EP1428959B1 - Motor vehicle door lock - Google Patents

Description

The present invention relates to a motor vehicle door lock with the Features of the preamble of claim 1 and a drive of the above Motor vehicle door lock with the features of the preamble of claim 9. In the present case, the term motor vehicle door lock are all Types of door, hood or flap locks summarized.

Modern motor vehicle door locks are increasingly motor-triggered Features equipped. Examples include the central locking function or the auxiliary opening function.

For the implementation of a motor-triggered function is usually a Drive with drive motor and actuator provided by one of the respective function associated adjustable functional element operable is. In the case of the auxiliary opening function is the adjustable functional element the pawl of the motor vehicle door lock.

To the circuit complexity for the motion control of To keep drive as low as possible and at the same time a low error rate To ensure the above drive is increasingly in the Block operation activated. This shows the known motor vehicle door lock (EP 0 811 101 B1), from which the invention proceeds, with reference to the above Opening auxiliary function. Here, the actuator of the drive has a Mitnehmerzapfen on, the pawl during an actuation operation pushes into the excavated position. Towards the end of the actuation process comes the driving pin in engagement with the pawl that the Drive motor is blocked, the motor current increases measurably and the drive motor is switched off after a certain delay time.

The problem with the known motor vehicle door lock is the fact that the above blockage of the drive in principle with an undesirable Impact noise is connected. Furthermore, the admission leads of the actuating element with a comparatively high torque for Danger of jamming in the above blockage.

The present invention is based on the problem that known motor vehicle door lock such and further develop that with the Block operation of the drive connected strokes noise as well as the jamming tendency be reduced.

The above problem is in a motor vehicle door lock with the Features of the preamble of claim 1 by the features of the characterizing Part of claim 1 solved.

Essential is the fact that the pawl does not blokkierend on the actuator engageable with the drive, but in the kinematic Chain seen from the drive motor to the actuator out in front of the actuator.

This has the advantage that the blocking required for block operation can be done at a location in the above kinematic chain at which the acting torque is comparatively low. The result is low Impact noise and a low tendency to jam.

There are a variety of ways of teaching the invention to design and develop. For this may refer to the dependent claims become.

With the preferred embodiment according to claim 2 ensures that At least at the output of the drive motor, the acting torque lower is as the torque acting on the actuator. The design of the Reduction gear with worm and worm wheel leads to a Robust realization, for the state of the art numerous standard solutions exist.

The symmetrical configuration of the actuating element according to claim 3 leads in that the control element after the motorized lifting of the pawl to stand so that a repeated lifting of the pawl - after repeated closing of the motor vehicle door - immediately possible is.

Depending on space, leverage ratios, speed requirements etc. the preferred embodiments offer optimal solutions.

There are a number of possibilities imaginable, at which point in the above said kinematic chain required for block operation Blocking of the drive. A preferred way is claim 5. Depending on the configuration of the worm wheel can be required for the blocking Set stop force in a simple manner. Another preferred Alternative shows a particularly high resulting compactness. A Another preferred embodiment ensures that when blocking the Drive no torques act on the pawl; so that the whole Stop force is absorbed by the storage of the pawl. This in turn leads to a particularly simple structural design.

Depending on the configuration of the adjusting element, in particular the engagement arrangement of the control element are certain reduction ratios between Worm wheel and actuator advantageous.

A particularly high flexibility, in particular with regard to the above-described Adjustability of the impact force on the worm wheel can be with reach the preferred embodiment according to claim 7.

The coupling of the latch and the pawl via a spring element according to Claim 12 results in that for the provision of these two components only a single spring element in the form of a tension spring is required. Furthermore, can be set by this coupling a reset behavior that from the respective position of the latch on the one hand and the pawl on the other is dependent. This can be advantageous in certain applications be. However, this is known per se from the prior art.

It is often the case that the pawl is coupled with another element is that expediently on the pivot axis for the pawl with is stored. This is often a pawl rocker arm, which creates a degree of freedom to the pawl over the Pre-rest in the main catch of the latch to get, if the drive already has reached its closed position. It is often realized by a "doubled" Ratchet lever. Is such coupled with the pawl Element present, it may be appropriate to further movement of the Drive in the sense of block operation by the coupled with the pawl Block element instead of the pawl itself.

According to another doctrine, which also has independent significance, is a drive for a motor vehicle door lock as such according to claim 9 claims. This drive can be any motor-triggered function be associated with a motor vehicle door lock. Moreover, may on the referenced above.

Fig. 1

in schematischer Darstellung ein Kraftfahrzeug-Türschloß mit Öffnungshilfsfunktion in der Vorraststellung,

Fig. 2

in schematischer Darstellung ein weiteres Ausführungsbeispiel eines Kraftfahrzeug-Türschlosses mit Öffnungshilfsfunktion in der Offenstellung,

Fig. 3

das Kraftfahrzeug-Türschloß gemäß Fig. 2 in der Hauptraststellung,

Fig. 4

in perspektivischer Darstellung das Kraftfahrzeug-Türschloß gemäß Fig. 2 in der Offenstellung.

In the following the invention will be explained in more detail with reference to a drawing illustrating only embodiments. In the drawing shows

Fig. 1

a schematic representation of a motor vehicle door lock with auxiliary opening function in the pre-locked position,

Fig. 2

a schematic representation of another embodiment of a motor vehicle door lock with an auxiliary opening function in the open position,

Fig. 3

the motor vehicle door lock according to FIG. 2 in the main latching position,

Fig. 4

in a perspective view of the motor vehicle door lock of FIG. 2 in the open position.

In Fig. 1, the latch 1 and the latch 1 associated, preferably by a spring 3 biased pawl 2 of a motor vehicle door lock shown. The latch 1 is in an open position, in a Pre-locked position and can be brought into a main position. For this purpose, the Lock catch 1 a Vorrast 4 and a main 5 on. The in the Vorraststellung located latch 1 is shown in Fig. 1. The lock latch acts 1 in a known manner with a locking pin 1 ', together. in principle can also be dispensed with the Vorraststellung, what is irrelevant to the proposed solution.

The pawl 2 has a hook-shaped formation 6 which engages with the pre-catch 4 or with the main catch 5 can be brought and the latch 1 then holds in the respective position. For this purpose, the latch 1 is also, in Fig. 1 on the right, biased.

The pawl 2 is present as a two-armed lever with two partial levers 7, 8 configured, wherein the first part lever 7 (in Fig. 1, the lower part of the lever) the has hook-shaped shape 6. The second partial lever 8 (in Fig. 1 of the Upper part lever) has a first actuating surface 9 and a second actuating surface 10 on.

It may be noted that the pawl 2 as one-armed Levers can be designed and that in addition to rotary and linear variants the pawl 2 are conceivable.

It is essential first that the pawl 2 by the in Fig. 1 shown Drive 11 can be lifted. Here, the actuating surfaces 9, 10 play a important role, as explained below.

In the present case, the drive 11 has the components drive motor 12, actuating element 13 and worm wheel 14 on. In this case, the drive motor 12 with a Worm 15 equipped with the external teeth of the worm wheel 14 combs. The external teeth of the worm wheel 14 meshes again with an external toothing on the adjusting element 13, so that by the drive motor 12, the adjusting element 13 is adjustable. By the above worm-worm wheel coupling is between the drive motor 12 and the actuator 13 a reduction gear interposed.

The adjusting element 13 has an engagement arrangement 16, which on the front side of the adjusting element 13 is arranged. It can also be provided that the engagement arrangement 16 in the sense of a control roller on the outer circumference of the adjusting element 13 is arranged.

In detail, the engagement arrangement 16 is over the adjustment range of the actuating element 13 seen symmetrically constructed and has three from the center of the actuating element 13 outgoing elongated control cam 17. There are the switching cam 17 is arranged so that after the motorized lifting of the Pawl 2 and - the repeated closing of the motor vehicle door - the subsequent collapse of the pawl 2 in the pre-restraint 4 and in the Main rest 5, the pawl 4 comes to stand in a position out of the a further lifting of the pawl 2 by the corresponding nearest Control cam 17 is possible. Depending on the application, it can too be advantageous to provide more than three switching cam 17. It is also conceivable to provide only a single switching cam 17 on the actuating element 13. On the preferred embodiment of a equipped with two switching cam 17 Control element 13 will be discussed below.

The lifting of the pawl 2 from the in the Vorrast 4 and in the main catch 5 sunken position takes place in such a way that an adjustment of the actuating element 13, in Fig. 1 to the left, the engagement of the switching cam 17 with the actuating surface 9 of the pawl 2 causes, whereby the pawl 2, in Fig. 1 on the left, is pivoted. This is the hook-shaped Ausformung 6 of the pawl 2 out of engagement with the pre-catch 4 and with the Main catch 5, so that the latch 1 falls in its open position. In this Position, it is such that the pawl 2 by their bias with a Bearing surface 18 in contact with a corresponding contact surface 19 at the latch 1 comes and is held in the pivoted position. In Fig. 1, the pivoted position of the pawl 2 in thin line thickness shown.

Essential to the present invention is the fact that the Schnekkenrad 14 has a stop 20, which is arranged on the worm wheel 14 is that he after the motorized pivoting of the pawl 2 before Block against the actuating surface 10 on the pawl 2 runs (the Schnekkenrad 14 rotates for this purpose in Fig. 1 on the right). It is preferable provided that the line of action of the impact force substantially through the pawl axis 21 of the pawl 2 runs and thus no undesirable Torque causes.

With the above-described stop 20 on the worm wheel 14 is first achieved that the shutdown of the drive motor 12 after the operation, ie the lifting of the pawl 2, in block mode is possible.

Particularly advantageous here is the fact that the stop 20 on Schnekkenrad 14 is arranged, and not on the actuator 13. This advantage becomes clear against the background that the coupling between the drive motor 12 via the worm wheel 14 with the actuator 13 as a reduction gear is designed. It is preferably provided that starting from the drive motor 12 with each gear stage, the speed drops and the torque increases. So it is so that the acting on the actuator 13 Torque is greater than the torque acting on the worm wheel 14. As a result, the resulting impact force between the stopper 20 and the actuating surface 10 of the pawl 2 comparatively small.

Basically, as explained in the general part of the description, with a reduction of the impact force a reduction of impact noises and a reduction in the tendency to jam.

The arrangement of the stopper 20 is not on the arrangement on the worm wheel 14 limited. Rather, it is inventively provided, the stop 20 along the kinematic chain from the drive motor 12 via the Schnekkenrad 14 as far as the actuating element 13 as close as possible to the drive motor 12 to provide. Therefore, a preferred embodiment provides the stop 20 directly to the worm 15 of the drive motor 12 to be arranged. The The opposite applies to the engagement arrangement 16, or for the switching cam 17, in the above kinematic chain as far as possible "removed" from the drive motor 12 should be arranged so that here the highest possible torque acting on the pawl 2 and a secure operation of the pawl 2 is guaranteed.

There are a number of other advantageous embodiments conceivable below to be discribed.

For example, it may be advantageous that the worm wheel 14 not only one single stop 20 has, but several on the adjustment seen the worm wheel 14 successively arranged stops 20th This is advantageous if an actuating operation of the pawl second not a full revolution of the worm wheel 14 required.

Further, instead of the worm wheel 14 or in addition to the worm wheel 14 any gear arrangement are provided, which may be at any Position the stop 20 or more stops 20 has. It may also be that the resulting transmission is designed in one stage, that So the worm 15 directly with the external teeth of the actuating element 13th meshes, so that the stop 20 is preferably, as already described above, is arranged on the worm 15 itself. Again, it is like any conceivable Embodiments preferably provided that the force of action line the impact force essentially passes through the pawl.

Basically, in the construction with the above concept, the Possibility, the actuator 13 with the worm wheel 14 largely arbitrary to pivot about the pawl axis 21. So it's a compact one Arrangement depending on space conditions possible. It is also possible to to pivot the drive motor 12 about the worm wheel axis 22. In the construction, therefore, a number of degrees of freedom are possible, the allow optimal utilization of space conditions.

It should also be noted that it is in the drive 11 does not have to act around a rotary drive, but that the inventive Success also with a linear drive possibly with return spring can be achieved. Essential is the thought, explained by the fundamental Stop 20 arrangement minimum impact forces in block operation to reach.

However, the rotary drive 11 described above offers the Advantage that no energy losses, usually with the use of a Return spring (see linear drive) are connected, are present. Finally, another advantage of the above detailed construction is that that the running noise of the resulting transmission between the drive motor 12 and actuator 13 is low, since the first gear stage as Schneckenradstufe is designed.

In the illustrated in Fig. 1 and so far preferred embodiment is the worm wheel 14 coupled to the actuator 13 such that three revolutions of the worm wheel 14 correspond to one revolution of the actuating element 13. The detailed design of this coupling depends essentially on the torque required on the adjusting element 13 and of the embodiment the engagement assembly 16 from.

A particularly preferred embodiment of the motor vehicle door lock according to the invention 2 to 4. Fig. 2 can be seen that the basic structure of this motor vehicle door lock identical to the in Fig. 1 illustrated motor vehicle door lock. Again, there is a latch 1 and a pawl 2 is provided, wherein the pawl 2 via a Drive 11 can be lifted. The drive 11 in turn has a drive motor 12, an actuating element 13 and a worm wheel 14.

A difference from the motor vehicle door lock shown in Fig. 1 consists in that the actuating element 13 is equipped with an engagement arrangement 16 is the only two outgoing from the center of the control element 13 elongated cam 17 has. By closing the motor vehicle door falls the pawl 2 of the open position shown in Fig. 2 in the in Fig. 3 illustrated main locking position. The adjusting element 13 is, as described above, designed so that the re-motorized lifting of the pawl 2 can take place directly - symmetry -. A rotation of the actuator 13 in Fig. 3 on the left causes the engagement of one of the switching cams 17 with the actuating surface 9 of the pawl 2, whereby the pawl second in Fig. 3 is pushed to the left in their Aushebestellung. It is the Control surface on the control cam 17 preferably designed such that initially a high torque with low speed on the pawl 2 is transferred to the between the latch 1 and the pawl 2 acting frictional forces to overcome safely. In the further Course of the rotation of the actuating element 13 then accelerates the Aushebevorgang. As in the embodiment shown in Fig. 1, it is such that the Pawl 2 in its raised position with a contact surface 18 in Appendix on a corresponding contact surface 19 on the latch 1 comes.

Also in accordance with the motor vehicle door lock shown in Fig. 1 has the worm wheel 1 a stop 20, in the same Way cooperates with the actuating surface 10 on the pawl 2. Again, it is so that the line of action of the impact force substantially through the pawl axis 21 of the pawl 2 is running.

Corresponding to the fact that the engagement arrangement 16 shown in Fig. 2 Embodiment has only two switching cam 17, that is Worm wheel 14 coupled to the actuator 13 such that two revolutions the worm wheel 14, in a particularly preferred embodiment four Revolutions of the worm wheel 14, one revolution of the actuating element 13 correspond. Determining which of the translations is chosen depends significantly on the torque required on the actuator 13 or the demanded at the actuator 13 speed.

Figs. 2 to 4 can be seen that the outer teeth of the Schnekkenrads 14 a first toothed portion 23 for coupling to the Drive motor 12 and a second gear portion 24 for the coupling having the actuating element 13. In this case, the stop 20 along the Worm wheel axis 22 seen between the two toothed sections 23, 24 arranged. In a preferred embodiment, the two gear sections 23, 24 a different diameter, so that a Further adjustment of the worm wheel 14 and the actuator 13th is given acting torques.

Particularly advantageous is the coupling shown in Figs. 2 to 4 between the latch 1 and the pawl 2. Here is a spring element 25 in Form of a helical tension spring provided in such a way with the lock latch. 1 coupled on the one hand and with the pawl 2 on the other hand, that the spring force on the pawl 2 in the direction of arrival and on the latch 1 in Direction of the open position acts. The connected with this special coupling Advantages have been explained in the general part of the description.

Finally, it should be noted that the pawl 2 a Coupling point 26, which is a manual lifting of the pawl 2, allowed for example via a cable, not shown. Further, a Microswitch 27 shown, the monitoring of the pawl position guaranteed.

In Fig. 4 is only hinted at recognizing that the pawl. 2 may be divided into two, so one coupled to the pawl 2 element can then have the blocking function for further movement can be assigned to the drive 11.

After another doctrine, which has independent significance, becomes one Drive a motor vehicle door lock claimed as such. This drive includes the drives shown in FIGS. 1 to 4, so that in so far on the above statements may be referenced. As in general Part of the description explains, but this is not limiting be understood.

Claims (10)

1. Motor vehicle door lock having locking elements, such as a lock latch (1) and pawl (2) and having a lock mechanism, the lock mechanism having a drive (11), the drive (11) having a driving motor (12) or the like and an adjusting element (13), it being possible for the pawl (2) to be lifted out by the drive (11) and, during the motorized lifting-out operation, the pawl (2) coming into the operative region of the drive (11) in such a manner that the further movement of the drive (11) can be blocked by the pawl (2) and the drive (11) can therefore be switched off in the blocking mode, characterized in that the pawl (2) in the kinematic chain, as seen from the driving motor (12) to the adjusting element (13), can be brought into engagement with the drive (11) in a blocking manner upstream of the adjusting element (13) and not at the adjusting element (13).
2. Motor vehicle door lock according to Claim 1, characterized in that a step-down gear mechanism is connected between the driving motor (12) and the adjusting element (13), the step-down gear mechanism preferably having a worm wheel (14) and a worm (15) driving the worm wheel (14).
3. Motor vehicle door lock according to Claim 1 or 2, characterized in that the pawl (2) can be lifted out by motor by means of actuation of the adjusting element (13), and in that the adjusting element (13) has an engagement arrangement (16) for engagement with the pawl (2), the engagement arrangement (16) preferably being of symmetrical construction, as seen over the adjustment region of the adjusting element (13).
4. Motor vehicle door lock according to Claim 3, characterized in that the engagement arrangement (16) has at least three, preferably precisely three, elongate switching cams (17) which emanate from the central point of the adjusting element (13), or in that the engagement arrangement (16) has two elongate switching cams (17) which emanate from the central point of the adjusting element (13).
5. Motor vehicle door lock according to Claim 2 and, if appropriate, according to Claim 3 or 4, characterized in that the worm wheel (14) has a stop (20) and in that, after the motorized lifting-out operation of the pawl (2) for blocking the drive (11), the stop (20) runs against the pawl (2) upstream of the block, or in that the worm (15) has a stop (20) and in that, after the motorized lifting-out operation of the pawl (2) for blocking the drive (11), the stop (20) runs against the pawl (2) upstream of the block, preferably in that the drive (11) between the driving motor (12) and the adjusting element (13) is configured as a single-stage gear mechanism, the force action line of the stop force preferably running through the pawl axis (21) during the blocking of the drive (11).
6. Motor vehicle door lock according to Claim 2 and, if appropriate, according to one of Claims 3 to 5, characterized in that the worm wheel (14) is coupled to the adjusting element (13) in such a manner that three revolutions of the worm wheel (14) correspond to one revolution of the adjusting element (13) or in that the worm wheel (14) is coupled to the adjusting element (13) in such a manner that two, preferably four, revolutions of the worm wheel (14) correspond to one revolution of the adjusting element (13).
7. Motor vehicle door lock according to Claim 2 and, if appropriate, according to one of Claims 3 to 6, characterized in that the external toothing of the worm wheel (14) has a first toothing section (23) for the coupling to the driving motor (12) and a second toothing section (24) for the coupling to the adjusting element (13), preferably in that the two toothing sections (23, 24) have a different diameter.
8. Motor vehicle door lock according to one of the preceding claims, characterized in that a spring element (25) is provided, and in that the spring element (25) is coupled to the lock latch (1), on the one hand, and to the pawl (2), on the other hand, in such a manner that the spring force acts on the pawl (2) in the latching direction and on the lock latch (1) in the direction of the open position, and/or in that the further movement of the drive (11) can be blocked not by the pawl (2) itself but rather by an element, for example a pawl-dragging lever, which is coupled to the pawl (2).
9. Drive for a motor vehicle door lock having adjustable functional elements, preferably according to one of the preceding claims, the drive (11) having a driving motor (12) or the like and an adjusting element (13), a functional element being adjustable by the drive (11) and, during the motorized adjustment of the functional element, the functional element coming into the operative region of the drive (11) in such a manner that the further movement of the drive (11) can be blocked by the functional element and the drive (11) can therefore be switched off in the blocking mode, characterized in that the functional element in the kinematic chain, as seen from the driving motor (12) to the adjusting element (13), can be brought into engagement with the drive (11) in a blocking manner upstream of the adjusting element (13) and not at the adjusting element (13).
10. Drive according to Claim 9, the motor vehicle door lock having locking elements, such as a lock latch (1) and pawl (2), and the functional element which can be adjusted by the drive (11) being the pawl (2) of the motor vehicle door lock, characterized by the features of the characterizing part of one or more of Claims 2 to 8.

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