EP4006275B1 - Agencement de mouvement pour un dispositif de poignée de porte - Google Patents

Agencement de mouvement pour un dispositif de poignée de porte Download PDF

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Publication number
EP4006275B1
EP4006275B1 EP21215453.8A EP21215453A EP4006275B1 EP 4006275 B1 EP4006275 B1 EP 4006275B1 EP 21215453 A EP21215453 A EP 21215453A EP 4006275 B1 EP4006275 B1 EP 4006275B1
Authority
EP
European Patent Office
Prior art keywords
spring
lever
door handle
tensioning lever
spring tensioning
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP21215453.8A
Other languages
German (de)
English (en)
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EP4006275A1 (fr
Inventor
Markus Herdering
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Witte Automotive GmbH
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Witte Automotive GmbH
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Filing date
Publication date
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Publication of EP4006275A1 publication Critical patent/EP4006275A1/fr
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Publication of EP4006275B1 publication Critical patent/EP4006275B1/fr
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B85/00—Details of vehicle locks not provided for in groups E05B77/00 - E05B83/00
    • E05B85/10—Handles
    • E05B85/103—Handles creating a completely closed wing surface
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B85/00—Details of vehicle locks not provided for in groups E05B77/00 - E05B83/00
    • E05B85/10—Handles
    • E05B85/107—Pop-out handles, e.g. sliding outwardly before rotation
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B15/00—Other details of locks; Parts for engagement by bolts of fastening devices
    • E05B15/04—Spring arrangements in locks
    • E05B2015/0496—Springs actuated by cams or the like
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/02—Power-actuated vehicle locks characterised by the type of actuators used
    • E05B81/04—Electrical
    • E05B81/06—Electrical using rotary motors
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/24—Power-actuated vehicle locks characterised by constructional features of the actuator or the power transmission
    • E05B81/32—Details of the actuator transmission
    • E05B81/42—Cams

Definitions

  • the invention relates to a movement assembly for a door handle assembly.
  • Door handle arrangements with a recessed door handle, in particular for vehicles, in particular for vehicle doors, are generally known from the prior art.
  • the door handle driven by an electric motor, is extended from a position that is lowered into the vehicle door into a position for use. After opening the vehicle door, the door handle is moved back into the lowered position by an electric motor.
  • the motor vehicle door includes a door lock and a door handle system, which is positioned in the area of a door recess and interacts with the door lock to open the motor vehicle door.
  • the door handle system has a door handle, which is movably mounted between a rest position positioned flush with an outer door skin and a functional position projecting outwards over the outer door skin.
  • the door handle system is associated with parallel guidance kinematics.
  • the parallel guide kinematics are designed as pivot kinematics that define a pivot axis for the door handle that extends in the longitudinal direction of the vehicle and is spaced apart from the door handle in the vertical direction of the vehicle.
  • the door handle system comprises a door handle unit that is movably mounted between a rest position that is flush with the door and an extended functional position, as well as an electric drive system for moving the door handle unit between the rest position and the functional position.
  • the door handle unit has a drive plate and a door handle element assigned to the drive plate.
  • the drive plate is movably mounted to move the door handle unit into the functional position or the rest position and is operatively connected to the drive system.
  • the door handle element is movably mounted relative to the drive plate.
  • a restraining device secures the door handle element with limited force in a contact position on the drive plate.
  • the handle device includes a door handle, which is articulated at both ends to electrically driven movement kinematics.
  • a first end of the door handle is outwardly rotatable via a powered pivoting lever.
  • a push rod is articulated on the swivel lever, the other end of which is articulated on a locking lever which acts on a pair of toggle levers, one end of a first toggle lever being articulated on a second end of the door handle and one end of a second toggle lever being rotatably mounted on the housing side.
  • the Locking lever is configured to lock movement of the door handle back to a rest position in a ready position and to allow movement to an open position.
  • the handle control for a handle for unlocking vehicle doors.
  • the handle In a rest position, the handle can be lowered flush with an outer contour in a trough of the vehicle door and can be transferred out of the trough in a controlled manner into a ready position for opening the vehicle door and then further pivoted out against a spring force by actuating a lock release.
  • the handle control comprises two swiveling levers, which are hinged to the door on one side and articulated to the handle on the other side, which when swiveled in a controlled manner move the handle into a ready position in the same direction as the outer contour of the door, and which then perform an additional swiveling movement on one side of the handle against the force allow a feather.
  • the object of the present invention is to specify a movement arrangement for a door handle arrangement which is improved compared to the prior art.
  • a door handle arrangement in particular an outside door handle arrangement, is provided for a door, in particular for a vehicle door. It includes a door handle that can be moved from a retracted position into a usage position.
  • the door handle is moved, for example, electrically, in particular by means of an electric motor.
  • the door can be opened by operating and/or touching the door handle. In normal operation, this occurs after the door handle is placed in the use position. i.e. the door handle is first sunk out of the position, in particular in the door, into the position, in particular out the door extended, usage position moves in which it is easily accessible for actuation and / or touch.
  • an emergency release can also be provided for emergency operation, for example in the event of a failure of the electrical power supply or due to another cause, so that the door handle can no longer be moved into the usage position.
  • the door handle can also be actuated and/or touched in the retracted position to open the door.
  • the door handle arrangement also includes a return spring, in particular for returning the door handle from the use position to the retracted position or at least to support this return.
  • the return spring is coupled to the door handle, for example directly to the door handle or via a connecting lever connected to the door handle, and in the retracted position and in the use position to a counter bearing which is at least then fixed, for example directly or via a spring tensioning lever.
  • one spring limb or at least one spring limb of the return spring is coupled to the door handle or to the connecting lever, in particular rests against it
  • the other spring limb or at least one other spring limb of the return spring is coupled with the counter bearing or with the spring tensioning lever, in particular rests against in particular in such a way that the return spring is increasingly tensioned or would be tensioned by a relative movement of the connecting lever and spring tensioning lever in one direction and is increasingly relaxed or would be relaxed in the other direction.
  • the restoring spring is used in particular for a coupling, in particular an elastic coupling, of the connecting lever and spring tensioning lever and thus a coupling, in particular an elastic coupling, of the door handle and spring tensioning lever, for example to enable anti-trap protection, in particular during movement into the retracted position.
  • the return spring is decoupled from the abutment between the retracted position and the use position and/or the abutment assumes a retracted abutment position in the retracted position and an extended abutment position in the use position and is out during the movement of the door handle from the retracted position to the use position the retracted counter-bearing position can be converted into the extended counter-bearing position, in which case it advantageously covers a movement path, for example the same movement path, in the same time as the door handle and/or, if present, its connecting lever.
  • the spring tensioning lever on which the return spring rests and thus also the return spring, is decoupled from the counter bearing between the retracted position and the use position, the spring tensioning lever advantageously being moved with the door handle and thus with the return spring.
  • the drive in particular the electric motor
  • the drive has a larger power reserve and/or it can
  • a smaller drive in particular an electric motor
  • the return spring would be additionally tensioned with each movement of the door handle into the use position, causing unnecessary losses in the drive and increasing wear on the drive and the return spring, thus shortening service life.
  • the solution described avoids this, reduces wear and increases the service life.
  • the door handle assembly includes a spring tensioning lever and an eccentric unit.
  • the return spring is coupled to a spring contact area of the spring tensioning lever.
  • the eccentric unit is rotatably mounted and has a spring tensioning lever eccentric curve for guiding the spring tensioning lever.
  • the spring tensioning lever eccentric cam is designed in such a way that the spring tensioning lever rests against the spring tensioning lever eccentric curve in the retracted position of the door handle and in the use position of the door handle and is spaced from the spring tensioning lever eccentric curve in between.
  • the eccentric unit forms the counter bearing for the restoring spring, which is coupled to the eccentric unit via the spring tensioning lever in the retracted position and the use position.
  • the eccentric unit is arranged on a component of the door handle arrangement, for example on a bearing bracket, which is stationary, at least stationary when the door handle is in the retracted position and in the usage position.
  • the door handle arrangement is fastened or can be fastened to the door via this bearing bracket.
  • the restoring spring is part of a movement arrangement, in particular for moving the door handle from the retracted position to the usage position and back.
  • This movement arrangement comprises the connecting lever coupled, in particular pivotably coupled, to the door handle, in particular to an end region of the door handle, the spring tensioning lever, the restoring spring and the eccentric unit.
  • the eccentric unit forms the counter bearing for the restoring spring, which is coupled to the eccentric unit via the spring tensioning lever in the retracted position and the use position.
  • the eccentric unit is arranged on a component of the door handle arrangement, for example on the bearing bracket, which is stationary, at least stationary when the door handle is in the retracted position and in the usage position. The door handle arrangement is fastened or can be fastened to the door via this bearing bracket.
  • the connecting lever and the spring tensioning lever are advantageously mounted pivotably about a common pivot axis and pivotable relative to one another about this pivot axis.
  • the restoring spring is advantageously coupled to a spring contact area of the connecting lever and to the spring contact area of the spring tensioning lever, in particular with a spring leg in each case, such that it can be released by a pivoting movement of the spring contact area of the spring tensioning lever in the direction of the spring contact area of the connecting lever and can be tensioned by an opposite pivoting movement.
  • the return spring is coupled in the retracted position and in the use position via the spring tensioning lever to the eccentric unit forming the counter bearing, so that the spring tensioning lever is then immovable and thus, for example, also keeps the connecting lever and thus also the door handle immovable due to the pretension of the return spring .
  • this prevents the door handle from rattling, for example.
  • the eccentric unit is rotatably mounted, for example rotatably mounted on the bearing bracket, and advantageously has a connecting lever eccentric curve for guiding the connecting lever and the spring tensioning lever eccentric curve for guiding the spring tensioning lever.
  • These eccentric cams are advantageously arranged in two different planes, so that the eccentric unit has two eccentric disks which are arranged one above the other and are fixed to one another or designed in one piece, each with one of the eccentric cams.
  • the connecting lever can thus be pivoted about the pivot axis from a connecting lever initial position (retracted position of the moving arrangement) into a connecting lever end position (extended position of the moving arrangement) by means of the connecting lever eccentric cam.
  • the spring tensioning lever is located in the retracted position of the movement arrangement in a tensioning lever initial position, the spring contact areas of the spring tensioning lever and connecting lever advantageously being spaced apart from one another in such a way that the return spring is pretensioned, i.e. slightly tensioned, in particular in such a way that it rests firmly on the two spring contact areas and therefore does not rattle.
  • the spring tensioning lever In the extended position of the movement arrangement, the spring tensioning lever is in a tensioning lever end position, the spring contact areas of the spring tensioning lever and connecting lever advantageously being spaced apart again in such a way that the return spring is pretensioned, i.e. slightly tensioned, in particular in such a way that it rests firmly on the two spring contact areas and therefore not rattling.
  • the spring clamping lever In the clamping lever initial position and clamping lever end position, the spring clamping lever is in contact with the spring clamping lever eccentric curve. In between, i.e.
  • the spring clamping lever is at a distance from the spring clamping lever eccentric curve, i.e. it no longer rests against it and can therefore freely move around the Swivel swivel axis. Due to the previously preloaded return spring between the spring tensioning lever and the connecting lever, the spring contact area of the spring tensioning lever approaches the spring contact area of the connecting lever while the return spring relaxes and is then pivoted together with the connecting lever and the return spring due to the connection via the return spring.
  • the eccentric unit and/or the pivot axis are arranged on the bearing bracket and are therefore immovable components, with the exception of the rotation of the eccentric unit, i. H. the eccentric unit itself is in a fixed position, it only rotates, in particular on a drive axle which is arranged in the bearing bracket, so that the eccentric cams move accordingly.
  • the eccentric unit thus forms the counter bearing for the return spring. Spring tensioning lever and connecting lever move by pivoting around the pivot axis.
  • the eccentric unit is advantageously arranged fixedly on the drive axle or is formed in one piece with it and can be rotated by rotating the drive axle.
  • the door handle is thus driven to move it into the usage position via the eccentric unit.
  • the eccentric unit is advantageously arranged on the bearing bracket via the drive axle, which is rotatably mounted in the bearing bracket. As already mentioned, it is therefore arranged in a fixed position on the bearing bracket and thus forms the counter bearing for the return spring. The position of the counter bearing is changed by turning the eccentric unit, whereby the spring tensioning lever rests on different areas of the spring tensioning lever eccentric curve.
  • the movement arrangement in particular the connecting lever, is advantageously coupled to a further movement arrangement which is coupled to the other end region of the door handle, in particular is pivotably coupled.
  • both end regions of the door handle can be moved by means of a single drive unit, so that the door handle can be moved from the retracted position into the use position, for example by a parallel displacement.
  • a force transmission rod is advantageously arranged between the movement arrangement, in particular its connecting lever, and the further movement arrangement.
  • the door handle arrangement advantageously comprises such a movement arrangement as already described above.
  • the connecting lever eccentric cam is advantageously designed in such a way that the connecting lever rests against a first connecting lever contact section in the retracted position and against a second connecting lever contact section of the connecting lever eccentric cam in the extended position, with the first connecting lever contact section being at a smaller distance from the drive axle than the second connecting lever contact section, with the first connecting lever contact section has the smallest distance between the connecting lever eccentric cam and the drive axle, and the second connecting lever contact section has the greatest distance between the connecting lever eccentric cam and the drive axle.
  • the spring tensioning lever eccentric cam is advantageously designed such that the spring tensioning lever rests against a first spring tensioning lever contact section in the retracted position and against a second spring tensioning lever contact section of the spring tensioning lever eccentric curve.
  • the first spring tensioning lever contact section is at a greater distance from the drive axle than the second spring tensioning lever contact section, with the first spring tensioning lever contact section having the greatest distance between the spring tensioning lever eccentric cam and the drive axle, and the second connecting lever contact section having the smallest distance between the spring tensioning lever eccentric curve and the drive axle.
  • the first spring tensioning lever contact section of the spring tensioning lever eccentric curve forms the abutment for the spring tensioning lever and thus for the return spring, with the abutment thus being in the retracted abutment position, and in the tensioning lever end position, i.e.
  • the spring tensioning lever has a recess for the passage of the first spring tensioning lever contact section during the rotary movement of the eccentric unit.
  • the connecting lever has, for example, a roller for rolling on the connecting lever eccentric curve of the eccentric unit. This enables the connecting lever and thus the door handle to be moved with little friction and little wear, so that only a small amount of force is required for the drive unit and a long service life is achieved.
  • an electric motor is advantageously provided as the drive unit for rotating the eccentric unit. This enables the door handle to be moved electrically into the use position and back.
  • the eccentric unit is advantageously arranged in a fixed manner on the drive axle or is formed in one piece with it and can be rotated by rotating the drive axle.
  • the drive axle is then advantageously coupled to the electric motor, in particular via a gear, in particular via a worm gear, crown gear, bevel gear or gear transmission. This enables, for example, a force deflection and/or a step-up or step-down.
  • the Figures 1 to 7 show a movement assembly 1 for a door handle assembly 2 and FIG figures 8 and 9 the door handle arrangement 2 with such a movement arrangement 1.
  • the movement arrangement 1 is in figure 1 in a retracted position, in figure 2 in an intermediate position and in figure 3 shown in an extended position.
  • the Figures 4 to 7 show another representation of the movement arrangement 1, which is also shown here in figure 4 in the retracted position, in figure 5 in an intermediate position, in figure 6 in another intermediate position and in figure 7 shown in the deployed position.
  • the door handle assembly 2 is in figure 8 shown in a lowered position, in which the movement arrangement 1 is in the retracted position, and in figure 9 shown in a use position in which the movement assembly 1 is in the extended position.
  • the door handle arrangement 2 is designed in particular as an outside door handle arrangement. It is intended for a door, in particular for a vehicle door. It includes a door handle 3 that can be moved from the retracted position into the usage position. The door handle 3 is moved, for example, electrically, in particular by means of an electric motor (not shown here).
  • the door can be opened by actuating and/or touching the door handle 3 .
  • this takes place after the door handle 3 is arranged in the usage position. i.e. the door handle 3 is first moved from the recessed position, in particular in the door recessed position, into the usage position, in particular extended out of the door, in which it is easily accessible for actuation and/or touching.
  • an emergency release can also be provided for emergency operation, for example in the event of a failure of the electrical power supply or due to another cause, so that the door handle 3 can no longer be moved into the use position.
  • the door handle 3 can also be actuated and/or touched in the retracted position to open the door.
  • the door handle arrangement 2 also includes a return spring 4, in particular for returning the door handle 3 from the usage position to the retracted position or at least to support this return.
  • the return spring 4 is coupled to the door handle 3, for example directly to the door handle 3 or, as in the example shown here, via a connecting lever 5 connected to the door handle 3, and in the retracted position and in the use position with an abutment that is at least then fixed G, for example directly or, as in the example shown here, via a spring tensioning lever 6.
  • a spring leg 4.1 or at least one spring leg 4.1 of the return spring 4 is coupled to the door handle 3 or, as in the example shown here, to the connecting lever 5 in particular, and the other spring leg 4.2 or at least one other spring leg 4.2 of the return spring 4 is connected to the counter bearing G or, as in the example shown here, to the spring tensioning lever 6 and via this at least in the retracted position and in the use position with the counter bearing G, with this other spring leg 4.2 resting against the spring tensioning lever 6, in particular in such a way that the return spring 4 is increasingly tensioned or would be tensioned in one direction and is increasingly relaxed in the other direction or would be relaxed.
  • the return spring 4 serves in particular for a coupling, in particular an elastic coupling, of the connecting lever 5 and the spring tensioning lever 6 and thus a coupling in particular an elastic coupling of the door handle 3 and the spring tensioning lever 6, for example to enable anti-trap protection, in particular during movement into the retracted position.
  • the return spring 4 is used in particular to carry the door handle 3, more precisely the connecting lever 5 and thus the door handle 3, while it is being moved back into the retracted position.
  • the spring tensioning lever 6 is moved and, due to the spring tension of the return spring 4, takes with it the door handle 3 coupled via the return spring 4 to the spring tensioning lever 6, more precisely the connecting lever 5 coupled via the return spring 4 to the spring tensioning lever 6 and thus also the door handle 3 .
  • the return spring 4 is decoupled from the abutment G between the retracted position and the use position and/or the abutment G assumes a retracted abutment position in the retracted position and an extended abutment position in the use position and is out of the retracted position while the door handle 3 is being moved into the usage position from the retracted counter-bearing position into the extended counter-bearing position, in which case it advantageously covers a movement path in the same time as the door handle 3 and/or, if present, its connecting lever 5.
  • the drive in particular the electric motor
  • the drive has a larger reserve of power and/or a smaller drive, in particular an electric motor, can be used, for example, whereby space advantages are achieved.
  • the return spring 4 would be additionally tensioned with each movement of the door handle 3 into the use position, causing unnecessary losses in the drive and increasing wear on the drive and the return spring 4, thus shortening the service life.
  • the solution described avoids this, reduces wear and increases the service life.
  • the Figures 1 to 9 show a possible embodiment for realizing the solution described.
  • the return spring 4 is part of the movement arrangement 1, in particular for moving the door handle 3 from the retracted position to the position of use and back.
  • This movement arrangement 1 comprises the connecting lever 5, which is coupled to the door handle 3, in particular to an end region of the door handle 3, in particular is pivotally coupled, as in FIGS figures 8 and 9 shown, as well as the spring tensioning lever 6, the return spring 4 and an eccentric unit 7.
  • the movement assembly 1 with its components and the operation of the movement assembly 1 is in the Figures 1 to 7 shown in detail and will be described in more detail below.
  • the eccentric unit 7 forms the part of the movement arrangement 1 driven by the drive unit, in particular the electric motor, and in turn drives in particular the connecting lever 5 in order to pivot it and thereby move the door handle 3 into the use position.
  • it is rotatably mounted, for example on a bearing bracket of the door handle arrangement 2.
  • it is fixedly arranged on a drive axle 8 and is rotatably mounted on the bearing bracket by means of this drive axle 8, i. H. the drive axle 8 is rotatably mounted on the bearing bracket.
  • the drive axle 8 and via this the eccentric unit 7 is coupled to the drive, in particular to the electric motor, for example via a worm gear or another gear.
  • the eccentric unit 7 forms the counter bearing G for the restoring spring 4, which is coupled to the eccentric unit 7 via the spring tensioning lever 6 in the retracted position and the use position.
  • the eccentric unit 7 is arranged on the bearing bracket and thus on a component part of the door handle arrangement 2 which is fixed, at least fixed when the door handle 3 is in the retracted position and in the usage position.
  • the door handle arrangement 2 is fastened or can be fastened to the door via this bearing bracket.
  • the connecting lever 5 and the spring tensioning lever 6 are pivotably mounted about a common pivot axis 9 and pivotable about this pivot axis 9 relative to one another.
  • the pivot axis 9 is also arranged in the bearing bracket and thus in a fixed position relative to the bearing bracket.
  • the return spring 4 is coupled to a spring contact area 10 of the connecting lever 5 and to a spring contact area 11 of the spring tensioning lever 6, in particular with a respective spring leg 4.1, 4.2, in such a way that it can be released by a pivoting movement of the spring contact area 11 of the spring tensioning lever 6 in the direction of the spring contact area 10 of the connecting lever 5 can be relaxed and tensioned by an opposite pivoting movement.
  • the return spring 4 is in the retracted position and the use position on the Spring tensioning lever 6 is coupled to the eccentric unit 7 forming the counter bearing G, so that the spring tensioning lever 6 is then immovable and thereby, for example, also keeps the connecting lever 5 and thus also the door handle 3 immovable due to the prestressing of the return spring 4 . In particular, in the lowered position, this prevents the door handle 3 from rattling, for example.
  • the eccentric unit 7 which is rotatably mounted by means of the drive axle 8 and is driven by the drive, in particular the electric motor, has a connecting lever eccentric cam 12 for guiding the connecting lever 5 and a spring tensioning lever eccentric curve 13 for guiding the spring tensioning lever 6 .
  • These eccentric cams 12, 13 are arranged in two different planes, so that the eccentric unit 7 has two eccentric discs which are arranged one above the other and are fixed to one another or are designed in one piece and each have one of the eccentric cams 12, 13.
  • the connecting lever 5 is thus moved about the pivot axis 9 by means of the connecting lever eccentric cam 12 from a connecting lever starting position (retracted position of the movement arrangement), shown in FIG figure 1 and figure 4 to a connecting lever end position (extended position of the moving assembly) shown in FIGS Figures 3 and 7 , pivotable, as in the figures 2 , 5 , 6 and 8th shown by a third movement arrow P3.
  • the spring tensioning lever 6 is in the retracted position of the movement arrangement 1 in a tensioning lever starting position ( figures 1 and 4 ), the spring contact areas 11, 10 of the spring tensioning lever 6 and connecting lever 5 being spaced apart from one another in such a way that the return spring 4 is pretensioned, i.e. slightly tensioned, in particular in such a way that it rests firmly on the two spring contact areas 11, 10 and therefore does not rattle.
  • This is in the figures 1 and 4 shown by the spaced apart spring abutment areas 10, 11 between which there is a gap.
  • the spring tensioning lever 6 is in a tensioning lever end position ( Figures 3 and 7 ), wherein advantageously the spring contact areas 11, 10 of the spring tensioning lever 6 and the connecting lever 5 are again spaced apart from one another in such a way that the return spring 4 is pretensioned, i.e. slightly tensioned, in particular in such a way that it rests firmly on the two spring contact areas 11, 10 and therefore does not rattle .
  • This is in the Figures 3 and 7 shown by the spring abutment areas 10, 11 again spaced apart, between which there is a gap.
  • the connecting lever eccentric cam 12 is designed in such a way that the connecting lever 5 in the retracted position ( figure 1 and figure 4 ) on one first connecting lever system section 12.1 and in the extended position ( figure 3 and figure 7 ) rests against a second connecting lever contact section 12.2 of the connecting lever eccentric cam 12, the first connecting lever contact section 12.1 being at a smaller distance from the drive axle 8 than the second connecting lever contact section 12.2.
  • the first connecting lever contact section 12.1 has the smallest distance between the connecting lever eccentric curve 12 and the drive axle 8 and the second connecting lever contact section 12.2 has the greatest distance between the connecting lever eccentric curve 12 and the drive axle 8.
  • the spring tensioning lever eccentric cam 13 is designed such that the spring tensioning lever 6 rests against a first spring tensioning lever contact section 13.1 in the retracted position and on a second spring tensioning lever contact section 13.2 of the spring tensioning lever eccentric curve 13.
  • the first spring clamping lever system section 13.1 has a greater distance to Drive axle 8 than the second spring clamping lever system section 13.2.
  • the first spring tensioning lever contact section 13.1 has the greatest distance between the spring tensioning lever eccentric curve 13 and the drive axle 8 and the second connecting lever contact section 13.2 has the smallest distance between the spring tensioning lever eccentric curve 13 and the drive axle 8. This ensures that the spring tensioning lever eccentric cam 13 rests against the spring tensioning lever 6 pivoted along with the connecting lever 5 in the tensioning lever end position.
  • the first spring tensioning lever contact section 13.1 of the spring tensioning lever eccentric curve 13 of the eccentric unit 7 forms the counter bearing G for the spring tensioning lever 7 and thus for the Return spring 4, as in the figures 1 and 4 shown, with the counter bearing G thus being in the retracted counter bearing position, and in the clamping lever end position, i.e.
  • the second spring tensioning lever contact section 13.2 forms the spring tensioning lever eccentric curve 13 of the eccentric unit 7, the counter bearing G for the spring tensioning lever 6 and thus for the return spring 4, as in the figures 4 and 7 shown, with the counter bearing G now being in the extended counter bearing position due to the rotation of the eccentric unit 7 .
  • the spring tensioning lever 6 advantageously has a recess for the passage of the first spring tensioning lever contact section 13.1 during the rotational movement of the eccentric unit 7. This enables the greatest possible rotational movement of the eccentric unit 7 in order to achieve the greatest possible movement path of the door handle 3 .
  • the passage of the first spring tensioning lever contact section 13.1 through this recess of the spring tensioning lever 6 is in figure 3 and figure 7 recognizable, whereby the Recess here on one of the eccentric unit 7 facing back of the spring tensioning lever 6 is located. This allows the eccentric unit 7 to rotate by 360°, for example, and in particular a particularly long connecting lever eccentric curve 12 for moving the connecting lever 5 is achieved, which can therefore be done with little effort, for example.
  • the connecting lever 5 has a roller 14 for rolling on the connecting lever eccentric curve 12 of the eccentric unit 7 .
  • the movement arrangement 1, in particular the connecting lever 5, is coupled to a further movement arrangement 15, which is coupled to the other end region of the door handle 3, in particular is pivotally coupled.
  • both end regions of the door handle 3 can be moved by means of a single drive unit, for example by means of a single electric motor, so that the door handle 3 can be moved, for example by a parallel displacement, from the retracted position to the use position, as compared in FIG figures 8 and 9 recognizable.
  • a force transmission rod 16 is arranged between the movement arrangement 1, in particular its connecting lever 5, and the further movement arrangement 15 and is connected to the movement arrangement 1, in particular to its connecting lever 5, and the further movement arrangement 15, so that the two movement arrangements 1, 15 are coupled to one another are.
  • the door handle 3 is moved into the retracted position, for example, by means of the spring tensioning lever 6, in particular by moving it by means of the eccentric unit 7 and the spring tensioning lever eccentric cam 13, in particular by rotating the eccentric unit 7 in the opposite direction to move the door handle 3 into the position of use.
  • the spring tensioning lever 6 pivots back about the pivot axis 9, ie in the opposite direction to moving the door handle 3 into the position of use.
  • the return spring 4 is used in particular to take the door handle 3, more precisely the connecting lever 5 and thus the door handle 3.

Landscapes

  • Lock And Its Accessories (AREA)

Claims (15)

  1. Agencement de mouvement (1) pour un agencement de poignée de porte (2), comprenant un levier de liaison (5) servant pour la liaison à une poignée de porte (3), un levier de tension de ressort (6), un ressort de rappel (4) et une unité excentrique (7), le levier de liaison (5) et le levier de tension de ressort (6) étant disposés de façon à pouvoir pivoter autour d'un axe de pivotement (9) commun et pouvant les faire pivoter l'un par rapport à l'autre autour de cet axe de pivotement (9), le ressort de rappel (4) étant couplé de telle sorte à une zone de butée de ressort (10) du levier de liaison (5) et à une zone de butée de ressort (11) du levier de tension de ressort (6), qu'il peut être détendu par le mouvement de pivotement de la zone de butée de ressort (11) du levier de tension de ressort (6) en direction de la zone de butée de ressort (10) du levier de liaison (5) et qu'il peut être tendu par le mouvement de pivotement opposé, dans lequel l'unité excentrique (7) est disposée de façon à pouvoir pivoter et présentant une courbe excentrique de levier de liaison (12) servant au guidage du levier de liaison (5) et une courbe excentrique de levier de tension de ressort (13) servant au guidage du levier de tension de ressort (6), et dans lequel les courbes excentrées (12, 13) sont réalisées de telle sorte que :
    - l'agencement de mouvement (1) pouvant être transféré d'une position rentrée jusque dans une position sortie par pivotement de l'unité excentrique (7) ;
    - le levier de liaison (5) et le levier de tension de ressort (6) sont positionnés les uns par rapport aux autres dans la position rentrée et dans la position sortie de telle sorte que le ressort de rappel (4) soit tendu en partie ;
    - le levier de liaison (5) s'appuie contre la courbe excentrique de levier de liaison (12) pendant le mouvement de pivotement de l'unité excentrique (7) ; et
    - le levier de tension de ressort (6) s'appuie contre la courbe excentrique de levier de tension de ressort (13) dans la position rentrée et la position sortie et est placé à une certaine distance par rapport à la courbe excentrique de levier de tension de ressort (13) entre les deux positions.
  2. Agencement de mouvement (1) selon la revendication 1, dans lequel la courbe excentrique de levier de liaison (12) est réalisée de telle sorte que le levier de liaison (5) s'appuie dans la position rentrée contre une première section de butée de levier de liaison (12.1) et s'appuie dans la position sortie contre une deuxième section de butée de levier de liaison (12.2) de la courbe excentrique de levier de liaison (12), dans lequel notamment la première section de butée de levier de liaison (12.1) présente une distance plus petite par rapport à un axe d'entraînement (8) que la deuxième section de butée de levier de liaison (12.2), dans lequel notamment la première section de butée de levier de liaison (12.1) présente la plus petite distance entre la courbe excentrique de levier de liaison (12) et l'axe d'entraînement (8) et la deuxième section de butée de levier de liaison (12.2) présente la plus grande distance entre la courbe excentrique de levier de liaison (12) et l'axe d'entraînement (8).
  3. Agencement de mouvement (1) selon la revendication 2, dans lequel la courbe excentrique de levier de tension de ressort (13) est réalisée de telle sorte que le levier de tension de ressort (6) s'appuie dans la position rentrée contre une première section de butée de levier de tension de ressort (13.1) et dans la position sortie contre une deuxième section de butée de levier de tension de ressort (13.2) de la courbe excentrique de levier de tension de ressort (13), dans lequel la première section de butée de levier de tension de ressort (13.1) présente notamment une plus grande distance par rapport à l'axe d'entraînement (8) que la deuxième section de butée de levier de tension de ressort (13.2), dans lequel la première section de butée de levier de tension de ressort (13.1) présente notamment la plus grande distance entre la courbe excentrique de levier de tension de ressort (13) et l'axe d'entraînement (8) et la deuxième section de butée de levier de tension de ressort (13.2) présente la plus petite distance entre la courbe excentrique de levier de tension de ressort (13) et l'axe d'entraînement (8).
  4. Agencement de mouvement selon la revendication 3, dans lequel le levier de tension de ressort (6) présente un évidement pour le passage de la première section de butée de levier de tension de ressort (13.1) pendant le mouvement de pivotement de l'unité excentrique (7).
  5. Agencement de mouvement (1) selon l'une quelconque des revendications précédentes, dans lequel le levier de liaison (5) comporte un rouleau (14) de déroulement au niveau de la courbe excentrique de levier de liaison (12) de l'unité excentrique (7).
  6. Agencement de mouvement (1) selon l'une quelconque des revendications précédentes, dans lequel un moteur électrique est prévu pour faire tourner l'unité excentrique (7).
  7. Agencement de mouvement (1) selon l'une quelconque des revendications 2 à 6, dans lequel l'unité excentrique (7) est disposée fixement sur l'axe d'entraînement (8) ou est réalisée d'un seul tenant avec lui et peut tourner par pivotement de l'axe d'entraînement (8).
  8. Agencement de mouvement (1) selon la revendication 6 ou 7, dans lequel le moteur électrique est couplé à l'axe d'entraînement (8), notamment via un engrenage à vis sans fin, un engrenage à roue conique ou un engrenage à roue dentée.
  9. Agencement de mouvement (1) selon l'une quelconque des revendications précédentes, dans lequel l'agencement de poignée de porte (2), notamment l'agencement de poignée extérieure de porte, est prévu pour une porte, notamment pour une porte de véhicule, et comprend le ressort de rappel (4) et la poignée de porte (3) pouvant être déplacée d'une position abaissée jusque dans une position d'utilisation, dans lequel le ressort de rappel (4) est couplé à la poignée de porte (3) et est couplé dans la position abaissée et dans la position d'utilisation à un contre-palier de roulement (G) y étant au moins alors fixé, dans lequel le ressort de rappel (4) est découplé du contre-palier de roulement (G) entre la position abaissée et la position d'utilisation et/ou dans lequel le contre-palier de roulement (G) prend dans la position abaissée une position rentrée de contre-palier de roulement et prend dans la position d'utilisation une position sortie de contre-palier de roulement et peut être transmis pendant le déplacement de la poignée de porte (3) de la position abaissée jusque dans la position d'utilisation, depuis la position rentrée de contre-palier de roulement jusque dans la position sortie de contre-palier de roulement.
  10. Agencement de mouvement (1) selon la revendication 9, dans lequel l'agencement de poignée de porte (2) comprend le levier de tension de ressort (6) et l'unité excentrique (7), dans lequel le ressort de rappel (4) est couplé à la zone de butée de ressort (11) du levier de tension de ressort (6), dans lequel l'unité excentrique (7) est disposée de façon à pouvoir pivoter et présente la courbe excentrique de levier de tension de ressort (13) servant au guidage du levier de tension de ressort (6) et dans lequel la courbe excentrique de levier de tension de ressort (13) est réalisée de telle sorte que le levier de tension de ressort (6) s'appuie contre la courbe excentrique de levier de tension de ressort (13) dans la position abaissée de la poignée de porte (3) et dans la position d'utilisation de la poignée de porte (3) et est placé à distance par rapport à la courbe excentrique de levier de tension de ressort (13) entre les deux positions.
  11. Agencement de mouvement (1) selon la revendication 9 ou 10, notamment pour le déplacement de la poignée de porte (3) depuis la position abaissée jusque dans la position d'utilisation et vice-versa, dans lequel le levier de liaison (5) est couplé à la poignée de porte (3), notamment à une zone d'extrémité de la poignée de porte (3), notamment est couplé de façon à pouvoir pivoter, dans lequel dans la position rentrée, la poignée de porte (3) est positionnée dans la position abaissée et la poignée de porte (3) est positionnée dans la position d'utilisation dans la position sortie.
  12. Agencement de mouvement (1) selon l'une quelconque des revendications précédentes, dans lequel l'unité excentrique (7) et/ou l'axe de pivotement (9) sont disposés au niveau d'un étrier de palier de roulement pour l'agencement de poignée de porte (2).
  13. Agencement de mouvement (1) selon la revendication 12, dans lequel pour l'agencement de poignée de porte (2), l'unité excentrique (7) est disposée au niveau de l'étrier de palier de roulement via l'axe d'entraînement (8), ledit axe étant disposé de façon à pouvoir tourner dans l'étrier de palier de roulement.
  14. Agencement de mouvement (1) selon l'une quelconque des revendications 11 à 13, dans lequel pour l'agencement de poignée de porte (2), l'agencement de mouvement (1), notamment le levier de liaison (5), est couplé à un autre agencement de mouvement (15) qui est couplé à une autre zone d'extrémité de la poignée de porte (3), notamment de façon à pouvoir pivoter.
  15. Agencement de mouvement (1) selon la revendication 14, dans lequel pour l'agencement de poignée de porte (2), une barre de transmission de force (16) est disposée entre l'agencement de mouvement (1), notamment son levier de liaison (5), et l'autre agencement de mouvement (15).
EP21215453.8A 2019-05-02 2020-04-14 Agencement de mouvement pour un dispositif de poignée de porte Active EP4006275B1 (fr)

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DE102019206293.8A DE102019206293A1 (de) 2019-05-02 2019-05-02 Bewegungsanordnung und Türgriffanordnung
EP20169274.6A EP3734003B1 (fr) 2019-05-02 2020-04-14 Agencement de poignée de porte

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EP20169274.6A Division-Into EP3734003B1 (fr) 2019-05-02 2020-04-14 Agencement de poignée de porte
EP20169274.6A Division EP3734003B1 (fr) 2019-05-02 2020-04-14 Agencement de poignée de porte

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EP4006275B1 true EP4006275B1 (fr) 2023-07-12

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Publication number Priority date Publication date Assignee Title
DE4002963C1 (en) * 1990-02-01 1991-07-11 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De Vehicle door handle grip - has handle movement controlled by individual swivel levers used to hinge it
CN106837025B (zh) * 2012-06-15 2019-06-28 百乐仕株式会社 开闭体的锁止装置
DE102013112705A1 (de) * 2013-11-18 2015-05-21 Illinois Tool Works Inc. System aus einem Bauteil und einer Betätigungsvorrichtung für das Bauteil
WO2016113341A1 (fr) * 2015-01-16 2016-07-21 Bos Gmbh & Co. Kg Portière pour véhicule à moteur
US10501967B2 (en) * 2015-03-25 2019-12-10 Jaguar Land Rover Limited Retractable handle arrangement
DE102016112689A1 (de) * 2016-07-11 2018-01-11 Huf Hülsbeck & Fürst Gmbh & Co. Kg Griffvorrichtung mit einem flächenbündigen Griff
DE102016217647A1 (de) * 2016-09-15 2018-03-15 Bos Gmbh & Co. Kg Türgriffsystem für eine Fahrzeugtür
ES2761913T3 (es) * 2017-05-16 2020-05-21 U Shin Italia Spa Control de manilla al ras
DE102017010196B3 (de) * 2017-10-30 2019-04-25 Daimler Ag Griffvorrichtung für eine Kraftfahrzeugtür

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EP3734003A1 (fr) 2020-11-04
EP4006275A1 (fr) 2022-06-01
DE102019206293A1 (de) 2020-11-05
CN111877892A (zh) 2020-11-03
CN111877892B (zh) 2022-05-27

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