EP3426866B1 - Serrure de porte avec moteur - Google Patents

Serrure de porte avec moteur Download PDF

Info

Publication number
EP3426866B1
EP3426866B1 EP17718554.3A EP17718554A EP3426866B1 EP 3426866 B1 EP3426866 B1 EP 3426866B1 EP 17718554 A EP17718554 A EP 17718554A EP 3426866 B1 EP3426866 B1 EP 3426866B1
Authority
EP
European Patent Office
Prior art keywords
coupling
door lock
input element
contour
drive
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
EP17718554.3A
Other languages
German (de)
English (en)
Other versions
EP3426866A2 (fr
Inventor
Josef Hölzl
Günter Bruckbauer
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.)
Maco Technologie GmbH
Original Assignee
Maco Technologie GmbH
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 Maco Technologie GmbH filed Critical Maco Technologie GmbH
Priority to EP20162495.4A priority Critical patent/EP3686383B1/fr
Publication of EP3426866A2 publication Critical patent/EP3426866A2/fr
Application granted granted Critical
Publication of EP3426866B1 publication Critical patent/EP3426866B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B47/00—Operating or controlling locks or other fastening devices by electric or magnetic means
    • E05B47/06—Controlling mechanically-operated bolts by electro-magnetically-operated detents
    • E05B47/0611—Cylinder locks with electromagnetic control
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B47/00—Operating or controlling locks or other fastening devices by electric or magnetic means
    • E05B47/0001—Operating or controlling locks or other fastening devices by electric or magnetic means with electric actuators; Constructional features thereof
    • E05B47/0012—Operating or controlling locks or other fastening devices by electric or magnetic means with electric actuators; Constructional features thereof with rotary electromotors
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B17/00—Accessories in connection with locks
    • E05B17/04—Devices for coupling the turning cylinder of a single or a double cylinder lock with the bolt operating member
    • E05B17/047—Devices for coupling the turning cylinder of a single or a double cylinder lock with the bolt operating member with rotating output elements forming part of cylinder locks, e.g. locking cams of double cylinder locks
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B47/00—Operating or controlling locks or other fastening devices by electric or magnetic means
    • E05B47/0001—Operating or controlling locks or other fastening devices by electric or magnetic means with electric actuators; Constructional features thereof
    • E05B2047/0014—Constructional features of actuators or power transmissions therefor
    • E05B2047/0018—Details of actuator transmissions
    • E05B2047/0026—Clutches, couplings or braking arrangements
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B53/00—Operation or control of locks by mechanical transmissions, e.g. from a distance
    • E05B53/003—Operation or control of locks by mechanical transmissions, e.g. from a distance flexible

Definitions

  • the present invention relates to a door lock with a motor, in particular an electric motor, for motorized adjustment of a bolt and / or a latch of the door lock according to claim 1.
  • the adjustment in particular includes locking or unlocking and / or opening or closing the door lock.
  • the possibility of adjusting the bolt and / or the latch in a motorized manner can serve, for example, to improve comfort when operating the door lock.
  • an adjustment of the bolt or the latch can be triggered in this way without using a key or from a certain distance. There are basically no limits to the distance, so that remote control of the door lock is possible.
  • Another advantage results from the possibility of adjusting the bolt or the latch at defined times or according to other specifiable rules.
  • all different closing states of a door lock can be brought about in a motorized manner.
  • the motorization is only intended for a selection of the possible states and other states can only be set manually, for example.
  • the door lock is essentially similar to a conventional door lock and, in particular with regard to its dimensions and / or its interaction with other components, corresponds to current standards, for example with regard to the installation of the door lock in a door or the use of a locking cylinder with the door lock.
  • the bolt or the latch of the door lock are not only adjustable by motor, but this function is provided in addition to the usual manual adjustability. For safety reasons alone, it is important to ensure that the door lock can still be operated manually if the motorized drive fails.
  • a cylinder receptacle for a locking cylinder in particular for a locking cylinder of a known type, according to current standards such as a profile cylinder may be provided.
  • the lock cylinder is typically assigned one or more suitable keys with which the lock cylinder can be operated manually. An actuating torque exerted on the locking cylinder, usually a torque, can then be transmitted to the door lock.
  • the cylinder receptacle can have an input element which is designed to be driven by an output element of the locking cylinder in order to transmit an actuating torque to the door lock or ultimately to adjust the bolt and / or the latch of the door lock.
  • the output element can be, for example, a locking lug of the locking cylinder, which preferably projects radially to a cylinder axis and can be rotated about the cylinder axis.
  • the input element of the cylinder receptacle is to be regarded in particular as the element which is acted upon directly by the output element of the locking cylinder. The input element receives then, as the first element of the door lock, the actuating torque from the locking cylinder.
  • the locking cylinder could be replaced by a motor device which outputs a respective actuation torque. But then no conventional lock cylinders could be used with the door lock. In addition, manual actuation of the door lock using a key would generally no longer be possible. It is therefore advantageous to design the door lock itself in a motorized manner, that is to say in particular to provide a separate motor in the door lock that is independent of a respective lock cylinder.
  • a door lock according to the preamble of claim 1 is out DE 20 2004 020 588 U1 known.
  • a door lock with a freewheel gear in which gear wheels are connected via a spring arrangement arranged between them. which comprises a spring clip and two pins which are urged by the spring clip into a position in which they couple the two gears.
  • the pins are pushed out of this coupling position and the two gears can rotate relative to one another.
  • a door lock with a motor for a motorized adjustment of a bolt and / or a latch of the door lock and a freewheel gear via which a driving torque of the motor can be transmitted to the bolt and / or the latch
  • the freewheel gear having an input element , which is operatively coupled to the motor, and has an output element that is operatively coupled to the bolt and / or the latch
  • the freewheel transmission further comprises at least one coupling element that is effective between a coupling position in which it drives the input element and the output element couples with each other, and a free-wheeling position, in which it decouples the input element and the output element from one another in a drive-effective manner, is movable.
  • the position of the coupling element thus decides whether the input element and the output element of the freewheel gear for transmission of the drive torque are coupled to the drive effectively or not.
  • the coupling should take place as automatically as possible depending on whether the input element is currently being driven by the motor or not.
  • the input element has a drive contour which is designed to carry the coupling element when the input element is driven by the motor.
  • the drive contour is in particular formed by a special surface shaping of the input element in an area in which the input element can come into contact with the coupling element.
  • Carrying the coupling element through the drive contour of the input element advantageously leads to the coupling element also carrying out a drive movement of the input element.
  • This drive movement which is caused by the drive torque transmitted from the motor to the input element, is, for example, a rotary movement about an axis of rotation, so that in this case the coupling element, when it is carried along by the drive contour, is also moved about the axis of rotation .
  • the coupling element is preferably carried along by the drive contour of the input element, regardless of whether it is in the coupling position or in the freewheeling position, when the input element is driven by the motor. Motorized driving of the input element thus always leads to the coupling element being carried along. This fact can be used to put the coupling element into the coupling position at least when the input element is driven by the motor, so that a drive torque of the motor is transmitted from the input element to the output element through the freewheel gear.
  • the freewheel gear also has a guide element with a guide contour which is designed to urge the coupling element into the coupling position when it is carried along by the input element.
  • the guide element is in particular at least essentially static, i.e. stationary relative to the transmission, but a certain amount of play can be provided, as will be explained further below.
  • the guide contour can also be formed by a special surface shaping in an area in which the guide element can come into contact with the coupling element.
  • the guide element Since the guide element is static, the guide contour, unlike the drive contour, cannot itself drive or carry the coupling element to a movement. However, it can restrict the mobility of the coupling element, particularly in interaction with the drive contour that carries the coupling element.
  • the guide element can be arranged at least partially in the manner of a stop, a contact surface or a flank within a movement path along which the coupling element is actually carried in the freewheeling position, so that the coupling element meets the guide contour and is thereby pushed into the coupling position.
  • the coupling element is not actively driven or adjusted by the guide element, but is only guided passively by the guide contour deflecting the movement path of the coupling element carried by the drive contour of the input element.
  • a door lock designed in this way thus enables the drive torque output by the motor to always be transmitted through the freewheel gear and ultimately to the bolt and / or the latch of the door lock.
  • Additional components for transmitting the drive torque can be provided between the freewheel gear and the bolt or the latch, in particular a toothed belt and / or an input element of a cylinder receptacle for a locking cylinder, as described above.
  • the output element has an engagement contour, into which the coupling element engages in the coupling position.
  • the engagement contour can be formed by a surface shaping of the output element, which has one or more receptacles adapted to the coupling element.
  • the coupling element can be at least partially accommodated in a respective one of these receptacles when it moves or is moved from the freewheeling position into the coupling position.
  • the coupling element is carried along by the drive contour of the input element and is consequently pushed into the coupling position by the guide contour of the guide element, the coupling element consequently engages in the engagement contour of the output element.
  • the coupling element is carried along by the motor-driven input element, the output element is thus also driven. The drive-effective coupling of the input element to the output element via the coupling element then results directly from this.
  • the coupling element is preferably designed as a coupling pin.
  • the coupling element can, in particular, at least essentially have an elongated cylindrical shape.
  • the coupling element can cooperate, for example, in a first section of its longitudinal extent with the drive contour of the input element and the engagement contour of the output element, and in a second section of the longitudinal extent with the guide contour of the guide element.
  • the coupling element is biased into the freewheel position.
  • the freewheel position of the coupling element is defined, so to speak, as the basic state or normal state of the freewheel gear. Whenever there are no other forces that force the coupling element into the coupling position or hold it in the coupling position, the pretension can, if it is not already in the freewheeling position, move the coupling element into the freewheeling position. This takes place in particular when the motor does not output any drive torque to the input element of the freewheel gear.
  • the input element and the output element of the freewheel gearbox are at least essentially only coupled to one another via the coupling element when the motor drives the input element. Otherwise, the input element and the output element are or are decoupled from one another. Since the motor generally does not output any drive torque when the bolt or latch is in a defined position to be assumed, this ensures that the motor returns from the bolt or latch immediately after reaching the position to be assumed is decoupled, so that manual actuation of the bolt or the latch is immediately possible again.
  • the input element and the output element of the freewheel gear are rotatably mounted about a common axis of rotation.
  • the input element and the output element are thus aligned coaxially with one another.
  • the input element and the output element are preferably freely rotatable relative to one another about the axis of rotation as long as they are decoupled from one another. However, they can then be coupled to one another by the coupling element in such a way that they can only be rotated about the axis of rotation together, that is to say in particular at least essentially by the same amount and in the same direction.
  • the coupling element is designed as a coupling pin
  • the coupling element is furthermore preferably aligned with a longitudinal extent of the coupling pin parallel to the said axis of rotation and is in particular offset in parallel when there is a transition between the freewheeling position and the coupling position.
  • the coupling position and the freewheeling position of the coupling element are preferably defined by different radial distances of the coupling element from the axis of rotation. Since the radial spacing is then important for the differentiation of the positions, the respective position of the coupling element in the circumferential direction to the axis of rotation can be disregarded.
  • the coupling position of the coupling element can comprise several different positions of the coupling element, which differ with respect to their position in the circumferential direction, but all have the same radial distance from the axis of rotation (ie lie on a circular path).
  • the freewheeling position of the coupling element can comprise a plurality of different positions of the coupling element, all of which are the same, but are at a different radial distance from the axis of rotation in the coupling position (that is to say also lie on a circular path).
  • the coupling element can be carried by the input element both in the freewheeling position and in the coupling position if the input element is carried by the motor for rotation about the said axis of rotation. If the coupling element is then pushed into the coupling position by the guide contour of the guide element, this corresponds to a radial displacement of the coupling element, i.e. towards the axis of rotation towards or away from the axis of rotation, depending on whether the radial distance to the axis of rotation in the coupling position is smaller than in the freewheel position or vice versa.
  • the freewheel gear has a plurality of coupling elements which are arranged at least substantially along a circular path around the axis of rotation.
  • the coupling elements can in particular be regularly distributed along the circular path, so that successive coupling elements are each at the same distance from one another in the circumferential direction.
  • the coupling elements preferably maintain their orientation relative to one another at least substantially (in particular with regard to their distribution on a circular path about the axis of rotation), even if they are carried along by the input element about the axis of rotation and / or are displaced between the freewheeling position and the coupling position.
  • successive coupling elements are connected to one another along the circular path by a respective bow spring in such a way that the coupling elements are biased into the freewheeling position.
  • the loop springs can form a closed circle around the axis of rotation.
  • the bow springs can thus perform two functions in particular. On the one hand, they hold the coupling elements at least essentially in their relative arrangement to one another on the circular path. On the other hand, due to the spring elasticity of the bow springs, at least a certain change in the circular path, in particular with regard to its radius, is permitted, so that the coupling elements remain radially movable between the coupling position and the freewheel position, but are biased into the freewheel position.
  • the drive contour of the input element and the guide contour of the guide element and optionally also the engagement contour of the output element are rotationally symmetrical, in particular with respect to the axis of rotation.
  • the count of the rotational symmetry of the drive contour corresponds in particular to the number of coupling elements.
  • a rotationally symmetrical design of the guide contour and possibly also the engagement contour has the advantage that it does not so much for the pushing of a respective coupling element through the guide contour or the engagement of the respective coupling element in the engagement contour on the position of the coupling element in the circumferential direction about the axis of rotation the greater the number of the rotational symmetry, the less) arrives.
  • the drive contour revolves around the axis of rotation with a constant base radius and has at least one, preferably for each coupling element, a respective indentation with a radius deviating from the base radius in order to at least partially accommodate the coupling element in its freewheeling position.
  • the drive contour can in particular be formed by a surface which is aligned parallel to the axis of rotation and, since it rotates around the axis of rotation, is closed in a ring-like manner.
  • the drive contour does not consistently have the constant base radius. Rather, "basic radius" is to be understood in such a way that the drive contour is basically designed in such a way that it could theoretically be formed from a cylindrical outer surface with the basic radius, although deviations from this basic shape, in particular temporary increases or decreases, occur in one or more partial areas of the contour circumference Radius can be provided. Outside of such partial areas, however, the drive contour has the basic radius.
  • the base radius preferably corresponds to a minimum or a maximum radius of the drive contour.
  • a respective carry-in recess represents such a deviation from the base radius.
  • a respective carry-in recess can in particular correspond to an increase in the radius compared to the base radius.
  • a respective entraining recess can correspond to a reduction in the radius compared to the basic radius.
  • an entraining recess does not necessarily have a constant radius, but transitions to the base radius are preferably provided at the edges of the entraining recess.
  • the drive contour can thus allow a radial movement for a coupling element at least partially accommodated in the entraining recess, in particular between its coupling position and its freewheeling position. It is therefore particularly advantageous if a driving recess is formed in the drive contour for each coupling element of the freewheel gear.
  • a transition from the radius of the respective entraining recess to the base radius of the drive contour forms a flank which is designed to entrain the coupling element when the input element is driven by the motor. If the input element rotates as a result of the drive torque received by the motor, this can in particular result in such a transition rotating in the circumferential direction about the axis of rotation and therefore hitting the coupling element at least partially accommodated in the entraining recess. As a result, the coupling element can be acted upon in such a rotational direction that it is carried along by the input element of the freewheel gear when it rotates about the axis of rotation.
  • the guide contour in a manner comparable to the drive contour of the input element revolves around the axis of rotation with a constant basic radius and has at least one urging projection with a radius deviating from the basic radius, the coupling element having the urging projection in the coupling position, but not in the Freewheel position can happen in the direction of rotation.
  • the guide contour can be formed by a surface that is aligned parallel to the axis of rotation and closed like a ring.
  • the basic radius of the guide contour is not necessarily identical to the basic radius of the drive contour. Rather, it is preferred if the base radius of the guide contour at least substantially corresponds to the radius of a respective driving recess of the drive contour or deviates even more from the base radius of the drive contour.
  • the radial mobility of a coupling element accommodated in a respective driving recess is not further restricted by the guide contour, at least in areas in which no urging projection is provided.
  • the guide contour in contrast to the drive contour, does not have any recesses, but rather protrusions.
  • the number of push projections is preferably at least eight and / or is greater than the number of coupling elements, in particular a multiple thereof.
  • the radius at the highest point i.e. the radius of the urging projection which deviates the most from the basic radius.
  • a respective urging projection can, in particular, reduce the radius in the case of a guide contour oriented radially inwards, or in the case of a radially inward direction externally aligned guide contour in particular correspond to an increase in radius.
  • an urging projection of the guide contour can, so to speak, protrude into a driving recess of the drive contour (viewed in particular in the axial direction with respect to the axis of rotation, so that the drive contour and the guide contour appear superimposed).
  • the radial mobility of a coupling element accommodated in the entraining recess can advantageously be restricted, namely in particular to a radius corresponding to the coupling position.
  • a transition from the radius of the urging projection to the base radius of the guide contour preferably forms a flank which is designed to urge the coupling element into the coupling position when it is carried along by the input element.
  • a flank can thus, in particular, deflect the rotary movement of a coupling element, which is in the freewheeling position and is carried by the drive contour about the axis of rotation, to displace the coupling element into the coupling position. While the coupling element cannot pass the urging projection in the freewheeling position but hits the flank, it can then be guided past the urging projection in the coupling position.
  • a preload of the coupling element in the freewheel position and any frictional properties of the components of the freewheel transmission can be designed such that the coupling element remains in the coupling position after passing through an urging projection, as long as it is away from the drive contour is carried around the axis of rotation, ie as long as the motor transmits a drive torque to the input element.
  • the coupling element then advantageously only hits the flank of an urging projection at the beginning of a rotary movement and is thereby moved into the coupling position, whereupon it can then possibly pass through further urging projections without hindrance.
  • the coupling element is only put back into the freewheeling position by the pretensioning when the motor and thus the input element are stopped.
  • the motor is preferably stopped in such a way that, when the input element is at a standstill, no urging projection of the guide contour protrudes into a driving recess in the drive contour and all coupling elements can therefore be moved into the freewheeling position.
  • the guide element is supported with play, preferably pivotable about a pivot axis, in particular parallel to the axis of rotation, and biased into a basic position.
  • Said game preferably enables the guide contour to be displaced such that it no longer forces the coupling element into the coupling position.
  • this can mean that a respective urging projection can be displaced (against the pretension of the guide element) in such a way that it no longer prevents the coupling element from being moved into the freewheeling position or entrainment of the coupling element in the freewheeling position.
  • Such play can be particularly useful in cases where a coupling element is blocked from moving into the freewheeling position even though the motor does not drive the input element.
  • a coupling element is blocked from moving into the freewheeling position even though the motor does not drive the input element.
  • Such a case can occur, for example, when the engine stops unplanned, for example as a result of a malfunction, damage or wear, in particular if the engine is self-locking and is coupled to the input element in such a drive-effective manner that the input element is also blocked when the motor is at a standstill.
  • the drive contour of the input element and the guide contour of the guide element are aligned with each other during such a standstill in such a way that the coupling element is prevented from adopting the freewheel position, the output element of the freewheel gear mechanism and ultimately the bolt and / or the latch of the door lock could also be blocked, so that the door lock as a whole could no longer be operated.
  • the guide contour can, at least when there is sufficient force to overcome the preload, dodge, so that the blockage can be released.
  • Such action of force can in particular be brought about by manual actuation of the door lock, for example by turning a key or pressing a door handle.
  • the pretension of the guide element is designed such that the guide element is arranged at least approximately statically during normal operation, i.e. under forces such as occur regularly when the bolt or latch is adjusted by motorized means, and the function of urging the coupling element into the coupling position , if this is carried by the input element, can thus meet.
  • the force required for a significant displacement of the guide element therefore preferably exceeds the forces normally to be exerted when the door lock is operated manually.
  • the input element has a through opening, on the inner lateral surface of which the drive contour is formed
  • the guide element has a through opening, on the inner lateral surface of which the guide contour is formed, the coupling element at least partially within the through opening of the input element and at least is partially arranged within the through opening of the guide element.
  • the output element is at least partially arranged within the through opening of the input element.
  • the input element is designed as a gearwheel with external toothing, via which it receives the drive torque of the motor, and / or that the output element is designed as a gearwheel with external toothing, via which it outputs the drive torque of the motor .
  • Such toothing allows a simple drive-effective coupling with other components.
  • an external toothing of the input element can interact directly with an output element of the motor, for example in the manner of a worm gear with the input element of the freewheel gear as a worm wheel and the output element of the motor as a worm.
  • a toothed belt can roll on the external toothing of the output element of the freewheel gear, via which the toothed belt from the output element of the freewheel gear Output drive torque can be transmitted to an input element of a cylinder receptacle of the door lock, as described above.
  • the guide element comprises a first guide disk and a second guide disk, which are aligned parallel to one another and between which the input element is arranged, the guide contour being formed both on the first guide disk and on the second guide disk.
  • the part of the guide contour formed on the first guide disk and the part of the guide contour formed on the second guide disk are preferably aligned, in particular in the direction of the said axis of rotation.
  • the first guide disk and the second guide disk can be rigidly connected to one another.
  • a middle section of the coupling element can interact with the drive contour of the input element for the described pushing of the coupling element into the coupling position, and two opposite outer sections of the coupling element can interact with the guide contour of the guide disks.
  • This can prevent the input element and the guide element from exerting tilting moments on the coupling element, which could change its spatial orientation.
  • the arrangement contributes to the fact that the coupling element is displaced at least essentially exclusively in parallel between its free-wheeling position and its coupling position.
  • the door lock further comprises a cylinder receptacle for a locking cylinder which has an input element which is designed to be driven by an output element of the locking cylinder in order to adjust a bolt and / or a latch of the door lock, the motor, preferably via the freewheel gear and / or one Toothed belt, drive-operable with the input element of the cylinder receptacle is coupled or coupled to adjust the bolt and / or the latch regardless of whether a lock cylinder is received in the cylinder receptacle or not, via the input element of the cylinder receptacle.
  • the motor serves to be able to adjust the bolt and / or the latch in a motorized manner by means of the locking cylinder.
  • a motor is provided in the door lock, which is designed and arranged such that the bolt and / or the latch is motorized, i.e. is / are adjustable by means of the motor.
  • a motorized adjustment of the bolt or the latch is in particular independent of whether a locking cylinder is accommodated in the cylinder receptacle or not. If a locking cylinder is received in the cylinder receptacle, the bolt and / or the latch can / can thus advantageously be adjusted in two different ways, namely on the one hand by means of the locking cylinder and additionally or alternatively by means of the motor.
  • the motor is, in particular, designed independently and separately from the respective locking cylinder.
  • the bolt or latch is adjusted by the motor via the input element, that is to say that the motorized adjustment runs via the input element.
  • the input element is consequently located within the drive path, along which a drive torque of the motor is transmitted to the bolt or to the latch.
  • said second section that is to say that part of the drive path from the input element of the cylinder receptacle to the bolt or latch, can be designed as in a conventional door lock.
  • This not only has the advantage that this part of the door lock does not have to undergo any change compared to a conventional door lock. But in this way, the fact that this second section of the drive path from the input element to the bolt or to the latch is generally designed for comparatively low drive torques, as can typically be generated by hand using a key, is also advantageously used. Because the drive torque of the motor acts on the input element and is transmitted from there to the bolt or latch, the drive torque of the motor needs in order to be able to reliably adjust the bolt or latch, so that it is neither particularly large nor larger Forces to be translated.
  • the input element is, in particular, that element of the cylinder receptacle which is acted upon directly by the output element, for example a locking lug, of a locking cylinder accommodated in the cylinder receptacle when the locking cylinder is actuated.
  • the input element can also be designed in several parts, part of the input element being acted upon directly by the output element of the locking cylinder and the drive torque of the motor being transferred to another part. In this case, however, the parts of the input element are then rigidly coupled to one another or at least can be coupled in order to jointly form the input element of the cylinder receptacle.
  • locking cylinders are preferably to be used in such a door lock, the output element of which can move freely when the key is removed, in particular so-called free-running cylinders.
  • the drive-effective coupling of the motor to the input element of the cylinder receptacle can take place in various ways.
  • the coupling need not be permanent. Rather, it is sufficient if the motor can be coupled to the input element at least as required, that is to say whenever motorized adjustment is desired.
  • “connectable” does not mean a general general connectivity, but rather that the door lock is specifically designed so that such a coupling can take place if necessary.
  • the motor is coupled or can be coupled to the input element via a toothed belt in a drive-effective manner.
  • a toothed belt enables reliable drive-effective coupling even over comparatively long distances without taking up a lot of installation space.
  • the input element of the cylinder receptacle has a toothing on which the toothed belt rolls.
  • the toothed belt therefore acts directly on the input element.
  • the door lock comprises a device for detecting the circulating position of the toothed belt. Due to the drive-effective coupling of the toothed belt to the input element of the cylinder receptacle, a corresponding position of the input element and thus ultimately also a respective position of the bolt and / or the latch can be inferred from the circulating position of the toothed belt. This can be useful and important for controlling the motor.
  • a motor controller can be provided which receives the rotating position of the toothed belt from the device mentioned and takes it into account when driving the motor.
  • the motor in order to adjust the bolt or and / or the latch to a specific position, can be actuated in order to output a drive torque in the direction required until the determined rotational position of the toothed belt determines that the specific position is reached, whereupon the motor is stopped.
  • the device mentioned can have a gearwheel on which the toothed belt rolls.
  • the rotational position of the gear which can be detected, for example, as an electrical resistance or optically can then be output as a corresponding signal, from which the closed position of the toothed belt can then be deduced.
  • the gear is rotatably supported in both directions of rotation, it may be the case that it is not possible to differentiate between two rotational positions of the gear, which differ from one another by one or more full revolutions of the gear, since they lead to the same output signal.
  • Circumferential positions of the toothed belt can then only be clearly detected via a path corresponding to the circumference of the toothed wheel.
  • the toothed wheel would therefore have to have a sufficiently large circumference, which can be unfavorable in view of the limited installation space.
  • the device for detecting the rotational position of the toothed belt is therefore formed by an absolute rotary encoder with two toothed wheels, on which the toothed belt rolls and the number of teeth of which are relatively prime, preferably different from one another.
  • an absolute rotary encoder enables the rotational position of the gear wheel to be clearly detected over a long distance with comparatively small radii of the two gear wheels. Because due to the different number of teeth of the two gears, with one full rotation of the one gear the other gear has completed more or less than one full rotation, so that more rotation positions can be distinguished from the joint consideration of the rotational positions of both gears.
  • the two gearwheels when they are rotated from any starting rotational position, only then assume the starting rotational position again when they have been rotated by the smallest common multiple of their number of teeth. If the number of teeth is not uncommon, this corresponds to the product of two teeth numbers, so that the area of clearly detectable revolving positions is maximized.
  • the number of teeth differs exactly by one, they are always prime.
  • the radii of the two gearwheels hardly differ, so that a maximum range of revolving positions of the toothed belt can be clearly detected with two comparatively small gearwheels.
  • the number of teeth of the two gearwheels is selected such that their smallest common multiple is greater than or just corresponds to the number of teeth on the toothed belt, so that the circumferential position of the toothed belt can be clearly detected over its full length.
  • the motor can be coupled or coupled to the input element via a freewheeling drive.
  • the motor can be coupled in a drive-effective manner to the toothed belt mentioned via the freewheel gear.
  • the freewheel gear is then provided between the motor and the toothed belt.
  • the input element of the freewheel transmission which is coupled to the motor in an effective manner, can in particular be directly coupled to an output element of the motor.
  • the output element of the freewheel gear can be coupled to the input element of the cylinder receptacle in a drive-effective manner and in particular can be directly coupled to the toothed belt.
  • Direct coupling means in particular that the respective elements roll directly against one another.
  • the freewheel gear is designed to transmit a drive torque coming in at the input element of the freewheel gear through the freewheel gear to the output element of the freewheel gear, but not with a drive torque coming in at the output element of the freewheel gear To transfer input element of the freewheel gear. In the latter case, however, the transmission of the drive torque is not blocked. Rather, in the event of a drive torque arriving at the output element, the output element and the input element are decoupled in such a way that the output element can rotate freely without thereby driving the input element, which can therefore stand still. If, on the other hand, a drive torque is received at the input element, the input element and the output element are coupled to one another in such a way that the drive torque is transmitted to the output element so that it can be output there.
  • the coupling and / or the decoupling preferably take place independently of the direction, in particular the direction of rotation, of the drive torque.
  • the freewheel gear can thus prevent an actuation of the locking cylinder - or also of another element on the door lock intended for adjusting the bolt and / or the latch, such as a door handle - from being blocked by the motor at a standstill. Otherwise, this would be the case in particular with self-locking motors, such as with conventional electric motors.
  • the freewheel gear can be provided, which this function is passive, so to speak in particular automatically, depending on whether a drive torque is received at the input element.
  • FIG. 1 An embodiment of a door lock 11 according to the invention is shown.
  • the door lock 11 has a housing 13 and is designed to be inserted into the door leaf of a door.
  • the door lock 11 has a bolt 15 on the one hand and a latch 17 on the other, which are suitable for engaging in corresponding recesses in a striking plate in the door frame.
  • the door lock 11 has a square receptacle 19 for a door handle and a cylinder receptacle 21 for a locking cylinder, the cylinder receptacle 21 comprising an input element 23 which is designed to be driven by an output element of a locking cylinder received in the cylinder receptacle 21.
  • the input element 23 is designed such that it is rotated by a locking lug of the locking cylinder about a cylinder axis of a cylinder core of the locking cylinder when the locking cylinder is actuated, in particular by means of a key.
  • Both the bolt 15, which is movable between an unlocked, a single-locked and a double-locked state, and the latch 17, which are movable between a released and a closed state, are coupled to the input element 23 in a drive-effective manner via a gear arrangement 25, so that they can be adjusted between their respective positions in a manner known per se by, in particular, manual actuation of the locking cylinder.
  • the latch 17 can also be manually adjusted independently of the bolt 15 by means of the door handle.
  • the door lock 11 comprises an electric motor 27, which is coupled to the input element 23 of the cylinder receptacle 21 in a drive-effective manner.
  • the motor 27 is consequently also coupled to the bolt 15 and the latch 17 in a drive-effective manner via the input element 23.
  • the motor 27 can be controlled to adjust the bolt 15 or the latch 17 between their respective positions.
  • the control of the motor 27 can be current-limited, so that the motor 27 stops when the current required for a further output of a drive torque becomes too large, that is to say exceeds a predetermined limit value. In this way, the entire motor drive is protected from damage if an adjustment of the bolt 15 or the latch 17 should be blocked for any reason (for example if the door is not closed correctly, so that the door lock 11 and the striking plate are not opposite one another) or if the locking plate of the striking plate is blocked or insufficiently deep).
  • the motor 27 is coupled to the input element 23 of the cylinder receptacle 21 by means of a toothed belt 29 in a drive-effective manner.
  • the toothed belt 29 rolls directly on a toothing 31, which is provided on an outer surface of the input element 23 and almost completely surrounds the input element 23, in particular over an angular range of at least about 300 °, so that the input element 23 is gear-like.
  • guide surfaces, deflection rollers and a tensioning device can be provided in the door lock 11 in a generally known manner.
  • an absolute rotary encoder 33 is arranged on the toothed belt 29.
  • the absolute rotary encoder 33 comprises two gear wheels 35, 35 ', on which the toothed belt 29 rolls and the number of teeth of which differ from one another. The product of the two tooth numbers is greater than the number of teeth on the toothed belt 29. In this way, despite the small size of the two toothed wheels 35, 35 ', each rotating position of the toothed belt 29 can be clearly recorded, only limited by the basic resolution accuracy of the absolute rotary encoder 33 will.
  • a freewheel gear 37 is provided, which is designed to transmit a drive torque output by the motor 27 in the direction of the input element 23 of the cylinder receptacle 21 and thus ultimately to the bolt 15 or to the latch 17, but one conversely, drive torque transmitted from the input element 23 to the freewheel gear 37, not to be transmitted to the motor 27, but also not to be blocked. It is thereby achieved that the motor 27 can drive the input element 23 for a motorized adjustment of the bolt 15 or the latch 17, but that when the motor 27 is at a standstill, the motor 27 is not prevented from moving by the motor 27, but rather by the locking cylinder outgoing manual actuation remains movable.
  • the freewheel gear 37 has an input element 39, which is coupled to the motor 27 for effective driving, and an output element 41, which is operatively connected to the input element 23 of the cylinder receptacle 21 and above that with the Bolt 15 or the latch 17 is coupled.
  • the input element 39 is at least essentially designed as a gearwheel with external toothing 43 and, in the manner of a worm wheel, is in direct engagement with an output element 45, designed as a worm, of the motor 27 in order to receive a drive torque from the latter while the motor 27 is running.
  • the output element 41 of the freewheel gear 37 has, in the manner of a gear, an external toothing 47 on which the toothed belt 29 rolls. This results in a direct transmission of the drive torque from the motor 27 to the freewheel gear 37, from there to the toothed belt 29 and from there to the input element 23 of the cylinder receptacle 21. Since no further components are required, this entire motor drive is fundamentally particularly compact, the Toothed belt 29 at the same time enables the drive torque to be transmitted between the freewheel gear 37 and the cylinder receptacle 21 over a relatively large distance without taking up much space in the door lock 11 for this purpose.
  • the input element 39 and the output element 41 of the freewheel gear 37 are rotatably mounted about a common axis of rotation D and can be coupled for common rotation or decoupled for independent rotation.
  • the coupling advantageously takes place automatically when the input element 39 is driven by the motor 11. If, on the other hand, the output element 41 is driven in the opposite direction by the input element 23 of the cylinder receptacle 21, the input element 39 and the output element 41 are preferably decoupled from one another.
  • FIGS 2 to 6 An exemplary embodiment of a corresponding freewheel gear 37 is shown in FIGS 2 to 6 shown and is explained in more detail below with reference to these figures.
  • the input element 39 and the output element 41 of the freewheel gear 37 are arranged coaxially to one another and rotatably supported about the common axis of rotation D.
  • a stationary 2 to 6 Not shown) housing 13 arranged race 49 is provided, in which the input element 39 is rotatably held with an axial bearing portion 51.
  • a short bearing shaft 53 is likewise arranged in a fixed manner along the axis of rotation D in the housing 13, on which the output element 41 is mounted in the manner of an idler gear.
  • the input element 39 of the freewheel gear 37 has an axial through opening 55, on the inner lateral surface of which a drive contour 57 is formed.
  • An engagement contour 59 is formed axially adjacent to the external toothing 47 on an outer lateral surface of the output element 41 of the freewheel gear 37. Since both the input element 39 and the output element 41 are at least essentially rotationally symmetrical with respect to the axis of rotation D, the drive contour 57 and the engagement contour 59 are also rotationally symmetrical with respect to the axis of rotation D.
  • the output element 41 is arranged within the through opening 55 of the input element 39 in such a way that the drive contour 57 and the engagement contour 59 have the same axial position relative to the axis of rotation D and thus face each other in the radial direction. Since a maximum radius of the engagement contour 59 is smaller than a minimum radius of the drive contour 57, there is an intermediate space 61 extending in a ring around the axis of rotation D between the drive contour 57 and the engagement contour 59 (cf. in particular 5 and 6 ). In this intermediate space 61, two coupling elements 63 designed as coupling pins and aligned parallel to the axis of rotation D are accommodated.
  • the drive contour 57 has a respective entraining recess 65, which is characterized by a larger radius than the otherwise constant base radius of the drive contour 57.
  • the two entraining recesses 65 are provided diametrically to one another with respect to the axis of rotation D.
  • a coupling element 63 can in each case be at least partially received in a driving recess 65 of the drive contour 57.
  • the respective coupling element 63 is basically still radially movable between a coupling position, which in this respect corresponds to a minimum radial distance of the coupling element 63 from the axis of rotation D, and a free-wheeling position, which in this respect corresponds to a maximum radial distance of the coupling element 63 from the axis of rotation D.
  • the radial distance of the coupling element 63 from the axis of rotation D is sufficient for it not to engage in the engagement contour 59 of the output element 41, so that the output element 41 can be freely rotated about the axis of rotation D.
  • the coupling element 63 engages in the engagement contour 59.
  • the coupling element 63 is received in a valley between two teeth of the engagement contour 59.
  • the engagement of the coupling element 63 in the engagement contour 59 leads to the coupling element 63 positively driving the output element 41 of the freewheel gear 37 to rotate about the axis of rotation D when the coupling element 63 is itself rotated about the axis of rotation D.
  • the input element 39 and the output element 41 of the freewheel gear 37 can be coupled to one another in a drive-effective manner.
  • the coupling elements 63 must first be placed in the coupling position and then also held in it, since they are otherwise attached the teeth of the engagement contour 59 would slide past, especially since they are biased by two bow springs 67 into the freewheeling position, that is to say in the direction of a larger radial distance from the axis of rotation D.
  • the bow springs 67 are bent in a semicircle and each connect corresponding axial ends of the coupling elements 63 to one another in such a way that the bow springs 67 completely rotate around the axis of rotation D.
  • the coupling elements 63 are moved into the coupling position in the interaction of the drive contour 57 with a guide contour 71 formed on an at least essentially static guide element 69 of the freewheel gear 37.
  • the guide element 69 is designed as two guide disks 73, 73 ', which are at least essentially identical in shape and are arranged parallel to one another and perpendicular to the axis of rotation D, the input element 39 of the freewheel gear 37 being arranged between the guide disks 73, 73 '.
  • the 5 and 6 differ only in that the in Fig. 6 shown upper guide washer 73 in Fig. 5 is not shown.
  • the guide element 69 has a through opening 75, on the inner lateral surface of which the guide contour 71 is formed.
  • parts of the guide contour 71 which are identical to one another are formed on the two guide disks 73, 73 'and are aligned with one another.
  • Both the output element 41 of the freewheel gear 37 and the coupling elements 63 are located at least partially within the through opening 75 of the guide element 69.
  • the coupling elements 63 can in this way radially outward at the same time both with the drive contour 57 of the input element 39 and with the Interacting guide contour 71 of the guide element 69.
  • the guide contour 71 regularly has a total of eight pushing projections 77 distributed along its circumference, in which the radius of the guide contour 71 is opposite a basic radius of the guide contour 71 is reduced.
  • the urging projections 77 consequently project radially in the direction of the axis of rotation D.
  • the distance of a respective urging projection 77 from the axis of rotation D is so small that a coupling element 63 can only pass an urging projection 77 in the circumferential direction to the axis of rotation D if it is in the coupling position and consequently engages in the engagement contour 59 of the output element 41.
  • the basic radius of the guide contour 71 corresponds approximately to the radius of an entraining recess 65, so that a coupling element 63 can assume the freewheel position outside of an urging projection 77.
  • transitions to the respective base radius at the edges of the entraining recesses 65 and the urging projections 77 form flanks which are suitable for interacting with a respective coupling element 63 during a rotary movement.
  • a respective coupling element 63 is carried in the direction of rotation by the corresponding flank of the respective driving recess 65 into which it is received.
  • the coupling element 63 Since the guide element 69, unlike the input element 39, is not rotatably supported about the axis of rotation D, the coupling element 63, which is initially in the freewheeling position due to the pretensioning by the bow springs 67, strikes the corresponding flank of the next urging projection 77 of the guide contour in the direction of rotation 71. The fixed flank of the urging projection 77 then pushes the coupling element 63 into the coupling position, in which it can pass through the urging projection 77, but necessarily engages in the engagement contour 59 of the output element 41 of the freewheel gear 37. In this way, when the input element 39 is driven, its drive-effective coupling to the output element 41 takes place automatically.
  • the coupling element 63 After the coupling element 63 has passed an urging projection 77, it preferably remains in the, in particular due to friction effects Coupling position as long as the input element 39 is driven, and thus further pushing projections 77 can pass through. Basically, however, it can also be the case that the coupling element 63 is moved back into the freewheeling position after each passing protrusion 77 due to the pretension by the bow springs 67 and is pushed back into the coupling position by the next urging protrusion 77 upon further rotation.
  • the freewheel position defines a kind of basic state of the freewheel gear 37, in which the input element 39 and the output element 41 are decoupled from one another in a drive-effective manner. If a drive torque is transmitted in this state, for example from the input element 23 of the cylinder receptacle 21 via the toothed belt 29, to the output element 41 of the freewheel gear 37, the output element 41 rotates without the coupling elements 63 being thereby put into the coupling position. Therefore, the drive torque is not transmitted from the output element 41 to the input element 39. This prevents an actuation of the input element 23 of the cylinder receptacle 21 from being blocked when the engine 27 is at a standstill.
  • the guide element 69 is pivotably mounted about a pivot axis S oriented parallel to the axis of rotation D, whereby it is held in a basic orientation by a return spring 79 , in which the guide contour 71 is preferably arranged rotationally symmetrical to the axis of rotation D.
  • the pivotable mounting allows a certain amount of play of the guide element 69 against the pretension of the return spring 79. It is thus possible, by applying sufficient force, to force an urging projection 77 of the guide contour 71 far enough that the respective coupling element 63 moves past the urging projection 77 and in the release position can be moved.
  • the force acting on the coupling element 63 originates in particular from the output element 41 and results, for example, from a vigorous manual actuation of a key in a locking cylinder accommodated in the cylinder receptacle 21. In this way, the door lock 11 is particularly protected against being able to be operated manually if the motorized drive fails.

Landscapes

  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Lock And Its Accessories (AREA)

Claims (15)

  1. Serrure de porte (11) comportant
    - un moteur (27) pour déplacer par voie motrice un verrou (15) et/ou un pêne (17) de la serrure de porte (11), et
    - un mécanisme à roue libre (37) par lequel un couple d'entraînement du moteur (27) peut être transmis au verrou (15) et/ou au pêne (17), dans laquelle
    le mécanisme à roue libre (37) comprend un élément d'entrée (39) couplé en entraînement au moteur (27) et un élément de sortie (41) couplé en entraînement au verrou (15) et/ou au pêne (17),
    le mécanisme à roue libre (37) comprend en outre au moins un élément de couplage (63) mobile entre une position de couplage dans laquelle il couple en entraînement l'élément d'entrée (39) et l'élément de sortie (41) l'un à l'autre, et une position de roue libre dans laquelle il découple en entraînement l'élément d'entrée (39) et l'élément de sortie (41) l'un de l'autre, l'élément d'entrée (39) présente un contour d'entraînement (57) réalisé pour emmener l'élément de couplage (63) lorsque l'élément d'entrée (39) est entraîné par le moteur (27),
    caractérisée en ce que
    le mécanisme à roue libre (37) comprend en outre un élément de guidage (69) ayant un contour de guidage (71) réalisé pour pousser l'élément de couplage (63) jusque dans la position de couplage lorsqu'il est emmené par l'élément d'entrée (39).
  2. Serrure de porte selon la revendication 1,
    dans laquelle
    l'élément de sortie (41) présente un contour d'engagement (59) dans lequel s'engage l'élément de couplage (63) en position de couplage.
  3. Serrure de porte selon la revendication 1 ou 2,
    dans laquelle
    l'élément de couplage (63) est réalisé sous forme de tige de couplage et/ou est précontraint vers la position de roue libre.
  4. Serrure de porte selon l'une au moins des revendications précédentes,
    dans laquelle
    l'élément d'entrée (39) et l'élément de sortie (41) du mécanisme à roue libre (37) sont montés de façon mobile en rotation autour d'un axe de rotation commun (D),
    et, de préférence, la position de couplage et la position de roue libre de l'élément de couplage (63) sont définies par différentes distances radiales de l'élément de couplage (63) par rapport à l'axe de rotation (D).
  5. Serrure de porte selon la revendication 4,
    dans laquelle
    le mécanisme à roue libre (37) comprend plusieurs, de préférence deux éléments de couplage (63) qui sont disposés au moins sensiblement le long d'une trajectoire circulaire autour de l'axe de rotation (D),
    et, de préférence, des éléments de couplage successifs (63) sont reliés l'un à l'autre par un ressort en étrier respectif (67) le long de la trajectoire circulaire de telle sorte que les éléments de couplage (63) sont précontraints vers la position de roue libre.
  6. Serrure de porte selon la revendication 4 ou 5,
    dans laquelle
    le contour d'entraînement (57) de l'élément d'entrée (39) et le contour de guidage (71) de l'élément de guidage (69) sont réalisés à symétrie de révolution, en particulier par rapport à l'axe de rotation (D).
  7. Serrure de porte selon l'une au moins des revendications 4 à 6,
    dans laquelle
    le contour d'entraînement (57) tourne avec un rayon de base constant autour de l'axe de rotation (D) et présente au moins un renfoncement entraîneur (65), de préférence un renfoncement entraîneur respectif pour chaque élément de couplage (63), dont le rayon diffère du rayon de base, pour recevoir dans celui-ci au moins partiellement l'élément de couplage (63) dans sa position de roue libre,
    et, de préférence, une transition du rayon du renfoncement entraîneur (65) vers le rayon de base du contour d'entraînement (57) forme un flanc qui est réalisé pour emmener l'élément de couplage (63) lorsque l'élément d'entrée (39) est entraîné par le moteur (27).
  8. Serrure de porte selon l'une au moins des revendications 4 à 7,
    dans laquelle
    le contour d'entraînement (57) tourne avec un rayon de base constant autour de l'axe de rotation (D) et présente au moins une saillie de poussée (77) dont le rayon diffère du rayon de base, l'élément de couplage (63) pouvant passer en direction de rotation devant la saillie de poussée (77) dans la position de couplage, mais non pas dans la position de roue libre, et, de préférence, une transition du rayon de la saillie de poussée (77) vers le rayon de base du contour de guidage (71) forme un flanc qui est réalisé pour pousser l'élément de couplage (63) jusque dans la position de couplage lorsqu'il est emmené par l'élément d'entrée (39).
  9. Serrure de porte selon la revendication 8,
    dans laquelle
    l'élément de guidage (69) est monté avec jeu de préférence autour d'un axe de basculement (S) en particulier parallèle à l'axe de rotation (D) et est précontraint vers une position de base.
  10. Serrure de porte selon l'une au moins des revendications 4 à 9,
    dans laquelle
    l'élément d'entrée (39) présente une ouverture traversante (55), sur la surface enveloppe intérieure de laquelle est réalisé le contour d'entraînement (57), et
    l'élément de guidage (69) présente une ouverture traversante (75), sur la surface enveloppe intérieure de laquelle est réalisé le contour de guidage (71), et
    l'élément de couplage (63) est disposé au moins partiellement à l'intérieur de l'ouverture traversante (55) de l'élément d'entrée (39) et au moins partiellement à l'intérieur de l'ouverture traversante (75) de l'élément de guidage (69),
    et, de préférence, l'élément de sortie (41) est disposé au moins partiellement à l'intérieur de l'ouverture traversante (55) de l'élément d'entrée (38).
  11. Serrure de porte selon l'une au moins des revendications précédentes, dans laquelle
    l'élément de guidage (69) comprend une première rondelle de guidage (73) et une seconde rondelle de guidage (73') qui sont orientées parallèlement l'une à l'autre et entre lesquelles est disposé l'élément d'entrée (39), le contour de guidage (71) étant réalisé aussi bien sur la première rondelle de guidage (73) que sur la seconde rondelle de guidage (73').
  12. Serrure de porte selon l'une au moins des revendications précédentes, dans laquelle
    la serrure de porte (11) comprend en outre un logement à cylindre (21) pour un cylindre de fermeture, qui présente un élément d'entrée (23) réalisé pour être entraîné par un élément de sortie du cylindre de fermeture pour déplacer un verrou (15) et/ou un pêne (17) de la serrure de porte (11),
    et le moteur (27) est couplé ou peut être couplé en entraînement à l'élément d'entrée (23) du logement à cylindre (21) pour déplacer par voie motrice le verrou (15) et/ou le pêne (17) par l'intermédiaire de l'élément d'entrée (23) du logement à cylindre (21), indépendamment de savoir si un cylindre de fermeture est reçu ou non dans le logement à cylindre (21).
  13. Serrure de porte selon la revendication 12,
    dans laquelle
    le moteur (27) est couplé ou peut être couplé en entraînement à l'élément d'entrée (23) du logement à cylindre (21) par une courroie dentée (29).
  14. Serrure de porte selon la revendication 13,
    dans laquelle
    l'élément d'entrée (23) du logement à cylindre (21) présente une denture (31) sur laquelle s'engage la courroie dentée (29).
  15. Serrure de porte selon la revendication 13 ou 14,
    comportant un dispositif (33) pour détecter la position de rotation de la courroie dentée (29), qui est formé de préférence par un codeur absolu (33) à deux roues dentées (35, 35') sur lesquelles s'engage la courroie dentée (29) et dont les nombres de dents sont premiers entre eux, de préférence différents de un l'un de l'autre.
EP17718554.3A 2016-04-26 2017-04-24 Serrure de porte avec moteur Active EP3426866B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20162495.4A EP3686383B1 (fr) 2016-04-26 2017-04-24 Serrure de porte avec moteur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016107717.8A DE102016107717A1 (de) 2016-04-26 2016-04-26 Türschloss
PCT/EP2017/059671 WO2017186646A2 (fr) 2016-04-26 2017-04-24 Serrure de porte

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP20162495.4A Division EP3686383B1 (fr) 2016-04-26 2017-04-24 Serrure de porte avec moteur
EP20162495.4A Division-Into EP3686383B1 (fr) 2016-04-26 2017-04-24 Serrure de porte avec moteur

Publications (2)

Publication Number Publication Date
EP3426866A2 EP3426866A2 (fr) 2019-01-16
EP3426866B1 true EP3426866B1 (fr) 2020-06-03

Family

ID=58579194

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20162495.4A Active EP3686383B1 (fr) 2016-04-26 2017-04-24 Serrure de porte avec moteur
EP17718554.3A Active EP3426866B1 (fr) 2016-04-26 2017-04-24 Serrure de porte avec moteur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP20162495.4A Active EP3686383B1 (fr) 2016-04-26 2017-04-24 Serrure de porte avec moteur

Country Status (4)

Country Link
EP (2) EP3686383B1 (fr)
CN (1) CN109477345B (fr)
DE (1) DE102016107717A1 (fr)
WO (1) WO2017186646A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201807748D0 (en) * 2018-05-13 2018-06-27 Laporta Giovanni A cylinder lock
US11359418B2 (en) 2018-07-19 2022-06-14 Brose Schliesssysteme Gmbh & Co. Kg Motor vehicle lock
US11619078B2 (en) * 2018-07-19 2023-04-04 Brose Schliesssysteme Gmbh & Co. Kommanditgesellschaft Motor vehicle lock

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3620799A1 (de) * 1985-08-12 1987-02-19 Bauer Kaba Ag Multifunktions-einsteckschloss
DE3606531A1 (de) * 1986-02-28 1987-09-03 Fliether Karl Gmbh & Co Schliesszylinder mit antrieb
DE19757192A1 (de) 1997-12-22 1999-06-24 Wilka Schliestechnik Gmbh Mit Schließzylinder ausgerüsteter, einen Antriebsmotor aufweisender Verschluß
US6354121B1 (en) * 2000-07-21 2002-03-12 Harrow Products, Inc. Mortise lockset with internal clutch
DE10210945A1 (de) 2002-03-13 2003-09-25 Winkhaus Fa August Verriegelungseinrichtung für eine Tür
DE10225649B4 (de) * 2002-06-10 2005-10-06 Sancak, Mehmet Ferngesteuert freigebbarer Schließzylinder
CN2697237Y (zh) * 2004-01-19 2005-05-04 陈海平 带有机械钥匙锁头的电动门锁
CN2707908Y (zh) * 2004-04-21 2005-07-06 李勇 遥控自动防盗报警门锁
DE202004020588U1 (de) * 2004-04-30 2005-08-25 Elv Elektronik Ag Schlüsselbetätigungsvorrichtung
CN2871746Y (zh) * 2006-03-29 2007-02-21 陈海平 带磁性离合装置的机电锁
DE202007006589U1 (de) 2007-05-08 2008-09-18 Mayer & Co. Motorschloss mit Mehrpunktverriegelung
NL2001321C2 (nl) 2008-02-27 2009-08-31 Loxx B V Op afstand bedienbare module voor cilinderslot.
CN103184812B (zh) * 2011-12-29 2015-07-08 台湾福兴工业股份有限公司 可换向把手装置
CN104863420B (zh) 2015-05-25 2020-11-03 刘申川 一种电动与手动两用开闭锁器及安全智能锁

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102016107717A1 (de) 2017-10-26
CN109477345A (zh) 2019-03-15
WO2017186646A3 (fr) 2018-01-25
EP3686383A1 (fr) 2020-07-29
EP3686383B1 (fr) 2022-01-19
EP3426866A2 (fr) 2019-01-16
CN109477345B (zh) 2020-10-27
WO2017186646A2 (fr) 2017-11-02

Similar Documents

Publication Publication Date Title
EP2920020B1 (fr) Dispositif de verrouillage permettant de verrouiller des connecteurs électriques mâles
DE102007044088B9 (de) Binär codierter Schlüssel und manipulationssicheres Schloss
EP0755476B1 (fr) Serrure permettant notamment d'executer des fonctions de verrouillage sur des vehicules automobiles
EP2715188B1 (fr) entraînement à vis
DE102015112859B3 (de) Türdrücker und Antriebsträger
EP0981696B1 (fr) Transmission a roue dentee excentrique
EP3426866B1 (fr) Serrure de porte avec moteur
EP2107187B1 (fr) Ferrure pour fenêtres ou portes
EP0064763B1 (fr) Commande, en particulier commande de déplacement dans un véhicule à moteur
EP1144219B1 (fr) Dispositif de reglage permettant notamment de regler un siege de vehicule
WO2020001778A1 (fr) Agencement d'actionneur et entraînement électrique comprenant un tel agencement d'actionneur
DE29603652U1 (de) Beschlag für ein Schloß
DE3833758A1 (de) Beschlag mit einer handhabe zur betaetigung der schlossnuss eines in eine tuer od. dgl. eingesetzten schlosses
EP1117558A1 (fr) Mecanisme de blocage manoeuvrable
DE60009812T2 (de) Türschlossvorrichtung mit abnehmbarem Betätigungsgriff
DE19959833C1 (de) Schließvorrichtung für insbesondere an Fahrzeugen vollziehbare Schließfunktionen
EP2248958B1 (fr) Fenêtre coulissante de toit
EP3527755B1 (fr) Boîte de vitesses pour un agencement de ferrure d'une fenêtre, d'une porte ou analogue
DE102010030018B4 (de) Drehbeschlag mit integrierter Bremsvorrichtung
EP2738325B1 (fr) Cylindre anti-panique
EP3620598B1 (fr) Dispositif de couplage pour une ferrure de porte, système de ferrure de porte et procédé de couplage ou de découplage d'un dispositif de couplage
EP4086414B1 (fr) Agencement de cylindre de fermeture pourvu d'accouplement à poignée
DE102014106110B4 (de) Kupplungsvorrichtung
DE102009009259B4 (de) Zuhaltung für ein Bauteil zum Verschließen einer Öffnung
EP1268960B1 (fr) Dispositif de fermeture a cliquet anti-surcharge pour vehicules

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20181008

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20191106

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1277175

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200615

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502017005561

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200904

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200903

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200903

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201006

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201003

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502017005561

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

26N No opposition filed

Effective date: 20210304

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210424

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201003

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20170424

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230426

Year of fee payment: 7

Ref country code: FR

Payment date: 20230424

Year of fee payment: 7

Ref country code: DE

Payment date: 20230420

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20230420

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20230419

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200603