DE102019109639A9 - Operating gear for raising and lowering a lift and slide element and lift and slide element equipped with such an operating gear - Google Patents

Abstract

The present invention relates to an operating mechanism for raising and lowering a lift and slide element, which is displaceable along a guide rail and can be transferred from a lowered position, in which the lift and slide element is immovable, to a raised position, in which the lift and slide element is displaceable is. The actuating gear comprises an input shaft, which can be rotated by means of an actuating lever about an axis between a locking position corresponding to the lowered position and an unlocking position corresponding to the raised position, and a coupling element for drivingly coupling the input shaft to a connecting rod, which is drivingly coupled to a lifting element and which is attached to a Pivot point is eccentrically articulated to the input shaft. In its locked position, the input shaft is preloaded by the coupling element in such a way that it experiences a restoring moment acting in the direction of its locked position.

Description

The present invention relates to an operating mechanism for a lift and slide element, such as for a lift and slide door or a lift and slide window, which can be displaced along a guide rail and is transferred from a lowered position, in which the lift and slide element cannot be displaced, to a raised position in which the lift-slide element can be slid along the guide rail, the operating gear comprising an input shaft which, by means of an operating lever, rotates about an axis between a locking position corresponding to the lowered position of the lift-slide element and one corresponding to the raised position of the lift-slide element unlocking position is rotatable, and comprises a coupling element for drivingly effective coupling of the input shaft with a drivingly effective coupling with a lifting element for raising and lowering the lifting and sliding connecting rod, wherein the coupling element has an articulation point, ie e is eccentrically articulated to the input shaft.

The lifting element in question for raising and lowering the lifting and sliding element is usually what are known as carriages, which are arranged in a receptacle formed on the underside of the lifting and sliding element. These carriages have a raised position and a lowered position, where they stand up on the guide rail in the lowered position and thus transfer the weight of the lifting and sliding element to the guide rail. In the raised position, on the other hand, the carriages are no longer in contact with the guide rail or the carriages are not on the guide rail, so that the lifting and sliding element rests directly on the rail and transfers its weight directly to the same.

The carriages are actuated by rotating the input shaft of an actuating gear by means of an actuating lever, this rotational movement being transmitted to the carriages via the actuating gear and a connecting rod coupled thereto. When the carriages are lowered from their raised position to their lowered position, the actuating lever usually performs an idle stroke over an angle of about 40° until the rollers of the carriage stand up on the guide rail. During this idle stroke, no forces or only negligible frictional forces act on the carriages and thus on the actuating lever. Only when the actuating lever is pivoted further after the idle stroke does the weight of the lift and slide element rest on the carriages, so that from now on a larger actuating force or a larger actuating moment is required to lift the lift and slide element using the actuating lever.

As previously mentioned, the operating lever is essentially free of force during the idle stroke, which can result in it being inadvertently tilted if an operator inadvertently catches on the operating lever or inadvertently brushes against it. The risk of an unintentional misalignment of the actuating lever can also be increased, for example, by an actuating force reduction device such as a (gas pressure) spring, which counteracts the weight of the lifting and sliding element both during the lowering and during the raising of the lifting and sliding element. By means of such an actuating force reduction device, the actuating lever can, under certain circumstances, even execute an idle stroke without the action of an external force and thus become crooked in an undesired manner.

The invention is therefore based on the object of further developing an actuating gear of the type mentioned at the outset in such a way that no unintentional misalignment of the actuating lever can occur, in particular when using an actuating force reduction device.

Based on an actuating gear of the type mentioned above, this object is achieved by the features of claim 1 and in particular by the fact that the input shaft, which can be, for example, a square socket that can be coupled to an actuating lever, is preloaded in its locking position by the coupling element in this way that it experiences a return element acting in the direction of its locking position.

According to one aspect of the invention, the coupling element itself can act as a kind of restoring spring, at least in the locked position, by applying an elastic prestressing force to the input shaft, through which it experiences a torque that pushes it toward its locked position. The restoring torque applied by the coupling element can thus compensate for a torque acting on the input shaft, for example from an actuating force reduction device, which would otherwise rotate the input shaft in the direction of its unlocked position and thus cause the actuating lever to be misaligned, which means that unintentional misalignment of the actuating lever can be prevented.

Since the coupling element, via which the input shaft is drivingly connected to the connecting rod, according to the invention to a certain extent itself acts as a kind of return spring, no separate or additional return spring is required to urge the input shaft into its locked position.

Preferred embodiments of the invention will now be discussed below. Further embodiments can also result from the dependent claims, the description of the figures and the drawings themselves.

According to one embodiment, it can be provided that the restoring torque experienced by the input shaft decreases to a value of zero when it is deflected from its locked position in the direction of its unlocked position, and it can be provided in particular that the input shaft then rotates at a further Deflection in the direction of its unlocked position undergoes a torque acting in the direction of its unlocked position. In the same way, during a movement starting from its unlocked position in the direction of its locked position, shortly before reaching the locked position, the input shaft initially experiences a torque acting in the direction of its unlocked position, which, however, decreases to a value of zero as the movement of the input shaft progresses, before the input shaft begins to rotate in the direction of its Locked position acting restoring moment learns. So if the lift and slide element is lowered by means of the operating lever, the operator experiences a certain resistance on the operating lever shortly before reaching the locking position, which, however, decreases to a value of zero as the movement of the operating lever progresses, whereupon as the movement of the operating lever progresses in the direction of its Locked position on the input shaft and thus on the actuating lever, a restoring moment acts, through which the input shaft and thus the actuating lever is urged towards its locked position.

Similar to the swing-top closure of a beer bottle, the operator initially feels a certain resistance when closing or lowering the lift/slide element, which has to be overcome before the force conditions reverse from a switching point, with the result that from this Switching point the input shaft and thus the actuating lever is automatically urged or tensioned in the direction of her/his locking position. The actuating gear according to the invention thus makes use of a type of snap-over mechanism which causes the input shaft to be automatically pushed in the direction of its locking position from a switchover point when it moves in the direction of its locking position. This snap-over mechanism also provides the operator with tactile feedback, letting him know that the lift-and-slide element is properly locked.

According to a further embodiment, the actuating gear can comprise an abutment on which a contact section of the coupling element remote from the articulation point is supported in the locking position or against which the contact section is braced in the locking position of the input shaft. Because the coupling element is clamped against the abutment via its contact section, the coupling element serving as a restoring spring is preloaded when the input shaft is transferred from its unlocked position into its locked position. Thus, from the point of switching over, a restoring torque acts on the input shaft in the desired manner, so that the input shaft is urged in the direction of its locked position.

So that the coupling element can be clamped against the abutment in the desired manner to obtain its prestress, it can be provided according to a further embodiment that in the unlocked position the distance between the point of articulation of the coupling element and the contact section of the same is smaller than in the locked position between the pivot point and the abutment. In other words, the distance between the articulation point of the coupling element and the contact section of the coupling element in the force-free state of the coupling element is smaller than the distance between the articulation point and the abutment in the locking position. Accordingly, the coupling element is elastically deformed and in particular stretched when the input shaft is transferred from its unlocked position to its locked position, so that in the locked state the distance between the articulation point of the coupling element and the contact section is just as large as in the locked position the distance between the Pivot point and the abutment.

According to a further embodiment, when the input shaft is in the locked position, the point of articulation of the coupling element, at which it is connected in an articulated manner to the input shaft, can be located on a first side of a first plane containing the axis of the input shaft and the abutment, with a deflection of the input shaft their locked position in the direction of their unlocked position, the pivot point on the other or second side of the first level arrives, on which there is also a free end of the coupling element that can be coupled to the drive rod, regardless of the position of the input shaft. The switching point of the snapping mechanism according to the invention is defined by the first level, since as long as the pivot point is on the first side of the first level, the preload of the coupling element has a force component, by which the input shaft is pushed in the direction of its locking position, whereas the preload of the Coupling element located on the second side of the first plane articulation point has a force component through which the input shaft is urged towards its unlocked position.

As already mentioned above, the coupling element is prestressed when it comes into contact with the abutment as part of the movement of the input shaft, starting from its unlocked position in the direction of its locked position. Correspondingly, when the input shaft is deflected from its locked position in the direction of its unlocked position, the coupling element undergoes an increasing elastic deformation up to a maximum value, with this elastic deformation then decreasing from its maximum value again, preferably, when the input shaft is deflected further in the direction of its unlocked position to a value of zero. Conversely, when the input shaft moves in the direction of its unlocked position, the elastic deformation of the coupling element initially increases to a maximum value near the switching point, whereupon the elastic deformation decreases again when the input shaft continues to move in the direction of its locked position, preferably to a value of zero. In the locked position of the input shaft, the coupling element is thus more or less free of stretching and thus free of stress, as a result of which fatigue fracture of the coupling element can be prevented.

According to a further embodiment, when the input shaft is in the locking position, the articulation point of the coupling element, at which it is articulated to the input shaft, can be located on one side of a second plane containing the axis of the input shaft, which is perpendicular to the abutment and the axis of the input shaft connecting straight lines, whereas the abutment is on the other side of the second level, on which the pivot point is also located in the unlocked position of the input shaft. In the locking point of the input shaft, the articulation point is located on the other side of the input shaft than the abutment, so to speak, which means that the input shaft is to a certain extent encompassed by the coupling element in the locking position.

Accordingly, according to a specific embodiment of the coupling element, it can be provided that it has a head section and a foot section, the head section being essentially T-shaped with a flange section and a web section which ends bluntly at the flange section, and the foot section having an im Has a substantially J-shape with a web section and an adjoining arc section. The curved section forms the articulation point of the coupling element, a first end of the flange section forms the contact section of the coupling element and a second end of the flange section forms a free end of the coupling element that can be coupled to the connecting rod. The web section of the head section transitions into the web section of the foot section of the coupling element or coincides with it, so that the coupling element, viewed globally, has a shape that essentially corresponds to the shape of the small Greek letter “τ”.

According to yet another embodiment, the coupling element can have a bracket section with a substantially U-shaped configuration, one end of the bracket section forming the contact section of the coupling element and the other end forming the articulation point of the same. In the embodiment described above, in which the coupling element essentially has the shape of the small Greek letter "τ", the strap section is thus formed by the web of the head section and the foot section and by the first end of the flange section and the arc section of the foot section. In the locking position, the bracket section thus encompasses the input shaft and the abutment, so that the two ends of the bracket section are elastically spread apart.

According to yet another embodiment, the actuating gear can comprise a connecting rod which is coupled in a drivingly effective manner to a lifting element such as a carriage, to which the coupling element is connected in an articulated manner, it being preferably provided that the coupling element is detachably connected to the connecting rod, in particular in such a way that the connecting rod is hooked in such a way that both longitudinal and transverse forces can be transmitted from the connecting rod to the coupling element. The coupling element is thus captively and articulatedly coupled to the drive rod, so that no additional guidance is required due to the articulated connection of the coupling element to the drive rod on the one hand and the input shaft on the other. by which the coupling element can be prevented from being disengaged from the connecting rod when the input shaft is rotated.

According to the above statements, the restoring moment acting on the input shaft or the function of the snapping mechanism described can be attributed to the elastic deformation of the coupling element according to one aspect of the invention. According to another aspect, the desired restoring moment can also be brought about by an actuating force reduction device such as a gas pressure spring or a helical spring, which is drivingly coupled to the connecting rod and which counteracts the weight of the lifting and sliding element both during the lowering and during the raising of the lifting and sliding element.

To be more precise, the actuating gear can comprise at least one actuating force reduction device which is drivingly coupled to the connecting rod and by means of which the input shaft is pretensioned in its locking position via the connecting rod and the coupling element in the direction of its locking position. The leverage for generating the desired restoring moment is thus generated indirectly by the actuating force reduction device and cannot be attributed to an elastic deformation of the coupling element.

According to a further embodiment, it can be provided that when the input shaft is in the locked position, the coupling element is acted upon by the actuating force reduction device via the drive rod with a restoring force, as a result of which the coupling element experiences a torque that prestresses the input shaft in the direction of its locking position and thus desired restoring moment experiences. In other words, the restoring force of the actuating force reduction device causes the coupling element to experience a torque, which in turn is responsible for the fact that a force acts on the eccentric cam of the input shaft, to which the coupling element is articulated, by which the input shaft moves in the direction of its locked position is biased. The actuating force reduction device is thus functionally coupled to the input shaft via the drive rod and the coupling element in such a way that the latter is indirectly prestressed in the direction of its locking position by the restoring force of the actuating force reduction device.

According to a further embodiment, the connection point between the drive rod and the coupling element can be designed in such a way that the restoring force with which the coupling element is acted upon in the locked position of the input shaft is converted into the torque by which the input shaft is prestressed in the direction of its locked position. For this purpose, the drive rod can have an opening which has a first edge section and a second edge section which is spaced from the first edge section in the longitudinal direction of the drive rod, with a free end of the coupling element extending through the opening between the two edge sections. When the input shaft is in the locked position, the free end of the coupling element makes contact with the first edge section at a first edge, which the first edge section forms together with a first surface of the connecting rod. Likewise, the free end of the coupling element contacts the second edge portion at a second edge that the second edge portion forms together with a second face of the drive rod that is opposite to the first face of the drive rod. The second surface of the connecting rod thus forms the surface of the connecting rod opposite the first surface of the connecting rod. The coupling element thus contacts the two edge sections of the drive rod opening on opposite sides of the drive rod.

Therefore, if the restoring or prestressing force of the actuating force reduction device has a value F ₀ and the thickness of the connecting rod is _t , this results in a torque MA acting on the coupling element by multiplying the prestressing force F ₀ by the connecting rod thickness t. In accordance with the above statements, this torque M _A in turn causes a force on the eccentric cam of the input shaft, as a result of which it experiences the desired restoring moment in the desired manner, by which it is prestressed into its locking position.

In order to ensure that the coupling element contacts the first and second edge sections in the manner described above in the area of opposite sides of the drive rod, it can be provided according to a further embodiment that the first edge section and/or the second edge section is opposite to the horizontal inclined surface forms. In addition or as an alternative to this, it can be provided that the surface(s) of the free end of the coupling element contacting the first and/or the second edge section is/are inclined with respect to the horizontal in the locking position of the input shaft.

The angle of inclination of the first edge section and/or the second edge section can be, for example, between 5 and 30° and preferably between 7 and 25°. Likewise, the angle of inclination of the at least one contacting surface of the free end of the coupling element can be between -5 and -30°, preferably between -7 and -25°. If both the edge sections and the contacting surfaces of the free end of the coupling element are inclined with respect to the horizontal, the angles of inclination of the edge sections must be inclined in the opposite direction to the contacting surfaces of the free end of the coupling element, since otherwise the inclination of the edge sections and could at least partially compensate for the contacting surfaces.

According to yet another embodiment, the coupling element can have an essentially ∫-shaped or essentially integral sign-shaped form, with at least one of the angled end sections together with the section connecting the two end sections forming an angle between 95° and 120°, preferably between 97 and 115°, includes.

• 1 eine schematische Darstellung eines Hebe-Schiebeelements mit einer Betätigungskraftreduzierungseinrichtung zeigt;
• 2 eine Schnittdarstellung durch einen Getriebekasten mit einem erfindungsgemäßen Betätigungsgetriebe zum Anheben und Absenken eines Hebe-Schiebeelements in einer ersten Stellung gemäß einer ersten beispielhaften Ausführungsform zeigt;
• 3 das Betätigungsgetriebe der 2 in einer zweiten Stellung zeigt, in der sich die Eingangswelle in ihrer Verriegelungsstellung befindet;
• 4 eine schematische Darstellung der auf die Eingangswelle der Ausführungsform gemäß den 2 und 3 wirkenden Kräfte in unterschiedlichen Drehstellungen zeigt; und
• 5 eine Schnittdarstellung durch einen Getriebekasten mit einem erfindungsgemäßen Betätigungsgetriebe zum Anheben und Absenken eines Hebe-Schiebeelements gemäß einer zweiten beispielhaften Ausführungsform zeigt.

The invention is described in more detail below using an exemplary embodiment with reference to the drawings, in which:

• 1 shows a schematic representation of a lift and slide element with an actuating force reduction device;
• 2 shows a sectional view through a gear box with an actuating gear according to the invention for raising and lowering a lift and slide element in a first position according to a first exemplary embodiment;
• 3 the actuating gear 2 in a second position in which the input shaft is in its locked position;
• 4 a schematic representation of the input shaft of the embodiment according to the 2 and 3 forces acting in different rotational positions; and
• 5 shows a sectional view through a gear box with an actuating gear according to the invention for raising and lowering a lift and slide element according to a second exemplary embodiment.

the 1 shows a schematic view of a lifting and sliding element 19 according to the invention, which can be displaced in the horizontal direction along a floor-side guide rail, not shown here. For this purpose, the lift and slide element 19 has two carriages 25 on its underside, which are arranged in a receiving section 21 in the form of a groove which is formed in the underside of a lower frame part 22 of the frame of the lift and slide element 19 .

The lift-slide member 19 has a lowered position and a raised position, and it cannot be slid in the lowered position unlike in the raised position. In order to be able to transfer the lift-and-slide element 19 between the lowered position and the raised position, the lift-and-slide element 19 has a lifting device denoted overall by the reference symbol “10”, by means of which the lift-and-slide element 19 can be selectively raised and lowered.

The lifting device 10 in question comprises an actuating lever 27 on a lateral frame part 23 of the lifting and sliding element 19, two lifting elements in the form of the two carriages 25 for raising and lowering the lifting and sliding element 19 and a transmission gear via which the two lifting elements in the form of the two carriages 25 are drivingly coupled to the operating lever 27 . The transmission gear comprises in particular a first connecting rod 26, which is drivingly coupled to the actuating lever 27 via an actuating gear 100, a second connecting rod 29, which is drivingly coupled to the two carriages 25, and a deflection device 32 in the form of a deflection gear, for example, via which the two connecting rods 26, 29 are in turn coupled to one another in the corner region of the frame of the lifting and sliding element 19 in a drivingly effective manner. By pivoting the actuating lever 27, starting from its locking position 27' shown in dashed lines, in which the lift-and-slide element 19 is in its lowered position, according to the arrow 28 into its open or unlocked position 27", the lift-and-slide element 19 can thus be both carriages 25 are raised in order to be able to move it along the guide rail, not shown.

The first connecting rod 26 runs in a receiving section 20 designed as a groove, which is designed in the lateral frame part 23 of the lift and slide element, whereas the second connecting rod 29 runs in the receiving section 21 designed in the underside of the frame of the lift and slide element 19, which also for receiving the two carriages 25 is used. The two receiving sections 20, 21, within which the two connecting rods 26, 29 are arranged, are thereby closed by a first and a second cover rail 34, 36, along which the respective connecting rods 26, 29 are slidably guided. however, the second faceplate 36 is not absolutely necessary since the lower receiving section 21 cannot be seen.

As the representation of 1 can also be removed, the fitting assembly also has a in the 1 actuation force reduction device 40 shown only schematically, which is here a gas pressure spring 40, although it can also be, for example, a coil spring or other preloading element. The actuating force reduction device 40 is coupled to the first connecting rod 26 on the one hand and to the first faceplate 34 on the other hand. In addition or as an alternative to this, the fitting arrangement can also include a second actuating force reduction device 42 which is coupled to the second drive rod 29 on the one hand and to the second faceplate 36 on the other hand. This actuating force reduction device 42 is also a gas pressure spring 42, although it can also be a coil spring or another preloading element, for example. The two gas pressure springs 40, 42 are each located behind the respective faceplate 34, 36 and the respective associated drive rod 26, 29 in the respective receiving section 20, 21 and are therefore not visible from the outside.

Since the gas pressure spring 40 or the gas pressure springs 40, 42 are thus coupled on the one hand with the respective connecting rod 26, 29 and on the other hand with the respectively associated faceplate 34, 36, which are fixedly attached to the lifting and sliding element 19, the respective gas pressure spring 40, 42 is thus increasingly prestressed when lowering the lifting and sliding element 19 and is increasingly relieved when it is raised. Because the respective gas pressure spring 40, 42 is coupled to the respective connecting rod 26, 29, it absorbs at least part of the potential energy of the lift/slide element 19 that is released when the lift/slide element 19 is lowered and stores it temporarily, in order to be able to give them back to the lifting and sliding element 19 when it is subsequently raised. The respective gas pressure spring 40, 42 is thus loaded when the lifting/sliding element 19 is lowered and consequently applies an increasingly increasing force to the respective connecting rod 26, 29 which opposes the direction of movement of the respective connecting rod 26, 29 when it is lowered. Thus, the holding force to be applied by means of the actuating lever 27 is reduced when lowering compared to the case without using a fitting arrangement according to the invention, so that the risk of the actuating lever 27 snapping upwards in the direction of its locking position is reduced.

If the operating lever 27, however, starting from its in the 1 shown locked position 27 'in the open or unlocked position 27 "according to the arrow 28 is pivoted downwards in order to be able to lift the carriages 25 and thus the lifting and sliding element 19, the force required for this is compared to the case without using an inventive Fitting arrangement is reduced, since part of the weight of the lift and slide element 19 that is to be lifted does not have to be applied via the actuating lever 27, but rather is made available as a counterforce by the gas pressure springs 40, 42. This is how the load is discharged during the lowering of the lift and slide element 19 Energy stored temporarily in the gas pressure springs 40, 42 when lifting the lifting and sliding element 19, with a force acting in the direction of movement of the respective connecting rod 26, 29 being applied to the same, making lifting easier Gas springs 40, 42 supports, so that less power to Pressing the lever 27 must be applied. However, since the actuating lever 27 initially performs an idle stroke when pivoting, starting from its locked position, until the carriages 25 stand up on the guide rail, there is a risk that the actuating lever 27 will be pushed in the direction of its unlocked position by the actuating force reduction device in the form of the gas pressure springs 40, 42 and is therefore easily skewed.

In order to prevent such a misalignment of the actuating lever 27, according to the invention in the embodiment according to FIG 2 until 4 A kind of snap-over mechanism is integrated into the actuating gear 100, by means of which it can be achieved that the input shaft 101 experiences a restoring moment in the region of its locked position, by which it is urged in the direction of its locked position. An embodiment of such a switching mechanism is described below with reference to FIG 2 and 3 explained in more detail.

the 2 shows a first embodiment of an actuating mechanism 100 according to the invention in a position in which the actuating lever 27 has been pivoted from its vertically aligned locking position by about 45° clockwise in the direction of its unlocking position. The actuating lever 27 has a square mandrel 102 which positively engages with a square nut 104 which is rotatably mounted inside a gear box 106 and forms the input shaft 101 of the actuating gear 100 . An eccentric cam 108 is formed on the square nut 104, on which the pivot point 112 of a coupling element 110 is articulated, which creates a driving connection between the input shaft 101 of the actuating gear in the form of the square nut 104 and the drive rod 26, which in turn is in turn in the above described manner is drivingly coupled to the carriages 25 of the lifting and sliding element 19. The coupling element 110 is connected in an articulated manner to the drive rod 26 , for which purpose it is hooked into the drive rod 26 or a corresponding opening in it such that both longitudinal and transverse forces can be transmitted from the drive rod to the coupling element 110 . The coupling element 110 is thus captively hooked into the connecting rod 26 so that no additional guide has to be provided to prevent the coupling element 110 from being able to detach from the connecting rod 26 when it is pivoted about its pivot point 112 .

Since the coupling element 110 is thus coupled to the drive rod 26 on the one hand and to the input shaft 101 or the square nut 104 on the other hand, due to the eccentric articulation of the coupling element 110 on the square nut 104, a rotary movement of the same is converted into a longitudinal movement of the drive rod 26, as is the case for Raising and lowering the carriage 25 is required.

However, since the gas pressure springs 40, 42 as an actuating force reduction device bias the connecting rod 26 upwards, there is a risk that the actuating lever 27, starting from its vertically upwardly aligned locking position, will move in the direction of its Unlocked position is pivoted and thus slightly tilted. In order to counteract such an inclined position of the actuating lever 27, according to the invention a type of snap-over mechanism is integrated into the actuating gear 100, by means of which such an inclined position can be prevented.

In order to implement this snapping action, the actuating gear 100 comprises an abutment 114 in the form of a bolt, for example, which is fastened to the gear box 106 and extends between the two opposite walls of the gear box 106 . In the locking position, the coupling element 110 is supported on this abutment 114 with a contact section 116 located at a distance from the articulation point 112, as a result of which the coupling element 110 is elastically stretched and thus prestressed. The coupling element 110 itself thus acts as a type of restoring spring by which the input shaft 101 is urged in the direction of its locked position, as will be explained in more detail below.

In the embodiment shown here, the coupling element 110 has a head section 118 with a substantially T-shaped configuration and a foot section 120 with a substantially J-shaped configuration. The essentially T-shaped head section 118 has a flange section 122 and a web section 124 which, in the embodiment shown here, is aligned essentially perpendicularly to the flange section 122 and ends bluntly thereon. The essentially J-shaped foot section 120 also has a web section 126 and an adjoining curved section 128 at which the articulation point 112 of the coupling element 110 is located, at which it is articulated to the input shaft 101 or the eccentric cam 108 of the square nut 104 is. The web section 124 of the head section 118 merges into the web section 126 of the foot section 120, so that the coupling element 110, viewed globally, has a shape that essentially corresponds to the shape of the small Greek letter “τ”. The flange section 122 has two free ends 130, 132, with the first end 130 forming the contact section 116 of the coupling element, which is designed to be braced against the abutment 114 in the locking position of the input shaft 101, cf 3 . The second end 132 of the flange section 122, on the other hand, has a notch 134, which makes it possible to hook the head section 118 and in particular the second end 132 of the flange section 122 into the drive rod 26, so that, viewed in the horizontal direction, a form-fitting connection between the drive rod 26 and the Head portion 118 of the coupling element 110 is given.

Like the 2 and 3 can be removed, the abutment 114 is offset slightly to the right with respect to a vertical line through the axis A of the input shaft 101 . In the locked position of the input shaft 101 according to 3 articulation point 112 is thus located on a first side of a first plane E containing axis A of input shaft 101 and abutment 114, whereas articulation point 112 of coupling element 110 is located when input shaft 101 is deflected out of its locked position in the direction of its unlocked position 2 reaches the first side of the first level E opposite the second side of the first level E.

Since the switching point of the snapping mechanism according to the invention is defined by the first plane E in question, the prestressing force acting in the coupling element 110 in the locking position causes a restoring moment, which pushes the input shaft 110 towards its locking position. If, on the other hand, the articulation point 112 is on the second side of the first plane E in question, the effect of the snap-over mechanism is reversed nism to, so that then acts on the input shaft 101 acting in the direction of its unlocked torque torque. The restoring torque experienced by the input shaft 101 thus decreases to a value of zero when the input shaft 101 is deflected from the locked position in the direction of its unlocked position up to the switching point and then reverses, as a result of which the input shaft 101 then acts in the direction of its unlocked position experiences torque. If one looks at the reverse sequence of movements, a torque acting in the direction of the unlocking position builds up, which then changes into a restoring moment when the switching point is reached, by which the input shaft 101 is pushed in the direction of its locking position. In the locking position, the web section 126 of the foot section 120 then engages in a slot formed on the circumference of the square nut 104 and rests against the square mandrel 102 of the lever 27, as a result of which further rotation of the input shaft 101 is prevented.

So that a preload can build up in the desired manner in the coupling element 110 when its contact section 116 comes into contact with the abutment 114 when the input shaft 101 moves in the direction of its locking position, the distance between the pivot point is in the unlocked position or when the coupling element is unloaded 112 of the coupling element 110 and the contact section 116 is slightly smaller than the distance between the pivot point 112 and the abutment 114 in the locking position. The consequence of this is that the coupling element 110 and in particular its U-shaped bracket section, which extends from the contact section 116 via the web sections 126, 128 to the arc section 128, is spread apart and thus elastically deformed when the input shaft 101 leaves its unlocked position rotated to its locked position. The coupling element 110 is prestressed in this way and thus acts as a kind of restoring spring, so that no additional or separate restoring spring is required to generate the desired restoring effect.

• In der 4 ist die erste Ebene E eingezeichnet, die die Achse A der Eingangswelle 101 und das Widerlager 114 enthält und durch die der Umschaltpunkt des Umschnappmechanismus definiert wird. Befindet sich die Anlenkstelle 112 rechts bzw. auf der ersten Seite der ersten Ebene E, so wirkt auf diese aufgrund der in dem Koppelelement 110 herrschenden Vorspannung eine Kraft F_Koppel, die in Richtung des Widerlagers 114 wirkt. Diese Kraft F_Koppel lässt sich in eine radial wirkende Kraftkomponente F_Koppel,rad und eine tangential wirkende Kraftkomponente F_Koppel,tang zerlegen, wobei letztere ein Dreh- bzw. Rückstellmoment M_rück bewirkt, durch das die Eingangswelle 101 in Richtung ihrer Verriegelungsstellung gedrängt wird.

Referring to the 4 the forces and torques that bring about the snapping effect according to the invention are now explained:

• In the 4 the first plane E is drawn in, which contains the axis A of the input shaft 101 and the abutment 114 and through which the switching point of the snap-over mechanism is defined. If the articulation point 112 is on the right or on the first side of the first plane E, a force F _Koppel acting in the direction of the abutment 114 acts on it due to the prestress prevailing in the coupling element 110 . This force F _coupler can be broken down into a radially acting force component F _coupler,rad and a tangentially acting force component F _coupler,tang , the latter causing a turning or restoring moment _Mback , which pushes the input shaft 101 toward its locked position.

If the input shaft 101 is now rotated clockwise in the direction of its unlocked position, the tangentially acting force component F _{coupling,tang} decreases to a value of zero. If the input shaft is then rotated further in a clockwise direction, the pretensioning force F _{coupling element} can again be broken down into two force components F _{coupling, wheel} and F _{coupling, tang} , which are aligned perpendicularly to one another, with the latter now causing a torque M to _unlock , as a result of which the input shaft 101 rotates in the direction of its Unlocking position is pushed.

The following will now refer to the 5 a second embodiment of an actuating gear according to the invention 100 'is described. The actuating gear 100 ′ of the second embodiment is similar in many respects to the actuating gear 100 of the first embodiment, which is why mainly only the essential differences compared to the actuating gear 100 of the first embodiment will be discussed below.

At the in the 5 The actuating gear 100' shown is the actuating lever 27, shown here only in broken lines, in its locking position 27'. Here, too, the locking lever 27 has a square mandrel 102 which positively engages with a square nut 104 which is rotatably mounted inside a gear box 106 and forms the input shaft 101 of the actuating gear 100'.

An eccentric cam 108 is formed on the square nut 104, on which a coupling element 110' is articulated at a pivot point 112, so that the coupling element 110' creates a driving connection between the input shaft 101 of the actuating gear 100' in the form of the square nut 104 and the connecting rod 26 , which in turn is drivingly coupled to the carriages 25 of the lever-sliding element 19 in the manner described above. The coupling element 110' is articulated to the drive rod 26, for which purpose it is hooked into the drive rod 26 or a corresponding opening 142 in it such that both longitudinal and transverse forces can be transmitted from the drive rod 26 to the coupling element 110'. The coupling element 110 'is thus captive in the drive hooked into the rod 26, so that no additional guide has to be provided to prevent the coupling element 110' from being able to detach from the drive rod 26 when it is pivoted about its pivot point 112 on the input shaft 101.

Since the coupling element 110' is thus coupled to the drive rod 26 on the one hand and to the input shaft 101 or the square nut 104 on the other hand, due to the eccentric articulation of the coupling element 110' on the square nut 104, a rotary movement of the same is converted into a longitudinal movement of the drive rod 26, such as this is required for raising and lowering the carriages 25.

Since the gas pressure springs 40, 42 as operating force reducing means bias the connecting rod 26 upwards, the operating lever 24 tends to rotate clockwise towards its unlocked position, whereby the lifting of the lift-and-slide element 19 is facilitated.

In order to prevent the actuating lever 27 from being pivoted from its illustrated locking position 27' into its unlocking position due to the prestressing effect of the gas pressure springs 40, 42, in this embodiment of the actuating gear 100' the connection point between the connecting rod 26 and the coupling element 110' specially designed so that the restoring force F ₀ , with which the coupling element 110' in the locked position 27' of the input shaft 101 is acted upon via the connecting rod 26 by the gas pressure spring 40 or by the gas pressure spring 42 as an actuating force reduction device, is converted into a torque M _A by that the input shaft 101 is biased toward its locked position. More precisely, the articulation point 112, at which the coupling element 110' is coupled to the eccentric cam 108 of the input shaft 101, experiences a force, referred to here as F _stop , which is shown in FIG 5 acts to the right, whereby the input shaft 101 and thus the operating lever 27 is biased towards its locking position 27 '.

As illustrated, the free end 140 of the coupling element 110' is hooked into a slot opening 142 formed in the drive rod 26 and bounded in the vertical direction by a lower or first edge section 144 and an upper or second edge section 146. The free end 140 of the coupling element 110 ′ has a notch 134 in which the second edge section 146 of the opening 142 comes to rest when the free end 140 is hooked into the drive rod 26 . In this regard, viewed in the horizontal direction, there is a form-fitting connection between the connecting rod 26 and the free end 140 of the coupling element 110'.

Once again 5 can also be seen, the two edge portions 144, 146 of the opening 142 are aligned substantially horizontally. In contrast, the lower surface 162 of the free end 140 of the coupling element 110', which contacts the first edge section 144, is inclined with respect to the horizontal.

The result of this is that the free end 140 of the coupling element 110' on its underside 162 contacts the first edge section 144 only at the illustrated contact point B and thus at a first edge 148, which the first edge section 144 together with the surface 152 of the drive rod 26 forms that faces the gear box 106 . Since the coupling element 110' is articulated at the articulation point 112 on the input shaft 101, the coupling element 110' rotates slightly clockwise due to the prestressing force F ₀ from the actuating force reduction device 40, 42. The groove base 156 of the indentation 134 at the free end 140 of the coupling element 110' is thus also slightly inclined relative to the horizontal. This in turn has the consequence that the free end 140 of the coupling element 110' and in particular the groove base 156 contacts the second edge section 146 only at the illustrated pivot point A _K and thus at a second edge 150, which the second edge section 146 together with that of the surface 152 of the drive rod 26 opposite second surface 154 of the drive rod 26 is formed, which faces away from the gear box 106.

Because the contact point B, at which the preload force F ₀ acts, is offset relative to the pivot point A _K by the thickness t of the drive rod 26, the coupling element 110' experiences the offset or preload torque M _A shown, which in turn is in the manner already described above, the force F causes a _stop on the pivot point 112, by means of which the input shaft 101 is pretensioned in the desired manner in the direction of its locking position 27'.

When referring to the 5 described embodiment, the underside 162 of the free end 140 of the coupling element 110 'inclined to the horizontal, whereas the two edge portions 144, 146 of the opening 142 are aligned substantially horizontally. Alternatively or additionally, however, the two edge sections 144, 146 can also be inclined relative to the horizontal in order to ensure that the contact point B, at which the prestressing force F ₀ acts on the coupling element 110', and the pivot point A _K through the thickness t of the drive rod 26 of each other are spaced. For example, the angle of inclination of the first edge section 144 and/or the second edge section 146 can be between 5° and 30°, preferably between 7° and 25°. In addition or as an alternative to this, the angle of inclination of the groove base 156 and/or the lower surface 162, with which the coupling element 110' contacts the first edge 144 of the opening 142, can be between -5° and -30°, preferably between -7° and - 25°. As can be seen from the different signs of the angles given above, the edge sections 144, 146 are to be inclined in the opposite direction to the corresponding surfaces at the free end 140 of the coupling element 110', in order to prevent the edge sections 144, 146 from not fully contacting the free end 140 of the coupling element 110', since in this case the prestressing torque M _A could not develop.

In the embodiment shown here, the coupling element 110' has an essentially ∫-shaped or essentially integral sign-shaped form, the free end 140 together with the connecting section 158 connecting the free end 140 to the end of the Coupling element 110 'connects, encloses an angle between 95 ° and 120 °, preferably between 97 ° and 115 °. The underside 162 of the free end 140 is thus inclined with respect to the horizontal between 5° and 30°, preferably between 7° and 25° with respect to the horizontal, as has already been explained above.

Once again 5 Furthermore, as can be seen, the lower surface 162 of the free end 140 of the coupling element 110 ′ contacting the first edge section 144 of the opening 142 has an indentation 160 outside and adjacent to the opening 142 . This indentation 160 ensures that the underside 162 of the free end 140 of the coupling element 110' does not collide with the first edge section 144 of the opening 142 when the actuating lever 27 is rotated clockwise, which causes the coupling element 110' to rotate about the pivot point A _K results.

Reference List

10

lifting device

19

lift and slide element

20

recording section

21

recording section

22

lower frame part

23

side frame part

25

trolley

26

first connecting rod

27

operating lever

27'

locked position

27"

open position

28

Arrow

29

second connecting rod

32

deflection

34

first faceplate

36

second faceplate

40

first gas spring, actuating force reduction device

42

second gas pressure spring, actuating force reduction device

100

actuating gear

100'

actuating gear

101

input shaft

102

square mandrel

104

square nut

106

gearbox

108

eccentric cam

110

coupling element

110'

coupling element

112

pivot point

114

abutment, bolt

116

contact section

118

head section

120

foot section

122

flange section

124

Web section of 118

126

Web section of 120

128

arc section

130

First end of 122

132

Second end of 122

134

notch

140

Free end of 110

142

opening in 26

144

First or lower border section

146

Second or upper edge section

148

First edge

150

second edge

152

First face

154

second face

156

groove bottom

158

connection section

160

indentation

162

lower surface 162 of 140

A

axis

AK

pivot point

B

touchpoint

E

first floor

F0

preload force

MA

preload torque

Claims (21)

Operating gear (100, 100') for raising and lowering a lift and slide element (19), such as a lift and slide door or a lift and slide window, which is displaceable along a guide rail and from a lowered position in which the lift and slide element (19 ) is immovable, can be transferred to a raised position in which the lifting and sliding element (19) can be moved, the actuating gear (100) having an input shaft (101) which, by means of an actuating lever (27), rotates about an axis (A) between a a locking position (27') corresponding to the lowered position of the lifting and sliding element (19) and an unlocking position corresponding to the raised position of the lifting and sliding element (19), and a coupling element (110) for drivingly coupling the input shaft (101) to a drivingly effective with a lifting element (25) coupled connecting rod (26) which at a pivot point (112) eccentrically articulated with the input shaft (101). ig connected; the input shaft (101) being preloaded in its locking position (27') by the coupling element (110) in such a way that the input shaft (101) experiences a restoring moment (M _back ) acting in the direction of its locking position (27'). Actuating gear (100) after claim 1 , characterized in that the restoring torque (M _back ) experienced by the input shaft (101) decreases to a value of zero when it is deflected from its locked position (27') in the direction of its unlocked position. Actuating gear (100) after claim 2 , characterized in that the input shaft (101) experiences a further deflection of the input shaft (101) in the direction of its unlocking position acting in the direction of its unlocking torque torque (M _unlock ). Actuating gear (100) according to at least one of the preceding claims, characterized in that the actuating gear (100) comprises an abutment (114) on which a contact section (116) of the coupling element (110) remote from the articulation point (112) rests in the locked position (27'). Actuating gear (100) after claim 4 , characterized in that in the unlocked position the distance between the articulation point (112) of the coupling element (110) and the contact section (116) is smaller than in the locking position (27') the distance between the articulation point (112) and the abutment (114 ). Actuating gear (100) after claim 4 or 5 , characterized in that in the locking position (27') of the input shaft (101), the pivot point (112), at which the coupling element (110) is articulated to the input shaft (101), is on a first side of an axis (A ) of the input shaft (101) and the first plane (E) containing the abutment (114), wherein when the input shaft (101) is deflected from its locked position (27') in the direction of its unlocked position, the articulation point (112) moves to the second side of the first level (E), it being provided, in particular, that a free end (132) of the coupling element (110) that can be coupled to the connecting rod (26) is also located on the second side of the first level (E). Actuating gear (100) according to at least one of the preceding claims, characterized in that the coupling element (110) experiences an increasing elastic deformation up to a maximum value when the input shaft (101) is deflected from its locked position (27') in the direction of its unlocked position. Actuating gear (100) after claim 7 , characterized in that with a further deflection of the input shaft (101) in the direction of its unlocked position, the elastic deformation of the coupling element (110) decreases from its maximum value again, preferably to a value of zero. Actuating gear (100) according to at least one of Claims 4 until 8th , characterized in that in the locking position (27') of the input shaft (101) the pivot point (112) at which the coupling element (110) is articulated to the input shaft (101) is on one side of the axis (A) the input shaft (101) containing the second plane is perpendicular to a the abutment (114) and the axis (A) of the input shaft (101) connecting straight line, whereas the abutment (114) on the other Ren side of the second level is, it being provided in particular that in the unlocked position of the input shaft (101) and the pivot point (112) is on the other side of the second level. Actuating gear (100) according to at least one of Claims 4 until 9 , characterized in that the coupling element (110) comprises a head portion (118) and a foot portion (120), wherein the head portion (118) has a T-shape with a flange portion (122) and a web portion (124) which butt ends with the flange section (122), and the foot section (120) has a J-shape with a web section (126) and an adjoining arc section (128), the arc section (128) being the articulation point (112) of the coupling element (110 ), a first end (130) of the flange section (122) the contact section (116) of the coupling element (110) and a second end (132) of the flange section (122) with the connecting rod (26) coupled free end of the coupling element (110) form. Actuating gear (100) according to at least one of Claims 5 until 10 , characterized in that the coupling element (110) has a bracket section with a U-shape, one end of which forms the contact section (116) of the coupling element (110) and the other end forms the articulation point (112) of the coupling element (110). Actuating gear (100) after claim 11 , characterized in that the bracket section in the locking position (27 ') encompasses the input shaft (101) and the abutment (114), the two ends of the bracket section being elastically pressed apart. Actuating gear (100) according to at least one of the preceding claims, characterized in that the actuating gear (100) comprises a connecting rod (26) which is operatively coupled to a lifting element (25) and to which the coupling element (110) is articulated, it being preferably provided is that the coupling element (110) is detachably connected to the drive rod (26), in particular hooked into it in such a way that both longitudinal and transverse forces can be transmitted from the drive rod (26) to the coupling element (110). actuating gear (100'). Claim 13 , characterized in that the actuating gear (100') further comprises at least one actuating force reduction device (40, 42) by which the input shaft (101) in its locked position (27') via the connecting rod (26) and the coupling element (110') in Is biased towards its locking position (27 '). actuating gear (100'). Claim 14 , characterized in that in the locking position (27') of the input shaft (101), the coupling element (110') is acted upon by the actuating force reduction device (40, 42) via the connecting rod (26) with a restoring force (F ₀ ), as a result of which the Coupling element (110 ') experiences a torque (M _A ) by which the input shaft (101) in the direction of its locked position (27') is biased. actuating gear (100'). Claim 14 or 15 , characterized in that the connection point between the drive rod (26) and the coupling element (110 ') is designed such that the restoring force (F ₀ ), with which the coupling element (110') in the locked position (27 ') of the input shaft ( 101) is acted upon, is converted into a torque (M _A ) by which the input shaft (101) is pretensioned in the direction of its locking position (27'). Actuating gear (100 ') according to at least one of Claims 13 until 16 , characterized in that the drive rod (26) has an opening (142) having a first edge portion (144) and a second edge portion (146) which is spaced from the first edge portion (144) in the longitudinal direction of the drive rod (26). , wherein a free end (140) of the coupling element (110') extends through the opening (142) between the two edge sections (144, 146), wherein in the locking position (27') of the input shaft (101) the free end (140 ) of the coupling element (110') contacts the first edge section (144) at a first edge (148), which the first edge section (144) forms together with a first surface (152) of the drive rod (26), and the second edge section (146 ) contacts at a second edge (150) formed by the second edge portion (146) together with a second face (154) of the drive rod (26). actuating gear (100'). Claim 17 , characterized in that the first edge section (144) and/or the second edge section (146) forms a surface inclined relative to the horizontal; and/or the surface (162, 156) of the free end (140) of the coupling element (110') contacting the first and/or the second edge section (144, 146) in the locking position (27') of the input shaft (101) opposite the Horizontals are/is inclined. actuating gear (100'). Claim 18 , characterized in that the angle of inclination of the first edge portion (144) and/or the second edge portion (146) is between 5° and 30°, preferably between 7° and 25°; and/or the angle of inclination of the at least one contacting surface (156, 162) of the free end (140) of the coupling element (110') is between -5° and -30°, preferably between -7° and -25°. Actuating gear (100 ') according to at least one of Claims 13 until 19 , characterized in that the coupling element (110 ') has a substantially ∫-shaped or substantially integral sign-shaped shape, wherein at least one of the angled end sections of the coupling element (110') together with the section (158) connecting the two end sections Angles between 95° and 120°, preferably between 97° and 115°. Lift-and-slide element (19), in particular lift-and-slide door or lift-and-slide window, with an actuating mechanism (100, 100') according to at least one of the preceding claims.

Images