Electromotive actuator for a central door locking system of a motor vehicle

The invention relates to an electromotive actuator with a housing for a central door locking system of a motor vehicle having a first slide adjustable by a first electric motor between two end positions. The first slide can be connected with a door lock of the motor vehicle independently of the end position and is preferably decoupled from the electric motor in the end positions, so that the first slide is manually adjustable between its end positions. Such an electromotive actuator is provided with a theft protection capability in the sense that, after a windshield of a motor vehicle is smashed in, an unlocking of the door by the inside locking handle is no more possible because the parts of the actuator are not actuated by operating the inside locking handle. Finally, an unlocking operation initiated from the outside is possible when the theft protection is put into operation. The theft protection capability is achieved by providing a second slide which can be coupled with the first slide by a latch adjustably guided at one of the two slides transversely to the moving direction of the slides and engaging the other slide under the effect of a spring element. The latch can be pulled back from engaging the other slide against the effect of the spring element from one coupling position into a theft protection position by a second electric motor and a control device so that the latch, together with the slide at which the latch is guided, can be moved away from the control device in the theft protection position.

BACKGROUND 
The invention refers to an electromotive actuator for a central door 
locking system of a motor vehicle having a slide which is adjustable 
between two end positions and connected to the door lock in either 
position and which can be decoupled from the electric motor in the end 
position so that it can be adjusted manually between the end positions 
easily. 
An electromotive actuator of this type is known from DE-OS 36 27 893. This 
actuator has the advantage compared with an electromotive actuator, for 
example known from DE-OS 32 10 923, that the slide can be smoothly 
manually adjusted from its end positions. In the actuator of DE-OS 32 10 
923 the electric motor and the gear wheels of the gearing, which is 
arranged behind said electric motor, have to co-rotate to allow manual 
shifting of the slide. 
The actuator shown in DE-OS 32 10 923 for a central door locking system of 
a motor vehicle does not only allow a central locking or unlocking of a 
motor vehicle door, but also provides a so-called theft protection. In a 
central door locking system for a motor vehicle which is equipped with a 
theft protection it is possible to lock and unlock the door lock from the 
outside. In principle this is also possible with a handle in the inside of 
the motor vehicle. However, if the theft protection is put into operation 
from the outside, it is no longer possible to unlock the door lock with 
the handle on the inside. This is meant to make it more difficult for 
thieves to get inside the motor vehicle. In other words, if the windshield 
of a motor vehicle was smashed in, it is not possible to unlock the door 
with the handle in the inside of the motor vehicle and to then open it. It 
is only possible to enter through the window. 
In the electromotive actuator according to DE-OS 10 923, the theft 
protection is realized by locking the slide by a latch which can be 
shifted by a second electric motor against movement in the unlocking 
direction. This has various disadvantages. In case of theft or in the case 
that the handle is operated from inside the motor vehicle, parts within 
the actuator are exposed to a major force, which can be effected by the 
handle on said parts. If no damage is accepted, the parts have to be 
designed correspondingly strong. It is also disadvantageous that it is 
impossible to unlock a vehicle door, once the motor operating the latch 
does not work in the theft protection position, for any reason. Finally, a 
lost travel in the gearing must be provided between the first electric 
motor, which is actuable, in principle, for locking in the reversed 
direction of rotation as well as for unlocking, in order to ensure that 
the blockage of the slide has been removed when the first motor engages in 
the slide. 
Thus, the object of the invention is to create an electromotive actuator 
for a central door locking system providing theft protection without parts 
of the actuator being excessively strained in a theft attempt, and in 
which manual unlocking is also possible from the outside, even if the 
theft protection cannot be reset by the motor. 
SUMMARY OF THE INVENTION 
These requirements are achieved by an electromotive actuator providing a 
second slide which can be coupled with the handle inside the motor vehicle 
at least for unlocking the door lock. Furthermore, the second slide can be 
coupled with the first slide by means of a latch, which is adjustably 
guided at one of the two slides transversely to the stroke of the slides 
and engages into the other slide under the effect of a spring element. 
Upon engagement of the latch, the two slides can be regarded as one slide 
for the stroke, so that unlocking is possible from outside of the motor 
vehicle without any problems. For theft protection, the latch is pulled 
back by a second electric motor by means of a control device, so that it 
does not engage the other slide against the effect of the spring element. 
In this way, a motion transfer from the second onto the first slide is no 
longer possible, so that the second slide can be moved in the case of a 
theft attempt, whether the latch is guided at the second or at the first 
slide, even though the door lock is not disengageable. The force 
introduced into the handle inside the motor vehicle is not received by 
parts of the actuator because the second slide is movable. 
Should the second electric motor fail to work for any reason while the door 
is locked and the theft protection is in operation, the first slide, 
regardless whether the handle is or is not guided at said slide, can still 
be brought from the locking position into the unlocking position from the 
outside or by the first electric motor. However, this also means that 
during the unlocking of the door lock from the theft protection position 
of the latch, a certain order in operating the latch and adjusting the 
first slide is not followed. 
An alternate embodiment which realizes the object also resides in an 
electromotive actuator having a first slide, which can be connected with a 
door lock of a motor vehicle independently of direction and a second slide 
which can be coupled with a handle in the inside of a motor vehicle for 
unlocking. Both slides engage into each other with a jut and a recess 
transversely to their moving direction, and for theft protection, a 
carrier of one of the two slides can be moved relative to the slide in the 
moving direction of the two slides by an electric motor, the carrier 
engaging one of the slides in order to form a gap. After forming the gap, 
the second slide can be moved freely by way of the handle inside the motor 
vehicle without the first slide being entrained and the door lock being 
unlocked as a result. 
In either embodiment, manual adjustment of the first slide is possible 
without having to move the first electric motor and gearing which is 
arranged behind the electric motor. 
Hence, the second slide can be entrained by the firs slide independently of 
the latch. Thus, the second slide can be entrained by the first slide at 
once, when the door lock is operated from the outside, without the theft 
protection having been reset by the second electric motor beforehand. 
The control device utilized is a control curve with a ramp. Seen from the 
fundamental mode of operation it is unimportant, whether the moving 
direction of the ramp at the latch when it is pulled back while setting 
the theft protection, corresponds with the direction of the slide during 
the locking or unlocking operation. It is more advantageous that while the 
latch is ascending the ramp, the ramp moves in a direction which 
corresponds to the moving direction of the slide during the locking 
operation. In this event, no force is effected by the ramp on the latch in 
the moving direction towards unlocking the slide so there is no danger 
that the setting of the theft protection is impaired or prevented by the 
slides moving slightly out of their end position. 
Although normally the electric motors used in electromotive actuators for 
central door locking systems work reliably over a long time period, it 
cannot be excluded that such an electric motor might fail to work, and 
that the gearing members arranged behind the electric motor might then be 
in an undefined position. A manual locking of the door has to be 
guaranteed even under these circumstances. How this problem can be solved 
with regard to the first electric motor is described in detail in DE-OS 36 
27 893. For the second electric motor, this problem is advantageously 
solved by providing that the latch can be pushed beneath the control curve 
when the slide is shifted out of the unlocking into the locking position. 
As the ramp of the control curve might be situated in the course of the 
latch, the ramp of the control curve is formed resiliently in such a way 
that the latch can be pushed beneath the ramp or that it can be pushed 
through beneath the ramp when the slide is shifted out of the unlocking 
into the locking position. The precondition for this resilient quality of 
the ramp certainly is that said ramp is separated from its support at its 
foot. 
In regard to the tool technics, the distance that the ramp is separated 
from its foot must not be too large to ensure the ascension of the latch 
onto the ramp. During the forming of the control curve, which is usually 
form from plastic material together with its support, the foot of the ramp 
has to be separated from its support by a tool section which is as thin as 
possible. So that this thin tool section does not have to be too long, the 
ramp is thinner at its foot than in the distance towards its foot. 
The control curve is preferably situated at a gearwheel which can be driven 
by the second electric motor. In this case, the already mentioned 
precautions in order to avoid a failure of the second electric motor can 
be realized most easily by arranging the control curve in such a way that 
the latch can be moved by the control curve in direction of the axis of 
the gearwheel. 
Following the ramp, the control curve advantageously comprises a plane 
section without a change of height. The second electric motor coasts for 
an uncertain period after it was switched off, which does not have an 
effect on the position of the latch, because of the plane section of the 
control curve. As long as the latch is guided at the second slide, it is 
moved to adopt the unlocking position together with the second slide in 
the case of a theft attempt. When the handle is set back inside the motor 
vehicle, it returns with the second slide into the locking position 
reaching again the plane section of the control curve. In order to 
facilitate this, the plane section comprises a slope declining in radial 
direction at its radial outside edge. 
In order to keep the expenditure in control for the second electric motor 
small, it is actuatable only in one direction in order not to require 
complicated mechanical change-over mechanisms. Also the gearwheel can be 
driven by an electric motor in only one single direction of rotation. The 
second electric motor can be switched on for pulling back the latch as 
well as for pushing forward the latch through the resilient element, the 
gearwheel then being rotatable by about 180 degrees each time after the 
electric motor is switched on. However, because the latch can also be 
moved away from the control curve when the theft protection is in 
operation, it is not necessary in principle, that the second electric 
motor be switched on in order to reset the theft protection. Therefore 
advantageously, it is provided that the second electric motor can be 
switched on only for pulling back the latch, the gearwheel preferably 
being rotatable by 360 degrees each time after the electric motor is 
switched on. In such a design the number of switch operations and, if the 
gearwheel is turned by less than 360 degrees, the whole time of operation 
of the second electric motor can also be reduced. Furthermore, only one 
break contact is necessary for the end switch so that the number of 
electric lines within the actuator can also be reduced. While it does not 
have any influence on the method of operation during an unlocking 
operation, whether the second electric motor begins to run before the 
first electric motor, together with the first electric motor, after the 
first electric motor or does not run at all, it is necessary for setting 
the theft protection that the latch with the slides is in the locking 
position, so that the control curve can engage into the latch. Therefore, 
a time delay is necessary between the beginning of the adjustment of the 
slide from the locking to the unlocking position and the engagement of the 
control curve into the latch. This time delay may be provided, for 
example, by a delayed switching on of the second electric motor. In 
particular, the second electric motor can only be switched on, when the 
slides have reached the locking position and when it is reported by a 
signal, for example by an electric switch in the door lock. However, a 
time delay might also be obtained in that the motors are switched on at 
the same time, yet the gearwheel with the control curve running 
essentially more slowly than the gearwheel with the crank adjusting the 
slides or, in the case that the gearwheel with the control curve is turned 
by 360 degrees each time, the ramp meets the latch only after a rotation 
angle which is essentially in excess of 180 degrees. However, the latter 
solutions are not very safe because the time period necessary for 
adjusting the slides by the first electric motor can vary within wide 
ranges. 
An advantageous embodiment of the electromotive actuator according to the 
invention with regard to the arrangement and guiding of the latch is 
realized by providing a helical spring situated in a blind-end bore of the 
latch and supported on an extension of the slide guiding the latch, which 
extension protrudes into the blind-end bore through a longitudinal slot, 
by which the blind-end bore is open to the outside. Consequently the latch 
is very long and can be guided correspondingly long. The travel of the 
latch out of its guiding is advantageously limited by a stop of the slide 
which does not guide the latch. In this way a stop at the slide guiding 
the latch is avoided so that the latch can be pushed easily into the 
guiding. The helical spring is laterally well supported in each position 
of the latch. 
The space conditions may make it seem favorable that the latch is guided at 
the second slide. If, in opposition thereto, the latch is guided at the 
first slide the latch will not be entrained once the theft protection is 
in operation and the handle in the inside of the motor vehicle is 
operated, which leads to a movement of the second slide, but it remains at 
the control curve. It has not to be taken care of, that the latch remains 
in the theft protection position for example, by means of a support area 
at the first slide or at the housing or that it is pushed back into this 
position when the second slide returns. 
The whole construction consisting of lock, electromotive actuator and 
handle in the inside of the motor vehicle as well as the mechanical 
connections between these parts may be chosen in the way that the second 
slide can be operated by means of the handle in the inside of the motor 
vehicle only in the sense of an unlocking of the door lock. To permit 
locking by way of the handle in the inside, it is provided that the slides 
be coupled via a carrier with the handle in the inside of the motor 
vehicle and that the carrier is situated in moving direction of the slides 
between said slides. On the other hand, when the second slide is operated 
via the handle in the inside of the motor vehicle in the sense of locking 
as well as in the sense of unlocking, the second slide can be directly 
form-fittingly coupled with the carrier into both moving directions. 
Advantageous embodiments of an electromotive actuator according to the 
invention with regard to the guiding of the slides are provided by guiding 
the first slide at the housing and the other slide at the first slide. A 
correct assembly of both slides onto each other is guaranteed by providing 
two narrow grooves on one slide and two narrow rails on the other slide 
which engage the grooves, with one groove and rail being lower at one side 
than at the other. 
In an electromotive actuator, the carrier can be moved advantageously 
against the effect of the spring element, which takes support at the 
associated slide. It seems also favorable that the carrier can be coupled 
with the associated slide by means of a locking device for limited force. 
In principle, this can happen in both operating positions of the carrier 
in relation to the associated slide. When a spring element is used, a 
coupling by a locking device for limited force only in one position is 
sufficient, namely in the one in which the jut is reduced or the recess 
enlarged. Without a spring element, one single locking device for limited 
force in the said position of the carrier is sufficient, if theft 
protection is provided for each locking operation. 
An electromotive actuator using only one single electric motor, the 
direction of rotation of which can be reversed, adjustably coupled to the 
carrier with the electric motor may take place by means of a gearwheel 
driven by the electric motor and a toothed rack of the carrier. In this 
case the direction of rotation of the motor during the operation of the 
theft protection advantageously corresponds with the direction of rotation 
during the locking operation and advantageously corresponds with the 
direction of rotation during the unlocking operation while the theft 
protection is not in operation.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
In the actuator according to FIGS. 1 and 2, a first electric motor 23 is 
fixed in a housing 20 consisting of two pieces with a housing pot 21 and a 
cover 22 made of plastic material. Electric motor 23 drives a crank wheel 
27 by means of a worm 25 situated on its shaft 24 and by means of a worm 
wheel 26 and a pinion which is integrally formed with the worm wheel 26. A 
conical reduced crank stud 28 sticks out of crank wheel 27, which 
therefore moves on a circuit. The axis of the worm wheel is marked with 
numeral 29. 
In the housing 20, a slide 30 is movably guided in the longitudinal 
direction of double arrow A. The slide 30 can be connected with a 
connecting rod via U-shaped recesses situated at a lug 32 protruding from 
the housing 20 to act upon the door locking mechanism of a motor vehicle. 
At an extension 35 of the slide 30 running parallely to the cover 22 as 
seen from the top view according to FIG. 1. At the bottom side of the 
extension 35, two stops 33 and 34 are provided which cooperate with the 
crank stud 28. It can be seen from FIG. 1 that the distance B between the 
two stops 33 and 34 is much smaller than the radius of the crank wheel 27 
in its adjusting direction which means that the distance of the crank stud 
28 from the axis 29 of the crank wheel 27 is much smaller. This 
relationship facilitates a big stroke of the slide 30 if the radius of the 
crank wheel 27 is fixed. The distance D of the two stops 33 and 34 
transversely to the adjusting direction of the slide 30 is only slightly 
larger than the diameter of the crank stud 28. In the end position of the 
crank wheel 27 and the slide 30 shown in FIG. 1, the crank stud 28 is 
situated between the two stops 33 and 34 in the direction transverse to 
the adjusting direction of the slide 30. In this end position, the slide 
30 is completely decoupled from the crank stud 28 such that the crank 
wheel 27 and can be manually displaced from the shown end position into 
the other end position and back again by means of the already mentioned 
connecting rod. The same displacement of slide 30 applies if the crank 
wheel 27, the crank stud 28 and the slide 30 are situated in the other end 
position in which the crank wheel 27 is displaced by 180 degrees with 
respect to the position shown in FIG. 1. 
If, starting from the position shown in FIG. 1, the electric motor 23 
driving the crank stud 28 is switched on, the crank stud 28 rotates 
clockwise on its circular adjusting course. It then hits the stop of the 
slide 30 and is retrained by the stop 33 and slide 30 during the course of 
its movement into the other end position. After a rotation angle of 180 
degrees the crank stud is stopped again. When the electric motor 23 is 
switched on again, the crank stud 28 hits the stop 34 of the slide and 
resets the slide again into the end position shown in FIG. 1 corresponding 
to a locked door. 
On the whole this makes clear, that the crank stud 28 is rotated 
180.degree. in the same direction each time in each adjusting process. The 
crank stud 28 is coupled with the stops 33 or 34 and decoupled from the 
slide, only during the period its movement when it is located in the end 
positions, after a rotation angle of 180 degrees each time. 
In principle, the slide is arranged parallely to a side wall of the housing 
20 and engages with the thin extension 21 parallely to the cover and 
shortly beneath this cover into the housing pot 21. In the area of the 
side wall, at which the slide 30 is situated, a second slide 40 is guided 
in the direction of a possible movement of the second slide 40 relative to 
the first slide 30 in the direction of the double arrow A. The second 
slide 40 laterally comprises two rails 41 for guiding, which rails 41 
engage into grooves 42 of the first slide 30 which are open at one end in 
order to engage the second slide 40 into the first slide 30. As can be 
clearly seen from FIG. 2, the one side wall 43 of the grooves 42 is higher 
than the other side wall. Correspondingly, the rails 41 at the side turned 
towards the side wall 43 are higher than at the other side, so that the 
slide 40 can be engaged only in one single relative position to the slide 
30 into said slide. The open end of the grooves 42 is situated at the 
front side 44 of the slide 30. The two rails 45 of the slide 30, in which 
the grooves 42 are situated, are only connected in the area of the lug 32 
and at the other end of the grooves 42. Therefore, the second slide 40 is 
mounted to the car between the front side 44 and the lug 32 of the first 
slide 30 by means of a lug 46 through the opening 47 in the side wall 48 
of the housing 20, in a similar manner the slide 30 is mounted to the car 
with the lug 32. A catching plate can be inserted in a groove 49 in the 
lug 46 of the second slide 40, which, for example, can be operated by a 
handle in the inside of a motor vehicle via a Bowden cable. Therefore, the 
catching plate and second slide are form-fittingly coupled with each other 
in the direction of the double arrow A. In normal operation the two lugs 
32 and 46 are directly in abutment, as shown in FIG. 1. 
On the side of the second slide 40 turned away from the side wall 48 of the 
housing 20, a latch 50 is guided at slide 40 vertically to the adjusting 
direction of the slide 40, indicated by the double arrow A in FIG. 1 and 
vertically to the cover 22 of the housing 20. For guiding, the latch 50 
engages into two grooves 52 of the slide 40 by means of two lateral rails 
51. Grooves 52 are formed by two turned L-shaped rails 53 integrally 
formed onto the slide 40. The latch 50 is provided with a blind-end bore 
54 in guiding direction, which opens in a longitudinal slot 55 towards the 
slide 40. The width of the slot 55 however, is smaller than the diameter 
of the blind-end bore 54, so that a helical pressure spring 56 put into 
the blind-end bore 54 cannot fall out of the blind-end bore 54 through the 
slot 55. The helical pressure spring is supported at the bottom of the 
blind-end bore 54 and at an abutment 57 of the slide 40, which engages 
into the pocket bore 54 through the longitudinal slot 55. In FIG. 2 a 
first end position of the latch 50 is indicated in continuous lines and a 
second end position of the latch in broken lines. It can be seen that the 
abutment 57 is covered by the wall 58 situated opposite the longitudinal 
slot 55 in each position of the latch 50, so that the helical pressure 
spring 56 supports itself safely at the abutment 57 in the prearranged 
position. The grooves 52 of the slide 40 are open at both sides and the 
rails 51 of the latch 50 continually equal, so that the latch 50 can be 
smoothly inserted into the second slide 40 towards the direction of the 
support area of the helical pressure spring 56 at the abutment 57. There 
is a rectangular opening 58 in the extension 35 of the first slide 30, 
into which the helical pressure spring 56 can press the head 59 of the 
latch 50 to the extent that the opening 58 aligns with the guide of the 
latch 50, until the latch 50 hits the side of the cover 22 opposite the 
extension 35 by means of a step. In a cross-section lying parallely to the 
extension 35 of the slide 30, especially in moving direction of the slides 
30 and 40, the dimensions of the opening 48 and of the head 59 of the 
latch 50 are coordinated in such a way that only a little play exists 
between them. 
When the head 59 of latch 50 engages into the opening 58 of the extension 
35, the slides 30 and 40 are coupled with each other in both moving 
directions. From the fact that the lugs 32 and 46 abut into each other 
follows, that from the end position of the two slides 30 and 40, shown in 
FIG. 1, which corresponds to a locked door lock, the slide 30 can entrain 
the slide 40 by means of the lug 32 independently of the latch 50 into the 
end position, which corresponds to an unlocked door. In this case it is of 
no importance, whether the slide 30 is adjusted normally by the closing 
cylinder or by the electric motor 23. During the locking operation of the 
door locks, consequently, in case of a shifting of the slide 30 from the 
second end position into the end position shown in FIG. 1, the second 
slide 40 is entrained by the first slide 30 by means of the latch 50, 
wherein it is again of no importance, whether the first slide 30 is 
adjusted manually or by the electric motor. 
Upon the engagement of the latch 50 into the opening 58 it is possible, to 
unlock or to lock a motor vehicle door by means of the inside locking 
handle. When the door is locked and the inside locking handle is operated, 
the second slide 40 is entrained by a carrier plate situated in the groove 
49 of the lug 46 of the second slide 40 and the first slide 30, which 
transfers the movement onto the door lock by the latch 50. During a 
locking operation the slide 40 entrains the first slide 30 by means of the 
lug 46 respectively the latch 50. 
While it should be possible to unlock the door from the inside at any time 
if the motor vehicle door is locked from inside, it is requested to have 
the ability to make it impossible to unlock the door from the inside, if 
the door is locked from the outside. It shall be avoided in this way, that 
in case of a theft attempt after the windshield of a motor vehicle was 
smashed in, the doors are to be unlocked by an operation of the inside 
locking handle providing easy access to the motor vehicle. 
In order to facilitate this theft protection, latch 50 is provided which 
can be pulled back from the opening 58 of the slide 30 by a second 
electric motor 65, as long as the two slides 30 and 40 are in the locking 
position and the electric motor 65 is put under electric power. The 
electric motor 65 drives a gearwheel 70 by means of a worm 67 situated on 
its shaft 66 and by means of a worm wheel 68 and a pinion 69 integrally 
formed with the worm wheel 68. Gearwheel 70 is provided with a gear ring 
71 directly beneath the extension 35 of the slide 30 and, from the point 
of view of the extension 35 comprises a control curve 75 beyond the gear 
ring 71, which control curve 75 spaced apart from the gear ring 71 on a 
radial flange 76 of the gearwheel 70, at the opposite side from gear ring 
71. 
Details of gearwheel 70 can be seen in FIG. 3 to 5. The control curve 75 
extends over an angle of approximately 205 degrees and consists of a ramp 
77 rising from the bottom side of the gear ring 71 and extending over an 
angle of 60 degrees and of a plan section 78 joining the ramp whose length 
extends 245 degrees. At the end 79 of the plane section 78 the control 
curve 75 stops abruptly. The flange 76 carrying the control curve 75 is 
cut free from the gear ring 71 by a surrounding groove 80, which is 
radially open to the outside. The groove 80 is wider than the curve 
follower 81 which is integrally formed with the latch 50 and which 
vertically extends the latch 50 towards the control curve 75 in the 
guiding direction of the latch 50. Curve follower 81 is situated directly 
beneath the gear ring 71 on the level of the groove 80 when the latch 50 
is latched in the slide 30, as can be seen from FIG. 2. The groove 80 also 
continues beneath the ramp 77, although continuously decreasing in width 
according to the sloped position of the ramp 77. Groove 50 then has a 
section with a constant width as the ramp 77 becomes thinner and finally 
decreases its width until it nearly reaches 0. That the ramp 77 is thinner 
at its foot than in the distances towards its foot 82 is for tool 
technical reasons. Namely the ramp 77 is not only radially outside, but 
also on its foot 82 separated from the rest of the material of the 
gearwheel 70. However, in order to ensure that the curve follower 81 
smoothly ascends the ramp 77, the distance between the foot 82 of the ramp 
77 and the rest of the material of the gearwheel 70 should be small. This 
small distance has to be made with a section of a form tool which is very 
thin and therefore, presents a risk of fracture. Because the ramp 77 is 
thinner at its foot 82 than in the distance to the foot 82, the length of 
the tool section becomes smaller in the direction of rotation which 
therefore diminishes the risk of fracture. The ramp 77 is also radially 
inside separated from the rest of the material of the gearwheel 70 by a 
free cut 83, which can be ejected by an opening 84 in the gear ring 71 of 
the gearwheel 70. As can be seen from FIG. 3, the free cut 83 starts in 
the distance in front of the foot 82 of the ramp 77, seen in circulation 
direction, and ends shortly behind the transition between the ramp 77 and 
the plane section 78. Only at this transition is the ramp 77 connected 
with the rest of the material of the gearwheel 70. Therefore, ramp 77 can 
easily spring away from the gear ring 71. 
The gearwheel 70 also carries a radial cam 85, by way of which an end 
position switch 86 for the electric motor 65 situated in the housing 20 
can be operated. The switch 86 is a changing switch which is controlled by 
the cam 85 such that electric motor 65, always running in the same 
direction of rotation, is switched off after a rotation of the gearwheel 
70 of approximately 180 degrees each time. The position of the cam 85 and 
the position of the control curve 75 are coordinated with each other in 
circulation direction such that the curve follower 81 of the latch 50 is 
situated shortly in front of the ramp 77 in one rest position, and in the 
other rest position of the gearwheel 70, shortly in front of the end 79 of 
the plane section 78 when the slides 30 and 40 are in locking position. 
The way the electromotive actuator works according to the FIGS. 1 to 5 
shall now be explained in detail by way of FIGS. 6 to 12. The FIGS. 6 and 
7 show the slides 30 and 40 in locking position from which they can be 
returned to the unlocking position by a movement to the right in FIG. 6. 
In the state according to FIGS. 6 and 7, the latch 50 engages the first 
slide 30 with its head 59. If the inside locking handle is operated, the 
slide 40 entrains the slide 30 by way of the latch 50 to the unlocking 
position, so that the lock is unlocked. There was no theft protection put 
into operation. If the door is locked and the theft protection put into 
operation, a signal is generated by a longer operating of the closing 
cylinder, by a repeated operating of the closing cylinder or also by an 
operating of the closing cylinder for more than a certain period, which 
causes the electric motor 65 to be supplied with power when the slide 30 
is in locking position. The electric motor 65 turns the gearwheel 70 
clockwise by 180 degrees, as seen from the point of view according to FIG. 
6, until it is switched off by the switch 86. The control curve 75 drives 
the ramp 77 under the curve follower 81 of the latch 50 and withdraws the 
head 59 from the opening 58 of the slide 30, with the position of the 
latch 50 being determined by the level of the plane section 78 of the 
control curve 75. When the electric motor 65 is switched off, the curve 
follower 81 of the latch 50 is situated near the end 79 of the plane 
section 78 in contrast to being located directly in front of the ramp 77 
before the gearwheel 70 was turned by 180 degrees. If now, an inside 
locking handle of the gearwheel is performed, starting from the state 
according to FIGS. 8 and 9, only the slide 40 is moved to the right into 
the unlocking position. The position of the slide 30 does not change, 
however, so the door lock remains locked. When the slide 40 is moved, the 
latch 50 can be moved away tangentially from the plane section 75 of the 
control curve 75 without any problems. As soon as the curve follower 81 
has left the plane section 78, the latch 50 is supported at a wall of the 
slide 30, so that curve follower 81 essentially keeps its level with 
regard to the control curve 75, and slides along the slide 30 with the 
slide 40. If the inside locking handle is moved back again, the slide 40 
also moves into the position shown in FIG. 8, wherein the curve follower 
81 again reaches the plane section 78 of the control curve 75. In order to 
facilitate the ascent onto the plane section 58, control curve 75 is 
provided with a slope 87 radially at the outside, as can be seen 
especially from FIG. 4. On the other hand, if the inside locking handle 
and with it the slide 40 remain in the unlocking position, the slide 30 
will be adjusted in case of an unlocking from the outside, such that In 
the unlocking position of the slide 30, the latch 50 engages the opening 
58 of the slide 30 under the power of the spring and in this way both 
slides are coupled again. The position of the single parts while the theft 
protection is in operation and after an operating of the inside locking 
handle into unlocking direction is shown in FIG. 10. 
Now it may happen, that the electric power supply for the second electric 
motor 65 fails to work. The gearwheel 70 may be either in rest position 
according to FIG. 6 or in rest position according to FIG. 8, or in any 
interim position. It should always be possible to move the two slides 30 
and 40 out of their unlocking position into the locking position, in order 
to be at least able to lock the door of the motor vehicle, even though it 
is not possible to protect against theft. In this case, the entire course 
for the curve follower 81 of the latch 50 has to be free. If the gearwheel 
70 is in the position according to FIG. 6, which corresponds to the theft 
protection not in operation, the latch 50 can be moved independently, so 
that a locking is possible. Latch 50 must also be moved independently if 
the circumference section of the gearwheel 70 not carrying a control curve 
is in the course of the curve follower 81. If, on the other hand, the 
gearwheel 70 takes another rest position, as shown in FIGS. 8, 10 and 11, 
the groove 80 between the flange 76 and the gear ring 71 of the gearwheel 
70 ensures that a locking is possible. In this locking operation the curve 
follower 81 can be pushed into groove 80, as can be seen from FIG. 12. If 
the ramp 77 is in the way of the curve follower 81 at the moment, curve 
follower 81 either slightly lifts the ramp 77 because of its resilient 
character or goes through completely beneath it. In this way, a locking is 
possible in each position of the gearwheel 70. Especially from FIG. 6, one 
can see that the direction of rotation of the gearwheel 70 when the curve 
follower 81 is ascending the ramp 77, is chosen in such a way that a power 
component actuated while curve follower 81 is ascending the ramp 77 acts 
to move the slides 30 and 40 in the locking direction. As the slides 30 
and 40 abut on a stop in this direction, this power can influence the 
position of the slides. This direction of rotation also ensures that, if 
the electric power supply fails, it is possible to drive the curve 
follower 81 under the ramp 77 so that the curve follower 81 does not 
ascend the ramp should the ramp 77 by chance be in the area of the curve 
follower 81. In this way it can be achieved that, in case of a failure of 
the electric power supply for the electric motor 65, the theft protection 
is not put into operation in any case via the inside locking handle. 
In the electromotive actuator according to the FIGS. 13 and 14, again a 
first slide 30 and a second slide 40 are provided. The second slide 40 
consists of two parts 95 and 96, which are spaced apart in the moving 
direction of the slides 30 and 40, which is again indicated by the double 
arrow A. The part 96 may be described as carrier, as it can be moved 
relative to the part 95 in direction of arrow A by an electric motor, when 
the part 95 of the slide 40 rests opposite the slide 30. For this reason, 
the carrier 96 is provided with a steering rack section 98, into which a 
pinion of the electric motor 97 engages. A recess 99 is formed by the 
distance between the parts 95 and 96 of the slide 40, into which recess 
99, the slide 40 is engaged by means of a jut 100. The two parts 95 and 96 
of the slide 40 are drawn onto each other by a helical spring 101. In 
addition a locking spring 102 is fixed at the part 95 of the slide 40, 
which attaches over the carrier 96 and which engages a locking recess 104 
of the carrier 96 by means of a locking device 103. The lock will be 
loosened in case of a certain influence of power in the moving direction 
of the slides, so that locking spring 102, locking device 103 and locking 
recess 104 can be described as a locking mechanism for limited power. 
In the electromotive actuator according to FIGS. 13 and 14, the slide 30 is 
also guided at a housing 20, while the parts 95 and 96 of the slide 40 are 
guided at the slide 30 independently of each other. 
The electric motor 97 is a motor with a reversible direction of rotation, 
which can be driven in one direction for the locking operation and the 
theft protection operation and in the other direction for the unlocking 
operation and for resetting the theft protection. 
In the state shown in FIG. 13, the slides 30 and 40 may be in the locking 
position. If the motor is now switched on into the direction of the arrow 
G, the carrier 96 is pushed to the left. The carrier 96 entrains the slide 
30 by means of the jut 100, so that the lock is unlocked. during the 
locking operation the electric motor 97 rotates into the other direction 
H, wherein the other part 95 and the slide 30 can be entrained by part 96 
of the slide 40 by means of a helical spring 101, until they are in the 
locking position. If the electric motor 97 rotates further in the same 
direction, only the carrier 96 is displaced because of the increased 
tensioning of the spring 101, until the locking device 103 engages into 
the locking recess 104. The limited power for loosing this lock is chosen 
in such a way that the tensioned spring 101 cannot loosen the lock on its 
own. Therefore, the parts 95 and 96 remain in the position shown in FIG. 
14, in which the recess 99 is essentially larger than the jut 100. If now 
an inside locking handle is operated which is connected with the part 95 
of the slide 40, the parts 95 and 96 of the slide 40 are urged to the 
left, but the slide 30 remains is rest position. Thus, an unlocking of the 
lock is not possible. 
During the unlocking operation according to the state shown in FIG. 14, the 
lock is disengaged at first so that the theft protection is reset and then 
the lock is unlocked by entraining the slide 30 because a certain 
resistance is put against the movement of part 95 of the slide 40 by the 
inside locking handle. 
However, it is also possible in the state according to FIG. 14, that at 
first only the parts 95 and 96 of the slide 40 will be displaced to the 
unlocking end position of the part 95 before the carrier 96 takes along 
the slide 30 after disengaging the lock between the locking device 103 and 
locking recess 104. 
The helical spring 101 is not necessary if a second locking recess for the 
locking device 103 in the carrier 96 is provided into which the locking 
device 103 can engage according to the position of the carrier 96 shown in 
FIG. 13. In this case, the carrier 96 entrains the part 95 of the slide 40 
and the slide 30 during the locking operation by means of this further 
lock. 
Finally, it is even possible to do without the helical spring 101 without a 
further lock if it is acceptable that during a locking operation only the 
carrier 96 is moved at first, enlarging the recess 99, until the locking 
device 103 engages into the locking recess 104 at which time the part 95 
of the slide 40 and the slide 30 are adjusted. In case of an unlocking 
operation, again only the parts 95 and 96 of the slide 40 would be moved, 
before the slide 30 is entrained. In this case, the theft protection would 
be set into operation before the locking operation and reset only after 
the unlocking operation.