Motor vehicle lock

Abstract

The invention relates to a motor vehicle lock having a lock bolt (4) and at least one locking pawl (5), wherein the lock bolt (4) can be transferred in a locking movement from an open position to a locked position during a locking process, and the locking pawl (5) can be transferred to a fallen-in state, wherein an electric drive (11) having an execution element (12) is provided, which displaces the execution element (12) during an opening process in such a way that the execution element (12) transfers the locking pawl (5) to a lifted state, in which the locking pawl (5) releases the lock bolt (4) so that the lock bolt (4) can realize an opening movement from the locked position to the open position. It is proposed that the execution element (12) is additionally coupled with the lock bolt (4) via a guide assembly (15) in such a way that the electric drive (11) guides the opening movement of the lock bolt (4) at least in one phase of the opening process and / or the locking movement of the lock bolt (4) at least in one phase of the locking process by means of the guide assembly (15).

Description

[0001] The present invention relates to a vehicle lock according to the preamble of claim 1, a vehicle locking system according to claim 19, and a method for operating the vehicle locking system according to the preamble of claim 20.

[0002] The vehicle locks discussed can be used for all types of locking elements in motor vehicles. These specifically include locking elements such as side doors, rear doors, tailgates, tailgates, engine hoods, etc. These locking elements can, in principle, be designed as revolving doors or sliding doors.

[0003] The prior art upon which this invention is based (DE 10 2008 035 183 A1) relates to a motor vehicle lock having a latch and a locking pawl as locking elements. The latch can be brought to a locked position, in which the latch is engaged with a locking component, and in which the latch is secured by the locking pawl. The motor vehicle lock has an electric actuator configured to lift the locking pawl during opening. Furthermore, the locking pawl is supported on a lever pivotable about a latch axis. Thus, via the electric actuator, the locking pawl axis can be displaced relative to the latch. Therefore, the locking pawl enables a locking-assisted process for displacing the latch to the locked position, and for unloading the latch during opening.

[0004] The challenge lies in the limitations of the engagement design between the locking pawl and the latch, and the relatively complex structure of the locking pawl, which needs to perform various functions beyond its actual blocking action. Furthermore, a separate motor is required to lift the locking pawl, leading to further complexity and additional manufacturing costs.

[0005] The present invention is based on designing and improving known motor vehicle locks in such a way that further optimizations are made to address the aforementioned challenges.

[0006] The above problem is solved by the features of claim 1.

[0007] The starting point of this invention is that an electric actuator, through the displacement of an actuating element, switches a locking pawl to a raised state. At its core is the fundamental concept that the actuator, which thus functions as an opening actuator, also guides the movement of the latch. Latch guidance is achieved here through additional coupling with the latch, and therefore not necessarily through the locking pawl, thereby allowing for a more flexible allocation of functions related to the opening and / or locking processes to the actuator.

[0008] Specifically, it is proposed that the actuator is additionally coupled to the latch via a guide assembly such that the electric actuator guides the opening movement of the latch at least in one phase of the opening process and / or guides the locking movement of the latch at least in one phase of the locking process.

[0009] Particularly preferably, the guide assembly according to claim 2 is used to delay the opening movement of the latch in order to minimize the contact force of the locking pawl and the noise generated during opening. Especially for large locking elements with large-area inner seals (such as tailgates), the latch experiences significant forces in the locked position due to its interaction with the locking components; these forces are released relatively quickly by the lifting of the locking pawl. The electric actuator can at least partially compensate for these forces via the actuating element and the guide assembly. This allows for unloading of the latch, or even displacement in the opposite direction of opening, thereby enabling easy lifting of the locking pawl with minimal noise.

[0010] Preferably, the delay until the middle position of the latch is reached, as described in claim 3, combines the acoustic advantages of latch guidance with a rapid opening process.

[0011] The design according to claim 4 involves moving the latch and thus the locking element outward via a guiding component. This outward movement is primarily used to break up ice buildup on the locking element to ensure it can be opened. Furthermore, it allows for outward movement of locking elements, particularly those without handles, so that an operator can insert their hand into the opening gap of the locking element to manually open it further.

[0012] Also preferred is the locking assist function according to claim 5, which electrically assists the locking process. For example, the locking assist function moves the latch from the pre-locked position to the main locking position, thereby providing electrical assistance for the final segment of the locking movement that must overcome the sealing pressure inside the door. With the proposed solution, the same electric actuator and actuator can be used again, thus simplifying the structure of the vehicle lock.

[0013] According to claim 6, the actuator holds the locking pawl in the raised position at the end of the opening process, thereby preventing the locking pawl from prematurely falling back to the lowered position. This reliably prevents accidental entry into the pre-locked state during the opening process. Similarly, a snow load function can also be implemented, wherein the locking pawl can only return to the lowered position after the latch has reached the open position.

[0014] Particularly preferably, the guiding component is implemented via a crank-lever mechanism as described in claim 7. This crank-lever mechanism allows the transmission ratio of the force guiding the latch to remain variable during the opening and / or locking processes. For example, this can generate a larger, subsequently decreasing, delaying force at the beginning of the opening process. Furthermore, the locking assist force can be optimized based on the reaction force generated by the door sealing pressure and increasing with the locking process.

[0015] The overtravel position achievable by the latch via the locking assist function can be achieved by a longitudinal guide of the crank lever mechanism, which in particular has an elastic housing with a pivot bearing to achieve acoustic optimization, which is also the subject of claims 8 and 9.

[0016] According to claim 10, further acoustic optimization of the crank lever mechanism is achieved via a damping device formed by the latch cover of the first guide rod.

[0017] The preferred designs according to claims 11 and 12 relate to functional and opening profiles of the actuator, which allow for precise matching between the guidance of the latch and the opening process of the locking pawl. Claim 13 provides a particularly compact actuator design in which the profiles are arranged in different planes.

[0018] In the design according to claim 15, the pivotable actuator allows for lifting and resetting to the initial position during opening by means of cyclic displacement of the actuator along the same rotational direction. Therefore, for controlling the actuator, it is sufficient, particularly to acquire the initial position solely by means of a sensor.

[0019] In a further preferred embodiment according to claims 17 and 18, a locking lever is provided for locking the pawl, which, in particular, prevents the locking pawl from rotating into a raised state due to inertia in the event of a collision. The locking lever can also be actuated by an actuator.

[0020] According to another embodiment of claim 19, which has independent significance, a vehicle locking system is claimed, the vehicle locking system having the proposed vehicle lock and a control component for controlling an electric actuator. Reference can be made to all statements regarding the proposed vehicle lock.

[0021] According to a further embodiment of claim 20, which is also independently significant, a method for operating a motor vehicle locking system is claimed. Here, the core element is additionally coupled to the latch via a guide assembly such that the electric actuator guides the opening movement of the latch at least during one phase of the opening process, and / or guides the locking movement of the latch at least during one phase of the locking process. Reference can be made to all embodiments of the proposed motor vehicle lock and the proposed motor vehicle locking system.

[0022] The invention will be explained in more detail below with reference to the accompanying drawings, which illustrate embodiments only. In the drawings:

[0023] Figure 1 Subfigure a) shows a motor vehicle with the proposed motor vehicle locking system, subfigure b) shows the motor vehicle lock of the motor vehicle locking system, and subfigures c) and d) show corresponding perspective views of the actuating elements of the motor vehicle lock.

[0024] Figure 2 Show Figure 1 The vehicle lock in b) has been removed, along with the actuator component.

[0025] Figure 3 Neutron diagrams a), b), and c) show side views of the vehicle lock during the opening process.

[0026] Figure 4 Neutron diagrams a), b), and c) show side views of the vehicle lock during the opening process.

[0027] Figure 5 Neutron diagrams a), b), and c) show side views of the vehicle lock during the locking process, and

[0028] Figure 6 Neutron diagrams a), b), and c) show side views of a vehicle lock during the opening process.

[0029] The embodiment shown in the figure, and preferred in this respect, relates to a motor vehicle lock 1 for a locking element 2 of a motor vehicle 3. Regarding the design of the locking element 2, reference can be made to the introductory description, which illustrates the working principle of a motor vehicle lock 1 for a locking element 2 designed as a tailgate or tailgate. However, all embodiments are equally applicable to all other types of locking elements of the motor vehicle 3.

[0030] The vehicle lock 1 is equipped with a latch 4 and at least one locking pawl 5. The latch 4 can be moved to at least one locked position, in which case, and preferably the master locked position, is located. Figure 3 a); Figure 6 a)), and can be moved to the pre-locked position when appropriate ( Figure 5(b)) is used to remain engaged with the locking component 6 and can be moved to the open position. Figure 4 c) and 5a) are used to release and accommodate the locking component 6, which in this case and preferably by pivoting about the geometric latch axis 7. The locking component 6 can be a locking bracket, locking bolt, etc. In this case and preferably, the vehicle lock 1 is arranged at the locking element 2, while the locking component 6 is fixedly arranged at the body of the vehicle 3, wherein the opposite arrangement is conceivable.

[0031] The locking pawl 5, which interacts with the latch 4, can be brought into the dropped state. Figure 3 a), 5b), 5c); 6a)) and the state of being lifted ( Figure 3 b), 3c), 4, 5a), 6c), in this case and preferably by pivoting about the geometric locking pawl axis 8. In the locked state, the locking pawl 5 prevents the latch 4 in the locked position from shifting in its opening direction.

[0032] During the locking process, the latch 4 can transition from the open position to the locked position during the locking motion, while the locking pawl 5 can simultaneously transition to the engaged state. By pivoting the latch 4 in the locking direction opposite to the opening direction, it can move from the open position to the locked position, thereby allowing the locking pawl 5 to engage with the main latch 9 (main locked position) or the pre-locking latch 10 (pre-locked position) of the latch 4 through the engaged action. In this case, the locking motion corresponds to the pivoting motion of the latch 4, which in... Figure 5 The center points clockwise. In this case, and preferably, a spring load is applied to the locking pawl 5 in the direction of the falling-in state, so that the locking pawl 5 falls in during the locking process by reaching the main locking position or the pre-locking position. The locking process is particularly based on the manual and / or electric locking of the locking element 2, wherein when the latch 4 is in the open position, the locking member 6 is introduced into the locking member receiving portion of the latch 4.

[0033] An electric actuator 11 with an actuating element 12 is provided, which displaces the actuating element 12 during the opening process such that the actuating element 12 switches the locking pawl 5 to a raised state. Preferably, the electric actuator 11 has a rotary drive motor 13, the output motion of which is converted into the displacement of the actuating element 12. The lifting of the locking pawl 5 is thus achieved during the opening process from the displacement of the actuating element 12. Particularly preferably, the actuating element 12 is designed to be pivotable about a geometric actuating element axis 14 by means of the actuator 11. Figure 3 The sequence of a), 3b), and 3c) exemplarily illustrates the pivoting of the actuator 12 in a clockwise direction, thereby achieving the transition of the locking pawl 5 to the lifted state.

[0034] In the lifted position, locking pawl 5 releases latch 4, thereby enabling latch 4 to move from the locked position to the open position. Latch 4 can be switched to the open position, for example, by spring preload, by removing locking member 6, and / or by electric drive (see [link to relevant documentation]). Figure 4 (sequences a), b), and c).

[0035] At this point, the key point is that the actuator 12 is additionally coupled to the latch 4 via the guide assembly 15 such that the electric actuator 11 guides the opening movement of the latch 4 at least in one phase of the opening process, and / or guides the locking movement of the latch 4 at least in one phase of the locking process.

[0036] The guide assembly 15 is additionally and thus coupled to the latch 4 independently of the locking pawl 5. In this case, the guide assembly 15 preferably does not assume a locking effect with respect to the latch 4. The guide assembly 15 is adapted to introduce forces into the latch 4 during the opening and / or locking movements, these forces being used to guide the movement of the latch 4 and to enable the opening and / or locking movements to be performed in a manner controlled via the actuator 12 and the driver 11.

[0037] Here, the latch 4 can be guided in one direction, so that only forces assisting or resisting the corresponding movement are introduced. Alternatively, the latch 4 can be guided bidirectionally, wherein, for example, during a phase of the corresponding movement, the positions of the latch 4 and the actuator 12 are mutually dependent in a defined manner.

[0038] Particularly preferably, the actuator 12 is coupled to the latch 4 via the guide assembly 15 such that during the opening process, a delaying force resisting the opening movement can be introduced into the latch 4 via the electric actuator 11 through the guide assembly 15.

[0039] This delaying force can slow down the opening motion, thereby achieving acoustic optimization of the vehicle lock 1. Figure 3 a) This shows the main locking state at the start of the opening process. As the actuator 12 shifts, the locking pawl 5 shifts in the lifting direction, wherein... Figure 3 b) shows the state when latch 4 is released.

[0040] When the latch 4 is subjected to significant door sealing pressure due to its interaction with the locking member 6, the release of the latch 4 typically results in the sudden disengagement of the locking pawl 5 and the springing open of the vehicle lock 1, accompanied by noise (opening sound). However, here, the actuator 12 introduces a delaying force into the latch 4 via the guide assembly 15, preferably at least when the latch 4 is released via the locking pawl 5. Here, the delaying force slows down the opening movement. Furthermore, it can be configured to hold the latch 4 by means of the guide assembly 15 during release, thereby temporarily stopping it during the opening movement. Additionally, it is conceivable that, before and / or during release, the latch 4 is shifted in the opposite direction to the opening direction by means of the guide assembly 15 to unload the locking pawl 5 when shifting to the lifted state, and further minimize noise generation.

[0041] Furthermore, in this case and preferably configured, the actuating element 12 is coupled to the latch 4 via the guide assembly 15 such that as the latch 4 reaches the intermediate position during the opening movement, the guide assembly 15 releases the latch 4 to move to the open position.

[0042] The intermediate position of the latch 4 is particularly located between the locked and open positions and is preferably reached during the opening movement after the latch 4 is released via the locking pawl 5, for example... Figure 3 As shown in c). Thus, even after the latch 4 is released via the locking pawl 5, the door sealing pressure acting on the latch 4 can still be released in a controlled manner by a delaying force. This also prevents the latch 4 from springing open during this phase of the opening movement.

[0043] In another design, the actuator 12 is coupled to the latch 4 via the guide assembly 15 such that an external force for opening movement can be introduced into the latch 4 via the guide assembly 15 during the opening process by means of the electric actuator 11. Preferably, this external force can be introduced until the latch 4 reaches the open position.

[0044] The external displacement force can be utilized when the latch 4, after being released and especially after reaching the intermediate position, has not reached the open position (for example, this can occur when the shifting element is frozen). To assist in opening the shifting element, the latch 4 is electrically moved in the opening direction by means of the actuator 12 and the guide assembly 15, the process of which is exemplarily described in [reference needed]. Figure 4 The sequence is a) and b). Through interaction with the locking component 6, the locking element 2 can preferably be pushed open and the icing state undone. It is also conceivable that this outward force is only introduced until an outward displacement position is reached, positioned between the locked and open positions. In this outward displacement position, the operator can insert their hand into the gap of the locking element 2, thus allowing the locking element 2 to be designed as a handle-less type.

[0045] In another design, the actuator 12 is coupled to the latch 4 via the guide assembly 15 such that a locking auxiliary force for locking movement can be introduced into the latch 4 via the guide assembly 15 during the locking process by means of the electric actuator 11. Preferably, the locking auxiliary force can be introduced until the latch 4 reaches the overtravel position.

[0046] The locking process, including the locking assistance function thus implemented, is exemplarily described in [reference needed]. Figure 5 The sequences a), b), and c). Figure 5 a) Shows a vehicle lock 1 in the open position, with the locking component 6 being introduced, causing the latch 4 to shift towards the pre-locking position to achieve... Figure 5 b) shows the pre-locked state. Preferably, the locking assist force is introduced after reaching the pre-locked position. The locking assist force is applied to the latch 4 in the locking direction via the guide assembly 15 by the displacement of the actuator 12 (pivoting the actuator 12 clockwise in the figure). Here, the locking movement of the latch 4 "achieved" by the locking assist force should be interpreted broadly, wherein the locking assist force may also only assist the locking movement already performed by the locking displacement element driven manually and / or electrically. However, it is particularly preferred that the locking element 2 is independently electrically pulled by the locking assist force by displacing the latch 4 to the locked position.

[0047] Overtravel position ( Figure 5 c) The latch 4 continues in the locking direction from the locked position, specifically corresponding to the position where the mechanical end stop of the latch 4 is reached. In the overtravel position, the locking pawl 5 reliably engages. Upon reaching the overtravel position, the latch 4 can be released by the guide assembly 15, allowing the latch 4 to return to the locked position via door sealing pressure.

[0048] Furthermore, in this case and preferably configured, the actuating element 12 holds the locking pawl 5 in the raised state as the opening process ends, preferably until the latch (4) reaches the open position.

[0049] The actuator 12 and the drive 11 are specifically designed to be self-locking, such that upon reaching the lifted state, the drive 11 can be de-energized, causing the locking pawl 5 to remain in the lifted state. By retaining the locking pawl 5, premature falling of the locking pawl 5 is prevented. This retention continues until the latch 4 reaches the open position and / or a predetermined time period is reached.

[0050] Furthermore, in this case and preferably configured, the guide assembly 15 has a crank lever mechanism via which the actuator 12 guides the latch 4. Preferably, the first guide rod 16 of the crank lever mechanism is pivotally arranged on the latch 4 and coupled to the second guide rod 17 of the crank lever mechanism via an elbow joint 18, which is particularly supported by a housing-fixed pivotal configuration.

[0051] Depend on Figure 3 and Figure 4 As can be seen from the sequence, the opening process is preferably accompanied by the extension of the elbow joint 18. Specifically, this allows for the application of a force to the latch 4 at the beginning of the opening process that is greater than the force at the end of the opening process. Figure 5 As can be seen from the sequence, the locking process is preferably accompanied by buckling of the elbow joint 18. In particular, this often allows a force greater than that at the beginning of the locking process to be introduced into the latch 4 at the end of the locking process. Particularly preferably, the dead point of the crank lever mechanism is not crossed during the opening and / or locking processes.

[0052] More preferably, the actuator 12 guides the latch 4 via mechanical contact with the guide element 19 on the elbow joint 18. Here, the guide element 19 may be configured as an extension of the elbow joint pivot. Thus, the actuator 12 can easily guide the extension or flexion movement of the elbow joint 18, and thereby guide the latch 4.

[0053] Furthermore, in this case and preferably configured, the crank lever mechanism has a pivot support structure within the longitudinal guide 20 for introducing a locking auxiliary force until the latch 4 reaches the overtravel position, preferably, the second guide rod 17 is supported via the longitudinal guide 20.

[0054] Figure 5 The diagram illustrates a longitudinal guide 20 implemented via an elongated hole according to a preferred design, which in this case, and preferably, is located on the second guide rod 17. A pivot support structure, particularly housing-fixed, is guided within the longitudinal guide 20. Here, the longitudinal guide 20 enables the introduction of a locking auxiliary force via the first guide rod 16, moving from the locked position to the overtravel position. Figure 5 c)).

[0055] Particularly preferably, the pivot support structure within the longitudinal guide 20 is elastically pre-tightened. This pre-tightening can be performed perpendicular to the extension direction of the longitudinal guide 20, such that the pivot support structure can only move primarily along the extension direction. Figure 5In the design, the movement follows the elongated direction of the long hole. This avoids undesirable lateral relative movement between the pivot support structure and the longitudinal guide 20, which could cause a clicking sound during operation. Preferably, the longitudinal guide 20 may have a spring pocket (not shown) for pre-tensioning the pivot support structure, wherein, for example, the second guide rod 17 is equipped with a plastic cover that has a groove in the region of the longitudinal guide 20 to form the spring pocket. It is also conceivable that a rib-like structure is formed at the longitudinal guide 20 by the plastic cover.

[0056] Further, and preferably in this configuration, the support structure of the first guide rod 16 is pivotally supported on the latch 4 via an acoustic damping device. In a preferred design, the latch 4 has a plastic cover that conventionally provides acoustic damping between itself and the locking pawl 5, the support structure of the latch 4, and / or the locking member 6. Here, the plastic cover can be extended to provide acoustic damping for the pivot 21 of the first guide rod 16. Here, the pivot 21 can be fixed to the first guide rod 16 and accommodated by a sliding support structure of the plastic cover.

[0057] Particularly preferably, the actuating element 12 is configured to have at least one functional profile for mechanical contact with the guide assembly 15 used to guide the latch 4. Preferably, the at least one functional profile is capable of mechanical contact with the guide element 19 of the guide assembly 15, wherein the guide element 19 slides and / or rolls, in particular, along the corresponding functional profile.

[0058] Preferably, as a functional profile, a delay profile 22 is provided for introducing a delaying force (see...). Figure 3 b)). Additionally, an outward displacement profile 23 for importing outward displacement forces can be set (see [link]). Figure 4 ), and / or set the locking assist profile 24 for importing locking assist force ( Figure 5 c)). By designing the corresponding functional profiles, the force relationships during the opening and locking processes can be set according to the requirements of the electric actuator 11 and the locking element 2. In a preferred design of the pivotable actuator 12, these functional profiles can be designed as eccentric profiles relative to the actuator axis 14, which is particularly evident in Figure 1 c) and d).

[0059] Furthermore, in this case and preferably configured, the actuating element 12 has an opening profile 25 for switching the locking pawl 5 to the raised state. Preferably, a trigger rod 26 is provided, which can be displaced during the opening process via mechanical contact with the opening profile 25, such that the trigger rod 26 switches the locking pawl 5 to the raised state.

[0060] Preferably, the trigger lever 26 is designed to pivot about the geometric trigger lever axis 27. It is also conceivable that the actuator 12 and the locking pawl 5 interact via direct mechanical contact. In a preferred design of the pivotable actuator 12, the opening profile 25 may be designed as an eccentric profile relative to the actuator axis 14.

[0061] Furthermore, in this case and preferably, the at least one guide profile and the opening profile 25 are disposed in different planes of the actuator 12. In this case and preferably, these planes are disposed perpendicular to the actuator axis 14. Thus, the opening profile 25 and the guide profile can be designed to be highly independent of each other. Figure 1 c), d) and Figure 2 In the illustrated embodiment, the functional profile lies within a first plane. The opening profile 25 lies within a second plane, from... Figure 1 c) and Figure 2 From this perspective, the second plane is located in front of the first plane. Here, the guide element 19 only extends into the first plane. Figure 1 d) shows the difference between Figure 1 c) The execution element 12 viewed from the opposite perspective.

[0062] Furthermore, in this case and preferably configured, the electric drive 11 has a transmission 28 for displacing the actuating element 12, preferably the actuating element 12 is formed by the transmission assembly of the transmission 28, or is torsionally coupled to the transmission element of the transmission 28.

[0063] The driver 11 with transmission 28 in Figure 1 This is further illustrated in b). Figure 2 To illustrate the other components, a vehicle lock 1 without the actuator 11 and transmission 28 is shown. In this case, and preferably, the transmission 28 has (particularly multi-stage) a cylindrical gear transmission and / or a worm gear transmission. The actuating element 12 is here torsionally coupled to one of the gears 29 of the transmission 28. Designs of the transmission 28 with a rope actuator, belt actuator, rack and pinion, or similar mechanisms are also conceivable.

[0064] In this case, and preferably, the actuator 12 is adapted to pivot from the initial position to the lifting position in the lifting direction by means of the electric actuator 11 during the opening process, so that the locking pawl 5 is switched to the lifting state, and continues to pivot in the lifting direction to the initial position as the opening process ends.

[0065] During the opening process, the actuator 12 shifts along the lifting direction. Figure 3 and Figure 4 The center pivots counter-clockwise. When latch 4 reaches... Figure 4After reaching the open position shown in c), the actuator 12 can continue to pivot in the lifting direction, which is again counterclockwise in the illustration, back to the initial position. To acquire the initial position in a sensor-like manner, an actuator sensor 30 is provided, which thereby determines, for example, the start and end points controlled by the driver 11 during the opening process.

[0066] Therefore, the actuator 12 can be adapted to pivot in the reverse lifting direction from the initial position during the locking process using the electric actuator 11 to introduce a locking assistance force. Preferably, the actuator 12 is adapted to pivot back to the initial position in the lifting direction using the electric actuator 11 as the locking process ends.

[0067] Therefore, compared to the opening process, the actuator 11 can operate in reverse during the locking process, which is achieved here. Figure 5 The actuator 12 pivots clockwise. The control start point of the actuator 11 is determined, for example, by the locking pawl 5 reaching the engaged state and the latch 4 being in the pre-locked position. The control end point of the actuator 11 is determined, for example, by reaching the engaged state and the latch 4 being in the overtravel position.

[0068] In this case, and preferably, a locking pawl sensor 31 is provided, which collects the landing state of the locking pawl 5. Particularly preferably, the landing position of the locking pawl 5 differs between the pre-locked state and the main locking state, for example, by using a design scheme via the main locking 9 and the pre-locking 10 to position the locking pawl 5 at different angles around the locking pawl axis 8. The locking pawl sensor 31 may have multiple sensing elements, through which the landing state in the pre-locked state and the main locking state can be distinguished. In a preferred design, the locking pawl sensor 31 and / or the actuator sensor 30 have microswitches, Hall sensors, and / or reed switches. In this case, and preferably, the locking pawl sensor 31 has two microswitches, neither of which is activated in the main locking state. Figure 3 a)). In the pre-locked state, only one microswitch is activated ( Figure 5 b)), and in the open state, both microswitches are activated ( Figure 5 a)).

[0069] Furthermore, in this case and preferably configured, a locking lever 32 is provided, which prevents the locking pawl 5 in the lowered state from changing to the raised state in the locked state, and the actuating element 12 causes the locking lever 32 to enter the released state during the opening process, in which the locking pawl 5 is released to change to the raised state.

[0070] Locking lever 32 is exemplarily in Figure 6As shown, and in this case, preferably designed to pivot about the geometric locking lever axis 33. Preferably, the locking lever 32 is configured as an additional anti-collision protection device for the locking pawl 5, and prevents the locking pawl 5 from shifting to the lifted state due to inertia via mechanical contact with the locking pawl 5, a process exemplarily described in Figure 6 a) shows the main locked state.

[0071] In a preferred design, not shown, the locking pawl sensor 31 acquires the engagement state of the locking pawl 5 via a locking lever 32. For example, at least one of the following states can be acquired by actuating a microswitch via the locking lever 32: a primary locking state, a pre-locking state, and / or an open state.

[0072] Furthermore, in this case and preferably configured, the actuator 12 causes the locking lever 32 to enter the release state via the trigger lever 26 during the opening process, so as to lift the locking pawl 5. Preferably, the locking lever 32 is subjected to a spring load in the locking state direction by means of the trigger lever 26.

[0073] In this case, and preferably, the trigger lever 26 has a locking lever guide 34 so that the locking lever 32 enters the release state during the opening process, such as Figure 6 As shown in b). Here, the locking engagement between the locking lever 32 and the locking pawl 5 is released. As the opening process continues, in this case, and preferably with the trigger lever 26 pivoted by means of the actuator 12, the locking pawl 5 is brought into the lifted state, as shown in b). Figure 6 As shown in c). In this case, and preferably, the trigger lever 26 has a center of gravity located on the trigger lever axis 27 to prevent the trigger lever 26 from pivoting due to inertia.

[0074] Spring loading can also be achieved via the locking lever guide device 34. In the open state (not shown), the locking lever 32 is engaged with the locking pawl 5, and when the locking process is repeated and the main locking state is reached, it will re-enter the locked state. In particular, this locked state is only set for the main locking state.

[0075] According to another embodiment, a vehicle locking system is proposed, which includes a proposed vehicle lock 1 and a control component for controlling an electric actuator 11. Preferably, the control component is adapted to control the electric actuator 11 according to control regulations to introduce a delaying force.

[0076] According to a preferred design, the control component can be part of a control device separate from the vehicle lock 1. Examples of such control devices are valve control devices and door control devices, which may also implement other electronic functions in the locking element 2. However, the control device is not mandatory to be part of the vehicle locking system. The control component can also be integrated into the housing of the vehicle lock 1, which also houses the lock assembly.

[0077] The control protocol can be designed such that the control component interrupts or terminates control of the opening actuator to introduce a delaying force. Here, the opening actuator can be de-energized after the opening movement begins and re-controlled at a subsequent time. If terminated, the vehicle lock 1 can continue to open autonomously. Here, the opening movement is delayed by the passive actuator 11, for example, through the frictional effect within the transmission 28 and the positioning torque of the drive motor 13. The opening actuator can also be energized to generate an action against the opening movement. Here, the drive power actively counteracts the opening movement. Furthermore, the control component can also cause the actuator 11 to operate as a resistance brake, in which case, in the simplest case, the terminals of the drive motor 13 are short-circuited. Similarly, a switchable braking resistor can also be provided.

[0078] According to another embodiment, a method for operating a vehicle locking system is proposed, the vehicle locking system having a vehicle lock 1 having a latch 4 and at least one locking pawl 5, wherein the latch 4 is displaceable to an open position for releasing and accommodating a locking member 6 and at least one locked position for maintaining engagement with the locking member 6, wherein in the lowered state, the locking pawl 5 prevents the latch 4 in the locked position from displacing in its opening direction, wherein during locking, the latch 4 is capable of switching from the open position to the locked position during locking movement, and the locking pawl 5 is capable of switching to the lowered state, wherein an electric actuator 11 is provided, which, during opening, displaces an actuator 12 such that the actuator 12 switches the locking pawl 5 to a raised state, in which the locking pawl 5 releases the latch 4, thereby enabling the latch 4 to perform an opening movement from the locked position to the open position.

[0079] According to this alternative approach, the core element is that the actuator 12 is additionally coupled to the latch 4 via the guide assembly 15 such that the electric actuator 11 guides the opening movement of the latch 4 at least in one phase of the opening process and / or guides the locking movement of the latch 4 at least in one phase of the locking process.

Claims

1. A vehicle lock having a latch (4) and at least one locking pawl (5), wherein the latch (4) is displaceable to an open position for releasing and receiving a locking member (6) and at least one locked position for maintaining engagement with the locking member (6), wherein in the engaged state, the locking pawl (5) prevents the latch (4) in the locked position from displacing in its open direction. During the locking process, the latch (4) can switch from the open position to the locked position during the locking movement, and the locking pawl (5) can switch to the dropped state. The device includes an electric actuator (11) with an actuating element (12). During the opening process, the electric actuator shifts the actuating element (12) such that the actuating element (12) switches the locking pawl (5) to a raised state. In the raised state, the locking pawl (5) releases the latch (4), thereby enabling the latch (4) to move from the locked position to the open position. Its features are, The actuator (12) is additionally coupled to the latch (4) via the guide assembly (15) such that the electric actuator (11) guides the opening movement of the latch (4) at least in one phase of the opening process and / or guides the locking movement of the latch (4) at least in one phase of the locking process by means of the guide assembly (15).

2. The motor vehicle lock according to claim 1, characterized in that, The actuator (12) is coupled to the latch (4) via the guide assembly (15) in such a way that a delaying force against the opening movement can be introduced into the latch (4) via the guide assembly (15) during the opening process via the electric actuator (11).

3. The motor vehicle lock according to claim 2, characterized in that, The actuator (12) is coupled to the latch (4) via the guide assembly (15) such that as the latch (4) reaches the intermediate position in the opening movement, the guide assembly (15) releases the latch (4) to move to the open position.

4. The motor vehicle lock according to any one of the preceding claims, characterized in that, The actuator (12) is coupled to the latch (4) via the guide assembly (15) such that an external force for achieving the opening movement can be introduced into the latch (4) via the guide assembly (15) during the opening process by means of the electric actuator (11), preferably the external force can be introduced until the latch (4) reaches the open position.

5. The motor vehicle lock according to any one of the preceding claims, characterized in that, The actuator (12) is coupled to the latch (4) via the guide assembly (15) such that a locking assist force for achieving the locking movement can be introduced into the latch (4) via the guide assembly (15) during the locking process via the electric actuator (11), preferably the locking assist force can be introduced until the latch (4) reaches the overtravel position.

6. The motor vehicle lock according to any one of the preceding claims, characterized in that, The actuator (12) holds the locking pawl (5) in the lifted state as the opening process ends, preferably until the latch (4) reaches the open position.

7. The motor vehicle lock according to any one of the preceding claims, characterized in that, The guide assembly (15) has a crank lever mechanism via which the actuator (12) guides the latch (4). Preferably, the first guide rod (16) of the crank lever mechanism is pivotally supported on the latch (4) and coupled to the second guide rod (17) of the crank lever mechanism via an elbow joint (18). The second guide rod is pivotally supported, particularly in a housing-fixed manner. More preferably, the actuator (12) guides the latch (4) via mechanical contact with a guide element (19) on the elbow joint (18).

8. The motor vehicle lock according to claim 7, characterized in that, The crank lever mechanism has a pivot support structure within a longitudinal guide (20) for introducing a locking auxiliary force until the latch (4) reaches the overtravel position. Preferably, the second guide rod (17) is supported via the longitudinal guide (20).

9. The motor vehicle lock according to claim 8, characterized in that, The pivot support structure within the longitudinal guide device (20) is elastically pre-tightened. Preferably, the longitudinal guide device (20) has a spring pocket portion for pre-tightening the pivot support structure.

10. The motor vehicle lock according to any one of claims 7 to 9, characterized in that, The support structure of the first guide rod (16) is pivotally supported on the latch (4) via an acoustic damping device. Preferably, the latch (4) has a plastic cover, through which the pivot (21) of the first guide rod (16) is supported.

11. The motor vehicle lock according to any one of the preceding claims, characterized in that, The actuator (12) has at least one functional profile for making mechanical contact with the guide assembly (15) for guiding the latch (4). Preferably, as a functional profile, it is provided with a delay profile (22) for introducing the delay force, an outward movement profile (23) for introducing the outward movement force, and / or a locking auxiliary profile (24) for introducing the locking auxiliary force.

12. The motor vehicle lock according to any one of the preceding claims, characterized in that, The actuator (12) has an opening profile (25) for switching the locking pawl (5) to the lifted state. Preferably, a trigger rod (26) is provided, which can be displaced during the opening process via mechanical contact with the opening profile (25) such that the trigger rod (26) switches the locking pawl (5) to the lifted state.

13. The motor vehicle lock according to claims 11 and 12, characterized in that, The at least one guide profile and the opening profile (25) are disposed in different planes of the actuator (12).

14. The motor vehicle lock according to any one of the preceding claims, characterized in that, The electric drive (11) has a transmission (28) for displacing the actuating element (12), preferably the actuating element (12) is formed by a transmission assembly of the transmission (28) or is torsionally coupled to a transmission element of the transmission (28).

15. The motor vehicle lock according to any one of the preceding claims, characterized in that, The actuator (12) is adapted to pivot from the initial position to the lifting position in the lifting direction by means of the electric actuator (11) during the opening process, so that the locking pawl (5) is switched to the lifting state, and continues to pivot in the lifting direction to the initial position as the opening process ends.

16. The motor vehicle lock according to claim 15, characterized in that, The actuator (12) is adapted to pivot in the opposite direction of the lifting direction from the initial position by means of the electric actuator (11) during the locking process to introduce a locking assist force. Preferably, the actuator (12) is adapted to pivot back to the initial position in the lifting direction by means of the electric actuator (11) as the locking process ends.

17. The motor vehicle lock according to any one of the preceding claims, characterized in that, A locking lever (32) is provided, which prevents the locking pawl (5) in the lowered state from changing to the raised state when the locking state is locked, and the actuator (12) causes the locking lever (32) to enter the released state during the opening process, in which the locking pawl (5) is released to change to the raised state.

18. The motor vehicle lock according to claim 17, characterized in that, The actuator (12) causes the locking lever (32) to enter the released state via the trigger lever (26) during the opening process, thereby lifting the locking pawl (5). Preferably, the locking lever (32) is subjected to a spring load along the locked state direction by means of the trigger lever (26).

19. A motor vehicle locking system having a motor vehicle lock (1) according to any one of the preceding claims and a control component for controlling the electric actuator (11), preferably, the control component being adapted to control the electric actuator (11) to introduce the delay force according to a control provision.

20. A method for operating a motor vehicle locking system, the motor vehicle locking system having a motor vehicle lock (1), the motor vehicle lock having a latch (4) and at least one locking pawl (5), wherein the latch (4) is displaceable to an open position for releasing and receiving a locking member (6) and at least one locked position for maintaining engagement with the locking member (6), wherein in a fallen-in state, the locking pawl (5) prevents the latch (4) in the locked position from displacing in its open direction. During the locking process, the latch (4) can switch from the open position to the locked position during the locking movement, and the locking pawl (5) can switch to the dropped state. An electric actuator (11) is provided, which, during the opening process, displaces the actuator (12) such that the actuator (12) switches the locking pawl (5) to a lifted state. In the lifted state, the locking pawl (5) releases the latch (4), thereby enabling the latch (4) to move from the locked position to the open position. Its features are, The actuator (12) is additionally coupled to the latch (4) via the guide assembly (15) such that the electric actuator (11) guides the opening movement of the latch (4) at least in one phase of the opening process and / or guides the locking movement of the latch (4) at least in one phase of the locking process by means of the guide assembly (15).

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