EP3686383A1 - Door lock with motor - Google Patents

Abstract

A door lock comprises a cylinder receptacle for a locking cylinder, which has an input element, the input element being 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, and a motor to supplement it the adjustability by means of the locking cylinder to be able to adjust the bolt and / or the latch in a motorized manner, the motor being able to be coupled or coupled with the input element in order to adjust the bolt and / or the latch in a motorized manner via the input element.

Description

The present invention relates to a door lock with a motor, in particular an electric motor, for the motorized adjustment of a bolt and / or a latch of the door lock. Door locks according to the preamble of claim 1 are, for example DE 36 06 531 A1 , DE 197 57 192 A1 , EP 2 096 239 A1 , EP 1 990 492 A2 , DE 102 10 945 A1 and CN 104 863 420 A known.

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. For example, the bolt or the latch can be adjusted 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.

Basically, all different closing states of a door lock (for example: open latch, closed latch, bolt unlocked, bolt simply locked, bolt double locked) can be brought about in a motorized manner. However, it can also be provided that the motorization is only intended for a selection of the possible states and other states can only be set manually, for example.

Such motorized door locks should be usable wherever possible where conventional door locks can also be used. Therefore, it is preferred if 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.

Furthermore, it is advantageous if 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 if the motorized drive fails, the door lock can still be operated manually.

Therefore, with such a motorized door lock, 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.

For this purpose, 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, for example, be 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 of the locking cylinder.

In principle, for a motorized adjustment of the bolt or the latch, the locking cylinder could be replaced by a motor device which outputs a respective actuating 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 as a motor, that is to say in particular to provide a separate motor in the door lock that is independent of a respective lock cylinder.

If a motorized adjustment of the bolt and / or the latch is to be possible in addition to a manual actuation of the door lock starting from a conventional locking cylinder, the problem arises as to how a motor can be coupled to the bolt or latch in a drive-effective manner, so that actuation of the door lock remains possible by means of a locking cylinder accommodated in the locking cylinder receptacle.

Another difficulty arises from the fact that a drive torque output by a motor must be suitably adapted depending on the motor in order to be transmitted to the bolt or the latch with sufficient force for the adjustment, but not excessive to avoid damage. It may therefore be necessary to provide a gearbox with a corresponding gear ratio or reduction between the motor and the bolt or the latch to ensure reliable power transmission. However, only a small amount of installation space is available for a door lock of conventional dimensions.

It is an object of the invention to provide a door lock which enables a motorized adjustment of a bolt and / or a latch of the door lock in addition to manual actuation, is of compact design and can be used instead of conventional door locks without substantial adjustments, and reliable drive torque transmission from the motor to Bolt or trap guaranteed.

The object is achieved by a door lock with the features of claim 1.

The door lock includes a cylinder receptacle for a locking cylinder, which has an input element, the input element being 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. In addition, the door lock includes a motor in order to be able to adjust the bolt and / or the latch in a motorized manner in addition to the basic adjustability by means of the locking cylinder. In other words, a motor is provided in the door lock, which is designed and arranged such that the bolt and / or the latch 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 lock cylinder is accommodated in the cylinder receptacle or not. If a locking cylinder is accommodated in the cylinder receptacle, the bolt and / or the latch 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 independent and separate from the respective locking cylinder.

The object of the invention is achieved in particular in that the motor can be coupled or coupled to the input element in order to adjust the bolt and / or the latch in a motorized manner via the input element. An essential aspect of the invention is therefore that the bolt or the 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. This means in particular that a first section of the drive path runs from the motor to the input element and a second section of the drive path runs from the input element to the bolt or latch, the first and second sections of the drive path being disjoint, that is to say not a common one with the exception of the input element Have drive element.

In particular, the 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 to the latch, can be designed as in a conventional door lock. This not only has the advantage that for the door lock according to the invention 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. Due to the fact that 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 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, the element of the cylinder receptacle which is directly from the output element, for example a locking lug, of a locking cylinder received in the cylinder receptacle is actuated when the lock cylinder is actuated. In principle, the input element can also be designed in several parts, with a 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, 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.

Since the drive torque of the motor is transmitted via the input element to the bolt or latch and the input element is designed to be driven by the output element of the locking cylinder during a motorized adjustment of the bolt or the latch, the input element, if it is driven by a motor, conversely also drives the output element of the locking cylinder to move. Therefore, locking cylinders are preferably to be used in such a door lock, the output element of which can be moved freely when the key is removed, in particular so-called freewheel 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 a motorized adjustment is desired. In this respect, "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.

According to an advantageous further development, the motor is coupled or can be coupled to the input element in a drive-effective manner via a toothed belt. A toothed belt enables reliable drive-effective coupling even over comparatively long distances without taking up a lot of installation space. It is preferred if the input element of the cylinder receptacle has a toothing on which the toothed belt rolls. In this embodiment, the toothed belt therefore acts directly on the input element. This makes it possible to arrange not only the engine, but also a gear possibly associated with the engine at a clear distance from the cylinder receptacle and in particular from the entire further drive path from the cylinder receptacle to the bolt or latch. These elements of the door lock can therefore be configured essentially unchanged compared to a conventional door lock. This simplifies the design development of a door lock according to the invention. Because the space for the motor and possibly a gear can then be chosen relatively freely within the door lock.

In addition, there is the possibility of providing the motor and, if appropriate, components additionally provided for the motorized actuation of the door lock, such as a transmission in a part or module which is essentially separate from the rest of the door lock and which can be designed to be connectable to an initially non-motorized door lock. For the drive-effective connection of such a module to the input element and ultimately to the bolt or the latch, it is then only necessary to apply the toothed belt to the input element of the cylinder receptacle.

Furthermore, it is advantageous if 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 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.

For example, 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. For example, in order to adjust the bolt or and / or the latch to a specific position, the motor can be driven 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.

In order to detect the rotational position of the toothed belt, the device mentioned can have a gearwheel on which the toothed belt rolls. The rotational position of the gear, e.g. can be detected 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.

In particular, if 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. In order to be able to clearly detect circumferential positions over the full length of the toothed belt, the toothed wheel would therefore have to have a sufficiently large circumference, which can be unfavorable in view of the limited installation space.

In a preferred embodiment, the device for detecting the rotational position of the toothed belt is therefore formed by an absolute rotary encoder with two gear wheels, on which the toothed belt rolls and the number of teeth of which are relatively prime, preferably different from one another. Such an absolute rotary encoder enables the rotational position of the gearwheel to be clearly detected over a long distance with comparatively small radii of the two gears. Because due to the different number of teeth of the two gears, with one full rotation of 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.

In particular, 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. In the case of tooth numbers that are not common to the part, this corresponds to the product of the two tooth numbers, so that the area of clearly detectable rotating positions is maximized.

If the number of teeth differs exactly by one, they are always prime. In addition, 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. In particular, 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.

According to an advantageous development, the motor can be coupled or coupled to the input element in a drive-effective manner via a freewheel gear. In particular, the motor can be coupled to the toothed belt in a drive-effective manner via the freewheel gear. The freewheel gear is then provided between the motor and the toothed belt.

In this case, the freewheel gear can have an input element which is coupled to the motor for effective driving and in particular is directly coupled to an output element of the motor. In addition, the freewheel gear can have an output element which is coupled to the input element of the cylinder receptacle in a drive-effective manner and in particular is directly coupled to the toothed belt. Direct coupling is to be understood in particular to mean that the respective elements roll directly onto one another.

Such a freewheel gear is designed to transmit a drive torque arriving at the input element of the freewheel gear through the freewheel gear to the output element of the freewheel gear, but not to transmit a drive torque arriving at the output element of the freewheel gear to the 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 for self-locking motors, such as common electric motors. To prevent the motor from being operated manually must be actively decoupled from the bolt and / or the latch or, conversely, that the motor for motorized adjustment must first be actively coupled to the bolt and / or the latch, consequently the freewheel gear can be provided, which passively, so to speak, this function in particular automatically, depending on whether a drive torque is received at the input element.

The above-mentioned object is - in principle independent of the door locks described above or also as a further development thereof - also achieved by a door lock with a motor for motorized adjustment of a bolt and / or a latch of the door lock as well as a freewheel gear via which a drive torque of the motor is applied the bolt and / or the latch is transferable, the freewheel gear having an input element which is coupled to the motor for effective driving, and having an output element which is operatively coupled to the bolt and / or the latch, the freewheeling mechanism further comprising at least one coupling element has, which is movable between a coupling position in which it couples the input element and the output element with one another for driving purposes, and a freewheeling position in which it decouples the input element and the output element with one another in a driving manner.

The position of the coupling element thus decides whether or not the input element and the output element of the freewheel transmission are coupled in a drive-effective manner for transmission of the drive torque. The coupling should take place as automatically as possible depending on whether the input element is currently being driven by the motor or not.

For this purpose, the input element can have 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 through a special surface shaping of the input element in one area formed 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.

For this purpose, the freewheel gear can also have 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 arranged at least essentially statically, that is to say in a stationary manner relative to the transmission, but a certain play can be provided, as will be explained further below. Similar to the drive contour, 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.

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. For example, 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. In this respect, 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.

According to a preferred embodiment, the output element has an engagement contour, into which the coupling element engages in the coupling position. In this way, the output element and the coupling element, when this is in the coupling position, are coupled to one another in a drive-effective manner. 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. This can be done in each of these recordings Coupling element are at least partially included when it moves or is moved from the freewheeling position into the coupling position.

If, in this embodiment, 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. When 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. In this respect, the coupling element can, in particular, at least essentially have an elongated cylindrical shape. In this way, the coupling element can, for example, cooperate with the drive contour of the input element and the engagement contour of the output element in a first section of its longitudinal extent and with the guide contour of the guide element in a second section of the longitudinal extent.

Furthermore, it is preferred if the coupling element is biased into the freewheel position. By prestressing the coupling element 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 occurs in particular when the motor does not output any drive torque to the input element of the freewheel gear.

In such an embodiment, 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 only outputs no drive torque when the bolt or latch is in a defined position to be assumed, it is ensured in this way 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 then immediately possible again.

According to a preferred embodiment, the input element and the output element of the freewheel gear are rotatably mounted about a common axis of rotation. In this respect, 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.

If the coupling element is designed as a coupling pin, the coupling element is also 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.

In an embodiment with a common axis of rotation of the input element and the output element of the freewheel transmission, the coupling position and the freewheel position of the coupling element are preferably different radial distances of the coupling element to the axis of rotation defined. 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. Thus, 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). Correspondingly, 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).

Therefore, the coupling element can be carried by the input element both in the freewheel position and in the coupling position if the input element is carried by the motor to rotate 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 less than in the freewheel position or vice versa.

According to a further embodiment, 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. There are preferably two coupling elements. These can consequently be aligned with one another in particular diametrically with respect to the axis of rotation.

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.

It is preferred if 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. Overall, the loop springs can form a closed circle around the axis of rotation. The bow springs can thus perform two functions at the same time. 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, the spring elasticity of the bow springs allows at least a certain change in the circular path, in particular with regard to its radius, so that the coupling elements remain radially movable between the coupling position and the free-wheel position, but are biased into the free-wheel position.

According to an advantageous embodiment, 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 is 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 (depending the greater the number of the rotational symmetry, the less) arrives.

Furthermore, it is preferred if 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 depression represents such a deviation from the base radius. If the drive contour is a surface that is radially inward with respect to the axis of rotation, a respective carry-in depression can in particular correspond to an increase in the radius compared to the base radius. Conversely, a respective entraining recess can correspond to a reduction in the radius compared to the base radius in the case of a drive contour oriented radially outwards. In this case, an entraining recess does not necessarily have a constant radius, but preferably transitions to the basic radius are provided at the edges of the entraining recess. As the mentioned radius of the entraining recess deviating from the base radius is then in particular the deepest radius, that is to say the radius of the recess that deviates the most from the basic radius.

In the area of a respective 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.

According to a preferred development, 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.

Furthermore, it is preferred if 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. Like the drive contour, the guide contour can be formed by a surface that is aligned parallel to the axis of rotation and closed in a ring-like manner. The above explanations on the basic radius also apply accordingly to the guide contour.

However, 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. Thus, 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.

In contrast to the drive contour, the guide contour, as deviations from a basic shape, in particular in the form of a cylindrical surface, 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. In particular, 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 correspond in particular to a reduction in radius in the case of a radially inwardly oriented guide contour or in particular to an increase in radius in the case of a radially outwardly oriented guide contour. Depending on the rotational position of the input element, an urging protrusion of the guide contour can, so to speak, protrude into a driving recess of the drive contour (in particular viewed in the axial direction with respect to the axis of rotation, so that the drive contour and the guide contour appear superimposed). As a result, 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. Such a flank can thus, in particular, deflect the rotary movement of a coupling element, which is located 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.

Carrying the coupling element is therefore not blocked by the urging projection, but it is only ensured that when the input element is rotated and the coupling element is carried along as a result, the coupling element inevitably assumes the coupling position and can be carried along in this coupling position

In particular, 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 carried along by the drive contour about the axis of rotation, i.e. 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 unhindered.

Preferably, the coupling element is only put back into the freewheeling position by the pretension when the motor and thus the input element be 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.

According to an advantageous development, 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 makes it possible to displace the guide contour in such a way that it no longer forces the coupling element into the coupling position. In particular, in the above-mentioned embodiments 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 a game can be particularly useful in cases where the coupling of a coupling element into the freewheeling position is blocked, although the motor does not drive the input element. Such a case can occur, for example, in the event of an unscheduled standstill of the motor, for example as a result of a malfunction, damage or wear, in particular if the motor is coupled to the input element in a self-locking manner and in such a drive-effective manner that the input element is also blocked when the motor is at a standstill.

If 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 assuming the freewheel position, this could also block the output element of the freewheel gear and ultimately the bolt and / or the latch of the door lock, so that the door lock as a whole could no longer be operated. Because of the above However, the guide contour can avoid play, at least if sufficient force is applied to overcome the pretension, 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 forcing the coupling element into the coupling position if this is carried along by the input element, can thus meet. The force required for a significant displacement of the guide element therefore preferably exceeds the forces usually to be exerted when the door lock is operated manually.

By mounting the guide element with a certain amount of play, it can thus be ensured in a comparatively simple manner that the door lock can always be operated manually, that is to say even if the motor function fails. This is particularly important from a security perspective.

According to a further embodiment, it is provided that the input element has a through opening, on the inner lateral surface of which the drive contour is formed, and that 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. Such embodiments allow a particularly compact structure of the freewheel gear.

In such an embodiment, it is further preferred if the output element is arranged at least partially within the through opening of the input element. This enables a particularly direct coupling of the input element and the output element of the freewheel transmission to be achieved, in particular since the coupling element can then be arranged between the input element and the output element.

According to a further development of such embodiments, it is provided that the input element is designed as a gearwheel with external teeth, via which it receives the drive torque of the motor, and / or that the output element is designed as a gearwheel with external teeth, via which it outputs the drive torque of the motor . Such toothing allows a simple drive-effective coupling with other components.

In particular, 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. Furthermore, a toothed belt can roll on the external toothing of the output element of the freewheel transmission, via which the drive torque output by the output element of the freewheel transmission can be transmitted to an input element of a cylinder receptacle of the door lock, as described above.

According to a further development, 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 the mentioned axis of rotation, with each other. The first guide disk and the second guide disk can be rigidly connected to one another.

With such an arrangement of the input element between the two guide disks, 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. Instead, the arrangement contributes to the coupling element being displaced at least essentially exclusively in parallel between its free-wheeling position and its coupling position.

The object of the invention is further achieved by a door lock with a cylinder receptacle for a locking cylinder which has an input element, the input element being 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 , with a motor in order to be able to adjust the bolt and / or the latch in a motorized manner in addition to the adjustability by means of the locking cylinder, and with a freewheel gear via which a drive torque of the motor can be transmitted to the bolt and / or the latch, the freewheel gear has an input element that is operatively coupled to the motor, and has an output element that is operatively coupled to the bolt and / or the latch, wherein the freewheel transmission further comprises at least one coupling element that is between a coupling position in which it is the input element and the output element of the freewheel drive coupled to each other in a drive-effective manner, and a freewheel position in which it drives the input element and the output element of the freewheel gear from one another in a drive-effective manner is decoupled, movable, the input element having a drive contour, which is designed to carry the coupling element when the input element is driven by the motor, and wherein the freewheel gear further comprises a guide element with a guide contour, which is designed to the coupling element in to urge the coupling position when it is carried along by the input element, wherein the motor, preferably via the freewheel gear and / or a toothed belt, can be coupled or coupled in a drive-effective manner to the locking element and / or the latch via the input element the motorized cylinder holder.

Advantageous further developments of such a door lock result in a corresponding manner from the above-described embodiments of door locks according to the invention.

Fig. 1

zeigt eine Ausführungsform eines Türschlosses in einer perspektivischen Ansicht.

Fig. 2

zeigt das Freilaufgetriebe einer Ausführungsform eines Türschlosses in einer Explosionsdarstellung.

Fig. 3

zeigt das Freilaufgetriebe in einer perspektivischen Darstellung.

Fig. 4

zeigt das Freilaufgetriebe in einer Seitansicht.

Fig. 5

zeigt einen Teil des Freilaufgetriebes in einer Aufsicht.

Fig. 6

zeigt das Freilaufgetriebe in einer Aufsicht.

The invention is explained in more detail below merely by way of example with reference to the figures.

Fig. 1

shows an embodiment of a door lock in a perspective view.

Fig. 2

shows the freewheel gear of an embodiment of a door lock in an exploded view.

Fig. 3

shows the freewheel gear in a perspective view.

Fig. 4

shows the freewheel gear in a side view.

Fig. 5

shows a part of the freewheel gear in a plan.

Fig. 6

shows the freewheel gear in a top view.

In 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. To lock the 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.

Furthermore, 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. In particular, 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, as well as the latch 17, which is movable between a released and a closed state, are drivingly coupled to the input element 23 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.

In order to enable a motorized adjustment of the bolt 15 and the latch 17, 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. Via the input element 23, the motor 27 is consequently also coupled to the bolt 15 and the latch 17 in a drive-effective manner. Thus, the motor 27 can be controlled to adjust the bolt 15 or the latch 17 between their respective positions.

Basically, i.e. Regardless of the specific embodiment shown, 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 so that it drives. 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 approximately 300 °, so that the input element 23 is designed like a gear. In order to guide the toothed belt 29, 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 in order to be able to detect the respective rotational position of the toothed belt 29, in order in particular to be able to determine the position of the input element 23 of the cylinder receptacle 21 and, above all, the latch 15 or the latch 17. 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 is the two tooth numbers larger than the number of teeth of 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 detected, only limited by the basic resolution accuracy of the absolute rotary encoder 33.

Between the toothed belt 29 and the motor 27, 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 block it. 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 the input element 23 is not prevented from moving by the motor 27 when the motor 27 is at a standstill, but for one 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 coupled for effective driving with the input element 23 of the cylinder receptacle 21 and above that with the bolt 15 or the latch 17. In this case, the input element 39 is at least essentially designed as a gearwheel with external toothing 43 and, in the manner of a worm wheel, engages directly with an output element 45 of the motor 27 designed as a worm, in order to receive a drive torque therefrom while the motor 27 is running.

The output element 41 of the freewheel gear 37 has, in the manner of a toothed wheel, an external toothing 47 on which the toothed belt 29 rolls. 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 takes place 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 making it possible to transmit the drive torque between the freewheel gear 37 and the cylinder receptacle 21 over a relatively large distance, without much space for this to claim in the door lock 11.

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.

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.

As especially in the exploded view of the Fig. 2 It can be seen that the input element 39 and the output element 41 of the freewheel gear 37 are arranged coaxially to one another and are mounted rotatably about the common axis of rotation D. On the one hand, there is a stationary in the (in 2 to 6 not shown) housing 13 arranged race 49, in which the input element 39 is rotatably held by an axial bearing portion 51. On the other hand, a short bearing shaft 53 is likewise arranged in a stationary 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 surface of which a drive contour 57 is formed. On an outer lateral surface of the output element 41 of the freewheel gear 37, an engagement contour 57 is formed axially adjacent to the external toothing 47. 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.

In the assembled state of the freewheel gear 37, 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 ).

Two coupling elements 63 designed as coupling pins and oriented parallel to the axis of rotation D are accommodated in this intermediate space 61. For each of these coupling elements 63, the drive contour 57 has a respective driving recess 65, which is characterized by a radius that is larger 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.

As a result, a coupling element 63 can be at least partially received in a driving recess 65 of the drive contour 57. The respective coupling element 63 is in principle still radially between a coupling position, which in this respect has a minimal radial distance between the coupling element 63 corresponds to the axis of rotation D, and a freewheeling position which in this respect corresponds to a maximum radial distance of the coupling element 63 from the axis of rotation D movably.

In the freewheeling position (shown in the figures), 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. In contrast, in the coupling position, the coupling element 63 engages in the engagement contour 59. In the embodiment shown, in which the engagement contour 59 is toothed, 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 in turn rotated about the axis of rotation D.

In this way, 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. For such a coupling, however, the coupling elements 63 must first be moved into the coupling position and then also held therein, since they would otherwise slide past the teeth of the engagement contour 59, especially since they are brought into the freewheeling position by two bow springs 67, that is to say in the direction of a greater radial distance are biased by 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 formed on an at least essentially static guide element 69 of the freewheel gear 37 71. The guide element 69 is designed as two guide disks 73, 73 'which are at least substantially 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.

Similar to the input element 39, the guide element 69 has a through opening 75, on the inner lateral surface of which the guide contour 71 is formed. In this case, parts of the guide contour 71 which are identical to one another are formed on the two guide disks 73, 73 'and are arranged in alignment 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. In particular, 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 reduced compared to a basic radius of the guide contour 71. The urging projections 77 consequently project radially in the direction of the axis of rotation D. In particular, 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, on the other hand, 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.

The 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. When the input element 39 is driven, 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.

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, meets 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 inevitably 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.

After the coupling element 63 has passed an urging projection 77, it preferably remains in the coupling position, in particular due to friction effects, as long as the input element 39 is driven, and thus further urging projections 77 can pass. 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.

If the input element 39 is no longer driven and is at a standstill, the coupling elements 63 are set into the freewheeling position by the clip springs. In this respect, 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 with the effect of the drive. 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.

Basically, situations are conceivable in which the input element 39 of the freewheel gear 37 comes to a standstill in such a way that the coupling elements 63 cannot be moved into the freewheel position despite the pretension by the bow springs 67. This can be the case in particular when the input element 39 just stops such that a respective urging projection 77 of the guide contour 71 is located in the area of a driving recess 65 of the drive contour 57. Such a condition is generally preferably avoided by the motor control, but cannot be ruled out in principle.

In order to enable a decoupling of the input element 39 and the output element 41 of the freewheel gear 37 from one another in such situations, 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. However, 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 guiding contour 71 far enough that the respective coupling element 63 moves past the urging projection 77 and in the release position is offset can be. 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.

Reference list

11

Door lock

13

casing

15

bars

17th

Cases

19th

Square mount

21

Cylinder mount

23

Input element of the cylinder holder

25th

Gear arrangement

27

Electric motor

29

Timing belt

31

Gearing

33

Absolute encoder

35, 35 '

gear

37

Freewheel gear

39

Input element of the freewheel gear

41

Output element of the freewheel gear

43

External teeth

45

Output element of the engine

47

External teeth

49

Race

51

Storage section

53

Bearing shaft

55

Through opening

57

Drive contour

59

Engagement contour

61

Space

63

Coupling element

65

Carrying deepening

67

Bow spring

69

Guide element

71

Guide contour

73, 73 '

Guide washer

75

Through opening

77

Jostling

79

Return spring

D

Axis of rotation

S

Swivel axis

Claims (6)

Door lock (11) with - A cylinder receptacle (21) for a locking cylinder, which has an input element (23), the input element (23) being designed to be driven by an output element of the locking cylinder, around a bolt (15) and / or a latch (17 ) to adjust the door lock (11), and a motor (27) in order to be able to adjust the bolt (15) and / or the latch (17) in a motorized manner in addition to the adjustability by means of the locking cylinder, characterized,
that the motor (27) can be operatively coupled to the input element (23) or coupled to the bolt (15) and / or the latch (17) regardless of whether a lock cylinder is accommodated in the cylinder receptacle (21) or not to adjust the input element (23) in a motorized manner. Door lock according to claim 1,
wherein the motor (27) can be coupled or coupled to the input element (23) in a drive-effective manner via a toothed belt (29). Door lock according to claim 2,
wherein the input element (23) of the cylinder receptacle (21) has a toothing (31) on which the toothed belt (29) rolls. Door lock according to claim 2 or 3,
which comprises a device (33) for detecting the rotational position of the toothed belt (29). Door lock according to claim 4,
The device for detecting the rotational position of the toothed belt (29) is formed by an absolute rotary encoder (33) with two toothed wheels (35, 35 '), on which the toothed belt (29) rolls and the number of teeth of which are different from one another, preferably by one . Door lock according to at least one of the preceding claims, wherein the motor (27) can be coupled or coupled to the input element (23) in a drive-effective manner via a freewheel gear (37).

Images