CN115961841A - Vehicle door handle with adjusting function - Google Patents

Abstract

A vehicle door handle (1) comprises a handle support (2) and a circumferentially graspable handle, which is adjustable between a rest position and a protracted position. The handle (3) and the grip support (2) are coupled by a guiding mechanism (5 a, 5 b), and the adjustment lever (12) is coupled with the guiding mechanism (5 a, 5 b) to move the handle along the adjustment path. The adjusting lever (12) is pretensioned by a return spring (13) to move the handle into the rest position. The synchronization lever (10) is coupled with at least one extension spring (11), wherein a force acting on the actuating device tensions the extension spring. A coupling device (14) temporarily couples the synchronization lever and the adjustment lever to transmit the force of the projecting spring to the adjustment lever and to move the handle (3) in the rest position into the projecting position and to tension the return spring (13) in the process; and the coupling device moves the handle from the protruding position to the rest position by the resilient force of the return spring when the coupling is released.

Description

Vehicle door handle with adjusting function

Technical Field

The present invention relates to a door handle for a vehicle. In particular, the invention relates to a vehicle door handle with a handle bracket, which can be fastened to a vehicle door or a vehicle hood. A circumferentially graspable handle is mechanically coupled to the handle bracket, which may be circumferentially grasped by a user for manipulating the door or the cover panel. The handle is adjustable relative to the handle support between a rest position and a protracted position. In the rest position, the handle assumes a drive-in/return state, in which, for example, and when installed in a vehicle, the surface of the handle can be flush with the surface of the surrounding body component. For use, the handle can be moved out of the rest position and can be extended out of a handle support, which is fixedly fastened to the vehicle body relative to the holding position. In this protruding state, the user can hold the handle and use it as a door handle or a lid handle.

Background

In order to guide the movement of the handle relative to the handle support, the handle and the handle support are coupled to each other by a guiding mechanism. The guiding mechanism ensures that the handle is guided between the rest position and the protracted position along a predetermined adjustment path. In this case, the handle has a defined position at any time. To this end, the handle can be adjusted and guided, in particular, along the entire extension of the handle. In particular, at least two bearings can be foreseen on the handle, on which the parts of the guiding mechanism act to adjust the handle in the desired position between the rest position and the extracted position. The adjustment lever is coupled with the guiding mechanism or with the handle itself in order to move the handle along the adjustment path during a force-actuated movement of the adjustment lever, while the guiding mechanism ensures guiding along the adjustment path of the handle. The adjustment lever is thus a force-transmitting component which exerts the original adjustment force, while the guide mechanism ensures that the force is adjusted along the adjustment path.

From the prior art, adjustable handles on vehicle door handles are known. In general, such a door handle is referred to as an "extendable door handle" or a "flush door handle". European patent application EP 3803 005 shows, for example, a door handle that can be extended out and that comprises a guide mechanism, as can be used in principle within the framework of the invention. Since various guiding mechanisms are known, but the exact design of the guiding mechanism is not crucial to the invention, the invention is described in the following, but the guiding mechanism is not specifically determined. The embodiments described hereinafter correspondingly illustrate an exemplary specific structure.

The extendable door handle is usually equipped with a motor drive which drives both the movement from the rest position into the extended position and the return guide into the rest position. There are also spring-pretensioned systems which, when the locking device is released or when the spring is tensioned, bring the handle from the rest position into the extended position and allow the handle to be pressed into the rest position again.

In principle, it is ensured that the door handle is accessible even when the drive energy is removed. This results in a large part of the handle still being usable by unauthorized users, which can thus be brought into the extended position, for example, as a result of an emergency activation or without actual intention of use. On the one hand, such a continuously projecting handle is undesirable because of the risk of possible damage, and in addition, it exposes regions in the vehicle body which would otherwise be covered by the handle and the associated sealing device.

Disclosure of Invention

The object of the invention is to provide a vehicle door handle which makes it possible to actuate and adjust a handle between a rest position and a retracted position in an improved, currentless manner.

This object is achieved by a vehicle door handle having the features according to the independent claim.

According to the invention, a vehicle door handle of this type has a return spring on its adjusting lever, which is pretensioned in one direction to move the handle into the rest position under the force transmission of the adjusting lever. As already described in the foregoing, the adjustment lever is coupled with the guiding mechanism and transmits the adjustment force to the guiding mechanism or to the handle coupled thereto to adjust the handle under the guidance of the guiding mechanism. The return spring is arranged on the adjusting lever and is dimensioned such that it has a sufficient resilience to convey it back to the rest position if the handle is in the protracted position. If the handle is thus released in the extended position, the pretensioning of the return spring causes the handle to move back again into the rest position, in which it is moved along a predetermined adjustment path by the guide mechanism.

Additionally, the door handle has a synchronization lever coupled with a pop-out spring. In addition to this, the synchronization lever is coupled with the actuating device, to be precise in such a way that a force acting on the actuating device moves the synchronization lever and tensions the extension spring. If a force is thereby exerted on the actuating device, it causes the force to actuate the loading of the extension spring. As will be described further below, this force loading of the pop-out spring is used to adjust the handle from the rest position to the pop-out position. The extension spring is dimensioned such that it has a greater adjusting force than the return spring.

Thus, according to the invention, the system has at least two springs, namely on the one hand a return spring which provides a force for guiding the handle from the protracted position back to the rest position and on the other hand a protracted spring which provides a force for moving the handle from the rest position to the protracted position. If a force is applied to the actuating device and the extension spring is pretensioned or loaded, the system has sufficient stored energy available to move the handle from the rest position into the extension position and back again into the rest position.

A coupling device is arranged on the synchronization lever or the adjustment lever, which temporarily couples the synchronization lever and the adjustment lever in order to transmit the force of the tensioned extension spring to the adjustment lever via the synchronization lever and to move the handle from the rest position into the extended position by the spring-back force of the extension spring. Thus, during coupling, the pretensioned or loaded extension spring acts via the synchronization lever on the actuating lever, which transmits this force again to the handle or to the guide mechanism coupled thereto and moves the handle from the rest position into the extension position. During this movement, the restoring spring is tensioned or loaded. Although the adjusting lever is pretensioned in the opposite direction by the restoring spring, this is still achieved because the spring force of the restoring spring is weaker than the extension spring. During the movement to the extended position, the return spring is tensioned. The coupling device between the actuating lever and the synchronization lever acts here such that, after the extended position has been reached, the coupling between these components is released by the handle, so that the handle is then moved from the extended position into the rest position by the restoring force of the restoring spring.

In summary, according to the invention, it is provided that the spring-driven movement from the rest position into the extended position and the return guidance into the rest position are realized, wherein the force provided by the spring force for turning out the door handle is greater than the return guidance into the rest position. In other words, a part of the energy initially introduced into the system by the actuating device for tensioning the extension spring is used for adjusting the handle from the rest position into the extension position, while the remaining part, i.e. the part of the energy used for tensioning the return spring during the extension of the handle, is used for the return. Thus, both springs are loaded during operation of the system, wherein, however, the first spring, which has a greater resilience, is loaded by the actuating device, and the second spring is loaded by the first spring during the relaxation of the first spring again.

Thus, according to the invention, a vehicle door handle with a handle is provided, which is energized for its protraction or egress and its entry or return by a single actuation of an actuating device.

In this case, it can be provided that the movement process is continued, so that the handle is thereby directly retracted again after being retracted. This gives the user the opportunity to grip the handle in the retracted state and hold it against the force of the return spring. Alternatively, it can also be provided that a locking device is provided which fixes the handle in the extended position and thus prevents a direct return guide back to the rest position. The locking can thus be released by the user or by a control signal with the actuator, so that the return spring can bring the handle into the rest position again. In this case, however, it is also provided according to the invention that by tensioning the return spring during the retraction of the handle for the retraction process, a system charge of the door handle (i.e. in the tensioned retraction spring) which is achieved as a result of the force acting on the actuating device and the tensioning of the retraction spring associated therewith stores sufficient energy for retraction and retraction of the handle again.

In a development of the invention, the actuating device is formed by a section of the handle itself, wherein the section moves the synchronization lever in the rest position of the handle when a force acts on the section of the handle and the spring is tensioned by the synchronization lever.

The arrangement of the actuating device on the handle itself or the handle also forming the handle construction of the actuating device allows a particularly compact construction and intuitive operation. Thus, for example, it is possible in its rest position (i.e. retracted position) to act on the end section of the handle in order to transmit a force to the synchronization lever and to tension the extension spring by means of the existing effective connection. In this case, the operator can thus press in the door handle, which is retracted flat into the vehicle door, and thus tension the extension spring. Subsequently, the loaded extension spring relaxes, the handle is extended and the return spring is tensioned in the process. If the handle is completely extended, the tensioned return spring can finally relax when the synchronization lever is decoupled from the adjustment lever and in the process transfer the handle again into the rest position.

In a preferred embodiment of the invention, the synchronization lever and the adjustment lever are mounted rotatably on parallel pivot axes.

Both the synchronization lever and the adjustment lever can be designed as a projection on the pivot bearing. For parallel pivot axes, the transmission and coupling between the synchronization lever and the adjustment lever is particularly simple, since in this case, for example, simple gear teeth allow the coupling. In a particularly preferred embodiment, the synchronization lever and the adjustment lever have the same pivot axis, so that force transmission and coupling between the two components can be realized particularly simply. The synchronization lever and the setting lever can then be arranged, for example, one above the other on a common pivot axis and be coupled, for example, by means of a coupling in the axial direction.

In a preferred embodiment of the invention, the synchronization lever has an actuating projection which engages behind a projection of the adjustment lever for coupling with the adjustment lever. In one such configuration, the synchronization lever may also have a plurality of lever arms extending from the pivot bearing. When one of the lever arms is operatively coupled, for example for loading a projecting spring, the other actuating projection can act on the adjusting lever in the form of the lever arm. This multiple-arm lever design makes possible a particularly simple design, in which case the more complex deflection and transmission systems are dispensed with.

In a particularly advantageous configuration of the invention, the synchronization lever has a bearing in which the synchronization lever is moved back and forth (or up and down) in the axial direction of its pivot shaft during the pivoting movement.

The movement of the synchronization lever along the synchronization lever pivot axis makes it possible to provide a dependent coupling between the synchronization lever and the adjustment lever in different axial positions. For example, the coupling may be established along a first section of the axial position of the synchronization lever, while in a second section of the axial position of the synchronization lever there is no coupling between the adjustment lever and the synchronization lever. If, for example, the synchronization lever approaches the direction of the actuating lever, the actuating projection of the synchronization lever can act on the actuating lever, however, when the synchronization lever is moved away from the actuating lever in the axial direction of its pivot axis, a gap is produced, so that the transmission of force from the synchronization lever to the actuating lever is suppressed.

In order to thereby enable or release the coupling between the synchronization lever and the adjustment lever, in this variant of the invention the synchronization lever is axially adjusted along its pivot axis.

It is particularly preferred that the coupling between the synchronization lever and the adjustment lever is achieved purely mechanically, depending on the component guidance and dimensioning. In a particularly preferred embodiment of the invention, the actuating lever has a sliding section for this purpose, on which the actuating cam of the synchronization lever can slide up and down during the rotation about its pivot axis. The actuating projection of the synchronization lever therefore slides over the sliding section of the actuating lever until it finally engages behind the projection of the actuating lever. For this purpose, the synchronization lever can be lowered behind the projection of the adjustment lever when it reaches the end of the sliding section in a certain direction and in this case be moved axially relative to its pivot axis in the direction of the adjustment lever. This lowering behind the projection of the adjusting lever can be achieved by spring-pretensioning the synchronizing lever in the axial direction of the pivot shaft of the synchronizing lever and in the direction of the adjusting lever to establish the coupling between the adjusting lever and the synchronizing lever. Hereinafter, such a configuration is explained with reference to the embodiment.

In a particularly preferred embodiment of the invention, the extension spring is designed as a torsion compression spring which presses the synchronization lever in the pivoting direction and in the axial direction of the synchronization lever pivot axis. The combined action of the torsion compression spring in the axial direction and in the radial direction allows a particularly simple and compact design, since only a single spring is used to facilitate the force storage for the extension movement of the handle and to provide the force for coupling the synchronization lever and the adjustment lever.

It is particularly advantageous to use a bearing arrangement comprising a ramp for coupling and decoupling the synchronization lever to the adjustment lever. This configuration makes it possible to provide a downward slide on the inclined surface during a rotation of the synchronization lever, so that an axial adjustment along the spiral is also achieved during the rotation. In this way, the coupling and decoupling between the synchronization lever and the adjustment lever can be achieved mechanically. If the synchronization lever is moved to load the extension spring coupled thereto, the synchronization lever pivots on its bearing and moves axially along the ramp in the direction of the adjustment lever. Thereby, a coupling is established between the synchronization lever and the adjustment lever. If the extension spring is later relaxed again, wherein the synchronization lever is moved into the initial position again, the synchronization lever is moved away from the adjustment lever again in the axial direction as a result of the ramp and the coupling is released.

In a further preferred embodiment of the invention, it is provided that the actuating device is coupled to the synchronization lever by means of a mechanical force deflection and a force transmission.

As described above, the actuation device may be formed either separately from the handle or by the handle itself. The lower force deflection and the force transmission allow a short adjustment path to be used to provide the force for loading the extension spring. In a door handle configuration, the adjustment path is typically set to be extremely short so that the user can convert the provided operating force into the spring loading force through a short operating path, which is typically achieved through a longer adjustment path.

In a preferred embodiment of the invention, it is also provided that, when the adjustment path increases, the force transmission provides an adjustment path conversion and a force conversion in the form of a force reduction for tensioning the extension spring.

Drawings

The invention will now be explained in detail with reference to the attached drawings.

FIG. 1a shows an embodiment of a vehicle door handle according to the present invention in an oblique perspective view;

fig. 1b shows the arrangement according to fig. 1a in a top view;

fig. 1c shows the arrangement according to fig. 1a in a partially transparent front view;

fig. 2a, 2b, 2c, 2d and 2e show the functional flow of the handle actuation in top view, including the subsequent movement of the handle from the rest position into the protracted position and the return guidance back to the rest position;

fig. 3a, 3b, 3c, 3d and 3e show the movement sequence according to fig. 2a to 2e in an oblique view;

FIGS. 4a, 4b, 4c and 4d illustrate the coaction of the subcomponents of the door handle during actuation;

fig. 5a, 5b, 5c and 5d show the state according to fig. 4a to 4d from another angle of view.

Detailed Description

The vehicle door handle 1 according to this embodiment has a handle 3 and a handle bracket 2. In fig. 1a, 1b and 1c, the handle 3 is in its rest position. The handle 3 and the grip holder 2 are coupled via guiding mechanisms 5a, 5 b. The guiding mechanism may comprise other components. The guiding mechanism ensures that: during the movement of the handle, the handle 3 is moved along a predetermined adjustment path by introducing a force into the guiding mechanism, as will be shown below.

The handle support 2 is fastened in or on the door (not shown) by means of a fastening device, so that the handle 3 extends flush with the surrounding body section in an opening of the body and can be pulled out of the opening. Around the handle 3, a seal may be arranged, however, for reasons of clarity, the seal is omitted here.

For the pivoting movement, the actuating lever 12 and the synchronization lever 10 are mounted on a common shaft. The adjusting lever 12 is coupled with the guide mechanisms 5a, 5b in such a way that during a pivoting movement of the adjusting lever 12 the handle can be extended by the guide mechanisms 5a, 5b and during a pivoting movement in the opposite direction is pulled back into the rest position again. A torsion spring 13 is assigned to the adjusting lever 12. A compression torsion spring 11 is assigned to the synchronization lever 10, which pretensions the synchronization lever 10 both in the pivoting direction and in the axial direction. In the axial direction, the synchronization lever 10 is pressed in the direction of the adjusting lever 12. The synchronization lever 10 is designed as a multi-armed lever. Which has a lever arm 10a that can be brought into contact with the transfer device 4 a. The transmission device 4a and the associated transmission device 4b are provided for providing a force deflection and a force transmission for the pretensioning spring 11 in the torsional direction. A projection 3a is formed on the handle 3, which projection acts on the transfer device 4 b. The transfer device slides down on the inclined surface of the transfer device 4a and presses it in the direction of the lever arm 10a of the synchronization lever 10. This process is described below and is advantageous for pre-tensioning the spring 11 by the lever arm 10a being deflected under the influence of the transmission device 4 a. Furthermore, the synchronization lever 10 has an actuating projection 10b, which is a shorter lever arm, connected integrally to the lever arm 10a by a common pivot bearing. If the lever arm 10a is pivoted, the entire synchronization lever 10 together with its actuating projection 10b pivots about the pivot axis.

In the side view of fig. 1c, in which the handle bracket 2 is shown transparent, the bearings of the return spring 13, the adjusting lever 12, the synchronization lever 10 and the extension spring 11 can be seen, which are arranged along a common pivot axis. The return spring 13 is tensioned between the handle support and the adjusting lever 12 in order to press the adjusting lever in a direction that brings the handle 3 into a return position in the rest position. The extension spring 11 is tensioned between the handle support or the associated housing part, so that tensioning of the spring 11 in a direction opposite to the tensioning direction of the spring 13 is possible. In addition, the spring 11 presses the synchronization lever 10 in the direction of the actuating lever 12.

Fig. 2a to 2e show the actuation process of the door handle according to this embodiment in plan view.

The rest position of the door handle is shown in fig. 2 a. The handle 3 is pulled back flush with the surrounding outer door panel into the handle bracket 2. In this state, the spring 13 is relaxed as much as possible like the spring 11.

In fig. 2b, an actuated state is shown, in which the user is acting on a section of the handle 3 with a force F and pushing the handle inwards. By coupling the projection 3a with the transfer devices 4a and 4b, the transfer device 4a is displaced in the direction of the synchronization lever 10 by the downward sliding of the transfer device 4b on the inclined surface of the transfer device 4 a. The transmission device 4a is in contact with the lever arm 10a and pivots the synchronization lever 10 about its pivot axis. As an integral component of the synchronization lever 10, the actuating projections 10b together perform this movement. As can be seen in the subsequent figures, in the process the actuating projection 10b slides down on the sliding surface 12a of the actuating lever 12 until the actuating section 10b is guided beyond the edge of the sliding surface 12a and falls behind it. This is possible because the bearing of the synchronization lever 10 has a bevel which makes possible an axial displacement in the direction of the adjusting lever 12 during the adjustment of the synchronization lever 10 (see subsequent figures). In the final state of the actuation according to fig. 2b, the spring 11 is therefore tensioned and the actuating projection 10b engages behind the projection of the actuating lever 12. In this state, the synchronization lever 10 is coupled with the adjustment lever 12 through its actuating boss 10 b. If the force F shown in fig. 2b is now removed, the spring 11 is thereby relaxed and entrains the adjusting lever 12 during the rotational movement of the synchronization lever 10, since the actuating projection 10b also engages behind the projection of the actuating lever 12. During this movement, which is effected by the entrainment, the adjusting lever urges the handle in the direction of the extended position.

Fig. 2c shows a state in which the handle has travelled half the path of movement in its guide. In the state of fig. 2c, the spring 11 is therefore not yet fully relaxed, but continues the extension movement pushing the handle 3. During this movement between fig. 2b and 2d, the spring 13 is also simultaneously tensioned when the handle 3 is extended. This is achieved in that the resilience of the spring 11 is greater than the resilience of the spring 13.

In fig. 2d, the handle is fully extended and in this state the spring 11 is again largely relaxed. Since the synchronization lever 10 has been moved into its initial position again and, during its rotation, is lifted up again by the ramp arrangement in its bearing and is spaced apart from the adjusting lever 12, the adjusting lever 12 is now free again, since the actuating projection 10b on the synchronization lever 10 no longer engages with it from behind. Driven by the force of the spring 13, the free adjusting lever 12 can now be moved into its initial position again and in the process guides the handle 3 back into the rest position again.

As is clearly visible in the subsequent figures, between fig. 2a and 2b the synchronization lever 10 is moved out of the plane of the drawing, while in fig. 2c and 2d to 2e the synchronization lever is moved into the plane of the paper again. By force actuation in fig. 2b, not only is the extension spring 11 tensioned, but the synchronization lever 10 is also axially adjusted and coupled with the adjustment lever 12 via a rear engagement. When the extension spring is relaxed as much as possible again, the decoupling of the two levers is achieved in fig. 2 d.

In fig. 3a to 3e, the process described with reference to fig. 2a to 2e is shown in another view, wherein like reference numerals designate like positions. The rear engagement of the actuating projection 10b on the corresponding projection of the setting lever 12 can be seen very well in fig. 3 b. The projections here define a sliding surface 12a on which the actuating projections slide down during the tensioning movement. If the rotational movement exceeds a certain angle, the actuating projection 10b descends behind the sliding surface and behind the projection of the setting lever 12. In fig. 3d, the state can be seen in which the handle 3 is fully extended and, by means of its restoring movement with the spring 11 relaxed, the synchronization lever 10 is again axially moved away from the adjustment lever, so that the adjustment lever can be moved with its sliding surface again through the underside of the actuating projection 10b and can restore the handle.

As already described above, it is possible that a locking of the handle (for example by a stop device) can be achieved between the fully extended state (i.e. the state in fig. 2d and 3 d) and the return guidance into the pulled-in position (shown in fig. 2e and 3 e), which locking can be released for example by a mechanically actuatable locking device or an electrically actuated switch. However, it is also possible to perform the damped movement in a continuous manner, i.e. to achieve the return guidance of the handle into the rest position again directly after full extension.

Fig. 4a to 4d and fig. 5a to 5d each show different views of the movement sequence, wherein the same reference numerals designate identical functional positions. The positions of the components in fig. 4a and 5a, 4b and 5b, 4c and 5c, and 4d and 5d correspond accordingly. The effect of the temporary coupling between the synchronization lever 10 and the adjustment lever 12 can be seen well in these figures. As coupling device 14, a beveled support bearing is provided here, which serves as a component of the bearing for synchronization lever 10. The synchronization lever 10 has a corresponding contour on its underside, so that during the rotational movement of the synchronization lever 10 it moves in the coupling device 14 in the axial direction of the pivot axis. Fig. 4a shows the effect of the force on the lever arm 10a and the initial sliding down of the actuating projection 10b on the sliding surface 12 a. Fig. 5a shows the corresponding content.

In fig. 4b, the tensioning of the spring 11 is completely performed by the actuating device exerting its force on the lever arm 10a of the synchronization lever 10. If this is possible by the contour of the coupling device 14 and of the underside of the synchronization lever 10 and by the complete sliding down of the actuating projection 10b on the sliding surface 12a, the synchronization lever 10 is now displaced in the axial direction in the direction of the adjustment lever 12, so that the actuating section 10b engages behind a section of the actuating lever 12. This is also shown in fig. 5b, in which the downward axial displacement of the synchronization lever 10 can be seen well. If the lever arm 10a is now released, the synchronization lever 10 cannot be moved under the force of the tensioned spring 11 without the adjustment lever 12. This is shown by the arrows in fig. 5 b. The synchronization lever 10 and the adjustment lever 12 correspondingly perform a common pivoting movement driven by the return force of the spring 11. This is illustrated in fig. 4c and 4 d. During this movement, the synchronization lever 10 follows the lower contour, passes the inclined surface of the coupling device 14 and is thus displaced in the axial direction on its pivot axis until the actuating section 10b no longer engages from below a section of the adjustment lever, but slides via the sliding surface 12a in the direction of the complete release of the synchronization lever 10. The adjusting lever 12 is now free of the tension of the spring 11, driven by the force of the return spring 13 which had been tensioned in the preceding movement step, moves back to the initial position and in the process moves the handle again into its rest position. It can be seen that, when the spring 11 is tensioned, the decoupling of the synchronization lever 10 from the adjustment lever 12 occurs first, and then, when the spring 11 is fully tensioned, the coupling between the levers is brought about by the axial adjustment of the synchronization lever 10, which then executes a common rotational movement, while one of the springs is relaxed and the other spring is tensioned. Subsequently, the lever is decoupled again and, with the driving lever in the rest position, the return guide of the actuating lever 12 is effected.

Thus, according to the invention, the interaction of the coupling and decoupling of the lever and the tensioning and relaxing of the spring is utilized to drive the protracting movement of the handle and the subsequent resetting movement into the rest position, wherein one mechanical loading by the actuating device is sufficient.

Claims (11)

1. Door handle (1) comprising a handle bracket (2) and a circumferentially graspable handle mechanically coupled thereto, wherein the handle (3) is adjustable between a rest position and an extended position relative to the handle bracket (2),

wherein the handle (3) and the handle bracket (2) are coupled via a guiding mechanism (5 a, 5 b) which guides the handle (3) along its extension between the rest position and the protracted position on a predetermined adjustment path,

wherein an adjustment lever (12) is coupled with the guiding mechanism (5 a, 5 b) to move the handle (3) along the adjustment path when the adjustment lever (12) is force-actuated adjusted,

it is characterized in that the preparation method is characterized in that,

pretensioning the adjusting lever (12) in one direction by means of a return spring (13) in order to move the handle (3) into the rest position,

is designed with a synchronization lever (10) which is coupled to at least one extension spring (11),

wherein the synchronization lever (10) is coupled with an actuating device (4 a, 4 b) such that a force acting on the actuating device moves the synchronization lever (10) and tensions the protruding spring (11),

wherein the resilience of the extension spring (11) is greater than the resilience of the return spring,

a coupling device (14) is arranged on the synchronization lever (10) or the adjustment lever (12), temporarily coupling the synchronization lever (10) and the adjustment lever (12) in order to transmit the force of the tensioned extension spring (11) to the adjustment lever (12) via the synchronization lever (10) and to move the handle (3) from the rest position to the extension position and to tension the return spring (13) in the process via the return force of the extension spring (11), and

wherein the coupling device temporarily decouples the synchronization lever (10) from the adjustment lever (12) so that the handle (3) is moved from the protruding position to the rest position by the return force of the return spring (13).

2. The vehicle door handle (1) according to claim 1, wherein the actuation device (4 a, 4 b) is coupled with a section of the handle (3) which, when a force acts on the section of the handle (3) in the rest position of the handle (3), by means of the actuation device (4 a, 4 b), moves the synchronization lever (10) and thereby tensions the protrusion spring (11).

3. The vehicle door handle (1) according to any one of the preceding claims, wherein the synchronization lever (10) and the adjustment lever (12) are rotatably supported on parallel pivot axes.

4. The vehicle door handle (1) according to any one of the preceding claims, wherein the synchronization lever (10) has an actuation projection (10 b) which engages behind a projection of the adjustment lever (12) for coupling with the adjustment lever (12).

5. The vehicle door handle (1) according to any one of the preceding claims, wherein the synchronization lever (10) has a bearing in which the synchronization lever (10) moves back and forth in the axial direction of its pivot axis during the pivoting movement.

6. The vehicle door handle (1) according to claim 5, wherein the temporary coupling and temporary decoupling between the synchronization lever (10) and the adjustment lever (12) is caused depending on the position of the synchronization lever along its pivot axis.

7. The vehicle door handle (1) according to any one of claims 4 to 6, wherein the adjusting lever (12) has a sliding section (12 a) on which the actuating projection (10 b) of the synchronization lever slides down until it engages behind a projection of the adjusting lever (12).

8. The vehicle door handle (1) according to any one of the preceding claims, wherein the protruding spring (11) is designed as a torsion compression spring which presses the synchronization lever (10) in the pivoting direction and in the axial direction of the pivot axis of the synchronization lever.

9. The vehicle door handle (1) according to any one of claims 5 to 8, wherein the coupling device (14) as a bearing for the synchronization lever has a ramp on which the synchronization lever (10) slides down during a pivoting movement about its pivot axis and changes its axial position along the pivot axis during this.

10. The vehicle door handle (1) according to any one of the preceding claims, wherein the actuation device is coupled with the synchronization lever (10) by means of a mechanical force deflection and force transmission.

11. The vehicle door handle (1) according to claim 10, wherein the force transmission comprises a force reduction when the adjustment path is increasing.

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