Abstract:
In a method, a device, a computer program and a computer program product for operating an internal combustion engine having a starter: a first threshold value and a second threshold value are specified; a first variable and a second variable are determined, which characterize the operating state of the internal combustion engine; the first variable is compared to the specified first threshold value and the second variable is compared to the specified second threshold value; and the starter starting, or not starting, the internal combustion engine as a function of the comparison result.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     The present application claims priority to Application No. 10 2008 044 249.6, filed in the Federal Republic of Germany on Dec. 2, 2008, which is expressly incorporated herein in its entirety by reference thereto. 
     BACKGROUND INFORMATION 
     The present invention relates to a method and device for starting an internal combustion engine. 
     BACKGROUND INFORMATION 
     German Published Patent Application No. 10 2006 047 608 describes a device and a method for starting an internal combustion engine, in which a pinion starter starts the internal combustion engine. The pinion starter includes a DC motor having a pinion, which is brought into engagement with a ring gear of the internal combustion engine and, in response to a startup request, cranks the internal combustion engine. The ring gear of the internal combustion engine is usually situated at the crankshaft. Moreover, conventional pinion starters include a so-called solenoid switch, which pulls up an engaging lever that engages the pinion in the ring gear of the internal combustion engine. As soon as the engagement relay has pulled up, a main current path, which supplies the starter with electric power, is automatically closed. This starts the actual cranking process. 
     Prior to the pinion engaging with the ring gear, conventional engine control systems check whether the internal combustion is at a standstill. This effectively reduces negative effects to be expected with respect to the service life of the mechanical subsystem as a result of, for example, thermal and/or mechanical loading of the mechanical subsystems. 
     In the case of current engine control systems, the standstill of the internal combustion engine is determined in that, following a run-down of the engine, for instance, an incremental encoder detects no sweeping gear tooth for a longer period of time, typically 200 ms. This dead time between detecting the standstill of the internal combustion engine and the earliest moment of the renewed startup is too long for comfortable start-stop systems or for direct start systems. 
     SUMMARY 
     According to example embodiments of the present invention, an internal combustion engine having a starter is operated such that: a first threshold value and a second threshold value are specified; a first variable and a second variable are determined, which characterize the operating state of the internal combustion engine; the first variable is compared to the specified first threshold value, and/or the second variable is compared to the specified second threshold value; and the starter starts, or does not start, the internal combustion engine as a function of the comparison result. 
     In this manner a comfortable start-stop or direct start system is realized, in which the start of the internal combustion engine is able to take place even if the internal combustion engine has not yet reached a standstill. The time period between the stop and the renewed start of the internal combustion engine can thereby be reduced from approximately 200 ms to approximately 10 to 100 ms. 
     The starter may start the internal combustion engine only if the first variable undershoots the first specified threshold value or if the second variable undershoots the specified second threshold value. 
     When the first threshold value is not attained, it is ensured that the starter starts the internal combustion only when the internal combustion engine has reached a standstill. When the second threshold value is not attained, it is ensured that the starter starts the internal combustion engine only if the relative rotational speed between the starter and the internal combustion engine or the crankshaft is sufficiently low. This prevents damage to the internal combustion engine or the starter or other mechanical subsystems by thermal and/or mechanical stressing. 
     The specified first threshold value and the specified second threshold value may be selected to be greater than zero. This makes it possible for the starter to start the internal combustion engine already when the internal combustion engine is still in a rotary motion that, as far as the relative rotational speed is concerned, lies below the critical conditions for thermal or mechanical damage. 
     The internal combustion engine may be operated in an operating state in which no combustion takes place. Thus, the starting operation is carried out only if the internal combustion engine is not already in operation. 
     An incremental encoder may be situated on a crankshaft in the internal combustion engine, and a time period may be selected as first variable that elapses after a first gear tooth of the incremental encoder has been detected. The time period that elapses after detection of the first gear tooth of the incremental encoder is an especially reliable variable having fine resolution for evaluating the operating state of the internal combustion engine. In particular, the standstill of the internal combustion engine is detected in an especially simple manner by comparing this variable to a dead time, which is specified as first threshold value. 
     The second variable may be selected as a function of a relative rotational speed, i.e., a difference in the rotational speeds between the starter and the crankshaft. The difference in the rotational speeds between the starter and the crankshaft maximally tolerated in view of thermal or mechanical damage is specified by the manufacturer of the starter or the crankshaft and amounts to 50/min, for instance. Therefore, this variable is especially suitable for evaluating the operating state of the internal combustion engine at a rotational speed other than zero. 
     The first specified threshold value may be selected as a function of a rotational speed of the crankshaft and/or a position of the crankshaft, in particular between 10 ms and 100 ms. The rotational speed of the crankshaft and/or the position of the crankshaft determine(s) the length of the time period that elapses while a magnet wheel of the incremental encoder moves through an angular range between two consecutive gear teeth of the magnet wheel. For example, the time period becomes longer with decreasing rotational speed. Moreover, in the case of a magnet wheel for which one or a plurality of tooth gaps is provided, the time period also changes as a function of the position of the crankshaft, since the time period for moving through the angular ranges of the tooth gap are longer. Taking this dependency into account ensures a very reliable detection of the standstill of the internal combustion engine with a very fine resolution. 
     A third variable may be determined as a function of the time interval between the detection of two consecutive gear teeth of the incremental encoder, and the first specified threshold value may be determined as a function of at least two values of the third variable, especially by extrapolation, using an approximation function of the first and/or second order, in particular. On this basis, a simple inference is made with regard to the time interval to be expected until the detection of the next gear tooth, based on the time interval between the detection of two consecutive gear teeth in the past, by extrapolation using the approximation function. The time interval to be expected lies in a range between the result of the linear extrapolation and the quadratic extrapolation. The use of an approximation function of the first and/or second order permits an efficient implementation in a control device. This spares the computing resources while providing sufficient accuracy. 
     The first specified threshold may be selected as a function of the larger value of the two results from the extrapolation, using the approximation function of the first and second order. Because of this maximum value generation, the first specified threshold value is selected such that it is always the longer expected interval that is selected, both for a convex tooth period characteristic (traveling through a low point) and also for a concave tooth period characteristic (traveling through a high point). This ensures that a standstill is not detected prematurely. 
     The first specified threshold value may be corrected as a function of a tolerance factor. By additionally taking a tolerance factor into account, it is possible to compensate for additional imprecisions arising from the approximation function or from tolerances in the signal acquisition. The time interval thus obtained is then able to be used as the new first specified threshold value. 
     The second specified threshold value may be selected as a function of the mechanical loading capacity of the starter and/or the crankshaft. The maximum mechanical loading capacity of the starter and/or the crankshaft is specified by the manufacturer of these components, for instance. Through the selection of the specified second threshold value the difference in the rotational speeds between the starter and the crankshaft is kept low enough to avoid damage during the startup of the internal combustion engine. For example, the difference in the rotational speed amounts to 50/min. 
     A check may take place as to whether a start has been requested before operating the starter. This excludes the possibility that the starter starts the internal combustion engine when the first threshold or the second threshold is undershot, although, for instance, no start was requested by the driver of a vehicle in which the internal combustion engine has been installed. An undesired startup of the internal combustion engine is therefore prevented in a reliable manner. 
     The starter may be a pinion starter. A pinion starter is a particularly effective and easily implementable mechanical component, which is suitable for start-stop and direct start methods, in particular. 
     Exemplary embodiments of the present invention are described below in more detail with reference to the appended Figures. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  schematically illustrates an internal combustion engine. 
         FIG. 2  is a flow chart of a method according to an example embodiment of the present invention. 
         FIG. 3  is a diagram of a time characteristic of performance quantities of the internal combustion engine. 
     
    
    
     DETAILED DESCRIPTION 
     In  FIG. 1 , an internal combustion engine is shown schematically and denoted by  100 . Internal combustion engine  100  includes a cylinder  101  and a piston  102 , which enclose a combustion chamber  103 . 
     Fresh air is introduced into combustion chamber  103  through an intake manifold  104  via an intake valve  105 . In addition, fuel is introduced into combustion chamber  103  via a fuel injector  106 . 
     A fuel/air mixture produced in combustion chamber  103  in this manner is ignited by a spark plug  107 , for example. A thermal energy generated in combustion chamber  103  by the combustion of the fuel/air mixture is at least partially converted into mechanical energy by piston  102 . The resulting downward motion of piston  102  inside cylinder  101  is converted into a rotary motion of a crankshaft  109  via a connecting rod  108 . Piston  102  travels from top dead center OT to bottom dead center UT inside cylinder  101 . 
     In an upward movement of piston  102  ensuing after the fuel/air mixture has combusted, a discharge valve  110  expels exhaust gas produced by the combustion into an exhaust pipe  111 . 
       FIG. 1  describes internal combustion engine  100  using the example of a four-stroke Otto engine having externally supplied ignition and direct injection. However, the method and the device hereof are analogously applicable to other internal combustion engines as well, such as two-stroke combustion engines or internal combustion engines having intake manifold injection, and also to Diesel engines. For reasons of clarity, only one cylinder  101  of internal combustion engine  100  is shown in  FIG. 1 . The device and the method are used in analogous manner for multi-cylinder internal combustion engines. 
     The control of intake valve  105  and discharge valve  110  is carried out in, e.g., a conventional manner, for instance via a camshaft not illustrated in  FIG. 1 . As an alternative, a variable valve drive may be employed as well. 
     The control of fuel injector  106  and spark plug  107  is implemented, e.g., in a conventional manner, for instance with the aid of an engine control device. This procedure will not be discussed here in greater detail. 
     An incremental encoder  112 , which induces an electrical signal with the aid of, for example, a magnet wheel  113 , is disposed on crankshaft  109 . The direction of rotation may also be determined, e.g., in a conventional manner, with the aid of an intelligent speed sensor, for example. Magnet wheel  113  is developed as toothed wheel having 60/2 teeth, for example. This means that magnet wheel  113 , and thus the position of crankshaft  109 , is subdivided into 60 angular segment of equal size, each representing a 6° arc of crankshaft rotation. 
     Magnet wheel  113  is coded by a tooth gap, i.e., two missing teeth, such that top dead center OT of piston  102  is attained when, for instance, two falling flanks of an electric signal were detected after a detected tooth gap, and a 72° arc of crankshaft rotation has passed in addition. 
     The method is used in analogous manner also for other codings of the magnet wheel. The method and the device may also be used for other incremental encoders  112  which do not operate according to the magnet principle. For example, it is possible to use incremental encoders  112  that utilize imaging measuring principles with the aid of a light source and photo-optical components. 
     Furthermore, an electric motor  114 , which is connected to a pinion  116  via a shaft  115 , is situated inside internal combustion engine  100 . Electric motor  114 , shaft  115 , and pinion  116  are part of a pinion starter, which is brought into engagement with a ring gear  117  permanently joined to crankshaft  109  for the startup of internal combustion engine. A solenoid switch is actuated for this purpose, which pulls up an engaging lever, thereby bringing pinion  116  into engagement with ring gear  117 . 
     Instead of the pinion starter shown in  FIG. 1 , it is also possible to utilize other starters. The method and the device are used in analogous manner in those instances as well. 
       FIG. 1  shows a control device  120 , which has a first setpoint selection device  121 , a second setpoint selection device  122 , a first determination device  123 , a second determination device  124 , a comparator  125 , and a third setpoint selection device  126 . 
     From the signal of the incremental encoder  112 , first determination device  123  determines a first variable, which is also referred to as tooth period TZ in the following text. Tooth period TZ is a time period representing the time interval between the detection of two consecutive teeth of incremental encoder  112 . This tooth period TZ is determined in the known manner, for instance from the intervals of two falling flanks of a voltage signal of incremental encoder  112 . Control device  120  has a clock generator for this purpose, which is not shown in  FIG. 1  and which provides information about the elapsed time to first determination device  123 . First determination device  123  transmits tooth period TZ to comparator  125  and to first setpoint selection device  121 . 
     Second determination device determines engine speed n of the internal combustion engine from the signal of incremental encoder  112 , in the usual manner. For this purpose, tooth periods TZ, for instance, are determined in the same manner as in first determination device  123 , whereupon an average tooth period TZ is determined by forming an average value. For a 60-2 magnet wheel, the rotational speed, in rotations per minute, then directly results as inverse value of the average value of tooth periods TZ. Moreover, in a conventional manner, it is monitored whether internal combustion engine  100  is in a reverse pendular motion. No engine speed n will be determined if this is the case, but the engine speed signal is set to an invalid value, for example. Second determination device  124  then compares the engine speed of internal combustion engine  100  to the engine speed of electric motor  114 . Since electric motor  114  is controlled by control device  120  with the aid of third setpoint selection device  126 , the engine speed of electric motor  114  is formed in a conventional manner, by modeling, from the control signal for electric motor  114 . It is assumed, for instance, that the engine speed of electric motor  114  corresponds to the setpoint engine speed. To this end, second determination device  124  receives the setpoint engine speed from third setpoint selection device  126 . As an alternative, an additional incremental encoder and an additional determination device may be provided, with whose aid the engine speed of electric motor  114  is determined. The engine speed of electric motor  114  typically corresponds to the rotational speed of pinion  116 . 
     As a second variable, second determination device  124  determines the difference between the engine speed of internal combustion engine  100  and the engine speed of electric motor  114  and in this manner determines the relative rotational speed or the rotational speed difference between the starter and the crankshaft. The difference in the rotational speeds between the starter and the crankshaft is transmitted to comparator  125  by second determination device  124 . 
     First setpoint selection device  121  specifies a first threshold value. The first specified threshold value is also referred to as dead time in the following text. 
     The first specified threshold value is selected as a function of the rotational speed of the crankshaft and/or a position of the crankshaft, for instance between 10 ms and 100 ms. A third variable is determined for this purpose as a function of the time interval between the detection of two consecutive teeth of magnet wheel  113 . It is determined by first determination device  123  as tooth time TZ and transmitted to first setpoint selection device  121 . Using three values of the third variable, or tooth period TZ, an inference as to the expected time interval until incremental encoder  112  detects the next tooth is then made via extrapolation with the aid of an approximation function. To this end, a first result is determined from an approximation function of the first order, and a second result from an approximation function of the second order. The approximation function of the first order is a linear function, for instance. For example, a straight line is selected that runs approximately through the last three detected tooth periods TZ. A square function, which is defined by the last three values of tooth periods TZ, for instance, is selected as approximation function of the second order, for example. 
     For storing the data, a memory is provided in control device  120 , in which individual tooth periods TZ are stored until the approximation function is calculated. For a function of the second order, for example, the three last tooth periods TZ are stored in the memory. It is provided that any new tooth period TZ replaces the oldest tooth period TZ in the memory. Provided sufficient memory and computing capacity are available, additional past values of tooth periods TZ may be taken into account as well. Given sufficient computing resources, it is also possible to determine only one approximation function, e.g., with the aid of a least-square approximation method. In this case, the first specified threshold value is determined as a function of the result of the extrapolation, using this one approximation function.  FIG. 3  shows a first time characteristic  301  of tooth periods TZ above advancing time  5 . Moreover, a second time characteristic  302  of a variable that is proportional to kinetic energy E of internal combustion engine  100  is shown in  FIG. 3 . Because of friction and the lack of new energy input through combustion, kinetic energy E decreases strongly when internal combustion engine  100  is running down. Furthermore, kinetic energy E is defined by the effective mass moment of inertia of crankshaft  109  of piston  102  of connecting rod  108  and possibly a dual-mass flywheel as well as other variables. The angular velocity of this rotating system is defined by its kinetic energy E. The relationship between kinetic energy E and the angular velocity or tooth periods TZ is shown in  FIG. 3 . 
     The run-down of internal combustion engine  100  starts with the end of the combustion of the fuel-air mixture inside combustion chamber  103 . Engine speed n of internal combustion engine  100  then decreases, which corresponds to a prolongation of tooth periods TZ. At very slow engine speeds n, e.g., 150 rotations per minute, the mechanical system made up of piston  102 , connecting rod  108 , crankshaft  109  and flywheel, begins a pendular motion. This pendular motion is due to the fact that kinetic energy E of the not fired internal combustion engine  100  is no longer sufficient to move the piston beyond top dead center OT. If kinetic energy E is insufficient to move the piston beyond top dead center OT, then a reverse pendular motion arises, which takes place between return point U 1  and a second return point U 2  in  FIG. 3  and is denoted by R. During this reverse pendular motion R, crankshaft  109  moves counter to the direction of rotation that prevails during fired operation of internal combustion engine  100 . In the reverse pendular motion, the energy of the compressed air in the cylinder (gas spring) is converted into mechanical energy. 
     Tooth periods TZ arising during the run-down of internal combustion engine  100  are illustrated in the form of points in  FIG. 3  on first time characteristic  301 . The connecting lines between the pints represent an approximation function of the second order, for instance, for tooth periods TZ. The tooth gap of magnetic wheel  113  is denoted by L in  FIG. 3 . 
     First time characteristic  301  of tooth periods TZ is subdivided into five consecutive ranges after first return point U 1 . A first range  303  denotes an interval during which crankshaft  109  is in an accelerated state of motion. This means that expected next tooth period TZ must be less than last tooth periods TZ currently available in the memory. First range  303  ends where consecutive tooth periods TZ differ only negligibly. 
     Range  304  following first range  303  includes the interval of a slowly decelerating state of motion. In this second range  304 , expected tooth period TZ, and thus also the dead time, is selected larger than instantaneously available tooth periods TZ. 
     The same applies to a third range  305 , which follows second range  304 . Second range  304  and third range  305  differ in that the difference between currently available tooth period TZ and tooth period TZ to be expected is considerably larger in third range  305  than in second range  304 . 
     A fourth range  306 , which follows third range  305 , corresponds to first range  303  as far as expected tooth period TZ is concerned, since a deceleration of crankshaft  109  is also expected in fourth range  306 . 
     Fifth range  307 , which follows fourth range  305 , corresponds to second range  304  with regard to expected tooth period TZ because a slow deceleration of crankshaft  109  is to be expected here, too. 
     The subdivision into ranges of different accelerations of crankshaft  109  is continued periodically for as long as internal combustion engine  100  is still in pendular motion during the run-down. Time characteristic  301  of the tooth periods is also subdividable into concave ranges and convex ranges. The concave and convex ranges alternately follow each other at points of inflection. The concave range is characterized by a low point, the convex range by a high point. 
     The differentiation of the ranges is meant to improve the approximation function and the extrapolation of the dead time. For instance, by comparing stored tooth periods TZ, first setpoint input device  121  ascertains in which range of first time characteristic internal combustion engine  100  happens to be. Depending on the range, the safety offset and the increment of the approximation method, for instance, are then adapted. 
     The quadratic extrapolation tends to supply excessive expected tooth periods in the concave case. The linear extrapolation tends to supply tooth periods that are too small in this case. Thus, both extrapolation methods define the range in which the expected tooth period will lie. The increments of the approximation method in the extrapolation are equal to the time interval between the two most recently detected tooth periods TZ, for instance. 
     Then the first specified threshold value, i.e., the dead time, is determined as a function of three values of the third variable. For the reliable detection of the standstill, for example, the dead time is used as maximum value of the two results from the linear and quadratic extrapolation. This avoids a too rapid detection of the standstill both for the convex and the concave case. Another selection, e.g., a weighted average value generation, is possible as well. 
     To be able to tolerate inaccuracies that result from the use of the approximation function, for instance, a safety offset, such as an additive term of 0.001 seconds per 6° arc of crankshaft rotation [S/6° CR], is added to the result of the extrapolation in addition. The value of the safety offset differs according to the range, for instance, and is adapted in an application. Then, first setpoint specification device  121  transmits the dead time to comparator  125 . 
     Second setpoint specification device  122  outputs as specified second threshold value a relative rotational speed between the starter or electric motor  114  and crankshaft  109 , which must be undershot before the engagement operation, i.e., the renewed startup of internal combustion engine  100 , may take place by the starter. The relative rotational speed is specified by, for example, the manufacturer of the mechanical subsystems, e.g., pinion  116  and/or ring gear  117 . The relative rotational speed amounts to approximately 
             20   ⁢           ⁢     ms     6   ⁢   °   ⁢           ⁢   C   ⁢           ⁢   A             
rotations per minute, for instance. The second specified threshold value is transmitted from second setpoint-specification device  122  to comparator  125 .
 
     Comparator  125  compares the first specified threshold value to the first variable, and/or the second specified threshold value to the second variable. 
     This means that comparator  125  uses the first variable to determine whether crankshaft  109  is already at rest, i.e., whether the time period that has elapsed since incremental encoder  112  detected the last tooth is greater than the dead time to be expected until the detection of the next tooth. This is the case especially when no information about the rotational speed of internal combustion engine  100  is available any longer because crankshaft  109  is in reverse-pendular motion R, for instance. 
     Comparator  125  also checks whether relative rotational speed R between starter or electric motor  114  and crankshaft  109  is smaller than the second specified threshold value. 
     If comparator unit  125  detects that internal combustion engine  100  is at standstill or that the relative rotational speed between the starter and crankshaft  109  is small enough, comparator  125  transmits a release signal to third setpoint specification device  126 . 
     Typically, it is first checked whether the relative speed is small enough. If this is impossible because of missing information regarding the rotational speed, then it is checked whether internal combustion engine  100  is standing still. To this end, comparator  125  checks whether the rotational speed signal has a valid value. 
     Third setpoint specification device  126  controls electric motor  114  as a function of the release signal. For example, third setpoint-specification device  126  triggers electric motor  114  by a current when the starting operation has been enabled. For this, it is checked, for one, whether the release signal from comparator  125  enables the starting operation. For another, in a vehicle, for instance, it is checked whether a driver request for a renewed startup of internal combustion engine  100  has been received. An electrical signal from a start button installed in the vehicle, for example, is transmitted to third setpoint specification device  126  as startup request. In this case, electric motor  114  is triggered by third setpoint specification device  126  only if the start button is depressed or a corresponding electric signal is applied. As an alternative, the signal from a driving pedal is monitored and the startup request is detected when the driver depresses the driving pedal. 
       FIG. 2  shows a flow chart of a method according to an example embodiment of the present invention. 
     The method is started in a step  200  as soon as internal combustion engine  100  transitions from the fired operating state into a first, non-fired operating state. 
     In step  200 , engine speed n of internal combustion engine  100  is determined in the usual manner. Then a step  201  is executed. 
     In step  201  it is checked whether a valid value was transmitted for engine speed n of internal combustion engine  100 . If engine speed n of internal combustion engine  100  was determined in a valid manner, then branching to a step  202  takes place. Otherwise, the method branches to a step  203 . 
     In step  202 , the second specified threshold value in input, i.e., the maximally permitted relative rotational speed between starter and crankshaft  109 . Then a step  204  is executed. 
     In step  204 , the rotational speed of the starter is determined, e.g., in a conventional, for example from a model of the starter. As an alternative, the rotational speed of the starter is measured by an incremental encoder, for example, at electric motor  114 . Then a step  205  is executed. 
     In step  205 , the difference between the rotational speed of the starter and engine speed n of internal combustion engine  100  is determined. Then a step  206  is executed. 
     In step  206 , it is checked whether the second specified threshold value is greater than the difference between the rotational speed of the starter and engine speed n of internal combustion engine  100 . If the difference between the rotational speed of the starter and engine speed n of internal combustion engine  100  is smaller than the second specified threshold value, then a step  207  is executed. Otherwise a step  208  is executed. 
     In step  207 , a release signal is generated. For example, one bit is set to the value 1. Then a step  220  is executed. 
     In step  208 , the release signal is reset. For example, the bit is set to the value 0. Then a step  220  is executed. 
     In step  203 , the dead time that may elapse before the next tooth of magnet wheel  113  is detected by a new pulse, e.g., a falling flank of the voltage signal of incremental encoder  112 . For instance, the dead time is determined from the approximation function as a function of tooth periods TZ by the described linear and/or quadratic extrapolation or by the least-square method. Then a step  209  is executed. 
     In step  209 , the time is determined that has elapsed since the last tooth was detected. Then a step  210  is executed. 
     In step  210 , it is checked whether the time that elapsed since the last tooth was detected is less than the dead period. If the time period that has elapsed since the last tooth is less than the dead period, then a step  211  is executed. Otherwise a step  212  is executed. 
     In step  211 , it is checked whether a new tooth has been detected. If no new tooth was detected, branching to step  209  takes place. Otherwise the program branches to step  213 . 
     In step  213 , the release signal is reset. For example, the bit is set to the value 0. Then a step  220  is executed. 
     In step  212 , the release signal is set. For example, the bit is set to the value 1. Then step  220  is executed. 
     In step  220 , it is checked whether a start request of the internal combustion engine is present. For this purpose, it is checked, for instance, whether the signal of a start button in a motor vehicle has a value that corresponds to the start request. If a start request for internal combustion engine  100  is present, then a step  221  is executed. Otherwise step  200  is executed. 
     In step  221 , the internal combustion engine is started in the known manner. Then the method is terminated. 
     In addition, the method is terminated at various other times, for example if the driver of the motor vehicle deactivates control device  120 .