Disclosed herein is a method of predicting engine knocking, which includes calculating initial pressure in cylinder based on operating data and pressure in intake manifold measured using manifold absolute pressure sensor, calculating pressure at spark timing in the cylinder by interpreting compression process as polytropic process based on the calculated initial pressure in the cylinder, calculating heat release rate for individual operating conditions based on the calculated pressure in the cylinder at spark timing, calculating pressure change in the cylinder based on the calculated heat release rate, calculating unburned gas temperature in adiabatic compression process based on the calculated pressure change in the cylinder, and determining whether knock occurs by calculating ignition delay based on the calculated unburned gas temperature and calculating unburned gas mass fraction at crank angle at the end of the ignition delay.

A method for operating an internal combustion engine having an injection system which has a high-pressure accumulator, high pressure in the high-pressure accumulator being controlled via a suction throttle on the low-pressure side, acting as a first pressure control element in a first high-pressure control loop. During normal operation, a high-pressure disturbance variable is produced by a pressure regulating valve on the high-pressure side, acting as an additional pressure control element, via which fuel is re-directed from the high-pressure accumulator into a fuel reservoir, the at least one pressure regulating valve being controlled, during normal operation, based on a set volumetric flow rate for the fuel to be re-directed. A temporal development of the set volumetric rate is sensed and the set volumetric flow rate is filtered, a time constant for the filtering of the set volumetric flow rate being selected as a function of the sensed temporal development.

A method for determining a combination of an actual intake camshaft phase position of an intake camshaft and an actual exhaust camshaft phase position of an exhaust camshaft of a production internal combustion engine having at least one cylinder, wherein the method is performed in operation of the production internal combustion engine and the relevant actual phase position of the camshafts is determined in relation to an operating point of the production internal combustion engine.

A method for controlling and/or regulating an exhaust gas turbocharger of an internal combustion engine, the exhaust gas turbocharger being protected against an exceeding of a maximum rotational speed, an actual boost pressure being compared with a setpoint boost pressure. The risk of a maximum rotational speed of the exhaust gas turbocharger being exceeded is prevented in that a manipulated variable assigned to the exhaust gas turbocharger is compared with a manipulated variable limit characteristic and is limited, if necessary, the manipulated variable limit characteristic having a time-limited, first portion and a chronologically subsequent, second portion following a change in the setpoint boost pressure, the first portion ending after a predetermined target time, the second portion of the manipulated variable limit characteristic being reduced with respect to the first portion in such a way that the maximum rotational speed of the exhaust gas turbocharger is not reached.

A method for controlling an air-cooled internal combustion engine (ICE) of a motor vehicle controlled by an electronic control unit, includes: activating the electronic control unit; zeroing stored values of temperature of the ICE and the filtered filtering coefficient; in one iteration, —determining whether the ICE is operating, determining a filtering coefficient and a temperature setpoint, —determining a filtered filtering coefficient based on the filtering coefficient and the stored filtered filtering coefficient value, —determining temperature of the ICE according to the coefficient, temperature setpoint and stored temperature of the ICE, —determining whether the ICE is moving and whether the difference between engine temperature and admitted air temperature is below a threshold, ⋅ if not, storing the filtered filtering coefficient and the temperature of the ICE, then beginning a new iteration, and ⋅ if so, transmitting a signal authorizing the shutdown of the electronic control unit.

An example engine system is disclosed. The engine system may control a turbocharger of an internal combustion engine, and more particularly control a boost pressure provided by a turbocharger to an internal combustion engine. An example method for controlling a boost pressure provided by a turbocharger may include receiving a boost pressure demand and identifying a compressor speed demand to achieve the received boost pressure demand. The method may also include converting the compressor speed demand into a kinetic energy demand of the turbocharger rotating components and controlling the kinetic energy of the turbocharger rotating components to meet the kinetic energy demand by controlling power supplied by the turbine and the electric motor assist.

Aspects of the present invention relate to a control advanced system for controlling a valve actuator for an internal combustion engine, the control system comprising one or more controllers, the control system being configured to: receive a requirement signal retarded indicative of a requirement for valve actuation with a first valve timing characteristic; receive an expected flow signal indicative of expected mass flow rate of air, associated with the first valve timing characteristic; control the valve actuator to provide the first valve timing characteristic; receive an actual flow signal indicative of actual mass flow rate of air, associated with the control of the valve actuator; cause comparison of the actual flow signal with the expected flow signal; and cause an action to be performed in dependence on the comparison, wherein the action comprises a compensation action and/or a fault reporting action and/or determining camshaft phase information.

An injector diagnosis device 1 includes: an engine sound model generator 14 configured to generate a normal engine sound model and an abnormal engine sound model based on the number of cylinders of the engine and a combustion pattern of the engine; an operating sound obtainment unit 12 configured to obtain the operating sound of the engine operating with the combustion pattern; a frequency characteristics calculation unit 13 configured to calculate the frequency characteristics of the operating sound obtained by the operating sound obtainment unit 12; and an injector diagnosis unit 15 configured to diagnose whether or not the injectors have a failure based on the frequency characteristics of the operating sound which is calculated by the frequency characteristics calculation unit 13, and the normal engine sound model and the abnormal engine sound model which is generated by the engine sound model generator 14.

A computer-implemented method for ascertaining a closure point in time of an injector of an internal combustion engine using a classifier. The method includes: ascertaining a time series of input signals, each corresponding to a point in time within the time series, and each characterizing a deformation of the injector; ascertaining a plurality of first values using the classifier based on the time series, in each case a first value corresponding to a point in time of the time series, and the first value characterizing a probability that the closure point in time of the injector matches the point in time; ascertaining a plurality of second values, each being a sum of neighboring first values, of a first value and the first value, the second value corresponding to the point in time to which the first value corresponds; ascertaining the closure point in time based on the largest second value.

The invention relates to a method for operating an internal combustion engine (100) having an exhaust-gas turbocharger (5, 10, 15) for compressing the air fed to the internal combustion engine (100), wherein a drive power of a turbine (10) of the exhaust-gas turbocharger (5, 10, 15) in an exhaust tract (20) of the internal combustion engine (100) is changed through variation of a turbine geometry of the turbine (10), wherein, in a first control algorithm (I), a setpoint charge pressure (pL.sub.Soll) at the outlet of the compressor (5) of the exhaust-gas turbocharger (5, 10, 15) in the air feed tract (50) upstream of the combustion motor (55) is controlled in a manner dependent on a setpoint exhaust-gas back pressure (pT1.sub.Soll) to be set in an exhaust tract (20) downstream of the combustion motor (55) upstream of the turbine (10) of the internal combustion engine (100), wherein the setpoint charge pressure (pL.sub.Soll) is assigned an opening cross-sectional area of the turbine (10), which is controlled, by means of an actuating stroke of an actuating element (25) assigned to the turbine (10), in a manner dependent on a setpoint value (25.sub.Soll) assigned to the predefined setpoint charge pressure (pL.sub.Soll). According to the invention, provision is made for the actuating element (25), which is actuated by means of the first control algorithm (I), of the turbine (10) to be controlled by means of a second control algorithm (II), with predefinition of an upper threshold value of the setpoint exhaust-gas back pressure (pT.sub.1Soll) in the exhaust tract (20) upstream of the turbine (10) by intervention into the first control algorithm (I) with an adapted setpoint value (25′.sub.Soll), if, in a primary control path a) of the second control algorithm (II), a control deviation (ΔpT) upstream of the turbine (10) arises which is formed from an actual exhaust-gas back pressure (pT.sub.1lst) upstream of the turbine (10) and the predefined setpoint exhaust-gas back pressure (pT.sub.1Soll) upstream of the turbine (10), and, in a secondary control path b) of the second control algorithm (II), a control deviation (ΔpL) downstream of the compressor (5) arises which is formed from an actual charge pressure (pL.sub.lst) of the compressor (5) and the setpoint charge pressure (pL.sub.Soll) at the outlet of the compressor (5).