MOTOR-VEHICLE DOOR LOCK

Abstract

A motor vehicle door lock comprising a locking mechanism that essentially consists of a rotary latch and a pawl. In addition, a lock retainer interacting with the locking mechanism is produced, which is introduced into the locking mechanism in order to achieve the closed position and rests on a load arm of the rotary latch in the closed position of the locking mechanism. According to the invention, the load arm is provided with to force deflection contour for the lock retainer. The force deflection contour changes a force direction acting on the load arm from the lock retainer, at least in the event of an excessive impact of the lock retainer.

Claims

1. A motor vehicle door lock comprising: a locking mechanism that includes a rotary latch and a pawl; and a lock retainer interacting with the locking mechanism to achieve a closed position of the locking mechanism, wherein the lock retainer rests on a load arm of the rotary latch in the closed position of the locking mechanism, wherein the load arm includes a force deflection contour for the lock retainer which changes a force direction acting on the load arm from the lock retainer during an excessive impact of the lock retainer.

2. The motor vehicle door lock according to claim 1, wherein the force deflection contour includes a lug which interacts with the lock retainer when the rotary latch is moved in an opening direction out of the closed position.

3. The motor vehicle door lock according to claim 2, wherein the lug changes a force vector acting on the rotary latch in a direction of movement of the lock retainer when the lock retainer rests.

4. The motor vehicle door lock according to claim 2, wherein the lug is configured as a fang.

5. The motor vehicle door lock according to claim 1, wherein the rotary latch includes a casing.

6. The motor vehicle door lock according to claim 5, wherein the force deflection contour is embedded in the casing.

7. The motor vehicle door lock according to claim 5, wherein the casing damps movements of the lock retainer relative to the load arm in normal operation.

8. The motor vehicle door lock according to claim 5, wherein the casing enables the lock retainer to interact with the floor deflection contour in an emergency operation.

9. The motor vehicle door lock according to claim 1, wherein the lock retainer is bow-shaped and includes a cylindrical locking pin for interaction with the locking mechanism.

10. The motor vehicle door lock according to claim 1, wherein the force deflection contour interacts with the lock retainer only in a pre-closed position of the locking mechanism.

11. The motor vehicle door lock according to claim 1, wherein the lock retainer includes a cylindrical locking pin.

12. The motor vehicle door lock according to claim 1, wherein the rotary latch includes a ratchet arm that interacts with the pawl.

13. The motor vehicle door lock according to claim 12, wherein the lock retainer is received between ratchet arm and the load arm.

14. The motor vehicle door lock according to claim 12, wherein the ratchet arm and the load arm are spaced apart.

15. The motor vehicle door lock according to claim 2, wherein the force deflection contour has a run-up edge.

16. The motor vehicle door lock according to claim 11, wherein during the excessive impact of the lock retainer, the cylindrical locking pin rests tangentially on a stop edge of the load arm.

Description

[0022] The invention is explained in greater detail below with reference to drawings, which show only one embodiment. In the drawings:

[0023] FIG. 1 shows a motor vehicle door lock according to the state of the art and

[0024] FIG. 2 shows the motor vehicle door lock according to the invention, partially in an enlarged view.

[0025] A motor vehicle door lock is shown in the figures. This essentially comprises a locking mechanism 1, 2 that consists of a rotary latch 1 and a pawl 2. The rotary latch 1 and the pawl 2 are each mounted in a lock case 3. For this purpose, the rotary latch 1 has a rotary latch axis 4 and the pawl 2 has a pawl axis 5.

[0026] Both axes 4, 5 are defined by bearing pins anchored in the lock case 3. It can be seen that both locking mechanisms 1, 2 and consequently also the associated motor vehicle door locks according to FIGS. 1 and 2 each assume their pre-ratchet position or pre-closed position. In this pre-ratchet position or pre-closed position, the respective pawl 2 has engaged in a pre-ratchet recess 1a of the rotary latch 1. The rotary latch 1 also comprises a main ratchet stop 1b or a main ratchet recess.

[0027] The basic structure also includes a lock retainer 6, 7 interacting with the locking mechanism 1, 2. The lock retainer 6, 7 is composed of a U-shaped bracket and a cylindrical locking pin 7 that extends between the two bracket legs and is shown in schematic section in both FIGS. 1 and 2. The locking pin 7 or the lock retainer 6, 7 interacts as a whole with the locking mechanism 1, 2.

[0028] In the exemplary embodiment, the lock retainer 6, 7 may be connected to a motor vehicle body, whereas the motor vehicle door lock and with it the locking mechanism 1, 2 are located inside a motor vehicle door (not shown). As soon as the motor vehicle door is closed, the lock retainer 6, 7 is introduced into the locking mechanism 1, 2, in each case in the closing direction S indicated by an arrow in FIGS. 1 and 2. The opposite direction to the closing direction S denotes the opening direction of the lock retainer 6, 7. Both directions define a total direction of movement of the lock retainer 6, 7.

[0029] During this closing process and consequently the movement of the lock retainer 6, 7 in the illustrated closing direction S, the locking pin 7 of the lock retainer 6, 7 ensures that the rotary latch 1 is pivoted counterclockwise about its rotary latch axis 4 starting from an open position indicated in FIG. 1. As soon as the rotary latch 1 has achieved the pre-ratchet position or pre-closed position shown in FIGS. 1 and 2 in this way, the pawl 2 can engage in the associated pre-ratchet recess 1a of the rotary latch 1. A movement of the pawl 2 about its pawl axis 5, supported for example by a spring, also corresponds to this in the counterclockwise direction.

[0030] With a further movement of the lock retainer 6, 7 in the illustrated closing direction S, the rotary latch 1 is pivoted further counterclockwise about its rotary latch axis 4, starting from the pre-ratchet position according to FIGS. 1 and 2, until it has reached the main ratchet position or main closed position. In this case, the pawl 2 engages in the main ratchet or moves counter to the main ratchet or the main ratchet stop 1b of the rotary latch 1. This is indicated by an arrow in FIG. 1.

[0031] In the closed position or pre-closed position or pre-ratchet position of the locking mechanism 1, 2 shown in FIGS. 1 and 2, the lock retainer 6, 7 or its locking pin 7 rests on a load arm 1c of the rotary latch 1. In addition to the load arm 1c, the rotary latch 1 also comprises a ratchet arm 1d, which interacts with the pawl 2. If, in this pre-closed position or pre-ratchet position, the lock retainer 6, 7 is subjected to an excessive impact in the opening direction, for example as a result of a side impact, i.e. counter to the closing direction S indicated by the arrow, the locking pin 7 acts on the load arm 1c of the rotary latch 1.

[0032] In the event of an excessive impact of the lock retainer 6, 7 in the opening direction of the locking mechanism 1, 2, which can be observed in the pre-closed position, the almost tangential resting of the cylindrical locking pin 7 against a stop edge 8 on the load arm 1c of the rotary latch 1 ensures that the locking pin 7 or the lock retainer 6, 7 is moved in the opening direction of the rotary latch 1. This is explained as follows.

[0033] Due to the tangential resting of the cylindrical locking pin 7 on the inclined stop edge 8, the force acting on the lock retainer 6, 7 in the opening direction acts on the stop edge 8 in such a way that the associated force vector F.sub.1 shown in FIG. 1, starting from a center point of the locking pin 7, engages perpendicularly or normally to the inclined or tangential stop edge 8 on the rotary latch 1 or the load arm 1c. The force vector F.sub.1 acting on the rotary latch 1 in this way ensures that a torque is applied to the rotary latch 1 in the opening direction, which is composed of the vector product of the force on the locking bolt 7 or lock retainer 6, 7 and the distance A of the force vector F.sub.1 from a distance line parallel through the center of the rotary latch axis 4. This is indicated in FIG. 1 by the relevant distance A.

[0034] The application of torque in the opening direction of the rotary latch 1, i.e. in the direction of a clockwise movement about the rotary latch axis 4, results from the fact that the force vector F.sub.1 encloses an acute angle with the closing direction S or the general direction of movement of the locking mechanism 1, 2 or lock retainer 6, 7 and at the same time the force vector F.sub.1 is oriented clockwise, i.e. in the opening direction of the rotary latch 1, pivoted away from the closing direction S. This applies to a motor vehicle door lock according to the state of the art, as shown in FIG. 1.

[0035] In contrast, FIG. 2 shows a motor vehicle door lock according to the invention. This is characterized in that the load arm 1c of the rotary latch 1 is provided with a force deflection contour 9, 10 which can be seen in particular in the enlarged detailed view. The force deflection contour 9, 10 interacts with the lock retainer 6, 7, but in the context of the exemplary embodiment only and exclusively in the event of an excessive impact of the lock retainer 6, 7 and only when the locking mechanism 1, 2 is in the pre-closed or pre-ratchet position shown in FIG. 2. If, on the other hand, the locking mechanism 1, 2 assumes the main ratchet position or main closed position (not shown), the cylindrical locking pin 7 is then accommodated and enclosed practically over at least half of its circumference by a contour 11 at the end of a fork jaw accommodating the locking pin 7 inside the rotary latch 1. In the main ratchet position or main closed position, unintentional opening of the locking mechanism 1, 2 without its destruction is consequently not possible. The fork jaw adjusts itself automatically between the load arm 1c and the ratchet arm 1d because the two arms 1c, 1d are spaced apart from one another.

[0036] The force deflection contour 9, 10 on the load arm 1c of the rotary latch 1 is only implemented in the motor vehicle door lock according to the invention according to FIG. 2, but not in the motor vehicle door lock according to the state of the art, as shown in FIG. 1. The load arm 1c of the rotary latch 1 provided with the force deflection contour 9, 10 in this way ensures that a force direction or force F.sub.1 acting on the load arm 1c from the lock retainer 6, 7 changes the force direction at least in the event of an excessive impact of the lock retainer 6, 7 in the opening direction of the locking mechanism 1, 2.

[0037] Applied to the specific exemplary embodiment, this means that the opening force on the lock retainer 6, 7 without a force deflection contour 9, 10 according to the state of the art according to FIG. 1 corresponds to the force vector F.sub.1, whereas the force deflection contour 9, 10 in the motor vehicle door lock according to the invention according to FIG. 2 results in the force vector F.sub.2 deviating from the opening force acting on the lock retainer 6, 7.

[0038] For this purpose, the force deflection contour 9, 10 is provided with a lug 9. In addition, the force deflection contour 9, 10 has a run-up edge 10, as evidenced by the enlarged view. The lug 9 ensures that the lock retainer 6, 7 moved in the opening direction of the rotary latch 1 interacts with the lug 9. The run-up edge 10 corresponds to the stop edge 8.

[0039] In fact, an excessive force on the lock retainer 6, 7 in the opening direction in the motor vehicle door lock according to the invention according to FIG. 2 initially leads to the force direction F.sub.1 being established. This is because the cylindrical locking pin 7 again rests tangentially against the stop edge 8 during this process. The stop edge 8 is defined according to the exemplary embodiment and not in a limiting manner by a casing 12 of the rotary latch 1. In fact, the rotary latch 1 is predominantly encased by the casing 12 in question, which is applied to the rotary latch 1 in the course of a plastic injection molding process. In the region of the stop edge 8, the force deflection contour 9, 10 is embedded in the casing 12, as the schematic and enlarged sectional view in FIG. 2 makes clear.

[0040] In normal operation, the casing 12 ensures that movements of the lock retainer 6, 7 and consequently its locking pin 7 relative to the load arm 1c of the rotary latch 1 are damped. As long as the conditions for normal operation prevail, during the closing process and when the lock retainer 6, 7 moves into the fork recess or fork jaw of the rotary latch 1, the rotary latch 1 is pivoted counterclockwise about the rotary latch axis 4 as described from its open position beyond the pre-ratchet position shown in FIG. 2 until it reaches the main closed position or main ratchet position.

[0041] If, on the other hand, emergency operation occurs in the pre-ratchet position or pre-closed position of the locking mechanism 1, 2 in the motor vehicle door lock according to the invention according to FIG. 2, the casing 12 initially gives way to the lock retainer 6, 7 or its locking pin 7. The locking pin 7 can consequently penetrate into the casing 12, as represented by a dot-dash line in FIG. 2. The force vector F.sub.1 corresponds to this because the cylindrical locking pin 7 rests predominantly tangentially on the stop edge 8 and the force vector F.sub.1 or a comparable scenario as described with reference to FIG. 1 is thereby established.

[0042] As soon as the casing 12 has given way and the locking pin 7 meets the leading edge or run-up edge 10, the movement of the locking pin 7 relative to the load arm 1c of the rotary latch 1 ensures that the locking pin 7 is moved in the direction of the lug 9 following the force vector F.sub.1 in the illustration according to FIG. 2. This means that the force deflection contour 9, 10 or its lug 9 interacts with the lock retainer 6, 7 moved in the opening direction of the rotary latch 1. This is because the movement of the locking bolt 7 relative to the load arm 1c of the rotary latch 1 also means that the rotary latch 1 is acted upon in the opening direction, i.e., clockwise about its rotary latch axis 4.

[0043] As soon as the lock retainer 6, 7 or its locking pin 7 interacts with the force deflection contour 9, 10 or the lug 9 designed as a fang, the lug 9 changes the force vector F.sub.1 acting on the rotary latch 1 in the closing direction S of the lock retainer 6, 7 when the lock retainer 6, 7 rests. This means that when the locking bolt 7 rests on the lug 9, in contrast to the force vector F.sub.1 that is initially formed, the opening force results in a changed force direction and consequently the force vector F.sub.2 shown in FIG. 2. The force vector F.sub.2 is oriented in the closing direction S of the lock retainer 6, 7 or opposite thereto or generally in its direction of movement. In other words, when the lock holder 6, 7 rests, the lug 9 changes its force vector F.sub.1 acting on the rotary latch 1 in the direction of movement of the lock retainer 6, 7, which corresponds to the closing direction S and the opening movement of the locking pin 7 directed opposite thereto. The force vector F.sub.1 becomes the force vector F.sub.2.

[0044] The result of this is that the force vector F.sub.2 has a reduced distance B compared to a parallel distance line drawn through the rotary latch axis 4. As a result, a reduced torque is applied to the rotary latch 1 at the same time, namely a torque reduction by at least a factor of 2. This is explained by the fact that the distance A is designed to be more than twice as large as the distance B. This means that due to the geometric design of the load arm 1c with the additional force deflection contour 9, 10, the torque acting on the rotary latch 1 in the pre-ratchet position or pre-closed position in the opening direction is almost halved or even further reduced. All of this is possible without additional measures to increase strength.