EP2321522A1

EP2321522A1 - Method for engaging a starting gear pinion of a starter device in a ring gear of an internal combustion engine

Info

Publication number: EP2321522A1
Application number: EP09781230A
Authority: EP
Inventors: Sven Hartmann; Juergen Gross
Original assignee: Robert Bosch GmbH
Current assignee: SEG Automotive Germany GmbH
Priority date: 2008-08-01
Filing date: 2009-07-29
Publication date: 2011-05-18
Anticipated expiration: 2029-07-29
Also published as: HUE050273T2; EP2321522B1; DE102008040945B4; DE102008040945A1; US9169819B2; US20120024253A1; WO2010012764A1

Abstract

Method for engaging a starting gear pinion (22) of a starter device (10) in a gear ring (25) of an internal combustion engine (20), wherein the starting pinion (22) has a circumferential speed (vR), and the ring gear (25) has a circumferential speed (vZK), wherein the starting pinion (22) engages axially along its rotational axis (276), wherein the starting pinion (22) makes contact with the ring gear (25) with a circumferential speed (vR) which is lower than the circumferential speed (vZK) of the ring gear (25).

Description

description

title

Method for engaging a starting pinion of a starting device in a ring gear of an internal combustion engine

State of the art

From the German patent application DE 2006 011 644 Al a method is known how two moving gears of a starting device and an internal combustion engine (pinion and ring gear) are to be brought into each other in the dynamic case. There is already described the case that the pinion in the so-called phasing out of the internal combustion engine ne in the ring gear of the internal combustion engine to be eingespurt. The object of the method disclosed therein is that a meshing of the pinion in the sprocket should take place at substantially the same circumferential speed of both gear parts.

In contrast, it is provided that a meshing of the pinion in the sprocket of the starting device is achieved by consciously and conditionally achieved by technical means that the starting pinion contacts the ring gear with a peripheral speed, which is smaller than the peripheral speed of the ring gear. This has the advantage that the engagement of the pinion in the ring gear as in the conventional case of engagement of a pinion of an ordinary starter can run into the sprocket. The conventional engagement process causes relatively low wear under normal conditions, which is particularly desirable in a vehicle having a start-stop system. For example, in a vehicle with a start-stop system, the number of starts compared to vehicles with a conventional start system is up to ten times higher. Against this background, it is particularly desirable to enable a low-wear meshing in a start-stop system. Disclosure of the invention

advantages

The method according to the invention with the features of the main claim has the advantage that when a Andrehritzels in the ring gear of an internal combustion engine meshing speed ratios are present, which lead to a relatively gentle, d. H. low-wear meshing a Andrehritzels is made possible in the sprocket.

According to a variant of the invention it is provided that the peripheral speed of the ring gear is not equal to zero when the starter pinion contacts the ring gear at a circumferential speed. In particular, in the event that the starter pinion is actively rotated for meshing, it is provided that the peripheral speed of the starter pinion is not equal to zero in order to achieve the particular intended kinematic and kinetic conditions.

The method is particularly reliable when the peripheral speeds of the sprocket and the Andrehritzels are oriented at their common point of engagement in the same direction. This means, for example, in the event that the sprocket and the starting pinion are each designed as externally toothed spur gears that move in opposite direction of rotation.

With regard to the different peripheral speeds of sprocket and starter pinion, it has been found by extensive experiments that special conditions should apply with regard to the peripheral speeds. Thus, it is provided that the peripheral speed of the ring gear at the moment of first contacting with the starter pinion or contacting the pinwheel with the ring gear, the peripheral speed of the ring gear maximally formed by a value of the product of 5 meters per second per millimeter and the module of the ring gear in millimeters larger and minimally larger than the peripheral speed of the Andrehritzels. The reliability of the method can be increased by the starter having a pinion shaft which drives the starter pinion, wherein acts between the starter pinion and the pinion shaft in the direction of its axis of rotation a spring force of a spring element, wherein by contacting the Andrehritzels with the ring gear, the spring element is compressed , The reliability of the system is not only improved by the resilient or elastic properties, but at the same time by the associated Dämp- tion processes, for example, caused by the friction of the spring with their counter bearings or any flow damping.

For the process is also important that the starter pinion is vorgespurt timely to the sprocket and timely achieved as intended high peripheral speed. Accordingly, it is important that a switching criterion is recognized by a control unit and the starting pinion is then pre-loaded in one step in the direction of the ring gear and rotated in another step, wherein the prevailing on the starter pinion peripheral speed when reaching the ring gear than the Circumferential speed of the ring gear is. These measures can ensure that the pinion contacts the ring gear at the right moment with a suitable property. It is initially irrelevant which switching criterion is used here. It is also irrelevant which control unit recognizes the switching criterion.

Thus, the switching criterion may be a signal which corresponds to a desire for switching off the internal combustion engine. The desire for switching off the internal combustion engine may be due, for example, to the fact that the speed of the vehicle is zero and / or the drive train is open or the vehicle speed is below a low speed threshold, for example <7 h / km. Another switching criterion may be, for example, a signal which corresponds to a speed characteristic of the ring gear of the internal combustion engine. A speed property of the ring gear would be, for example, the angular velocity of the ring gear or the change in the angular velocity of the ring gear, for example below a certain speed threshold, from which an upcoming standstill of the internal combustion engine can be derived. Such a characteristic could indicate that the internal combustion engine should be switched off (eg automatic swing automatic transmission). It is provided that, based on the switching criterion, a time is calculated, in addition, the starting device is activated. So z. B. defined that in the event that the internal combustion engine reaches a speed below 600 / min, the starting device is activated (turning the Andrehritzels, toads of Andrehritzels) to at a suitable time, the starter pinion with the appropriate property with the sprocket to contact. - A -

With regard to the method, it is particularly provided that the starting pinion is first set in rotation in one step and then pre-tapped in one step to the ring gear.

drawings

In the drawings, an embodiment of the method according to the invention is shown. Show it:

1 shows a starting device and a detail of an internal combustion engine with sprocket, Figure 2 is a schematic diagram of the system of internal combustion engine, starting device and control devices in a first embodiment,

FIG. 3 shows a schematic representation of the speed relationships at the time of the first contacting of the starting pinion on the sprocket,

FIG. 4 shows the sequence of the method on the basis of a few snapshots of situations during the course of the procedure up to cranking,

Embodiments of the invention

FIG. 1 shows an electrical machine 10 (starting device) in a longitudinal section. This electric machine 10 has, for example, an electric motor 13 (starter motor) and a pusher 16. The electric motor 13 and the pusher 16 are fixed to a common drive end plate 19. The electric motor 13 functions, for example, to drive a starting pinion 22 when it is meshed in the ring gear 25 of the internal combustion engine, not shown here.

The electric motor 13 has, as a housing 11, a pole tube 28, which carries pole shoes 31 on its inner circumference, which are each wound by an exciting coil 300, which is part of an exciter winding 34. The pole shoes 31 in turn surround an armature 37, which has an armature packet 43 constructed from fins 40 and an armature winding 49 arranged in grooves 46. The armature package 43 is pressed onto a drive shaft 44. At the end of the drive shaft 44 facing away from the starting pinion 22, a commutator 52 is further attached, which is constructed, inter alia, of individual commutator bars 55. The commutator fins 55 are electrically connected in a known manner to the armature winding 49 in such a way that when the commutator fins 55 are energized by brushes 58 results in a rotational movement of the armature 37 in the pole tube 28. A power supply 61 supplied in the on state, both the carbon brushes 58 and the field winding 34 with power. The drive shaft 44 is commutator side supported with a shaft journal 64 in a sliding bearing 67, which in turn is held stationary in a commutator bearing cover 70. The commutator 70 is in turn by means of tie rods 73 which are arranged distributed over the circumference of the pole tube 28 (screws, for example, two, three or four pieces) attached to the drive end plate 19. It supports the pole tube 28 on the drive bearing plate 19 and the Kommutatorlagerdeckel 70 on the pole tube 28th

In the drive direction, a so-called sun gear 80 connects to the armature 37, which is part of a planetary gear 83. The sun gear 80 is surrounded by a plurality of planet wheels 86, usually three planet wheels 86, which are supported by means of rolling bearings 89 on journals 92. The planet wheels 86 roll in a ring gear 95, which is mounted in the pole tube 28. In the direction of the output side, the planetary gears 86 are adjoined by a planet carrier 98, in which the axle journals 92 are received. The planet carrier 98 is in turn stored in an intermediate storage 101 and a slide bearing 104 arranged therein. The intermediate bearing 101 is designed cup-shaped, that in this both the planet carrier 98, and the planet wheels 86 are added. Furthermore, in the cup-shaped intermediate bearing 101, the ring gear 95 is arranged, which is ultimately closed by a de- partment 107 relative to the armature 37. Also, the intermediate bearing 101 is supported with its outer circumference on the inside of the pole tube 28. The armature 37 has on the end facing away from the commutator 52 end of the drive shaft 44 has a further shaft journal 110, which is also received in a sliding bearing 113, from. The sliding bearing 113 in turn is received in a central bore of the planet carrier 98. The planetary carrier 98 is integrally connected to an output shaft 116. This output shaft is supported with its end 119 facing away from the intermediate bearing 101 in a further bearing 122 which is fixed in the drive bearing plate 19. The output shaft 116 is divided into various sections. Thus, the section which is arranged in the sliding bearing 104 of the intermediate bearing 101, a portion with a so-called spur toothing 125 (internal teeth), which is part of a so-called shaft-hub connection. This shaft-hub connection 128 in this case allows the axially linear sliding of a driver 131. This driver 131 is a sleeve-like extension, which is integrally connected here, for example, with a cup-shaped outer ring 132 of the freewheel 137. This freewheel 137 (Richtgesperre) further consists of the inner ring 140 which is disposed radially within the outer ring 132. Between the inner ring 140 and the outer ring 132 clamping body 138 are arranged. These clamp bodies 138 prevent together with the inner and outer ring, a relative rotation between the outer ring and the inner ring in a second direction. In other words, the freewheel 137 allows a circumferential relative movement between inner ring 140 and outer ring 134 in one direction only. In this embodiment, the inner ring 140 is formed integrally with the starter pinion 22 and the toothing 143.

Subsequently, the Einspurmechanismus will be discussed. The pusher 16 has a housing 156, which is secured by means of a plurality of fastening elements 159 (screws) on the drive end plate 19. In the pusher 16, a winding 162 is further arranged for feeding. The winding 162 for retraction causes in the on state an electromagnetic field which flows through various components. Among other things, this magnetic field affects a linearly movable armature, which is designated here as a lifting means 168, and possibly a cover-like inference core 171 here. The lifting means 168 carries a push rod 174 which is moved to the right in the linear retraction of the lifting means 168.

The pushing device 16 or the lifting means 168 has the task of using a tensioning element 187 to move a lever 190 arranged in a rotatable manner in the drive bearing plate 19. This lever 190, usually designed as a fork lever, engages with two "tines" or fork arms, not shown here, on its outer circumference a driver ring 197 located between two disks 193 and 194 in order to move the latter toward the freewheel 137 against the resistance of the spring 200 and thereby the Andrehritzel 22 einzuspuren in the ring gear 25.

Alternatively, the electric motor 13 could also be permanently magnetically excited. In this case, the pole tube 28 on its inner circumference instead of each of an excitation coil 300 surrounded pole pieces 31 permanent magnets, which provide the corresponding magnetic opposing field to the armature 37.

FIG. 2 shows how the starting device 10 is electrically connected or interconnected to a starter control device 250. For example, this starter control unit 250 by means of an electric solenoid 253 (relay) controls a switch 256, which is responsible for the power supply of the starter motor 13. If this switch 256 is closed, then positive electric potential is applied from a starter battery or a starter accumulator 259 to the starter motor 13. As a result, the armature 37 begins to rotate, and the starter pinion 22 begins to rotate. Furthermore, the starter Control unit 250, the pusher 16. For this purpose, the winding 162 is energized for feeding by means of two electrical lines 262 and 265. As a result, the lifting means 168 which moves the pulling element 187 and subsequently the lever 190 moves. The starting pinion 22 is thus advanced axially in the direction of the output shaft 116 in the direction of the toothed rim 25.

The sequence according to the exemplary embodiment according to FIG. 2 is as follows: A speed sensor 270 transmits a signal to an engine control unit 273. Here, this signal corresponds to a speed characteristic of the ring gear 25 of the internal combustion engine 20. It is unimportant whether the speed sensor 270 determines the speed of the ring gear 25 or the speed of another connected to the ring gear 25 component transmitted. In question in this case, for example, the rotational speed of a camshaft of the internal combustion engine 20 could come. In the embodiment of Figure 2, the engine control unit 273 decides whether the starter control unit 250 should be activated or not. If the speed control gearshift is such that the starter pinion 22 is to be meshed with the ring gear 25, in this case the engine control unit 273 activates the starter control unit 250, which controls both the starter motor 13 (activation of the solenoid 253, closing of the switch 256) and activating the pusher 16 by switching the coil 162. There are alternatives to this activation process, which are mentioned below. According to the method described above, a method is provided for meshing a starting pinion 22 of a starting device 10 in a ring gear 25 of an internal combustion engine, wherein the starting pinion 22 due to a rotating starter motor 13 has a peripheral speed v _R and the ring gear 25 has a peripheral speed V _ZK , said Andrehritzel 22 along an axis of rotation 276 axially vorspurt. The starting pinion 22 contacts the ring gear 25 at a peripheral speed V _R , which is smaller than the peripheral speed v _Z κ of the ring gear 25.

3 shows a schematic view in the axial direction (rotation axis of starter pinion 22 and ring gear 25) an end view of the starter pinion 22 and the ring gear 25 in the moment before contacting the ring gear 25 by the starter pinion 22. It is shown that the ring gear 25th here is clockwise and the starter pinion 22 is left-turning. The ring gear 25 has at its outer periphery, ie here on the pitch circle diameter, a peripheral speed v _Z κ and the starter pinion 22 on its pitch diameter a peripheral speed V _R. As illustrated, the crank pinion 22 contacts the ring gear 25 at a peripheral speed v _R , wherein the peripheral speed V _{R is} smaller than the peripheral speed v _Z κ of the ring gear 25. FIGS. 4a to 4k show the course of the meshing operation in a highly schematic manner. The illustrations in FIGS. 4a to 4k show, in development, the course of engagement of the teeth of the starting pinion 22 with the tooth spaces of the ring gear 25. D. h. the circumference of the gears is shown here linear.

Thus, Figure 4a shows the situation of Andrehritzels 22 and the ring gear 25 after the Andrehritzel 22 has been set in rotational motion. The starter pinion 22 shows in the detail representation of a tooth ZRl and subsequently a tooth ZR2. These teeth ZR1 and ZR2 point in the direction of the end face 300 directed toward the ring gear 25

Slant 303, this bevel 303 faces the back of the teeth. Rear side here means that this bevel merges from the end face 300 to the rear side of the tooth, the back side of the tooth ZR1 or ZR2 being oriented counter to the direction of rotation. The ring gear 25 also has an end face 306. The teeth ZK1, ZK2, ZK3 and ZK4, representative of all the teeth on the outer circumference of the ring gear 25, likewise have a bevel 309. In contrast to the bevels 303 of the Andrehritzels 22, these bevels 309, starting from the end face 306 in the direction of rotation and thus the peripheral speed v _Z κ- the bevels 303 of the Andrehritzels 22 and the bevels 309 of the ring gear 25 are opposite to each other or show each other. The different peripheral speeds of the pitch circle of Andrehritzels 22 and the ring gear 25 are shown here with different large arrows.

Starting from FIG. 4a, FIG. 4b shows the next step. FIG. 4b shows the moment of contacting of the starting pinion 22 on the ring gear 25. This FIG. 4b shows the normal case of the first attempt to track a starting pinion 22 into the ring gear 25 of an internal combustion engine, namely the so-called tooth-on-tooth position. As can be clearly seen here, the end faces 300 and 306 of the teeth ZR1 and ZR2 and of the teeth ZK1 and ZK2 stand in each other's way. A smooth unimpeded meshing of Andrehritzels 22 in the ring gear 25 is not possible.

According to the further course of the Einspurverfahrens and the situation regarding the peripheral speeds V _R and V _ZK of Andrehritzel 22 and ring gear 25, the two gears rotate relative to each other. As a result, the teeth ZK1 and ZK2 of the ring gear 25 slide along the end faces of the teeth ZR1 and ZR2 until, theoretically, it would be possible for the teeth ZR1 and ZR2 to enter a tooth space ZL1 between them To einzuspuren teeth ZKl and ZK2. Due to the inertia of the Andrehritzels 22 and the relative speed, ie the difference of the peripheral speeds of Andrehritzel 22 and ring gear 25, the teeth ZRl and ZR2 initially fail to einzuspuren in the corresponding tooth gaps ZLl and ZL2 of the ring gear 25. Rather, the bevels 303 of the teeth ZR1 and ZR2 strike the bevels 309 of the teeth ZK2 and ZK3. This impacting or impacting causes the starting pinion 22 to rebound once from the bevels 309, but thereby loses kinetic energy, ie not spins back too far in the axial direction (axis of rotation 276), see also FIG. 4e. During this rebounding and not be meshed in the ring gear 25, the ring gear 25 rotates further relative to the starter pinion 22, so that the bevels of 303 of the teeth ZRl and ZR2 are now opposite the bevels 309 of the teeth ZK3 and ZK4, see also Figure 4g. The teeth of the Andrehritzels 22 beat due to the fact that the starter pinion now carries less kinetic energy in itself, not so hard on the bevels 309 of the teeth ZK3 and ZK4 of the ring gear 25 on. Furthermore, the toothed rim 25 has transmitted a certain angular momentum with the impact (FIG. 4d) of the starting pinion 22 (at the same time the ring gear has also been braked somewhat), so that the starting pinion 22 now has its teeth ZR1 and ZR2 is not or almost not rebounded by the bevels 309 of the teeth ZK3 and ZK4 and is pushed further into the tooth spaces ZL2 and ZL3 due to a biasing force of the spring 200 until they have left the bevels 309 of the ring gear 25 behind (Figure 4h).

The teeth ZR1 and ZR2 of the starting pinion 22 now slide - now driven in the circumferential direction through the ring gear or its teeth ZK3 and ZK4 further into the tooth gaps ZL3 and ZL2 until these teeth are fully inserted into the tooth spaces ZL2 and ZL3 (FIG. 4i and FIG 4j). Following this, the teeth ZR3 and ZR4 perform a system change (FIG. 4k), ie either the ring gear 25 brakes so sharply that the teeth ZK3 and ZK4 slow down and thus come into contact with the teeth ZR1 and ZR2 or that the starting pinion 22 accelerates so much that it now actively drives the ring gear 25 to turn the engine 20 over the ring gear 25 again (continued operation of the internal combustion engine). The latter case can occur when the driver has made a change in intent, while the meshing operation of the Andrehritzels 22 was in the ring gear 25 in progress. Such a change may occur, for example, when the driver is driven to a traffic light with his vehicle and intended to bring the vehicle to a standstill or has already stopped at very short notice. In such a case, the internal combustion engine just in the concept of In such a case, for example, by pressing a signal generator, which stands for a driver's request (accelerator pedal), the starter pinion 22 are suddenly accelerated and the situation shown in Figure 4k occur ( Keyword "mind change", new German for change of intent or change of attitude of the driver).

According to what has been described thus far, a method is provided for engaging a starting pinion 22 of a starting device 10 in a ring gear 25 of an internal combustion engine 20, wherein the starting pinion 22 has a peripheral speed v _R , and the ring gear 25 has a peripheral speed v _Z κ, wherein the starting pinion 22nd along its axis of rotation 276 axially biassing, wherein the starter pinion 22 contacts the ring gear 25 with a peripheral speed V _R , which is smaller than the peripheral speed V _{ZK of} the ring gear 25. It is clear that it depends on the speed ratios between the starter pinion 22 and the ring gear 25 in the process. Accordingly, several cases are distinguishable:

a) The first case is the case as shown in FIG. The peripheral speed of the ring gear v _Z κ is greater than the peripheral speed v _{R of} the Andrehritzels 22. It follows in turn that the starting pinion 22 with a peripheral speed v _R the ring gear 25 contacted, which is smaller than the peripheral speed V _{ZK of} the ring gear 25. The direction of rotation is in this case in the same direction as the intended or actual direction of rotation of a drive shaft 21 (for example, crankshaft) of the internal combustion engine 20 in the driving case and valued here in terms of value as positive. In this case, the peripheral speed v _Z κ of the ring gear 25 is not equal to zero. Likewise, the peripheral speed v _{R of} the Andrehritzels 22 is not equal to zero. Both circumferential velocities v _R , v _Z κ are oriented in the same direction, FIG. 3.

b) In this case, the peripheral speed v _Z κ of the ring gear 25 is still greater than the speed v _{R of} the Andrehritzels 22. This means that the direction of rotation of the Andrehritzels 22 in this case the direction of rotation of the Andrehritzels 22 from the case a is opposite , While in the case of a, the starter pinion 22 rotates at a rotation or angular speed which is opposite to the intended rotation of the drive shaft 21 in its driving state, in the case b prior to the contacting of the starter pinion 22 its angular velocity is in the same direction as the later one Angular velocity of the drive shaft 21. Under such velocity Conditions between the ring gear 25 and the starter pinion 22 may be the same relative movements as in the case a. In contrast to the case a, the direction of rotation and thus the angular velocity of the starter motor 13 is to turn over after the successful meshing of the Andrehritzels.

c) In case c, the peripheral speed v _Z κ of the ring gear 25 is greater

Zero and the peripheral speed v _{R of} the Andrehritzels 22 smaller than the peripheral speed V _ZK of the ring gear 25. The angular velocity of the ring gear 25 is the driving direction of rotation of the drive shaft 21 opposite. Such a case may occur when in the internal combustion engine 20 due to known

Leakage properties reverses the direction of rotation of the drive shaft 21. Thus, the phenomenon is known that a moving in an internal combustion engine to the so-called top dead center piston compresses the air provided for the combustion, while doing work against the air pressure in the combustion chamber above the piston. If the energy of the piston or the drive shaft 21 and the associated drive parts (piston, connecting rod, crankshaft) is not so high that the piston can exceed the upper dead center, then the drive shaft 21 will turn back again. This case is meant here with this case c. In such a situation, the drive shaft 21 rotates after it has not reached the top dead center, back and therefore has an angular velocity in the short term, which is opposite to the angular velocity in the drive case and also in the case of a. Such details on this subject are generally known from printed works on the technology of internal combustion engines. At the moment from the reversal of rotation and thus the assumption of an angular velocity of the drive shaft 21 and the ring gear 25, this angular velocity and thus the peripheral speed of the ring gear 25 is evaluated negatively in value. In other words, the angular velocity of the driving sprocket 22 must, until the moment of contacting, take on a value that is even more negative compared to the angular velocity of the sprocket 25 to be smaller than the angular velocity of the sprocket 25 as defined herein in this case, the circumferential speed v _{R of} the driving sprocket 22 is also smaller than the peripheral speed v _{Z of} the sprocket 25.

In this method, it is provided that the peripheral speed v _Z κ of the ring gear 25 at the moment of the first contacting maximally by a value formed from the product of 5m / (s * mm) [five meters per product of seconds and millimeters] and the module m _Z κ of the toothed rim 25 is larger in mm and slightly larger than the circumferential speed v _R of twisting sprocket 22. As an example, assume a value of 2.11 mm for the modulus m _Z κ of the toothed rim 25. This technical size module m is given for example in the German industrial standard DIN 868 and is a basic size for length dimensions of gears. The modulus m results as a quotient of the pitch p and the number π. The pitch p in turn is in a certain section of the teeth of the arc on the reference surface between the same flanks of two adjacent teeth, so for example the teeth ZKL and ZK2. Thus, if the module m has the stated value, then it is provided that the peripheral speed v _Z κ of the ring gear 25 is greater by a maximum of 10.55 meters per second than the peripheral speed v _{R of} the starting pinion 22. For a module m of 3 mm would result Thus, a value of 15 meters per second and for a module of 1.5 mm, a speed of 7.5 meters per second.

It is further provided that the starting device 10 has a pinion shaft in the form of the driver 131, which drives the starter pinion 22. In this case acts on the starting pinion 22, a spring force of the spring 200, wherein when contacting the Andrehritzels 22 with the ring gear 25, the spring 200 is compressed.

With reference to FIG. 2, it has already been explained that in the context of the method a switching criterion, for example, 1. Example, a speed of the ring gear 25 or the drive shaft 21 or a camshaft by a controller 273, there running recognized as engine control unit. As a result, the starter pinion 22 is vorgespurt in one step in the direction of the ring gear 25 and rotated in another step, the prevailing at the starting pinion 22 peripheral speed v _R when reaching the ring gear 25 is smaller than the peripheral speed v _Z κ. It is initially irrelevant whether the toeing of the Andrehritzels 22 takes place before the start of the rotation or in the reverse order.

A variant of the exemplary embodiment according to FIG. 2 can provide, for example, that the switching criterion, for example the rotational speed, is not recognized by the control unit 273 of the internal combustion engine 20, but, for example, by the controller 250 of the starter, which subsequently (in rotation) causes the already mentioned steps , Toe marks).

The switching criterion can be, for example, a signal which corresponds to a desire to switch off the internal combustion engine in general form. Such a desire can already appear, for example, in that the speed of the Vehicle is to be reduced. Such a speed reduction can result, for example, from the actuation of the brake pedal or the activation of a corresponding signal pickup, which processes the signals of the brake system. A corresponding other signal could also be the signal which is intended to signal the internal combustion engine 20 that it should now be controlled at idle (fuel cutoff).

Thus, it is provided according to the method or a variant of this method that, based on the switching criterion, a point in time is calculated, in addition to which the starting device is activated in order to achieve the desired conditions according to the invention. It is envisaged that the method is applied to an outgoing internal combustion engine 20, wherein the speed of the drive shaft 21 is reduced. According to a further method step, it is provided that the rotational speed of the starting pinion 22 is lowered to the value zero after meshing in the ring gear 25. As a consequence, this condition also applies to the ring gear 25.

In the context of the method is provided to control the starter motor 13 and the lifting means 16 separated from each other.

The spring 200 may for example be designed as a spiral spring or as a plate spring or another type of spring.

Claims

claims

1. A method for engaging a Andrehritzels (22) of a starting device (10) in a sprocket (25) of an internal combustion engine (20), wherein the starting pinion (22) has a peripheral speed (v _R ) and the sprocket (25) has a peripheral speed (v _Z κ), wherein the starter pinion (22) along its axis of rotation (276) axially ahead, characterized in that the starter pinion (22) at a peripheral speed (v _R ) the ring gear (25) contacted, which is smaller than the peripheral speed (v _Z κ) of the sprocket (25).

2. The method according to claim 1, characterized in that the peripheral speed (v _Z κ) of the ring gear (25) is not equal to zero.

3. The method according to claim 1 or 2, characterized in that the peripheral speed (v _R ) of the Andrehritzels (22) is not equal to zero.

4. The method of claim 1, 2 or 3, characterized in that the peripheral speeds (v _R , v _Z κ) are oriented in the same direction.

5. The method according to any one of the preceding claims, characterized in that the peripheral speed (v _Z κ) of the sprocket (25) at the moment of the first contacting a maximum value formed by the product of 5 meters per second per millimeter and the module m of the ring gear (25) in millimeters larger and minimally greater than the peripheral speed (v _R ) of the Andrehritzels (22).

6. The method according to any one of the preceding claims, characterized in that the starting device (10) has a pinion shaft which drives the starter pinion (22), wherein on the starter pinion (22) a spring force of a spring (200) acts, wherein upon contacting the Andrehritzels (22) with the ring gear (25), the spring (200) is compressed.

7. The method according to any one of the preceding claims, characterized in that a switching criterion by a control unit (273, 250) is detected and the starter pinion (22) in a step in the direction of the sprocket (25) vorspurt and offset in another step in rotation with the peripheral speed prevailing at the starter pinion (22). (v _R ) when reaching the sprocket (25) is smaller than the peripheral speed (v _Z κ) of the sprocket (25).

8. The method according to claim 7, characterized in that the switching criterion is a signal which corresponds to a desire for switching off the internal combustion engine (20).

9. The method according to claim 7 or 8, characterized in that starting from the switching criterion, a time is calculated, in addition, the starting device (10) is activated.

10. The method according to any one of claims 7 to 9, characterized in that first the starter pinion (22) is rotated in one step and then vorgespurt in one step to the ring gear (25).

11. The method according to any one of the preceding claims, characterized in that a speed of the ring gear (25) substantially lowers.

12. The method according to any one of the preceding claims, characterized in that the starter motor (13) and the lifting means (16) are driven separately from each other.