EP2738325B1 - Cylindre anti-panique - Google Patents

Cylindre anti-panique Download PDF

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Publication number
EP2738325B1
EP2738325B1 EP12195035.6A EP12195035A EP2738325B1 EP 2738325 B1 EP2738325 B1 EP 2738325B1 EP 12195035 A EP12195035 A EP 12195035A EP 2738325 B1 EP2738325 B1 EP 2738325B1
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EP
European Patent Office
Prior art keywords
gearwheel
cylinder
larger
locking cylinder
smaller
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
EP12195035.6A
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German (de)
English (en)
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EP2738325A1 (fr
Inventor
Herbert Meyerle
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.)
SimonsVoss Technologies GmbH
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SimonsVoss Technologies GmbH
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Publication date
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Priority to EP12195035.6A priority Critical patent/EP2738325B1/fr
Publication of EP2738325A1 publication Critical patent/EP2738325A1/fr
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Publication of EP2738325B1 publication Critical patent/EP2738325B1/fr
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Classifications

    • 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
    • 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
    • E05B9/00—Lock casings or latch-mechanism casings ; Fastening locks or fasteners or parts thereof to the wing
    • E05B9/04—Casings of cylinder locks
    • E05B2009/046—Cylinder locks operated by knobs or handles
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B9/00—Lock casings or latch-mechanism casings ; Fastening locks or fasteners or parts thereof to the wing
    • E05B9/04—Casings of cylinder locks
    • E05B2009/047—Means for returning cylinder locks to their neutral position

Definitions

  • the invention relates to an automatic return device for a cam of a lock cylinder, and a lock cylinder equipped therewith, preferably for use in anti-panic locks.
  • An anti-panic lock sometimes called a panic lock, is a lock that can be opened at any time, whether it is locked or not, from the inside by pressing the lever handle or a special crossbar.
  • This antipanic function e.g. in case of fire the possibility of escape through the emergency exit doors guaranteed.
  • the cam of the lock cylinder inserted in the lock is in a neutral position or rest position, otherwise he can block the pusher, so that the Lock does not open.
  • the cam of the lock cylinder must be in a lower position, as it could otherwise hinder the (anti) panic function of the lock.
  • only very specific positions or special angle ranges are permitted as rest position to ensure anti-panic function.
  • a lock cylinder which has a cam.
  • a core is offset from the axis.
  • a ball bearing is provided on the eccentric core.
  • a spring is further arranged radially to the ball bearing, which exerts a corresponding radial compressive force on the ball bearing. This causes the shaft and the associated locking bit to be automatically returned to a rest position after each turning operation in which it locks no blocking of a handle operation and thus the Anitpanikfunktion comes.
  • this reset system has the disadvantage that it requires a relatively large amount of space to dispose the eccentric core, the ball bearing and the spring. For this reason, it is also not suitable for every type of lock cylinder, since it can not be integrated without additional significant structural measures in such a rule.
  • DE 10 2008 056 627 B3 discloses a return mechanism biasing a lock cylinder pivotable lock key to preclude a predetermined angular range for a home position rest position, the reset mechanism comprising: at least one return member providing the force required for the return mechanism, a first gear having the lock bit rotatably connected, a second gear which can be engaged with the first gear, so that a force acting on the second gear by the return member is transmitted to the first gear, wherein the first gear and the second gear have the same number of teeth.
  • the object of the invention is therefore to provide an alternative automatic return device, which reliably moves the cam of a lock cylinder in a predetermined range and which can be easily integrated into a lock cylinder, in particular in a lock cylinder, which is suitable to be used in an anti-panic lock.
  • the invention relates to an automatic return device, preferably for a lock cylinder in a special lock / mortise lock or a special lock case with an anti-panic function (anti-panic lock) can be used.
  • the invention relates to an anti-panic cylinder or an anti-panic lock cylinder.
  • a mortise lock is a locking device in which a lock cylinder is used as a drive for the actual lock device.
  • a mechanical lock cylinder is the part of the lock which can be actuated by means of a mechanical key, and essentially consists essentially of a housing and a rotatable cylinder core.
  • lock cylinders such as profile cylinders (eg standard Euro profile cylinders according to DIN 18252 / EN1303), Round cylinders (eg Swiss Round, Scandinavian Round), oval cylinders (eg Scandinavian Oval, British Oval) and much more.
  • profile cylinders eg standard Euro profile cylinders according to DIN 18252 / EN1303
  • Round cylinders eg Swiss Round, Scandinavian Round
  • oval cylinders eg Scandinavian Oval, British Oval
  • the lock cylinder according to the invention has a locking bar rotatable with respect to its longitudinal axis, with which the bolt of the lock can be actuated.
  • the lock cylinder according to the invention has a return mechanism that biases the cam to preclude a predetermined angular range for the rest position of the Sch Camillbarts or to allow a certain angular range for the rest position.
  • the reset mechanism according to the invention has the advantage that a return member, which provides the required force for the return mechanism, can be accommodated outside the core region of the lock cylinder without significantly cutting the diameter of the core.
  • a large restoring element for example a large spring element, and thus a high degree of effectiveness is made possible without impairing the basic functionality determined by the core.
  • the return mechanism according to the invention has the advantage that the return mechanism exclusively uses the space of the lock cylinder itself, whereby compatibility with conventional, preferably standardized, locks can be ensured.
  • the return mechanism includes at least one return member that provides the required force for the return mechanism.
  • the return mechanism comprises at least a first larger gear which is rotatably connected to the lock bit and a second smaller gear the with the first larger gear engages or can come, so that a on the second smaller gear by the return member engaging force can be transmitted from the smaller gear to the first larger gear.
  • the relative terms “smaller” and “larger” gear refer to each other, making it clear that the larger gear is larger than the smaller gear.
  • size should refer to the diameter or radius of the gears, preferably the corresponding Wälznikischen dur. Although the two gears are different in size, the two gears should according to the invention have the same number of teeth.
  • the smaller gear is a wheel that has evenly distributed over the entire circumference of the wheel teeth, whereas the larger gear over an angular range of less than 360 ° (dentate angle range) , preferably less than 300 ° evenly distributed the same number of teeth.
  • the larger gear wheel has no teeth over an angular range of> 30 °, but preferably less than 180 °, which will be referred to below as "tooth-free region.”
  • the larger gear has at least one "toothed angular region” and at least one "tooth-free area”. More preferably, the larger gear has exactly one "toothed angle range” and exactly one "tooth-free area", wherein the sum of these two angular ranges gives 360 °.
  • a transmission between two rotations of the two gears is meant, i. when the teeth are engaged, they engage positively, and thus slip-free into each other.
  • a condition may occur in which the two gears are not engaged, i. There is a slip over the tooth-free area.
  • the first larger gear has no teeth over an angular range of 30-90 °.
  • the smaller gear and / or the larger gear is formed as a spur gear.
  • the larger and / or the smaller gear than External gear or internal gear are formed.
  • the toothing can also be straight (paraxial), oblique (helical toothing) or beveled (arrow toothing).
  • the invention is not limited to this type of gears and configurations in the form of bevel gear, Kegelplanrad, crown wheel and spindle wheel, etc. are also conceivable.
  • the lock cylinder according to the invention is designed as a profile cylinder (PZ cylinder).
  • the cylinder core of the profile cylinder is preferably rotatably mounted and preferably at least a portion of the cylinder core via a clutch with the lock bit rotatably coupled.
  • the lock cylinder is an electronic knob cylinder having one or two knobs.
  • a coupling mechanism between the knob and the lock bit is preferably provided which, depending on an authentication, couples the knob to the lock bit or decouples it or leaves it in the decoupled state.
  • both knobs can be coupled to the lock bit temporarily, for unlocking or closing, or only one of the two knobs, wherein the other knob is then preferably non-rotatably or permanently fixedly coupled to the lock bit.
  • the first larger gear is arranged in the lock cylinder, that it is rotatable about the longitudinal axis of the lock cylinder.
  • the axis of rotation of the first larger gear is preferably parallel to the longitudinal axis of the lock cylinder, preferably through the center axis of the cylinder core.
  • the lock cylinder according to the invention in particular in the form of a profile cylinder, has a cylindrical portion (cylinder core) and a radially projecting, preferably U-shaped, section thereof. These two sections are often referred to as cylindrical bearing section and flange section.
  • the first larger gear is preferably arranged in the cylindrical portion of the profile cylinder and the second smaller gear is arranged in the protruding portion of the profile cylinder.
  • the ratio of the diameter of the first larger gear to the diameter of the second smaller gear is in the range from 17/8 - 15/10, preferably at about 17/10.
  • the ratio of the "pitch circle diameter" of the two gears is in the range of 17/8 - 15/10.
  • the distance along the pitch circle diameter at the larger gear in the toothed area is equal to or substantially equal to the circumference of the smaller gear along the pitch circle diameter.
  • a profile cylinder according to DIN 18252 has an outer diameter of 17 mm in the cylindrical section and the width of the radially projecting section is 10 mm.
  • the return mechanism according to the invention has at least one return member, which has at least one spring element, which is preferably arranged in a profile cylinder in the protruding portion.
  • the spring element is not limited to a specific type and can be configured in principle as a torsion spring, spring or tension spring.
  • Non-limiting examples of possible spring elements are compression spring, tension spring, leaf spring, helical compression spring, helical tension spring, tortuous torsion spring, torsion spring, straight torsion spring, spiral spring, diaphragm spring, leaf spring, disc spring, elastomer spring, Evolutfeder, ring spring and coil spring.
  • the spring element is not limited to a particular material, but preferably made of spring steel or a copper-beryllium alloy.
  • the return member or the spring element engages at an eccentric position on the smaller gear, whereby the return member biases the smaller gear in a predefined position.
  • the restoring member should act on this eccentric position.
  • a person skilled in the art could be present on the smaller gear a projecting eccentric pin on which a train or compression spring attacks.
  • a recess for example, an eccentric bore to be formed in the smaller gear, in which a rod is used on the then the spring element transmits the restoring force.
  • FIG. 1 shows a first embodiment of the invention.
  • an electronic double-knob cylinder with the two knobs 3 and 4, which are attached to the two ends of the longitudinal axis A of the lock cylinder.
  • the lock cylinder is a profile cylinder with a round cylindrical core portion 1 and a radially projecting U-shaped portion 5.
  • the knob 3 should be an inner knob, which is preferably permanently rotatably coupled to the cam 2 , so that when the lock cylinder inserted in a lock the cam 2 can always be rotated via the knob 3.
  • the inner knob 3 contains important electronic Parts used to authenticate a user.
  • the knob 4 is used as an outer knob and is detachably mounted in this illustrated embodiment on the cylinder core 6, wherein the cylinder core is preferably rotatably mounted in the cylindrical portion 1 of the lock cylinder.
  • the removable outer knob 4 allows easy insertion of the lock cylinder in a lock case.
  • a coupling or a coupling mechanism between the outer knob 4 and the cam 2 preferably provided in the rotatable cylinder core portion 6 between the cam 2 and outer knob 4, so that rotation of the outer knob 4 in a rotation of the Schschschbarts 2 takes place only in the coupled state, the again depends on a successful authentication.
  • a signal is preferably transmitted through the cylinder core, preferably through the partially cylindrical or ring-shaped cam 2 as an electronic signal to an actuator in the coupling element, so that a coupling of the outer knob. 4 can be done with the cam 2.
  • the reset mechanism In order to bias the lock bit 2 into a rest position or a rest area, the reset mechanism according to the invention is provided which has a (first) larger gearwheel 20 and a (second) smaller gearwheel 10 as essential components.
  • the larger gear 20 is arranged concentrically with the cam or the annular part of the lock bar 2, so that the larger gear and the cam lock about a common axis (A; Fig. 3a ).
  • the larger gear 20 is preferably accommodated as large as possible within the cylindrical portion 1 of the lock cylinder.
  • the smaller gear 10 is housed in the illustrated embodiment in the radially projecting, U-shaped portion (here downwards) of the profile cylinder and also designed as large as possible within the available external dimensions.
  • the return mechanism according to the invention comprises a return element, preferably in the form of at least one spring.
  • this return element may also have a plurality of springs and additional lever elements, which according to the invention preferably in the radially projecting, downwardly directed, U-shaped section are housed.
  • This has the decisive advantage that the mechanism of the return element can be accommodated away from the rotatably mounted cylinder core 6, so that the already proven design of a double-knob cylinder, which should allow a rotational movement of the cylinder core 6 or data transmission within the cylinder core 6, is not hindered.
  • Fig. 1 In addition, some design features are shown, which are not described in more detail, since they are not relevant to the understanding of the return mechanism according to the invention.
  • FIGS. 2a and 2b show essential parts of the return mechanism according to the invention in two different positions, wherein the representation of FIGS. 2a and 2b essentially represents a cross section of the lock cylinder according to the invention perpendicular to the longitudinal axis A of the cylinder.
  • the FIGS. 2a and 2b show the area in which the cam 2 can be in the rest area.
  • the show FIGS. 2a and 2b the extreme positions of the rest area, that is, the cam 2 can move in the lower area without force and remain in each of these positions without the return mechanism moves the cam 2.
  • FIG. 2a shows the maximum deflection to the right over the angle ⁇ / 2, that is, a position in which the uppermost of the gears 13 of the small gear 10 is still within the tooth-free portion 22, but abuts the first tooth of the tooth portion 21 of the large gear 20 left
  • the maximum force-free deflection of the lock bar 2 to the left is shown in which the uppermost tooth of the gears 13 of the small gear 10 is also still in tooth-free area 22 of the large gear, but to the first tooth of the tooth portion 21 on the other side of the teeth-free area 22nd of the larger gear 20 abuts.
  • the uppermost tooth is meant with respect to the rest position of the small gear, that is, the tooth which is closest to the eccentric point 11 discussed below.
  • the deflection corresponds to ⁇ / 2 to the left of the maximum deflection by ⁇ / 2 to the right, in which case the rest region can be described as ⁇ .
  • This angle 80 ° corresponds essentially to the As soon as the gears 21 of the larger gear engage with the gears 13 of the smaller gear, the smaller gear 10 rotates and thus the eccentric point 11 of the small gear shifts from the in FIGS. 2a and 2b position shown; that is, the eccentric point 11 is turned down.
  • the spring element 30, which in Fig. 4 is shown trying to counteract such a rotation of the eccentric point of attack 11, thus causing a bias of the eccentric point 11 upwards, causing the larger gear is turned back to the "rest position".
  • FIGS. 2a and 2b shows a partial view of the return mechanism according to the invention.
  • the combination of the smaller gear 10 with the larger gear 20 may be described as a gear unit with a drive element and an output member which are relatively movable to each other, wherein in an engaged state, the two gears 10 and 20 are positively in operative connection, so that a power transmission between the gears is achievable.
  • the driven by the spring element gear can be referred to as a driving gear or pinion, the driven larger wheel as the output.
  • the tooth shape of the two wheels is preferably an involute toothing. Since the two gears can move freely in the "tooth gap area" of the output, you could call the larger gear as "output with freewheel".
  • Both gears 10, 20 are rotatably arranged and have the same number of teeth; eleven in the embodiment shown here.
  • an operative connection exists when the teeth of the smaller gear 10 with the gears of the toothed (angle) area 21 of the larger gear 20 engage with each other.
  • the larger gear Due to the "tooth space area” 22 (hereinafter also referred to as “tooth-free area”) in the larger gear 20, the larger gear can be moved via this tooth-free area 22 in a freewheeling state without a force from the smaller gear 10 transmitted to the larger gear 20 becomes. That is, when the larger gear 20 is in a position in which there is no operative connection to the small gear 10, then the return mechanism, the larger gear 22 can not rotate.
  • the tooth-free Area 22 defines the "rest position” or the “rest area” in which the larger gear 20 can remain force-free and thus defines the area in which the cam 2 - which is preferably rotatably connected to the larger gear 20 - may remain to still the To ensure anti-panic function of the anti-panic lock.
  • Fig. 4 shows similar to the FIGS. 2a and 2b a rest position within the rest area (freewheeling area), but with the additionally shown spring element 30 in the form of a compression spring.
  • the compression spring 30 tries to push the eccentric attached to the small gear 10 pin 11 still up; is reached this upper position is the smaller gear 10 in the rest position.
  • all the tooth elements of the smaller gear 10 and the larger gear 20 are made similar in geometry or identical to allow a safer intervention.
  • the invention is not limited to this type of gears.
  • the show FIGS. 3a to 3c and 5a to 5d an embodiment with the smaller gear 10 as a spur gear and the larger gear as a cylindrical sleeve with toothed elements 25 which extend in the axial direction of the sleeve.
  • the larger gear thus resembles a Kegelplanrad.
  • the gears may also be designed as bevel gears.
  • FIGS. 3b and 3c schematically a lock cylinder according to the invention in positions in which the return mechanism would like to push the cam back into the rest position.
  • Fig. 3a is essentially the same as in Fig. 4 position shown, but from the side.
  • the cam 2 is directed vertically downwards, the eccentric pin 11 is in its rest position above, which is achieved by the pressure spring shown here purely by way of example, which exerts a force upward.
  • the larger gear 20 is in the "free-running position" with respect to the smaller gear 10, that is, the cam 2 can by this vertically downward position by ⁇ / 2 to the right and left (in the side view to the rear or forward) force-free are moved without the return mechanism exerts a restoring force on the larger gear 20 and thus the cam.
  • Fig. 3b the cam 2 is not visible because it extends perpendicular to the rear with respect to the plane of the paper.
  • the positions of the locker of the FIGS. 3a and 3b are twisted by 90 °.
  • a rotation of the smaller gear 10 from its rest position is achieved by turning a knob causes a rotation of the larger gear 20, whereby the teeth 25 of the larger gear 20 with the gears of the smaller gear 10 are engaged, so that the smaller gear 10th is rotated from the rest position. Therefore, the eccentrically mounted pin 11 is rotated from the uppermost position to a changed position.
  • the spring 30 now tries to push the pin 11 upwards and thus generates a restoring force, i. a torque on the smaller gear 10, which in turn generates a torque on the larger gear 20.
  • Fig. 3c shows a further extreme position in which the return spring 30 is maximally compressed, that is, the eccentric pin 11 is in the maximum downward position.
  • the restoring mechanism according to the invention with the smaller and the larger gear 10, 20 is designed such that a complete 360 ° rotation of the pegs - and thus a corresponding 360 ° rotation of the larger gear - also causes a 360 ° rotation of the smaller gear 10, follows from the in Fig. 3c shown 180 ° rotation with respect to Fig. 3a Again, the smaller gear 10 and the larger gear 20 are engaged, so that a force exerted by the spring 30 force the eccentric pin 11 tries to push upward, creating a torque in the smaller gear 10th is generated, which in turn is transmitted to the larger gear 20.
  • FIGS. 5a to 5d in which the inner knob 3 with the cam 2, which is rotatably coupled to the larger gear 20 is shown in perspective.
  • the return mechanism only essential parts are shown, namely the smaller gear 10 and the return element 30 in the form of a spring, which acts on the eccentric pin 10 of the smaller gear 10.
  • the position of the return mechanism of Fig. 5a corresponds essentially to the position Fig. 3a respectively.
  • Fig. 4 The position of the Fig. 5c corresponds essentially to the position of Fig. 3b that is, a 90 ° rotation of the SchOUGbarts 2 from the vertically downward position, which is centered within the rest position according to the invention.
  • the invention also includes the exact or exact terms, features, numerical values, or ranges, etc., as above or below, of such terms, features, numerical values, or ranges in the context of terms such as "about, about, substantially,” Generally, at least, at least “etc.” (ie, “about 3” should also include “3” or “substantially radial” should also include “radial.")
  • the term “or” also means “and / or”.

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Claims (13)

  1. Mécanisme de rappel dans un cylindre (42) pour une serrure anti-panique, lequel précontraint une barbe de pêne (2) rotative du cylindre de serrure (42) pour exclure une plage angulaire définie pour une position de repos de la barbe du pêne, ledit mécanisme de rappel comprenant :
    au moins un élément de rappel (30) transmettant la force exigée pour le mécanisme de rappel,
    une première grande roue dentée (20) solidaire en rotation avec la barbe du pêne (2),
    une deuxième petite roue dentée (10) pouvant s'engrener avec la première grande roue dentée (20), de manière à transmettre à la première grande roue dentée (20) la force exercée par l'élément de rappel (30) sur la deuxième petite roue dentée (10),
    la première grande roue dentée (20) et la deuxième petite roue dentée (10) ayant le même nombre de dents.
  2. Mécanisme de rappel selon la revendication 1, où la première grande roue dentée (20) ne présente pas de dents sur une plage angulaire (22) de 30° à 90° et présente préférentiellement des dents sur une plage angulaire (21) de 330° à 270°.
  3. Mécanisme de rappel selon la revendication 1 ou la revendication 2, où la première et la deuxième roue dentée (20, 10) s'engrènent de sorte qu'une rotation de 360° de la première grande roue dentée (20) hors de la position de repos entraîne une rotation de 360° de la deuxième petite roue dentée (10).
  4. Mécanisme de rappel selon la revendication 1, la revendication 2 ou la revendication 3, où l'élément de rappel (30) comporte au moins un élément de ressort (30) et où celui-ci est préférentiellement disposé dans une partie faisant saillie d'un cylindre de serrure.
  5. Cylindre de serrure (42) pour une serrure anti-panique avec une barbe de pêne (2) rotative par rapport à un axe longitudinal (A) du cylindre de serrure, laquelle est précontrainte par un mécanisme de rappel, en particulier selon l'une des revendications 1 à 4, pour exclure une plage angulaire définie pour la position de repos, ledit mécanisme de rappel comportant :
    au moins un élément de rappel (30) transmettant la force exigée pour le mécanisme de rappel,
    une première grande roue dentée (20) solidaire en rotation avec la barbe du pêne (2),
    une deuxième petite roue dentée (10) pouvant s'engrener avec la première grande roue dentée (20), de manière à transmettre à la première grande roue dentée (20) la force exercée par l'élément de rappel (30) sur la deuxième petite roue dentée (10),
    la première grande roue dentée (20) et la deuxième petite roue dentée (10) ayant le même nombre de dents.
  6. Cylindre de serrure selon la revendication 5, où le cylindre de serrure (42) est un cylindre profilé avec un noyau (6) monté de manière rotative, le noyau ou une partie de celui-ci pouvant être accouplés à la barbe du pêne (2) de manière solidaire en rotation par un accouplement.
  7. Cylindre de serrure selon la revendication 5 ou la revendication 6, où le cylindre de serrure (42) présente une partie cylindrique (1) et une partie (5) faisant radialement saillie de celle-ci,
    où la première grande roue dentée (11) est disposée dans la partie cylindrique (1) du cylindre profilé et la deuxième petite roue dentée (10) dans la partie (5) en saillie du cylindre profilé, et où le rapport entre le diamètre du cercle de référence de la première grande roue dentée (20) et le diamètre du cercle de référence de la deuxième petite roue dentée (20) est compris entre 17/8 et 15/10, de préférence sensiblement égal à 17/10.
  8. Cylindre de serrure selon l'une des revendications 5 à 7, où l'élément de rappel (30) comporte au moins un élément de ressort (30), lequel est préférentiellement disposé dans la partie en saillie (5) d'un cylindre profilé.
  9. Cylindre de serrure selon l'une des revendications 5 à 8, où ledit cylindre de serrure est un cylindre à bouton électronique.
  10. Cylindre de serrure selon l'une des revendications 5 à 9, où la première grande roue dentée (20) est rotative autour de l'axe longitudinal (A) du cylindre de serrure.
  11. Cylindre de serrure selon l'une des revendications 5 à 10, où la première grande roue dentée (20) présente un alésage central parallèlement à l'axe longitudinal (A) du cylindre de serrure.
  12. Cylindre de serrure selon l'une des revendications 5 à 11, où le flux de la force de rappel de l'élément de rappel (30) va vers la première grande roue dentée (11) par la deuxième petite roue dentée (10).
  13. Cylindre de serrure selon l'une des revendications 5 à 12, où l'élément de rappel (30) contacte la deuxième petite roue dentée (10) à un emplacement (11) excentré.
EP12195035.6A 2012-11-30 2012-11-30 Cylindre anti-panique Active EP2738325B1 (fr)

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Application Number Priority Date Filing Date Title
EP12195035.6A EP2738325B1 (fr) 2012-11-30 2012-11-30 Cylindre anti-panique

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EP2738325A1 EP2738325A1 (fr) 2014-06-04
EP2738325B1 true EP2738325B1 (fr) 2017-06-14

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DE102017111353A1 (de) 2017-05-24 2018-11-29 Wilka Schließtechnik GmbH Schließzylinder mit Rückstellsystem

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DE10316522B3 (de) 2003-04-10 2004-07-08 Seccor High Security Gmbh Automatisches Rückstellsystem für elektronische Schließsysteme im Einsatz mit Panikschlössern
DE102008029686B4 (de) * 2008-01-19 2016-07-28 Dom Sicherheitstechnik Gmbh & Co. Kg Schließzylinder mit selbsttätiger Rückstellung des Schließgliedes
DE102008034070A1 (de) * 2008-07-22 2010-01-28 Wilka Schließtechnik GmbH Schließzylinder mit federkraftunterstützter Zylinderkernrückstellung
DE102008056627C5 (de) * 2008-11-10 2012-08-02 Wilka Schließtechnik GmbH Profilzylinderschloss mit einstückigem radialem Gehäuseansatz und mit automatischer Rückstellvorrichtung für einen Schließbart oder Mitnehmerkörper

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