EP3611323A1 - Actuating gear for lifting and lowering a lifting sliding element and lifting sliding element provided with such an actuating gear - Google Patents

Abstract

The present invention relates to an actuating gear for lifting and lowering a lifting and sliding element which is displaceable along a guide rail and which can be moved in the lifting and sliding element from a lowered position in which the lifting and sliding element cannot be moved to a raised position 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 drive rod which is operatively coupled to a lifting element and which is connected to a Articulation point is connected eccentrically 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 torque acting in the direction of its locked position.

Description

The present invention relates to an actuating gear for a lift and slide element, such as for a lift and slide door or a lift and slide window, which is displaceable along a guide rail and transferred from a lowered position in which the lift and slide element is immovable to a raised position in which the lifting and sliding element can be displaced along the guide rail, the actuating gear being an input shaft which, by means of an operating lever, about an axis between a locking position corresponding to the lowered position of the lifting and sliding element and one corresponding to the raised position of the lifting and sliding element Unlocking position is rotatable, and a coupling element for drivingly coupling the input shaft with a drivingly coupled to a lifting element for lifting and lowering the lift-slide element, the coupling element, a coupling point au has eccentrically connected to the input shaft.

The lifting element in question for lifting and lowering the lifting and sliding element is usually a so-called carriage which is arranged in a receptacle formed on the underside of the lifting and sliding element. These carriages have a raised position and a lowered position, standing in the lowered position on the guide rail and thus transferring the weight of the lifting and sliding element to the guide rail. However, the contact is in the raised position the carriages to the guide rail are lifted or the carriages do not stand on the guide rail, so that the lifting and sliding element rests directly on the running 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 rotary movement being transmitted to the carriages via the actuating gear and a drive rod coupled to it. When the carriage is lowered from its raised position into its lowered position, the actuating lever usually first performs an idle stroke over an angle of approximately 40 ° until the rollers of the carriage stand 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 lifting and sliding element bear on the carriages, so that from now on a greater actuating force or a greater actuating torque is required to lift the lifting and sliding element by means of the actuating lever.

As already mentioned, the actuation lever is essentially force-free during the empty stroke, which can lead to it being inadvertently tilted if an operator accidentally gets caught on the actuation lever or accidentally grazes it. The risk of 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 / sliding element both during lowering and during lifting of the lifting / sliding element. With such an actuating force reduction device, the actuating lever can thus possibly perform an idle stroke even without external force and can thus crooked in an undesired manner.

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

Starting from an actuating gear of the type mentioned, this object is achieved by the features of claim 1 and in particular by the fact that the input shaft, which can be a square nut that can be coupled to an actuating lever, for example, is preloaded in its locking position by the coupling element in this way that it experiences a restoring 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 return spring, at least in the locking position, by applying an elastic pretensioning force to the input shaft, by means of which it experiences a torque by which it is urged in the direction of its locking 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, by means of which the input shaft is otherwise rotated in the direction of its unlocked position and thus the actuating lever is possibly skewed, which can prevent unintentional misalignment of the actuating lever.

Since the coupling element, via which the input shaft is connected to the drive rod in a drive-effective manner, acts according to the invention to a certain extent as a type of return spring, no separate or additional return spring is therefore required to urge the input shaft into its locking 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.

Thus, according to one embodiment, it can be provided that the restoring torque which the input shaft experiences when it is deflected from its locking position in the direction of its unlocking position to a value of zero, it being possible, in particular, for the input shaft to be subsequently subjected to another Deflection in the direction of its unlocking position experiences a torque acting in the direction of its unlocking position. Likewise, when the input shaft moves from its unlocked position towards its locked position shortly before reaching the locked position, it initially experiences a torque acting in the direction of its unlocked position, which, however, decreases to a value of zero as the input shaft moves before the input shaft moves towards it Locking position experiences restoring torque. So if the lifting and sliding element is lowered by means of the actuating lever, the operator experiences a certain resistance on the actuating lever shortly before reaching the locking position, which, however, decreases to a value of zero with progressive movement of the actuating lever, whereupon as the actuating lever moves in the direction of it Locking position acts on the input shaft and thus on the actuating lever, a restoring moment by which the input shaft and thus the actuating lever is urged in the direction of its locking position.

Similar to a clasp closure of a beer bottle, the operator therefore feels a certain resistance when closing or lowering the lifting and sliding element, which has to be overcome before subsequently from a changeover point, reverse the force relationships, which means that from this changeover point the input shaft and thus the actuating lever is automatically pushed or tensioned in the direction of its / its locking position. The actuating gear mechanism according to the invention thus makes use of a type of snap mechanism which causes the input shaft to be automatically pushed towards its locking position when it moves in the direction of its locking position from a switching point. This snap mechanism also provides the operator with tactile feedback that he is informed that the lifting and sliding 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 that is 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. Characterized in that the coupling element is braced against the abutment via its contact section, the coupling element serving as a return spring is thus preloaded when the input shaft is transferred from its unlocking position to its locking position. As a result, a restoring torque acts on the input shaft in the desired manner from the switchover point, so that the input shaft is pushed in the direction of its locking position.

So that the coupling element can be clamped against the abutment in the desired manner in order to achieve its pretension, it can be provided according to a further embodiment that the distance between the articulation point of the coupling element and the contact section thereof is smaller in the unlocking position than the distance in the locking position between the articulation 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 less than in the locking position the distance between the articulation point and the abutment. Accordingly, the coupling element is elastically deformed and, in particular, stretched when the input shaft is transferred from its unlocking position into its locking 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 locking position the distance between the Articulation point and the abutment.

According to a further embodiment, in the locked position of the input shaft, the articulation point of the coupling element, at which it is articulatedly connected 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 the input shaft being deflected out its locking position in the direction of its unlocking position, the articulation point reaches the other or second side of the first level, 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 switchover point of the snap mechanism according to the invention is determined by the first level, since as long as the articulation point is on the first side of the first level, the pretension of the coupling element has a force component by which the input shaft is urged in the direction of its locking position, whereas the pretension of the Coupling element at the articulation point located on the second side of the first level has a force component by which the input shaft is urged in the direction of 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. The coupling element experiences accordingly in the event of a deflection the input shaft from its locking position in the direction of its unlocking position an elastic deformation increasing up to a maximum value, this elastic deformation then decreasing again from its maximum value when the input shaft is deflected further in the direction of its unlocking position, preferably to a value of zero. Conversely, when the input shaft moves in the direction of its unlocking position, the elastic deformation of the coupling element initially increases to a maximum value in the vicinity of the switchover point, whereupon the elastic deformation decreases again as the input shaft moves further in the direction of its locking position, preferably to one Value of zero. In the locked position of the input shaft, the coupling element is thus more or less free of tension and thus stress-free, which can prevent a fatigue fracture of the coupling element.

According to a further embodiment, in the locked position of the input shaft, 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 line, whereas the abutment is on the other side of the second level, on which the articulation point is also in the unlocked position of the input shaft. In the locking position of the input shaft, the articulation point is thus to a certain extent on the other side of the input shaft than the abutment, which means that in the locking position the coupling element is, as it were, encompassed by the coupling element.

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 having a substantially T-shaped shape with a flange section and a web section that is butted against the Flange section ends, and the foot section has a substantially J-shaped shape with a web section and an adjoining arch section. The arc section forms the articulation point of the coupling element, a first end of the flange section the contact section of the coupling element and a second end of the flange section a free end of the coupling element that can be coupled to the drive rod. The web section of the head section merges into or coincides with the web section of the foot section of the coupling element, so that, viewed globally, the coupling element has a shape which 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 an essentially U-shaped shape, one end of the bracket section forming the contact section of the coupling element and the other end forming the articulation point thereof. In the embodiment described above, in which the coupling element essentially has the shape of the small Greek letter "τ", the bracket 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 engages around the input shaft and the abutment, so that the two ends of the bracket section are spread apart elastically.

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

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

More precisely, the actuating gear can include at least one actuating force reduction device that is coupled to the drive rod in an operatively effective manner, by means of which the input shaft is pretensioned in the locked position via the drive rod and the coupling element in the direction of its locked position. The lever force for generating the desired restoring torque is thus generated indirectly by the actuating force reduction device and is not attributable to an elastic deformation of the coupling element.

According to a further embodiment, it can be provided that, in the locked position of the input shaft, the actuating force reducing device acts on the coupling element via the drive rod with a restoring force, as a result of which the coupling element experiences a torque, by means of which the input shaft is pretensioned in the direction of its locking position and thus that experiences the desired restoring torque. In other words, it works the restoring force of the actuating force reduction device that the coupling element experiences a torque, which in turn is responsible for the force acting on the eccentric cam of the input shaft to which the coupling element is articulated, by means of which the input shaft is biased in the direction of its locking position. The actuating force reduction device is thus functionally coupled to the input shaft via the drive rod and the coupling element such that the input shaft is biased indirectly 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 such that the restoring force with which the coupling element is acted upon in the locking position of the input shaft is converted into the torque by which the input shaft is biased in the direction of its locking 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 apart from the first edge section in the longitudinal direction of the drive rod, a free end of the coupling element extending through the opening between the two edge sections. In the locked position of the input shaft, the free end of the coupling element contacts the first edge section at a first edge, which the first edge section forms together with a first surface of the drive rod. Likewise, the free end of the coupling element contacts the second edge section at a second edge, which the second edge section forms together with a second surface of the drive rod, which lies opposite the first surface of the drive rod. The second surface of the drive rod thus forms the surface of the drive rod opposite the first surface of the drive 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 pretensioning force of the actuating force reduction device has a value F ₀ and the thickness of the drive rod t, this results in a calculated torque M _A acting on the coupling element by multiplying the pretensioning force F ₀ by the drive rod thickness t. This torque M _{A in} turn causes a force on the eccentric cam of the input shaft in accordance with the above statements, whereby this experiences the desired restoring torque in the desired manner, by which it is biased into its locking position.

In order to ensure that the coupling element contacts the first and second edge sections in the region of opposite sides of the drive rod in the manner described above, it can be provided according to a further embodiment that the first edge section and / or the second edge section is opposite the horizontal forms inclined surface. Additionally or alternatively, it can be provided that the surface (s) of the free end of the coupling element that contacts the first and / or the second edge section is / are inclined with respect to the horizontal in the locked 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, then the angle of inclination of the edge sections must be inclined in the other direction than the contacting surfaces of the free end of the coupling element, since otherwise the inclination of the edge sections and that could at least partially compensate for the contacting surfaces.

According to yet another embodiment, the coupling element can have a substantially J-shaped or substantially integral sign-shaped shape, at least one of the angled end sections together with the section connecting the two end sections having an angle between 95 ° and 120 °, preferably between 97 and 115 °.

Fig. 1

eine schematische Darstellung eines Hebe-Schiebeelements mit einer Betätigungskraftreduzierungseinrichtung zeigt;

Fig. 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;

Fig. 3

das Betätigungsgetriebe der Fig. 2 in einer zweiten Stellung zeigt, in der sich die Eingangswelle in ihrer Verriegelungsstellung befindet;

Fig. 4

eine schematische Darstellung der auf die Eingangswelle der Ausführungsform gemäß den Figuren 2 und 3 wirkenden Kräfte in unterschiedlichen Drehstellungen zeigt; und

Fig. 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 and with reference to the drawings, in which:

Fig. 1

shows a schematic representation of a lifting and sliding element with an actuating force reducing device;

Fig. 2

a sectional view through a gear box with an actuating gear according to the invention for lifting and lowering a lifting and sliding element in a first position according to a first exemplary embodiment;

Fig. 3

the actuating gear of the Fig. 2 shows in a second position, in which the input shaft is in its locking position;

Fig. 4

is a schematic representation of the input shaft of the embodiment according to the Figures 2 and 3 shows acting forces in different rotational positions; and

Fig. 5

a sectional view through a gear box with an actuating gear according to the invention for lifting and lowering a lift and slide member according to a second exemplary embodiment.

The Fig. 1 shows a schematic view of a lifting and sliding element 19 according to the invention, which can be moved in the horizontal direction along a bottom guide rail, not shown here. For this purpose, the lifting and sliding element 19 has on its underside two carriages 25 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 lifting and sliding element 19.

The lifting and sliding element 19 has a lowered position and a raised position, and in the lowered position, in contrast to the raised position, it cannot be moved. In order to be able to transfer the lifting and sliding element 19 between the lowered position and the raised position, the lifting and sliding element 19 has a lifting device, generally designated by the reference number “10”, by means of which the lifting and sliding element 19 can be selectively raised and lowered.

The lifting device 10 in question comprises an actuating lever 27 on a side frame part 23 of the lifting-sliding element 19, two lifting elements in the form of the two carriages 25 for lifting and lowering the lifting-sliding element 19 and a transmission gear via which the two lifting elements are in shape of the two carriages 25 are coupled to the actuating lever 27 in a drive-effective manner. The transmission gear comprises in particular a first drive rod 26, which is coupled to the actuating lever 27 by means of an actuation gear 100, a second drive rod 29, which is coupled to the two carriages 25, and a deflection 32 in the form of, for example, a deflection gear via which the two drive rods 26, 29 in turn in the corner region of the frame of the lifting and sliding element 19 are coupled to each other in a drive-effective manner. By pivoting the actuating lever 27 starting from its dashed locking position 27 ', in which the lifting and sliding element 19 is in its lowered position, according to the arrow 28 in its open or unlocking position 27 ", the lifting and sliding element 19 can thus be by means of two carriages 25 are raised so that it can be moved along the guide rail, not shown.

The first drive rod 26 runs in a receiving section 20 designed as a groove, which is formed in the side frame part 23 of the lifting and sliding element, whereas the second driving rod 29 runs in the receiving section 21 formed in the underside of the frame of the lifting and sliding element 19, which also serves to accommodate the two carriages 25. The two receiving sections 20, 21, within which the two drive rods 26, 29 are arranged, are closed by a first or a second faceplate 34, 36, along which the respective drive rods 26, 29 are slidably guided. however, the second faceplate 36 is not absolutely necessary since the lower receiving section 21 cannot be seen.

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

Since the gas pressure spring 40 or the gas pressure springs 40, 42 are thus coupled on the one hand to the respective drive rod 26, 29 and on the other hand to the respectively associated cuff rail 34, 36, which are fixedly attached to the lifting and sliding element 19, the respective gas pressure spring 40, 42 thus increasingly pretensioned when lowering the lifting and sliding element 19 and increasingly relieved when the same is lifted. Thus, due to the fact that it is coupled to the respective drive rod 26, 29, the respective gas pressure spring 40, 42 absorbs at least part of the positional energy of the lifting-sliding element 19 that is released when the lifting-sliding element 19 is lowered and stores it between, in order to be able to return them to the same when the lifting-sliding element 19 is subsequently raised. The respective gas pressure spring 40, 42 is thus loaded when the lifting / sliding element 19 is lowered and consequently applies a force which is opposite to the direction of movement of the respective driving rod 26, 29 and is increasing and increases on the respective driving rod 26, 29. Thus, the holding force to be applied by means of the actuating lever 27 is reduced compared to the case without using a fitting arrangement according to the invention when lowering, so that the risk of the actuating lever 27 flipping upwards in the direction of its locking position is reduced.

On the other hand, the actuating lever 27 is based on its in the Fig. 1 Locking position 27 'shown in the open or unlocked position 27 "pivoted downward according to arrow 28 to the carriage 25 and thus To be able to lift the lifting and sliding element 19, the force required for this is reduced compared to the case without using a fitting arrangement according to the invention, since part of the weight force to be raised of the lifting and sliding element 19 does not have to be applied via the actuating lever 27, but as a counterforce from the Gas pressure springs 40, 42 is provided. This is because the energy temporarily stored in the gas pressure springs 40, 42 during the lowering of the lifting and sliding element 19 is discharged when the lifting and sliding element 19 is raised, a force acting in the direction of movement of the respective drive rod 26, 29 being applied to the latter, which makes lifting easier becomes. The lifting of the lifting and sliding element 19 is thus supported by the gas pressure springs 40, 42, so that less force has to be applied to actuate the lever 27. However, since the actuating lever 27 initially performs an idle stroke when pivoting from its locked position until the carriages 25 stand 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 gas pressure springs 40, 42 and is thus easily crooked.

In order to prevent such an inclination of the actuating lever 27, the embodiment according to FIGS Figures 2 to 4 a type of snap mechanism is integrated into the actuating gear 100, by means of which it can be achieved that the input shaft 101 experiences a restoring torque in the region of its locking position, by means of which it is urged in the direction of its locking position. An embodiment of such a switching mechanism is described below with reference to FIG Fig. 2 and 3 explained in more detail.

The Fig. 2 shows a first embodiment of an actuating gear 100 according to the invention in a position in which the actuating lever 27, starting from its vertically oriented locking position, has been pivoted clockwise by approximately 45 ° in the direction of its unlocking position. The operating lever 27 has a square mandrel 102 which is in positive engagement 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. On the square nut 104, an eccentric cam 108 is formed, to which the articulation point 112 of a coupling element 110 is articulated, which creates an effective 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 in the manner described above and way is operatively coupled to the carriages 25 of the lifting and sliding element 19. The coupling element 110 is articulatedly connected to the drive rod 26, for which purpose it is hooked into the drive rod 26 or a corresponding opening in it 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 drive rod 26, so that no additional guide has to be provided, by means of which the coupling element 110 can be prevented from being detached from the drive rod 26 when it is pivoted about its articulation point 112.

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

However, since the gas pressure springs 40, 42 bias the drive rod 26 upward as an actuating force reduction device, there is a risk that the actuating lever 27, starting from its vertically upward locking position, due to the driving connection of the drive rod 26 via the coupling element 110 to the input shaft 101 in the direction of the latter unlocking is pivoted and thus slightly inclined. In order to counteract such an inclined position of the actuating lever 27, a kind of snap mechanism is integrated into the actuating gear 100 according to the invention, by means of which such an inclined position can be prevented.

To implement this snap 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 pretensioned. The coupling element 110 thus itself acts as a type of return spring by which the input shaft 101 is urged in the direction of its locking position, as will be explained in more detail below.

In the embodiment shown here, the coupling element 110 has a head section 118 with an essentially T-shaped shape and a foot section 120 with an essentially J-shaped shape. The essentially T-shaped head section 118 has a flange section 122 and a web section 124, which in the embodiment shown here is oriented essentially perpendicular to the flange section 122 and ends bluntly thereon. The essentially J-shaped foot section 120 likewise has a web section 126 and an adjoining arch section 128, at which the articulation point 112 of the coupling element 110 is located, at which the coupling element 110 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, viewed globally, the coupling element 110 has a shape which essentially corresponds to the shape of the small Greek letter "τ". The flange section 122 has two free ends 130, 132, 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 locked position of the input shaft 101, see FIG Fig. 3 , The second end 132 of the flange section 122, however, 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 positive connection between the drive rod 26 and the Head section 118 of the coupling element 110 is given.

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

Since the changeover point of the snap-in mechanism according to the invention is defined by the first level E in question, the biasing force acting in the coupling element 110 in the locking position thus results in a restoring moment by which the input shaft 110 is urged in the direction of its locking position. If, however, the articulation point 112 is located on the second side of the first plane E in question, the action of the snap mechanism reverses, so that a torque acting in the direction of its unlocked position then acts on the input shaft 101. The restoring torque experienced by the input shaft 101 thus takes on a deflection from the locked position of the input shaft 101 in the direction of its unlocked position to a switchover point to a value of zero and then reverses, as a result of which the input shaft 101 then experiences a torque acting in the direction of its unlocked position. If one looks at the reverse sequence of movements, a torque acting in the direction of the unlocking position is initially built up, which then, when the switchover point is reached, changes into a restoring torque by which the input shaft 101 is urged in the direction of its locking position. In the locked 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 bears against the square mandrel 102 of the lever 27, as a result of which a further rotation of the input shaft 101 is prevented.

So that a preload can build up in the coupling element 110 in the desired manner 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 articulation point is in the unlocking position or when the coupling element is not loaded 112 of the coupling element 110 and the contact section 116 is slightly smaller than the distance between the articulation point 112 and the abutment 114 in the locking position. This has the consequence 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 is thus elastically deformed when the input shaft 101 starts from its unlocked position is turned into its locking position. The coupling element 110 is biased in this way and thus acts as a kind of return spring, so that no additional or separate return spring is required to produce the desired return effect.

With reference to the Fig. 4 the forces and torques by which the snap action according to the invention is brought about are now explained:

In the Fig. 4 the first plane E is shown, which contains the axis A of the input shaft 101 and the abutment 114 and through which the switching point of the snap mechanism is defined. If the articulation point 112 is located on the right or on the first side of the first plane E, a force F _coupling acts on it due to the prestress in the coupling element 110, which acts in the direction of the abutment 114. This force F _Koppel can be _broken down into a radially acting force component F _{Koppel, rad} and a tangentially acting force component F _{Kop-pel, tang} , the latter causing a turning or restoring moment M _Rück , through which the input shaft 101 urges in the direction of its locking position becomes.

If the input shaft 101 is now rotated clockwise in the direction of its unlocking position, the tangential force component F _{coupling, tang} decreases to a value of zero. If the input shaft is subsequently turned clockwise, the preload force F _{coupling element can} again be _{broken down} into two force components F _{coupling, rad} and F _{coupling, tang} oriented perpendicular to one another, the latter now causing a torque M to _unlock , by means of which the input shaft 101 moves in the direction of its Unlocked position is pushed.

The following will now refer to the Fig. 5 describes a second embodiment of an actuating gear 100 'according to the invention. 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 only the essential differences from the actuating gear 100 of the first embodiment will be discussed below.

The one in the Fig. 5 Actuating gear 100 'shown, the actuating lever 27 shown here only in broken lines is in its locking position 27'. Here, too, the locking lever 27 has a square mandrel 102, which is positively engaged with a square nut 104, which is inside of a gearbox 106 is rotatably mounted 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 articulation point 112, so that the coupling element 110' establishes an effective connection between the input shaft 101 of the actuating gear 100 'in the form of the square nut 104 and the drive rod 26 which, in turn, is coupled to the carriages 25 of the lever-slide element 19 in a drive-effective manner in the manner described above. 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 142 in such a way 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 locked captively in the drive rod 26, so that no additional guide has to be provided, by which the coupling element 110 ′ can be prevented from detaching from the drive rod 26 when it is about its articulation point 112 on the input shaft 101 is pivoted.

Since the coupling element 110 'is thus coupled on the one hand to the drive rod 26 and on the other hand to the input shaft 101 or the square nut 104, due to the eccentric articulation of the coupling element 110' on the square nut 104, a rotary movement thereof is converted into a longitudinal movement of the drive rod 26, as is the case with this is necessary to raise and lower the carriages 25.

Since the gas pressure springs 40, 42 bias the drive rod 26 upward as an actuating force reduction device, the actuating lever 24 tends to rotate clockwise in the direction of its unlocked position, which makes it easier to lift the lifting and sliding element 19.

In order to prevent the actuating lever 27 from being pivoted out of its illustrated locking position 27 'due to the prestressing action by the gas pressure springs 40, 42, in this embodiment of the actuating gear 100' the connection point between the drive rod 26 and the coupling element 110 'is Specially designed so that the restoring force F ₀ , with which the coupling element 110 'in the locking position 27' of the input shaft 101 via the drive rod 26 is acted upon 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 towards its locking 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 the F _stop , which in the illustration of the Fig. 5 acts to the right, whereby the input shaft 101 and thus the actuating lever 27 is biased towards its / its locking position 27 '.

As shown, the free end 140 of the coupling element 110 'is hooked into an elongated hole opening 142 which is formed in the drive rod 26 and is delimited 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. To this extent, viewed in the horizontal direction, there is a positive connection between the drive rod 26 and the free end 140 of the coupling element 110 '.

Again Fig. 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 'contacting 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 on a first edge 148, which the first edge section 144 together with the surface 152 of the drive rod 26 forms, which faces the gearbox 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 pretensioning force F ₀ from the actuating force reduction device 40, 42. The groove base 156 of the notch 134 at the free end 140 of the coupling element 110 'thus also experiences a slight inclination with respect 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 only contacts the second edge section 146 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 which faces away from the gearbox 106.

Because the contact point B, at which the preload force F ₀ acts, is offset from the pivot point A _K by the thickness t of the drive rod 26, the coupling element 110 'thus experiences the offset or preload torque M _{A shown} , which in turn is in In the manner already described, the force F _stops on the articulation point 112, by means of which the input shaft 101 is biased in the desired manner in the direction of its locking position 27 ′.

When referring to the Fig. 5 In the embodiment described, the underside 162 of the free end 140 of the coupling element 110 'is inclined with respect to the horizontal, whereas the two edge sections 144, 146 of the opening 142 are oriented essentially horizontally. Alternatively or additionally, however, the two edge sections 144, 146 can also be inclined with respect 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 are spaced apart from one another by the thickness t of the drive rod 26. 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 °. Additionally or alternatively, 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 preceding angle information, the edge sections 144, 146 are to be inclined in the opposite direction here, like the corresponding surfaces at the free end 140 of the coupling element 110 ', in order to prevent the edge sections 144, 146 from not covering the entire surface Free end 140 of the coupling element 110 'rest, since in this case the preload torque M _A could not develop.

In the embodiment shown here, the coupling element 110 ′ has a substantially ∫-shaped or substantially integral-sign-shaped shape, the free end 140 together with the connecting section 158, which connects the free end 140 with the end of the joint articulated at the articulation point 112 Coupling element 110 'connects 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 the horizontal, as has already been stated above.

Again Fig. 5 can further 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 can ensure 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 results in a rotation of the coupling element 110 'about the pivot point A _K.

LIST OF REFERENCES

10

lifter

19

Lift and slide element

20

receiving portion

21

receiving portion

22

lower frame part

23

side frame part

25

carriage

26

first drive rod

27

actuating lever

27 '

locking position

27 "

open position

28

arrow

29

second drive rod

32

redirection

34

first faceplate

36

second faceplate

40

first gas pressure spring, actuating force reduction device

42

second gas pressure spring, actuating force reduction device

100

actuating mechanism

100 '

actuating mechanism

101

input shaft

102

Square spindle

104

Square hub

106

gearbox

108

eccentric cams

110

coupling element

110 '

coupling element

112

articulation

114

Abutment, bolt

116

Contact section

118

header

120

foot section

122

flange

124

Bridge section of 118

126

Bridge 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 edge section

146

Second or upper edge section

148

First edge

150

Second edge

152

First area

154

Second area

156

groove base

158

connecting portion

160

indentation

162

lower surface 162 of 140

A

axis

A _K

pivot point

B

contact point

e

first floor

F ₀

preload force

M _A

preload torque

Claims (15)

Actuating gear (100, 100 ') for lifting and lowering a lifting and sliding element (19) such as, for example, a lifting and sliding door or a lifting and sliding window, which can be moved along a guide rail and from a lowered position in which the lifting and sliding element (19 ) is immovable, can be transferred to a raised position in which the lifting and sliding element (19) can be displaced;
the actuating gear (100) having an input shaft (101) which, by means of an actuating lever (27) about an axis (A), between a locking position (27 ') corresponding to the lowered position of the lifting and sliding element (19) and one of the raised position of the lifting -Sliding element (19) corresponding to the unlocking position, and a coupling element (110) for driving coupling of the input shaft (101) with a drivingly coupled to a lifting element (25) connecting rod (26), which is eccentrically connected to the articulation point (112) Input shaft (101) is articulated;
wherein the input shaft (101) is preloaded in its locking position (27 ') by the coupling element (110) in such a way that the input shaft (101) experiences a restoring torque (M _back ) acting in the direction of its locking position (27'). Actuating gear (100) according to claim 1,
characterized in that
the restoring torque (M _return ), which the input shaft (101) experiences, decreases to a value of zero when deflected from its locking position (27 ') in the direction of its unlocking position;
it is provided in particular that the input shaft (101) experiences a torque (M _unlocking ) acting in the direction of its unlocking position when the input shaft (101) is deflected further in the direction of its unlocking position. 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) is supported in the locking position (27 '),
it is provided in particular 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) according to claim 3,
characterized in that
in the locked position (27 ') of the input shaft (101) the articulation point (112), at which the coupling element (110) is articulated to the input shaft (101), on a first side of the axis (A) of the input shaft (101 ) and the abutment (114) containing the first level (E), wherein the articulation point when the input shaft (101) is deflected from its locking position (27 ') in the direction of its unlocking position (112) reaches the second side of the first level (E), it being provided in particular that a free end (132) of the coupling element (110) which can be coupled to the drive rod (26) is also located on the second side of the first level ( E) is located. Actuating gear (100) according to at least one of the preceding claims,
characterized in that
When the input shaft (101) is deflected from its locking position (27 ') in the direction of its unlocking position, the coupling element (110) experiences an elastic deformation which increases up to a maximum value, it being provided in particular that when the input shaft (101) is deflected further in the direction of its unlocking position the elastic deformation of the coupling element (110) decreases again from its maximum value, preferably to a value of zero. Actuating gear (100) according to at least one of claims 3 to 5, characterized in that
in the locked position (27 ') of the input shaft (101) the articulation point (112), at which the coupling element (110) is articulated to the input shaft (101), on one side of the axis (A) of the input shaft (101) containing second plane, which is perpendicular to a straight line connecting the abutment (114) and the axis (A) of the input shaft (101), whereas the abutment (114) is on the other side of the second plane, it being provided in particular that the articulation point (112) is also on the other side of the second level in the unlocked position of the input shaft (101). Actuating gear (100) according to at least one of claims 3 to 6, characterized in that
the coupling element (110) comprises a head section (118) and a foot section (120), the head section (118) having a T-shaped shape with a flange section (122) and a web section (124) which is butted against the flange section (122) ends, and the foot section (120) has a J-shaped shape with a web section (126) and an adjoining arch section (128), the arch section (128) 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) form a free end of the coupling element (110) which can be coupled to the drive rod (26). Actuating gear (100) according to at least one of claims 3 to 7, characterized in that
the coupling element (110) has a U-shaped bracket section, one end of which forms the contact section (116) of the coupling element (110) and the other end the articulation point (112) of the coupling element (110),
it is in particular provided that the bracket section in the locking position (27 ') engages around 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 drive rod (26), which is operatively coupled to a lifting element (25) and to which the coupling element (110) is connected in an articulated manner, wherein it is preferably provided that the coupling element (110) is detachably connected to the drive rod (26) is connected, in particular is 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),
it is provided in particular that the actuating gear (100 ') further comprises at least one actuating force reduction device (40, 42) through which the input shaft (101) in its locking position (27') via the drive rod (26) and the coupling element (110 ' ) is biased towards its locking position (27 '). Actuating gear (100 ') according to claim 9,
characterized in that
in the locked position (27 ') of the input shaft (101) the actuating force reducing device (40, 42) applies a restoring force (F ₀ ) to the coupling element (110') via the drive rod (26), as a result of which the coupling element (110 ') experiences a torque (M _A ) by which the input shaft (101) is biased in the direction of its locking position (27 '). Actuating gear (100 ') according to claim 9 or 10,
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') is acted on in the locking position (27 ') of the input shaft (101), is converted into a torque (M _A ) by which the input shaft (101) is biased in the direction of its locking position (27 '). Actuating gear (100 ') according to at least one of claims 9 to 11, characterized in that
the drive rod (26) has an opening (142) which has a first edge section (144) and a second edge section (146) which is spaced apart from the first edge section (144) in the longitudinal direction of the drive rod (26), wherein between the a free end (140) of the coupling element (110 ') extends through the opening (142) in both edge sections (144, 146), the free end (140) of the coupling element (110) in the locking position (27') of the input shaft (101) ') contacts the first edge section (144) on 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) on a second edge (150) contacted, which the second edge section (146) forms together with a second surface (154) of the drive rod (26),
it being provided in particular that (i) the first edge section (144) and / or the second edge section (146) forms a surface inclined with respect to the horizontal; and or (ii) 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 Horizontal are inclined. Actuating gear (100 ') according to claim 12,
characterized in that
the angle of inclination of the first edge section (144) and / or the second edge section (146) is between 5 ° and 30 °, preferably between 7 ° and 25 °; and or
the angle of inclination of the at least one contacting surfaces (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 9 to 13, characterized in that
the coupling element (110 ') has a substantially ∫-shaped or substantially integral-sign-shaped shape, at least one of the angled end sections of the coupling element (110') together with the section (158) connecting the two end sections forming an angle between 95 ° and 120 °, preferably between 97 ° and 115 °. Lift-slide element (19), in particular lift-slide door or lift-slide window, with an actuating gear (100, 100 ') according to at least one of the preceding claims.

Images