EP2697458A1

EP2697458A1 - Locking system

Info

Publication number: EP2697458A1
Application number: EP12721712.3A
Authority: EP
Inventors: Thomas SCHÖNENBERG; Hendrik Wahmann
Original assignee: Kiekert AG
Current assignee: Kiekert AG
Priority date: 2011-04-09
Filing date: 2012-03-24
Publication date: 2014-02-19
Anticipated expiration: 2032-03-24
Also published as: KR101531126B1; KR20130140168A; JP6037143B2; CN103597156B; JP2014513220A; CA2832352A1; US9371670B2; EP2697458B1; US20140091580A1; WO2012139544A1; CN103597156A; DE202011005086U1

Abstract

The invention relates to a locking system, in particular motor vehicle door lock, with at least one lever (1), and with a position-securing unit (5, 6, 7, 8) for the lever (1), wherein the position-securing unit (5, 6, 7, 8) has at least one spring element (5) and is designed for defining at least one stable position (E) of the lever (1), wherein the spring element (5) reaches through the lever (1) in the region of an opening (8), and wherein the opening (8) permits pivoting movements of the lever (1) in relation to the spring element (5) within a predetermined pivoting angle range (9).

Description

locking system

Description:

The invention relates to a locking system, in particular a motor vehicle door lock, with at least one lever, and with a position assurance unit for the lever, wherein the position assurance unit has at least one spring element and is set up to define at least one stable position of the lever.

In a locking system of the construction described in the introduction according to DE 102008 011 545 A1, the spring serves in conjunction with an associated contour on the lever for the composite formation of the bistable position assurance unit. For this purpose, the spring is a leg spring with two spring legs. To support and support the spring or leg spring is a pin which passes through an associated spring coil. Within the framework of the likewise generic teaching according to DE 10 2007 055 413 A1, a locking system with multi-stable component-spring element device is described. Here, an eccentric portion is provided on a component which is pivoted along a movement path between at least a first stable position and a second stable position. In this case, the spring element between a fixed bearing and a floating bearing is clamped and formed from a single-straight spring wire, which is bent at both ends by 90 °.

In the prior art, the procedure is consistently that the spring element performs more or less pronounced movements when taking the at least one stable position or when changing position. In fact, in the context of DE 10 2008 011 545 A1, a rotational

movement of the torsion spring around the turn by reaching pin. In the teaching according to DE 10 2007 055 413 A1, at least in one variant, the procedure is such that the spring element performs a more or less pronounced linear movement, at least in the region of the movable bearing.

The described rotary and / or linear movements of the spring element are observed in addition to the already obligatory and elastic deformations of the spring element and occur. As a result thereof, fatigue problems of the spring element can occur during intensive and long-term use or there is the risk that the spring element does not or no longer completely fills the desired function. That is, on long time scales in the state of the art under certain circumstances, the functional safety is at risk. Here, the invention aims to provide a total remedy. To solve this technical problem, a generic locking system in the invention is characterized in that the spring element passes through the lever in the region of an opening, wherein the opening allows pivotal movements of the lever relative to the spring in a predetermined pivoting angle range.

According to an advantageous embodiment, the spring element is made predominantly of a straight spring wire. In addition, it is usually the procedure that the spring element is clamped at each endpoints. On the other hand, an intermediate region remaining between the two end points can be elastically deformed, the lever interacting with the spring element providing the desired elastic deformations of this intermediate region.

In the context of the invention, therefore, first and foremost, a spring element designed as a straight spring wire is used which adjoins

Endpoints is clamped. As a result, any linear movements, rotations, etc., of the spring element are not permitted in the beginning of operation, so that the previously described fatigue problems can not or no longer occur. However, the elasticity of the spring is used in the invention in order to represent the at least one stable position of the lever can.

In most cases, the position assurance unit is designed bistable. That is, the lever can be pivoted into two stable positions, wherein the two respective stable positions are defined by the interaction of the lever with the spring element respectively. This is done in detail by the fact that the spring or the spring element engages through the opening in the lever and the opening is designed so that the described pivoting movements of the lever are allowed. In most cases, the lever can be pivoted from one stable position to the other stable position, wherein the angular range between these two stable positions represents the predetermined swivel angle range.

To achieve this in detail, the opening in the lever advantageously has two substantially opposite and spaced contact surfaces for the spring element. In order to enable the pivoting of the lever relative to the spring element penetrating it, taking into account the predetermined pivoting angle range, the contact surfaces typically have a distance from each other which is a multiple of a diameter of the spring element. As already explained, the spring element is predominantly designed as a straight spring wire or produced predominantly from such a straight spring wire. The straight spring wire typically has a cylindrical shape with a circular cross-section and associated diameter. The diameter of the spring element fits

usually two or even three times side by side between the two defining the opening in the lever contact surfaces.

In other words, the distance between the two said contact surfaces, for example, twice, three times, etc., the diameter of the spring element. Of course, decimal multiples are conceivable and are included, for. B. such that the distance is 1, 5 times, 2.5 times the diameter of the spring element. The two defining the opening in the lever contact surfaces are designed differently. In fact, the contact surfaces are, on the one hand, a deflection surface and, on the other hand, a stop surface. The deflection surface abuts against the spring element during all pivoting movements of the lever. In contrast, the stop surface moves only to define the stable position against the spring element.

Due to this interpretation explains that the deflection deflects the spring element or the straight spring wire between the two stable positions on one side, that is in one direction. Because the spring wire or the spring element is clamped at its end points in each case, so that the spring element acting on the deflection surface for the described elastic deformation of the spring element in one direction, that is one-sided, provides. In the respectively stable position, however, the spring element undergoes substantially no deflection. That is, in this stable position, the deflecting surface does not or practically does not act on the spring element.

In this way, a tilting point of the lever between the two stable positions. In the region of this tilting point, the spring element undergoes a maximum unilateral deflection, with the aid of the deflection surface.

In fact, the tilting point corresponds to the fact that the spring element generates a maximum of the lever counteracting force by the maximum deflection, so that the lever is always anxious to avoid in one or the other direction compared to the tipping point. Because in both directions on both sides of the tipping point, the opposing forces built up by the spring element are designed to be smaller than in the region of the tipping point. This explains why the position assurance unit is designed to be bistable, because the two stable positions correspond to the fact that the spring element exerts no or at most a small counterforce on the lever and this logically assumes the relevant stable position advantageous.

In general, the tipping point is centered between the two stable positions. This central position is compared to the predetermined pivoting angle range. In addition to this predetermined pivoting angle range with end-side stable positions and central tilting point, an overstroke range is observed beyond the stable position. In this Überhubbereich the spring element undergoes a two-sided deflection. That is, the spring element is deflected in the overstroke in two directions, namely radially outwardly and radially inwardly compared to a pivot point or a rotation axis of the lever mounted on the relevant axis respectively pivot lever. In contrast, the spring element experiences in the tipping point and between the two stable positions only a deflection radially outward. The deflection of the spring element in the overstroke range both radially outwardly and radially inwardly causes the spring element to describe an approximately S-curved course in this overstroke region. As a result, the spring element builds up particularly strong and acting on the lever counter forces, which the lever in the direction of the stable

Apply position back. The two overstroke ranges, in each case beyond the stable position, thus represent, as it were, resilient end stops, so that the lever does not expressly travel against any mechanically strong end stops. Rather, the end stops - if you will - designed springy, namely, are in the form of each described Überhubbereiche ago. These overstroke ranges correspond to a two-sided deflection of the spring element and thus to the fact that the lever located in the overstroke region experiences a force acting on it in the direction of the stable position. Such a design is particularly advantageous in the light of the fact that the lever is typically a pivoting lever mounted on the axis already mentioned. In addition, the lever is usually equipped with a motor drive, which ensures a certain self-locking of the lever. That is, the opposing forces built up by the spring element assist in a motorized movement of the lever in the direction towards the stable position or counteract a motorized movement of the lever beyond the stable position. Thus, as soon as the motor drive acts on the lever beyond the stable position, the opposing forces of the spring element which then arise in the associated overstroke range ensure that the motor drive and with it the lever are, as it were, turned back. This explains the function of the thus realized elastic end stops.

In this way, the locking system according to the invention can be used particularly advantageously for the realization of a worm drive. That is, the lever including the motor drive advantageously acts as a worm drive, which can be used, for example, in conjunction with a locking lever, an anti-theft lever, etc. of a motor vehicle door lock. In this case, mechanical end stops are not required.

derlich, because the locking system according to the invention is equipped with alternative resilient end stops. This increases the service life and reliability, especially as fatigue phenomena of the spring element according to the invention - in contrast to the prior art - are no longer observed. Here are the main benefits.

In the following the invention will be explained in more detail with reference to a drawing showing only one exemplary embodiment; 1 to 3, the locking system according to the invention in different

Functional positions taking into account a predetermined swivel angle range and

4 and 5, the locking system according to FIGS. 1 to 3 in each case one

Overlift range or the functioning of the resilient end stops.

In the figures, a locking system is shown, in this case partially a motor vehicle door lock. From this motor vehicle door lock only a worm wheel 1 is shown, which is offset by means of a screw 2 in rotation about an axis 3. For this purpose, the worm wheel 2 is connected to an output-side output shaft of a motor drive 4. The motor drive 4 may be acted upon by a control unit, not shown.

In addition, the worm wheel 1 can work on a not explicitly shown central locking lever, an anti-theft lever, etc., or coincide with such a lever.

The basic mode of operation may in this case be designed as described in DE 197 13 864 C2 of the Applicant. In addition, reference should be made to the two publications DE 102008011 545 A1 and DE 10 2007 055413 A1, which were already mentioned in the introduction. In any case, the locking system according to the invention shown in excerpts is typically found in a motor vehicle door lock or is with such a congruent. This is not to be understood as limiting.

The worm wheel 1 and the lever 1 realized at this point are - as already mentioned - a lever or pivoting lever 1, which is mounted on the axle 3 and can perform pivoting movements about this axis 3. The pivoting movements of the lever 1 are limited, by a position assurance unit 5, 6, 7, 8 for the lever 1. The position assurance unit 5, 6, 7, 8 has at least one spring element 5. In addition, the position assurance unit 5, 6, 7, 8 is set up to define at least one stable position I of the lever 1.

In the context of the embodiment, two stable positions E of the lever 1 are observed, namely a first stable end position E as shown in FIG. 2 and a second stable end position E corresponding to FIG. 3. Between these two stable end positions E passes over the lever 1 a predetermined swivel angle range 9, which corresponds to an associated swivel angle α. In the exemplary embodiment, the pivot angle α is about 60 ° to 80 °, in particular about 70 °.

The spring element 5 is designed here as a straight spring wire 5. In addition, the spring element 5 is clamped at each end points 5 '. For this purpose, the straight spring wire 5 may be angled in the region of the end points 5 'by 90 ° in comparison to the plane of the drawing,

hearing receptive bores are anchored in a lock housing, not shown. In any case, the spring element 5 or the straight spring wire 5 according to the invention performs no linear movements, which can be traced back to its fixed clamping at the two associated end points 5 '.

It can be seen that the spring element 5 passes through the lever 1 in the region of an opening 8. In this case, the opening allows 8 pivotal movements of the lever 1 relative to the spring 5 and the spring element 5 in the predetermined pivoting angle range 9. To achieve this in detail, in the region of the opening 8, two substantially opposing and spaced bearing surfaces 6, 7 for the spring element 5 are realized.

The two contact surfaces 6, 7 have a distance A from each other, which is a multiple of a diameter D of the spring element 5. In fact, the spring element or the straight spring wire 5 is designed predominantly cylindrical with a circular cross section. The distance A between the two contact surfaces 6, 7 moves within the scope of the embodiment in the range of about three times the diameter. That is, it applies: A «3D.

In this way, the lever or pivot lever 1 perform the pivoting movements shown in FIGS. 1 to 3, taking into account the predetermined pivoting angle range 9 and the associated pivoting angle α.

The one bearing surface 7 is formed as a deflection 7. In contrast, the other contact surface 6 is an abutment surface 6. When comparing FIGS. 1 to 3, it can be seen that the deflecting surface 7 during

all pivotal movements of the lever 1 on the spring element or the straight spring wire 5 is applied. In contrast, the stop surface 6 moves only to define the respective stable position E as shown in FIGS. 2 and 3 respectively against the spring element 5. That is, as soon as the stop surface 6 moves against the spring element 5, the stable position E corresponding to FIG 2 or according to the Fig. 3 taken by the lever or pivot lever 1.

The deflection surface 7 ensures that the spring element 5 is deflected on one side, ie in one direction, between these two stable positions E previously referred to. In the present case experiences the spring element or the straight spring wire 5 through the deflection surface 7 a deflection radially outwardly compared to the axis of rotation 3 of the pivot lever 1. This is indicated by an arrow in Fig. 1 and results from the dashed or dash-dotted lines undeflected course of the spring element or of the straight spring wire in FIGS. 1 to 5.

It can be seen that the spring element 5 undergoes a maximum unilateral deflection radially outward in the region of a tilting point K according to FIG. In this case, the tilting point K is located between the two stable positions E according to FIG. 2 and FIG. 3. That is, the corresponding end position positions E. The tilting point K is approximately centered between the two stable positions with respect to the predetermined pivoting angle range 9 or between the two end positions E arranged.

As soon as the pivot lever 1 undergoes a movement beyond the stable positions or end positions E, as shown in FIGS. 4 and 5, the lever or pivoting lever 1 moves into an overstroke range Ü. In this area beyond the stable position E or in Überhubbereich Ü learns the

Spring element 5 a two-sided deflection. In fact, the spring element 5 is deflected in the overstroke range Ü on the one hand radially outwardly and on the other hand radially inwardly. The corresponding arrows in FIGS. 4 and 5 indicate this.

The deflection radially outward is effected again by the deflection surface 7, whereas the stop surface 6 ensures that the spring element 5 is additionally acted upon radially inwardly. As a consequence thereof, the spring element in the overstroke range Ü and beyond also describes an approximately S-curved course. Due to this S-curved course of the spring element 5 strong restoring forces are exerted on the lever 1 in the direction of the respective end position E, which pivot the lever or pivot lever 1 as it were in the direction of the end position E about the axis 3 or in this Apply direction. These forces may be so strong that possibly even the drive 4 is rotated back for the lever 1.

As a consequence thereof, the locking system described has, as it were, elastically formed end stops or resilient end stops which exert an effect in the overstroke range Ü. For as soon as the lever 1 is transferred into the respective overstroke range Ü beyond the stable end position E, these forces lead to the pivoting lever 1 being acted upon by retrograde forces as a result of the S-arc-shaped deformation of the spring element 5.

With reference to the preceding explanations it is clear that the two contact surfaces 6, 7 in conjunction with the opening 8 in the lever 1 in combination with the spring element 5 for the described positioning of the lever respectively pivot lever provide and can also provide. Logically define

the two contact surfaces 6, 7 in conjunction with the opening 8 and the spring element 5, the previously already referred to Positionssicherungs- unit 5, 6, 7, 8. Here, the stop surface 6 is designed predominantly circular, whereas the deflection 7 a T-shaped Character with two arcuate end portions T and a predominantly straight central portion 7 "As long as the lever 1 moves in the predetermined pivoting angle range 9, provides mainly the slightly curved central region 7" for the radially outward deflection of the spring element 5. In contrast, come arcuately curved end portions 7 'of the deflection surface 7 are predominantly used when the lever 1 moves into the respective overstroke range Ü.

Claims

claims:

1. Locking system, in particular motor vehicle door lock, with at least one lever (1), and with a position securing unit (5, 6, 7, 8) for the lever (1), wherein the position securing unit (5, 6, 7, 8) at least one spring element (5) and is arranged to define at least one stable position (E) of the lever (1), characterized in that the spring element (5) passes through the lever (1) in the region of an opening (8), wherein the opening (8) Pivoting movements of the lever (1) relative to the spring element (5) in a predetermined Schwenkwinkeibereich (9) permits.

2. Locking system according to claim 1, characterized in that the opening (8) in the lever (1) has two substantially opposite and spaced-apart contact surfaces (6, 7) for the spring element (5).

3. Locking system according to claim 2, characterized in that the abutment surfaces (6, 7) have a distance (A) from each other, which is a multiple of a diameter (D) of the spring element (5).

4. Locking system according to claim 2 or 3, characterized in that the bearing surfaces (6, 7) on the one hand as a deflection surface (7) and on the other hand as a stop surface (6) are formed, wherein the deflection surface (7) during all pivotal movements of the lever (1). on the spring element (5) is applied, whereas the stop surface (6) only to define the stable position (E) moves against the spring element (5).

5. Locking system according to one of claims 2 to 4, characterized in that the deflection surface (7) deflects the spring element (5) between two stable positions (E) on one side, whereas the spring element (5) in the respective stable position (E) in Essentially no deflection experiences.

6. Locking system according to one of claims 1 to 5, characterized in that the spring element (5) in the region of a tilting point (K) of the lever (1) has a maximum unilateral deflection.

7. Locking system according to claim 6, characterized in that the tilting point (K) is arranged centrally in relation to the predetermined pivoting angle range (9) between the two stable positions (E).

8. Locking system according to one of claims 1 to 7, characterized in that the spring element (5) beyond the respective stable position (E), in

Over-travel range (Ü), experiences a two-sided deflection.

9. Locking system according to claim 8, characterized in that the spring element (5) in the overstroke region (Ü) describes an S-curved course.

10. Locking system according to one of claims 1 to 9, characterized in that the spring element (5) extends linearly formed.

11. Locking system according to claim 10, characterized in that the spring element (5) is made predominantly of a straight spring wire (5).

12. Locking system according to one of claims 1 to 11, characterized in that the spring element (5) in each case at end points (5 ') is clamped, whereas an intermediate region between the end points (5') experienced by the lever (1) causes elastic deformations ,

13. Locking system according to one of claims 1 to 12, characterized in that the lever (1) as on an axis (3) mounted pivoting lever (1) is formed.

14. Locking system according to one of claims 1 to 13, characterized in that the lever (1) has a motor drive (4).

15. Locking system according to one of claims 1 to 14, characterized in that the lever (1) including the drive (4) is designed as a worm drive for example, a locking lever, an anti-theft lever, etc. of a motor vehicle door lock.