EP2738325A1 - Anti-panic cylinder - Google Patents

Abstract

The mechanism has a resetting unit for supplying necessary force for the mechanism and a large toothed wheel (20) connected with a closing burr (2) in a torque-proof manner. A small toothed wheel (10) stays in engagement with the large toothed wheel such that force produced at the small wheel is transferred to the large wheel. The wheels comprise equal number of teeth. The resetting unit has a spring element e.g. torsion spring, that is arranged in a projecting section of a locking cylinder (42). A drive element and a driven element are rotatable relative to each other. An independent claim is also included for a locking cylinder.

Description

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.

BACKGROUND OF THE INVENTION

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. By this antipanic function, e.g. in case of fire the possibility of escape through the emergency exit doors guaranteed. By pressing the lever handle latch and latch are pulled into the lock. For this purpose, however, it is usually necessary that the cam (often referred to as nose, driver, closing member or closing 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. Often, the cam of the lock cylinder must be in a lower position, as it could otherwise hinder the (anti) panic function of the lock. Depending on the anti-panic lock, only very specific positions or special angle ranges are permitted as rest position to ensure anti-panic function.

From the DE 103 16 522 is an automatic reset system for electronic locking systems in use with anti-panic locks known. In this case, the cam is returned to a rest position by the reset system after each rotation operation. For this purpose, a lock cylinder is provided which has a cam. On the shaft which carries the cam, a core is offset from the axis. On the eccentric core, a ball bearing is provided. In a housing connected to the cylinder, 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. However, 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.

The object of the invention is therefore to provide an 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.

This object is achieved with an automatic reset mechanism according to claim 1 and a lock cylinder according to claim 5. Further preferred embodiments are described in the further claims and in the embodiments discussed below.

SUMMARY OF THE INVENTION

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 a Antipaukfunktion (antipanic lock) can be used. In particular, 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.

There are different types of locking cylinders such as profile cylinders (eg standard Euro profile cylinder according to DIN 18252 / EN1303), round cylinders (eg Swiss Round, Scandinavian Round), oval cylinders (eg Scandinavian Oval, British Oval) and many more. We also speak of semi-cylinders if they only be closed and / or actuated from one side and of double cylinders, if they are closable and / or operable from both sides. Also are mechanical knob cylinders are known to be operated on one side with a key and on the other side with a fixed mounted rotary knob. A profile cylinder is the most common form of security door locks used today in Germany or Austria. Consequently, the invention will be described preferably with reference to a profile cylinder. However, the present invention is applicable to any type of lock cylinders, particularly but not limited to the variants exemplified above.

1. i) Als mechanisch kodierten Zylinder mit einer zusätzlichen elektronischen Verriegelung z. B. über einen Sperrmagneten. Der Schlüssel enthält die nötige Elektronik vorzugsweise in der Schlüsselreide und wird über Kontakte oder auch kontaktlos auf Schließberechtigung überprüft.
2. ii) Als ausschließlich elektronisch kodierten Zylinder. Der Schlüssel als solches wird vorzugsweise nur zum Drehen des Zylinders und als Identmittelträger benötigt. Diese Schlüssel können auch ein spezifisches mechanisches Profil enthalten, um auch die in einer Schließanlage enthaltenen rein mechanischen Zylinder zu schließen.
3. iii) Als Einfach- bzw. Doppelknaufzylinder weist der Zylinder auf einer bzw. beiden Seiten der Türe einen Drehknauf auf, welcher eine rein elektronische Verriegelung ermöglicht (elektronischer Knaufzylinder). Erst nach rein elektronischer Überprüfung der Schließberechtigung erfolgt die Freigabe und der Drehknauf kann zum Öffnen bzw. Schließen bedient werden, wodurch der Schließbart gedreht wird. Ohne Berechtigung dreht zumindest einer der genannten Knäufe leer durch, oder blockiert. Als Identmittel wird beispielsweise ein Keyfob, ein Armband, eine Chipkarte (z.B. Mifare Chipkarte), eine Funkkarte (beispielsweise RFID Karte) oder ein passiver bzw. aktiver Transponder verwendet, ohne darauf beschränkt zu sein. Die vorliegende Erfindung ist auf jegliche Art von elektronischen Schließzylindern anwendbar, insbesondere auf die oben beispielhaft genannten Varianten, ohne darauf beschränkt zu sein. Im Folgenden wird die Erfindung beispielhaft anhand eines elektronischen Doppelknaufzylinders beschrieben.

Preferably, the lock cylinder according to the invention is an electronic lock cylinder, which is often referred to as a digital lock cylinder or is referred to in one embodiment with a knob or two knobs as an electronic knob cylinder. In particular, a digital lock cylinder has the shape of a normal lock cylinder, but is preferably operated not with a mechanical key but with an electronic key. The electronic lock cylinder is preferably fed by means of batteries. These battery-operated electronic locking cylinders have the advantage that complicated cabling of individual components is eliminated, so that this type of cylinder is therefore suitable for uncomplicated retrofitting of existing mechanical systems. Electronic battery operated lock cylinders are available in three different versions.

1. i) As a mechanically coded cylinder with an additional electronic lock z. B. via a blocking magnet. The key contains the necessary electronics, preferably in the key crayon and is checked via contacts or contactless for locking authorization.
2. ii) As exclusively electronically coded cylinders. The key as such is preferably needed only for rotating the cylinder and as Identmittelträger. These keys may also contain a specific mechanical profile to close also the purely mechanical cylinders contained in a locking system.
3. iii) As a single or double knob cylinder, the cylinder on one or both sides of the door on a knob, which allows a purely electronic locking (electronic knob cylinder). Only after a purely electronic check of the locking authorization is the release and the knob can for Opening and closing are operated, whereby the cam is rotated. Without authorization, at least one of the mentioned knobs turns off, or blocks. For example, a keyfob, a wristband, a chip card (eg Mifare chip card), a radio card (for example RFID card) or a passive or active transponder are used as identification means, without being limited thereto. The present invention is applicable to any type of electronic lock cylinders, in particular, but not limited to, the variants exemplified above. The invention will be described below by way of example with reference to an electronic double-knob cylinder.

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 Schließbarts 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. As a result, in view of high restoring forces, a large return member, 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.

In addition, 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. In addition, the return mechanism comprises at least a first larger gear which is connected to the cam, preferably non-rotatably, and a second smaller gear which is engageable with the first larger gear or 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. It should be noted that the relative terms "smaller" and "larger" gear refer to each other, making it clear that the larger gear is larger than the smaller gear. In addition, the term size should refer to the diameter or radius of the gears, preferably the corresponding Wälzkreisdurchmesser. Although the two gears are different in size, the two gears should preferably have the same number of teeth.

In order to still allow engagement between the two gears, it is preferred that 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. In other words, 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." Preferably, 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 °.

Preferably, engagement of the two gears means transmission between two rotations of the two gears, i. when the teeth are engaged, they engage positively, and thus slip-free into each other. However, due to the tooth-free region, a condition may occur in which the two gears are not engaged, i. There is a slip over the tooth-free area. Preferably, the first larger gear has no teeth over an angular range of 30-90 °.

Preferably, the first and second gears are arranged to one another such that a 360 ° rotation of the first larger gear from the rest position preferably also causes a 360 ° rotation of the second smaller gear.

Preferably, the smaller gear and / or the larger gear is formed as a spur gear. In addition, it is conceivable that 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). However, 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.

Preferably, 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. According to a further preferred embodiment, the lock cylinder is an electronic knob cylinder having one or two knobs. In a single-knob cylinder or a half-cylinder with only one knob, 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. In a double-knob cylinder, 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.

Preferably, the first larger gear is arranged in the lock cylinder, that it is rotatable about the longitudinal axis of the lock cylinder. In other words, 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. Preferably, 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. Preferably, the ratio of the "pitch circle diameter" of the two gears is in the range of 17/8 - 15/10. In other words, 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 a Außenendurclunesser of 17mm in the cylindrical section and the width of the radially projecting portion is 10mm. In order to utilize this external conditions particularly effectively, it is preferable to install as large a gearwheel as possible in the cylindrical as well as in the radially projecting section. For example, if you install a gear that is always 1 mm away from the outer dimensions, you get two gears with 17mm-2mm = 15mm or 10mm-2mm = 8mm outer diameter.

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. Also, the spring element is not limited to a particular material, but preferably made of spring steel or a copper-beryllium alloy.

Preferably, 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. Again, there are several possibilities for a person skilled in the art how the restoring member should act on this eccentric position. For example, could be present on the smaller gear a projecting eccentric pin on which a train or compression spring attacks. According to a further embodiment, instead of an eccentric pin, 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.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1

eine Explosionszeichnung eines elektronischen Doppelknaufzylinders in der Ausgestaltung eines Profilzylinders;

Fig. 2a - 2b

eine Teilansicht des erfindungsgemäßen Rückstellmechanismus;

Fig. 3a-3c

Seitenansichten des erfindungsgemäßen Rückstellmechanismus in drei verschiedenen Zuständen;

Fig. 4

eine den Figuren 2a und 2b ähnliche Teilansicht des erfindungsgemäßen Rückstellmechanismus mit einem dargestellten Rückstellglied; und

Fig. 5a -5d

perspektivische Teilansichten des erfindungsgemäßen Rückstellmechanismus in vier verschiedenen Zuständen.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. Show it:

Fig. 1

an exploded view of an electronic double knob cylinder in the configuration of a profile cylinder;

Fig. 2a - 2b

a partial view of the return mechanism according to the invention;

Fig. 3a-3c

Side views of the return mechanism according to the invention in three different states;

Fig. 4

a the FIGS. 2a and 2b similar partial view of the return mechanism according to the invention with a return member shown; and

Fig. 5a -5d

partial perspective views of the return mechanism according to the invention in four different states.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

FIG. 1 shows a first embodiment of the invention. In the embodiment shown as exploded view 42 is a double-clutch electronic cylinder with the two knobs 3 and 4, which are attached to the two ends of the longitudinal axis A of the lock cylinder. In addition, in the illustrated lock cylinder is a profile cylinder with a round cylindrical core portion 1 and a radially projecting U-shaped portion 5. In the illustrated embodiment, 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. Preferably, 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. Preferably, 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 Schließbarts 2 takes place only in the coupled state, the again depends on a successful authentication. In other words, in a successful authentication by the transmitter in the inner knob 3, 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.

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. Preferably, 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 ). In other words, 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. In addition, the return mechanism according to the invention comprises a return element, preferably in the form of at least one spring. Preferably, however, 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. In 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. In particular, 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 β / 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 , Accordingly, in the Fig. 2b 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. Here, 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.

Due to the symmetrically configured embodiment, the deflection corresponds to β / 2 to the left of the maximum deflection by β / 2 to the right, in which case the rest region can be described as β. In the illustrated embodiment, the value of β / 2 = 40 °, so that the angular range of the rest region is 2 x β / 2 = 80 °. 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.

In other words, 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. 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. Again, in other words, 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.

If the cam is in the upper area (see for example Figures 5b-5d ), then engage the gears of the larger gear 20 in the teeth 13 of the smaller gear 10 a. The smaller gear 10 will therefore be made of the in Fig. 2a and 2b turn shown position, so that the eccentric point 11 is rotated at the small gear from rest position. But since the spring element 30 acts on the eccentric point 11 and always tries to move this point 11 in the rest position of the smaller gear 10 or rotate, the larger gear 20 is forcibly rotated together with the cam 2 in the allowable rest area for the cam ,

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.

Preferably, 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. However, the invention is not limited to this type of gears. For example, 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. According to further embodiments, not shown, the gears may also be designed as bevel gears. A person skilled in the art will readily recognize that there are a large number of possible embodiments in order to realize an inventive intervention of the two gears of different sizes.

In contrast to the FIGS. 2a and 2b in which positions of the return mechanism are shown within a rest position, show the 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 β / 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.

In Fig. 3b the cam 2 is not visible because it extends perpendicular to the rear with respect to the plane of the paper. In other words, the positions of the locker of the FIGS. 3a and 3b are twisted by 90 °. This 90 ° twisted position of the Fig. 3b thus exceeds the rest range of β / 2 = 40 °, so that the return mechanism tries to turn the cam 2 back to the rest position.

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. Since 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. Due to the different size of the two gears to obtain an advantageous gear ratio, that is limited by the structural conditions spring forces that can be accommodated in the radially projecting U-shaped portion of a profile cylinder are used very effectively due to this reduction ratio with respect to smaller and larger gear, whereby finally a large restoring force for the lock bit 2 can be provided.

Finally it will be on the FIGS. 5a to 5d referenced, in which the inner knob 3 with the cam 2, which is rotatably coupled to the larger gear 20 is shown in perspective. Again, to illustrate 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 Fig. 5c corresponds essentially to the position of Fig. 3b that is, a 90 ° rotation of the Schließbarts 2 from the vertically downward position, which is centered within the rest position according to the invention. Fig. 5b again shows a 90 ° twist of the Schließbts, but in the other direction than Fig. 5c , Finally, the position corresponds to the Fig. 5d the position of the lateral representation Fig. 3c , that is, the cam is directed upwards.

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".

Claims (13)

A return mechanism biasing a rotatable lock bit (2) of a lock cylinder (42) for an anti-panic lock to preclude a predetermined angular range for a rest position of the lock bar, the return mechanism comprising: at least one return member (30) providing the required force for the return mechanism, a first larger gear (20) which is rotatably connected to the cam (2), a second smaller gear (10) engageable with the first larger gear (20) so that a force applied to the second smaller gear (10) by the return member (30) is transmitted to the first larger gear (20) the first larger gear (20) and the second smaller gear (10) have the same number of teeth. A return mechanism according to claim 1, wherein the first larger gear (20) has no teeth over an angular range (22) of 30 ° -90 ° and preferably has teeth over an angular range (21) of 330 ° -270 °. A return mechanism according to claim 1 or 2, wherein the first and second gears (20, 10) mesh with each other such that a 360 ° rotation of the first larger gear (20) from the rest position causes a 360 ° rotation of the second smaller gear (10) , Return mechanism according to claim 1, 2 or 3, wherein the return member (30) has at least one spring element (30) and this is preferably arranged in a protruding portion of a lock cylinder. A lock cylinder (42) for an anti-panic lock having a cam (2) rotatable relative to a longitudinal axis (A) of the lock cylinder, biased by a return mechanism, in particular according to one of claims 1 to 4, to exclude a predetermined angular range for the rest position the reset mechanism has: at least one return member (30) providing the required force for the return mechanism, a first larger gear (20) which is rotatably connected to the cam (2), a second smaller gear (10) engageable with the first larger gear (20) so that a force applied to the second smaller gear (10) by the return member (30) is transmitted to the first larger gear (20) the first larger gear (20) and the second smaller gear (10) have the same number of teeth. Lock cylinder according to claim 5, wherein the lock cylinder (42) is a profile cylinder with a rotatably mounted cylinder core (6), wherein the rotatable cylinder core or a part thereof via a clutch with the cam (2) is rotatably coupled. Locking cylinder according to claim 1 or 2, wherein the lock cylinder (42) has a cylindrical portion (1) and a radially projecting portion (5),
wherein the first larger gear (11) is disposed in the cylindrical portion (1) of the profile cylinder and the second smaller gear (10) is located in the protruding portion (5) of the profile cylinder, and wherein the ratio of the pitch circle diameter of the first larger gear (20) the pitch circle diameter of the second smaller gear (20) in the range of 17/8 - 15/10, preferably at about 17/10. Lock cylinder according to one of the preceding claims 5 - 7, wherein the return member (30) has at least one spring element (30) which is preferably arranged in the protruding portion (5) of a profile cylinder. Lock cylinder according to one of the preceding claims 5-8, wherein the lock cylinder is an electronic knob cylinder. Lock cylinder according to one of the preceding claims 5-9, wherein the first larger gear (20) about the longitudinal axis (A) of the lock cylinder is rotatable. Lock cylinder according to one of the preceding claims 5-10, wherein the first larger gear (20) has a central bore parallel to the longitudinal axis (A) of the lock cylinder. Lock cylinder according to one of the preceding claims 5 - 11, wherein the power flow of the restoring force from the return member (30) via the second smaller gear (10) to the first larger gear (11). Locking cylinder according to one of the preceding claims 5 - 12, wherein the return member (30) engages an eccentric position (11) of the second smaller gear (10).

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