond to one of the actual engine speed (N) at the present time; and a converting circuit (38) for converting to a real manipulated variable the virtual manipulated variable calculated by said calculating means (32, 34) by using the relationships between the virtual manipulated variable and the real manipulated variable set by said setting circuit (36). An engine speed controlling apparatus for an internal combustion engine according to claim 5, wherein said setting circuit (36) sets the relationships between the virtual manipulated variable and the real manipulated variable by selecting a table corresponding to one of the actual engine speed (N) at the present time and the targeted engine speed (NR) at the present time from among a plurality of tables (Fig. 5) showing the relationships between the virtual manipulated variable and the real manipulated variable that correspond to one of the actual engine speed (N) and the targeted engine speed (NR). An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 6, wherein said converting means (36, 38) converts the virtual manipulated variable calculated by said calculating means (32, 52) by using the relationships between the virtual manipulated variable and the real manipulated variable that correspond to a predetermined targeted engine speed (NR). An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 7, wherein said converting means (36, 38) converts the virtual manipulated variable to the real manipulated variable by using the non-linear relationships (B) between the real manipulated variable and the torque and the linear relationships (A) between the virtual manipulated variable and the torque (Fig. 6). An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 7, wherein the relationships between the virtual manipulated variable and the real manipulated variable are determined on the basis of the non-linear relationships (B) between the real manipulated variable and the torque and the linear relationships (A) between the virtual manipulated variable and the torque. An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 7, wherein the relationships between the virtual manipulated variable and the real manipulated variable are determined in such a manner that the magnitude of the real manipulated variable with respect to the virtual manipulated variable becomes smaller as one of the actual engine speed and the targeted engine speed becomes greater. An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 10, wherein said governing means governs the engine speed (N) of said internal combustion engine by governing one of an air intake and an amount of fuel injection. An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 11, further comprising: an opening detecting means (22) for detecting one of an opening of a throttle lever (20) and a throttle opening; and a computing means (30) for computing the targeted engine speed (NR) on the basis of an output (ΘTH) of said opening detecting means (22). An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 12, wherein said calculating means (32, 34) includes a first transmitting element (34A) for outputting a signal proportional to a deviation between the actual engine speed (N) and the targeted engine speed (NR); a second transmitting element (34B) for outputting a signal in which an amount proportional to the deviation is totalized at each timing; a third transmitting element (34C) for determining a variation of the deviation and outputting a signal provided with filtering processing for controlling excess fluctuations in the variation; and an adder (34D) for adding the signals from said first to third transmitting elements. An engine speed controlling apparatus for an internal combustion engine according to any of claims 1 to 12, wherein said calculating means (32, 52) includes a first transmitting element (52A) for outputting a signal proportional to a deviation between the actual engine speed (N) and the targeted engine speed (NR); a second transmitting element (52B) for outputting a signal in which an amount proportional to the deviation is totalized at each timing; a third transmitting element (52C) for estimating an amount of state on the basis of the deviation and the virtual manipulated variable before each unit timing; a fourth transmitting element (52D) for outputting a signal proportional to the amount of state estimated by said third transmitting element (52C); a fifth transmitting element (52E) for outputting the virtual manipulated variable before the unit timing; and an adder (52F) for adding the signals from said first to fifth transmitting elements.

Inventors: KONDO, TAKAHITO, OSAWA, MASATAKA, KONDO, TAKAHITO, C/O KABUSHIKI KAISHA
Applicants: KABUSHIKI KAISHA  TOYODA JIDOSHOKKI SEISAKUSHO, KABUSHIKI KAISHA TOYOTA CHUO KENKYUSHO
Application year: 1990
Main classification: F02D41
IPC codes: F02D45, F02D41, F02D31, F02B1