EP3715565A1 - Öffnungskontrolle mit mechanischer aufstellung - Google Patents

Öffnungskontrolle mit mechanischer aufstellung Download PDF

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Publication number
EP3715565A1
EP3715565A1 EP19206818.7A EP19206818A EP3715565A1 EP 3715565 A1 EP3715565 A1 EP 3715565A1 EP 19206818 A EP19206818 A EP 19206818A EP 3715565 A1 EP3715565 A1 EP 3715565A1
Authority
EP
European Patent Office
Prior art keywords
handle
drive
control
chain
kinematic
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.)
Withdrawn
Application number
EP19206818.7A
Other languages
English (en)
French (fr)
Inventor
Delmiro Javier Couto Maquieira
Alberto Diez Estevez
Javier Casal Gomez
José Oscar VAZQUEZ CARBALLO
Julio GARCIA RODRIGUEZ
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.)
Akwel Vigo Spain SL
Original Assignee
Akwel Vigo Spain SL
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Akwel Vigo Spain SL filed Critical Akwel Vigo Spain SL
Publication of EP3715565A1 publication Critical patent/EP3715565A1/de
Withdrawn legal-status Critical Current

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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
    • E05B79/00—Mounting or connecting vehicle locks or parts thereof
    • E05B79/02—Mounting of vehicle locks or parts thereof
    • E05B79/06—Mounting of handles, e.g. to the wing or to the lock
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B81/00—Power-actuated vehicle locks
    • E05B81/54—Electrical circuits
    • E05B81/90—Manual override in case of power failure
    • 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
    • E05B85/00—Details of vehicle locks not provided for in groups E05B77/00 - E05B83/00
    • E05B85/10—Handles
    • E05B85/14—Handles pivoted about an axis parallel to the wing
    • 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
    • E05B15/0046—Ratchet mechanisms
    • 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
    • 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
    • E05B81/26—Output elements
    • E05B81/28—Linearly reciprocating elements
    • 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
    • E05B81/34—Details of the actuator transmission of geared transmissions
    • 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
    • E05B81/34—Details of the actuator transmission of geared transmissions
    • E05B81/36—Geared sectors, e.g. fan-shaped gears

Definitions

  • the present invention relates to an opening control for a motor vehicle opening.
  • the invention relates more particularly but not exclusively to an external opening control which comprises emergency mechanical unlocking means in the event of failure of the electrical actuating means of the opening control.
  • This opening command applies equally well to unlocking with a conventional lock or with an electrically actuated lock, also known under the expression “electronic lock” or alternatively according to the English terminology “electronic latch” or “e -latch ”.
  • an external opening control comprises a fixed support intended to be mounted on the opening and a handle movably mounted on the support, for example pivotally mounted on the support while being articulated in rotation about an axis.
  • the opening control also includes an unlocking mechanism, which when the handle is pulled in, unlocks the lock and thus opens the door.
  • the lock conventionally comprises a bolt integral with the door able to cooperate with a keeper integral with the bodywork. When the door is opened from outside the vehicle, the bolt is released from the strike by actuating the external opening control.
  • the invention relates more particularly to an opening control with a handle of the “flush” type, that is to say that the support on which the handle is movably mounted forms a cavity capable of receiving the handle in the retracted configuration.
  • the exterior surface of the handle In this retracted configuration, the exterior surface of the handle is flush with the exterior surface of the exterior wall of the opening.
  • the handle protrudes at least partially from the cavity of the support so that it can be grasped by a user of the vehicle in order to open the door. To do this, the user can move the handle further outward in order to control the door lock.
  • the opening control comprises an electric ejection mechanism of the handle to allow the grip of the handle by the user and the opening of the opening.
  • the electric ejection mechanism operates from an electric power supply supplied for example by a battery of the motor vehicle and can be controlled electronically remotely using a key, a mobile telephone or any other device allowing remote communication.
  • the object of the invention is to remedy these drawbacks and to provide a compact, robust opening control which allows an emergency mechanical unlocking of the opening control in a simple manner.
  • the invention relates to an opening control of a motor vehicle opening of the type comprising a handle mounted movably in rotation with respect to a support between at least one intermediate position of rest, an ejected position and a depressed position, a mechanism comprising a kinematic chain for driving the movement of the handle comprising at least one rotary member for driving the angular movement of the handle and at least one motor member configured to accumulate mechanical energy by mechanical work during a depressing action of the handle and to restore mechanical energy to the drive kinematic chain after release of the handle, characterized in that the handle comprises a means for stabilizing the drive kinematic chain configured to limit angulation of the rotating chain member to a predefined angle value while the handle is depressed.
  • the mechanism allows automatic retraction of the handle in its flush position without the aid of any electric assistance.
  • the stabilization means comprises a member for hooking the rotary element of the kinematic drive chain configured to hook the rotary element during the depression of the handle and limit its angular displacement.
  • the handle comprises a body delimited by a lower surface being provided locally with a hooking profile forming the stabilization means.
  • the hook profile has locally a generally arched shape with a concavity oriented towards the interior of the handle body, the curvature of the profile being determined in order to limit the angulation at an angle. predefined.
  • the hooking profile advantageously forms a curvilinear guide ramp configured to radially guide the rotary element.
  • This guide ramp has a curvilinear shape, for example circular, and is able to produce an effect regulating the movement of the handle 16 in its direction of drive.
  • the stabilization means being shaped as a hooking profile extending locally on an interior face of the handle, the rotating element is configured to engage tightly along the handle. profile when the handle is pushed in to limit its angulation to a predefined angle.
  • the kinematic drive chain comprises a drive toothed wheel configured to perform a rotation by an angle of 2 ⁇ + ⁇ , with the angle ⁇ greater than the angle of angulation, when the handle is pushed in.
  • control comprises means for reversible unidirectional coupling of the rotary member and the driving wheel in a driving direction of the wheel.
  • the coupling means comprise a snail-type cam provided with an end face and a locking element movable between a return position in engagement with the end face and an active retracted position. resting on the periphery of the cam.
  • the cam is carried by the drive wheel and the blocking element is mounted inside a cylindrical cage secured to the rotary element.
  • the rotating member comprises a lever for driving the handle in a reciprocating pivoting movement of the handle.
  • the drive lever comprises a rotatably mounted shaft and an eccentric mounted on the shaft.
  • the drive kinematic chain is configured to rotate the rotary element through at least one full turn in order to drive the ejection of the handle through a first half turn and on a second half-turn retraction of the handle.
  • control comprises a kinematic chain for charging the motor member with energy when the handle is pressed.
  • the kinematic loading chain comprises a spring pushing member forming a push-in stop for the handle and configured to initiate a movement when the handle is released.
  • the kinematic loading chain comprises at least one means of transmitting the driving movement of the handle to the motor member.
  • the transmission means is a lever mounted to pivot and has the shape of a circular sector pivotally connected at one end to the stopper member for driving the handle and forming the handle. at the other end an arc of a toothed gear circle.
  • the drive member comprises a torsion coil spring.
  • FIG. 1 An opening control of a motor vehicle opening according to a preferred embodiment of the invention.
  • This opening control is designated by the general reference 10.
  • the opening control 10 is designed to be mounted on an exterior panel (not shown) of the body of an opening which is for example a side door of a vehicle.
  • the opening control 10 comprises for example essentially a fixed support or housing 12 having a cavity 14 for receiving a handle and a handle 16 movably mounted inside the cavity 14.
  • the support 12 is intended to be fixed to the sash.
  • the handle 16 is in the example described mounted articulated relative to the panel, about a geometric pivot axis A1, on the support 12 and extends parallel to the general plane of the outer panel.
  • the support 12 has a general parallelepipedal shape and is suitable for being housed in a cutout or a recess in the outer panel of the opening so that its outer face is flush with the surface of the outer panel of the opening. .
  • the support 12 defines in this example a cavity 14 open on one side and intended to house the handle 16
  • the handle 16 has an external portion 16.1 that the user can grip. Opposite the external portion 16.1, the handle 16 has an internal portion 16.2 which is intended to extend inside the housing 14 of the housing or support 12 as can be seen on the figure. figure 1 .
  • the handle 16 is of the “flush” type, that is to say that the support 12 on which the handle 16 is movably mounted forms the cavity 14 capable of receiving the handle 16 in a retracted configuration.
  • the outer surface of the handle 16 is flush with the outer surface of the outer wall of the opening.
  • the handle 16 protrudes at least partially from the cavity 14 of the support 12 so that it can be grasped by a user of the vehicle in order to open the door. To do this, the user can pull handle 16 further outward in order to control the door lock.
  • the outer surface of the opening control 10 coincides with the outer surface of opening it.
  • This flush or “flush” arrangement known in the automobile industry, enhances the style of the vehicle and reduces aerodynamic drag.
  • the opening control 10 is preferably intended to cooperate with a lock (not shown) of the opening of the motor vehicle capable of adopting a locked configuration and an unlocked configuration.
  • a lock (not shown) of the opening of the motor vehicle capable of adopting a locked configuration and an unlocked configuration.
  • the pivoting of the handle 16 about its articulation axis A1 actuates the lock in one or the other of its two locked or unlocked configurations by means of an unlocking kinematic chain (not shown in the figures).
  • the opening control 10 comprises a return lever 20.
  • This return lever 20 comprises, in the example described, a rotary cage 22 and a return shaft 24 as well as a return spring 26 intended to be housed in the interior of the rotary cage 22.
  • the rotary cage 22 comprises, for example, means for retaining one end of a Bowden cable (not shown).
  • the assembly 20 is intended to be mounted on the support 12 as illustrated in figure 1 .
  • the opening control 10 comprises an electrical part 50 allowing electrical actuation of the ejection and / or the retraction of the handle 16.
  • the opening control 10 preferably further comprises a lever 30 for pivoting the handle 16 in ejection and / or retraction.
  • This pivot lever 30 is preferably mounted to tilt around the pivot axis A1 of the handle 16.
  • the pivot lever 30 is connected to the handle 16 by at least one common axis of rotation. A1 fixed in relation to the box 12.
  • This pivot lever 30 has for example the general shape of a bracket through which the internal portion 16.1 of the handle can be engaged ( figure 1 ).
  • the stirrup 30 preferably comprises a body delimiting a frame inside which the internal branch 16.2 of the handle 16 can be introduced.
  • the stirrup 30 preferably comprises a stirrup head extending above the handle 16 and a stirrup floor resting from below the handle 16.
  • the head and the floor are connected together preferably by two bent side branches at the top of which the stirrup 30 is articulated.
  • the bent side branches have for example a general shape of "L" and the top is formed at the angle of the "L".
  • the stirrup head preferably comprises an upper transverse connecting bar and the stirrup floor is formed by a lower transverse connecting bar.
  • the lower face 16l of the handle 16 comprises a shoulder delimiting a transverse bearing wall from which the internal branch 16.2 extends axially and against which the bracket 30 comes to bear from below to make pivot the handle 16.
  • the lower bar of the bracket 30 presses on this support wall at the level of the internal branch 16.2, to act as a lever and thus tilt the handle 16 to its position of ejection.
  • This stirrup 30 can for example pivot about a common axis A1 to the handle 16 which is integral with the housing 12.
  • the stirrup 30 comprises an articulation support, located at the location of the tops, provided on each side with two bearings for guiding the yoke 30 in rotation about the axis A1.
  • the stirrup 30 has the overall frontally a general shape of an arch inside which the internal branch 16.2 is introduced in a direction of introduction that is substantially perpendicular or slightly oblique to the plane containing the arch.
  • the hoop preferably connects the head and the floor by two arched side arms.
  • the ejection stirrup 30 has for example first and second solid lateral flanges parallel and perpendicular to the common axis of rotation A1.
  • the opening control 10 for example further comprises a return member 38 connected to the stirrup 30.
  • This return member 38 is preferably configured to return the stirrup 30 to a rest position corresponding to the flush configuration of the handle 16.
  • each of the two tabs of the caliper spring 38 is intended to be fixed to an interior wall of the housing 12.
  • the handle 16 is provided with a member 28 for returning the handle 16 which is placed between the bracket 30 and the internal portion 16.1 of the handle 16 and which have the axis A1 as a common axis.
  • the handle return spring 28 has in this example two tabs intended to be fixed to the bracket 30 and a central part in engagement with the internal portion 16.2.
  • the function of the handle return spring 28 is in this example, by a return force, to take up a play between the internal portion 16.1 and the yoke 30.
  • the handle 16 is configured to pivot freely inside. of the caliper 30 when the caliper 30 is stationary against the handle return spring 28 16 within the limit of a predefined angular displacement clearance inside the caliper 30.
  • the electrical operating portion 50 comprises in this example an electrical actuator 60 connected to an ejection arm 70 intended to extend transversely inside the housing 12 in a pivotal manner as seen in figure 1 .
  • the electric actuator 60 preferably comprises a linear actuator 62 provided with an end 64 cooperating with an end 72 of the ejection arm to rotate the ejection arm 70 about a vertical axis.
  • the end 64 includes a notch and the end 72 includes a protruding lug.
  • the ejection arm 70 is as shown in the example figure 2 , comprises an end 74 pivotally mounted between two parallel flanges 76 of the housing 12.
  • the opening control 10 also comprises a mechanism 100 allowing mechanical actuation of a movement of ejection and retraction of the handle 16.
  • the mechanism 100 is configured to be mechanically engaged in response to a pushing action into the housing 12 of the handle 16, the end of the driving or releasing action being able to trigger the triggering of the mechanism 100.
  • the backup mechanism 100 is designed to be mounted so as to cooperate with the handle 16.
  • the relief mechanism 100 is, as shown in figure 1 , mounted integral with the housing 12 for receiving the handle 16.
  • the mechanism 100 thus comprises a kinematic drive chain 150 in movement of the handle 16 to automatically drive the handle 16 in motion along all or part of a stroke starting from the depressed position of the handle 16 to the flush position passing through the ejected position.
  • the mechanism 100 is configured to drive the handle 16 in motion over the entire stroke.
  • the mechanism 100 comprises at least one motor member 110 configured to accumulate mechanical energy during the depressing action of the handle 16 and to restore the mechanical energy accumulated to the kinematic drive chain 150 after release of the handle 16.
  • the motor member 110 comprises a spring 112 capable of accumulating mechanical energy by working around its longitudinal axis.
  • the spring 112 is a coil spring comprising a spring body configured to work in compression, traction or torsion.
  • the motor member 110 can comprise any type of spring, and in particular not limited to a coil spring with turns.
  • the mechanism 100 comprises in this example a kinematic chain 120 for loading the spring 112 with energy when the handle 16 is pushed in.
  • the kinematic loading chain 120 comprises at least one means 130 for transmitting the driving movement of the handle 16 to the motor unit 110.
  • the kinematic loading chain 120 also comprises a member 122 forming a stopper for pushing in the handle 16 and configured to impulse a movement during the release of the handle 16.
  • This member 122 forming a stop comprises in the example a push element 124 with spring 126.
  • the push element 124 has for example the general shape of a cylindrical sleeve extended at one end by a rod axial around which the spring 126 is positioned and has at another end an elastomeric stopper 128.
  • the push-in stop member 122 is preferably intended to come into contact with a lower face 16l of the outer portion 16.1 of the handle 16.
  • the transmission means is a lever 130 mounted to pivot about an axis integral with the housing 12.
  • the lever 130 preferably has the shape of a circular sector pivotally connected at a first end 132 to the stop member 122 of depression of the handle 16 and forming at a second end 134 an arc of a toothed gear circle.
  • the end 132 of the transmission lever 130 ends in a fork 136 comprising two branches forming a “U” configured to support a transverse pivot axis A2 of the stop member 122.
  • the pivoting of the handle 16 around its axis A1 causes a displacement of the stop 122 by compression of its return spring 126.
  • the lower end of the stop member 122 is, in this example, connected in rotation to the transmission lever 130 by the axis A2, so that a displacement of the stop 122 causes the rotation of the transmission lever 130 about its axis A3 ( figures 13 and 14 ).
  • the kinematic drive chain 150 comprises at least one drive wheel 160 provided for example with a peripheral gear toothing.
  • This drive wheel 160 has the function of transmitting to the drive kinematic chain 150 the energy accumulated from the motor member 110.
  • the wheel 160 is coupled to the winding kinematic chain. 120 and is preferably mounted directly or indirectly under the voltage of the motor member 110.
  • the kinematic winding chain 120 also optionally comprises a transmission gear 140, interposed between the transmission lever 130 and the drive wheel 160.
  • This transmission gear 140 is composed, in the example, of a pinion input 142 cooperating with the gear 134 of the transmission lever 130 and an output pinion 144 cooperating with the input pinion 142 and the drive wheel 160.
  • the drive wheel 160 can be directly coupled with the gear 134 of the transmission lever 130.
  • the motor member 110 is housed coaxially in a cylindrical cavity 146 of the output pinion 144 of the gear train 140.
  • the motor member 110 may be mated directly to the drive wheel 160 or with another transmission chain configuration.
  • the kinematic chain 150 further comprises a rotary element 170 for transmitting an angular pivoting movement to the handle 16.
  • This rotary element 170 is preferably configured to transform a rotary movement, for example of the drive wheel 160. , in a reciprocating movement of the handle 16.
  • the rotary member 170 comprises a drive lever 170 of the handle 16 in a reciprocating pivoting movement of the handle 16 along said stroke.
  • the lever 170 comprises for example a drive shaft 172 rotatably mounted and provided with an eccentric 174.
  • the drive kinematic chain 150 is configured to rotate the drive lever 170 over at least one full turn in order to drive the ejection of the handle 16 over a first half-turn and over a second half-turn. retraction of the handle 16.
  • the transmission ratio of the transmission means 130 to the motor member 110 is preferably defined such that the depression of the handle 16 causes an angular rotation greater than 2 ⁇ of the drive pinion 160.
  • the opening control 10 comprises a means 190 for stabilizing or maintaining in a stable position of the kinematic drive chain 150 when the handle 16 is pushed in, visible on the figures. figures 7 and 8 .
  • This means 190 is preferably mounted on the handle 16.
  • This means 190 is configured to limit the angulation (or angular movement) of the lever 170 to a predefined value of angle ⁇ during the depression of the handle 16.
  • the holding means 190 preferably comprises a hooking profile 192 of the drive lever 170 shaped to limit the angulation of the lever 170 by a predefined angle ⁇ when the handle 16 is pushed in.
  • the handle 16 comprises a body delimited by a lower surface 16I and an upper surface 16E, the lower surface 16l being provided locally with the hooking profile 192.
  • the profile 192 has in this example locally a generally arcuate shape with a concavity oriented towards the inside of the body of the handle 16.
  • the curvature of the profile 192 is determined in order to limit the angulation of the lever 170 at the angle. ⁇ predefined.
  • the profile 192 forms a ramp or cam for guiding the lever 170 and its crankpin 172 configured to produce a regulating effect in the direction of drive S2 of the handle 16 in motion.
  • the guide ramp 192 has a curvilinear shape, preferably in an arc of a circle. The circular arc guide ramp 192 thus makes it possible to optimize the ejection forces with respect to a flat shape.
  • the kinematic drive chain 150 is configured to drive in rotation, for example by means of the drive wheel 160, the shaft 170 of the eccentric 172 over an angle of 2 ⁇ + ⁇ , with ⁇ greater than ⁇ to catch the angle of rotation ⁇ .
  • this angle of rotation will be absorbed by the excess rotation ⁇ .
  • the drive lever 170 and the toothed wheel 160 or drive pinion 160 comprise means 180 for reversible one-way coupling of the lever 172 and the wheel 160 in the driving direction.
  • the means 180 comprise for example a cam 184 of the snail type, spiral or in the form of a retraction ramp provided with at least one end face 188 and a locking element 182 movable between a return position in abutment against the end face 188 and a retracted active position resting on the periphery of the cam 184.
  • the cam 184 is carried by the toothed wheel 160 and the blocking element 182 or blocker 182 is mounted inside a cylindrical cage 186 secured to the drive shaft 170.
  • the cage 186 is shaped as a receiving hub body for the drive shaft 170, in particular by a splined connection of the hexagonal type 187.
  • the toothed wheel 160 comprises in an axial direction and mounted coaxially a toothed portion 162 and a portion 164 carrying a cam 184 mounted coaxially with the toothed portion 162.
  • the blocker 182 is movably mounted inside the cage 186 between a protruding interaction return position inside the cage 186 against the end face 188 and a retracted position tangentially to an internal wall of the cage 186.
  • the blocker 182 comprises for example a pivoting pawl resiliently returned to the return position by a spring 189.
  • the pivoting pawl 182 of the receiving cage 186 makes it possible to transmit the torque from the mainspring 110 to the receiving cage 186. The torque will be transmitted. once the power spring 112 is reassembled by one turn of the drive wheel 160.
  • the pawl 182 is biased against the cam 184 and by the action of its return spring.
  • the drive wheel 160 When reassembling the motor member 110 and therefore the depression of the handle 16, the drive wheel 160 is rotated in the direction S1 by the transmission lever 130 by means of the transmission gear 140. In this case, the pawl 182 is no longer in the locked position against the end stop face 188 which has already rotated integrally with the drive wheel 160. In addition, the drive lever 170 is able to move. inadvertently at the start of the depression in the two directions of rotation S1 and S2, for example by a friction effect.
  • the snail cam 184 gradually retracts the pivoting pawl 182 during its rotation by a full turn.
  • the drive wheel 160 returns to its initial position blocked by the pawl 182. It is therefore necessary for the pawl 182 to project inside the cam 184 and to engage with the end stop face 188. It is therefore necessary to ensure the absorption of an unwanted angular displacement of the device.
  • lever 170 within the possible predefined angulation ⁇ , in particular in the direction S2. This is ensured by a surplus ⁇ of rotation of the drive wheel 160 beyond one complete revolution.
  • the rotary pawl 182 again faces the stop 188 of the ramp of the cam 184, so that, when the handle 16 is released, the drive wheel 160 transmits its torque to the drive shaft 170 via the receiving cage 186 in the direction of rotation S2.
  • the opening control 10 further comprises a hard point passage system 200.
  • This hard point passage system is in this example optional.
  • the hard point passage means 200 comprises a pivoting member 210 about an articulation axis A3 carried by the transmission lever. 130 and an elastic return member 216 of the pivoting member 210.
  • the pivoting member 210 comprises a crank 212 movable around the articulation axis A2 and a crank pin 212 eccentric with respect to the axis A3 and forming a pawn 212.
  • the transmission lever 130 is provided with an orifice 220 and the pin 212 is configured to protrude inside the orifice 220 and is movable through the orifice 220. from an upper rest position in which it is resiliently biased by an elastic return member 216 to a lower active position for securing the transmission lever 130 in rotation.
  • the orifice 220 has a generally oblong shape.
  • the handle 16 is flush with the housing 12.
  • the depression stop member 122 is in a non-depressed state.
  • the drive lever 170 with the eccentric 172 is in a lower position without contact with the hooking profile 192.
  • an operator pushes the handle 16 inside the housing 12 so as to cause it to pivot about its articulation axis A1.
  • the handle 16 urges in compression the stop member 122 forming the driving member.
  • the axial depression of the pusher member 122 engages the kinematic chain for winding the motor member 110.
  • the handle 16 and more particularly the lower face 16l of this handle 16 acts on the depression stop member 122 and compress the depression stop spring 126. During this action, the transmission lever 130 is driven in pivoting.
  • the transmission lever 130 pivots around its axis A3 in an anti-clockwise direction by driving the drive wheel 160 in an anti-clockwise direction via the transmission gear 140.
  • the lever 170 During the depression of the handle 16, the lever 170 remains in a stable position thanks to the handle 16, which has a hooking profile 192 in the form of an arc of a circle and prevents the rotation of the lever 170 beyond a predefined angle " ⁇ ".
  • the transmission gear 140 drives the drive wheel 160 by rotating it through an angle of 360o + " ⁇ " (one revolution + a predefined overtravel angle) in the direction of rotation S1 ( figure 10 ).
  • the angle " ⁇ ” must be greater than the angle " ⁇ ”.
  • the angle “ ⁇ ” is absorbed by the overtravel angle “ ⁇ ”.
  • This excess angle makes it possible to compensate for an untimely angular movement of the drive lever 170.
  • this makes it possible to ensure that at the end of the recharging of the helical spring 112, as illustrated in figure 10 , the pawl 182 is in abutment against the end face 188 ready to start in the opposite direction of rotation S2 to actuate the drive chain 150 and drive the movement of the lever 170.
  • the emergency mechanism 100 is of very simple and very robust design. Even in the event of inadvertent rotation of the drive lever 172 during the depression of the handle 16, this rotation is, on the one hand, limited to a predefined maximum angle ⁇ and in addition makes it possible to ensure in all cases the complete recharging of the system 10 and allow the completion of the full stroke of the handle 16 from its depressed position to its flush position through the ejected position.

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EP19206818.7A 2018-12-20 2019-11-04 Öffnungskontrolle mit mechanischer aufstellung Withdrawn EP3715565A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1873588A FR3090719B1 (fr) 2018-12-20 2018-12-20 Commande d’ouverture à remontage mécanique.

Publications (1)

Publication Number Publication Date
EP3715565A1 true EP3715565A1 (de) 2020-09-30

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Application Number Title Priority Date Filing Date
EP19206818.7A Withdrawn EP3715565A1 (de) 2018-12-20 2019-11-04 Öffnungskontrolle mit mechanischer aufstellung

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US (1) US11512508B2 (de)
EP (1) EP3715565A1 (de)
CN (1) CN111350425B (de)
FR (1) FR3090719B1 (de)

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US20200199918A1 (en) 2020-06-25
US11512508B2 (en) 2022-11-29
CN111350425A (zh) 2020-06-30
FR3090719A1 (fr) 2020-06-26
FR3090719B1 (fr) 2021-01-22

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