EP0740041A1 - Check for windows, doors or the like - Google Patents

Abstract

The extension arm (4) pivots at one end (4a) on the fixed frame (2) at the hinge axis, while at the other (4b) it pivots and slides on the leaf (1) and on an axis parallel to the hinge axis in the shut position. The supporting arm (14) hinges at opposite ends on the extension arm at a point between the ends of the extension arm, and on the leaf, both the hinge axes also being parallel to the main one in the shut position. A drive mechanism with rod (32) sliding parallel to the tilt axis acts on a component actuating the leaf. The component (20) and rod have teeth intermeshing over part at least of the tilt angle, typically consisting of rack teeth on the rod and a gear sector on the component.

Description

The present invention relates to an opening device for windows, doors or the like with a tilt and turn sash having an axis of rotation and an essentially orthogonal tilt axis, comprising:
a deployment arm which defines a maximum tilt opening angle, which is pivotably articulated at a first deployment arm end at a frame articulation point lying on the axis of rotation on the fixed frame about the axis of rotation, and which at its second articulation arm end at a first wing articulation point which can be displaced essentially parallel to the tilting axis a first axis which is substantially parallel to the axis of rotation when the wing is closed is pivoted; a support arm which is articulated on a first support arm end at an extension arm articulation point on the extension arm lying between the first and the second deflecting arm end, about a second axis which is essentially parallel to the axis of rotation when the wing is closed, and which is connected at its second end on a second wing arm. Articulation point on the wing is pivoted about a third axis which is substantially parallel to the axis of rotation when the wing is closed, the raising arm articulation point being arranged between the first and second wing articulation points when the wing is closed; a drive element that can be coupled to a manually and / or motor-operated drive unit, essentially parallel to the tilt axis and displaceable parallel to it, in particular drive rod section; and an actuating element which can be actuated directly or indirectly on the extension arm and can be actuated by the drive element for pressing on or pushing off the wing.

Such an opening device enables a simplified tilt opening of the wing or a simplified closing of the tilt opened wing by actuating the drive unit with a wing impression or wing pressure which has been achieved. Of particular importance is the wing pressure or tightening which is forcibly achieved during the transition from the tilt opening position via the tilt closing position to the ready-to-turn position of the wing, as a result of which malfunctions are avoided.

Under certain circumstances, such opening devices can also be designed so that intermediate tilt opening positions can be set and maintained.

An opening device of the type mentioned is known from DE 33 45 870 C2. This known opening device has an actuating element designed as a separate element, which engages at one end via a bolt-bolt guide connection on the opening arm and with its other end at a third wing articulation point on the wing, which is displaceable in motion and is coupled to the driving element and is coupled to the driving element when the wing is closed, the fourth axis, which is essentially parallel to the axis of rotation, is pivoted. The actuating element has a cam pin guide which is engaged by a guide pin which is stationary with respect to the wing. The guide curve of the bolt-bolt guide connection is designed in such a way that at the beginning of the tilting movement, the wing is pressed off by the relative displacement between the guide bolt and the guide curve due to a displacement of the driving element and when the wing is closed from the tilted position again by a relative displacement of the guide bolt and the Guide curve due to a displacement of the driving element in the opposite direction, a tightening or pressing of the wing on the fixed frame is achieved.

A disadvantage of this known device is that the extension arm loaded by the wing when the wing is tilt-open is weakened by an elongated hole which receives a bolt on the actuating element for producing the bolt-bolt guide connection. The cost of materials in the manufacture of the actuating element is also quite large, since the actuating element is relatively wide in order to form the required guide curve. Larger tilt opening widths (especially in the case of large sash formats) may not be possible at all with this opening device due to the width of the actuating element limited by the rebate width. The assembly effort is relatively high because of Extension arm and the wing are connected to each other via a total of six articulation, connection or actuation points.

The object of the invention is to provide a mechanically stable opening device of the type mentioned, which is characterized by high reliability even with high forces to be transmitted.

This object is achieved in that the actuating element and the driving element each have a toothed section or the like, which mesh with one another at least in a partial region of the maximum tilt opening angle for pressing on or pressing off the wing by the actuating element.

Since a positive intermeshing connection can be established between the actuating element and the driving element via the toothed sections, even high forces can be transmitted safely from the driving element to the actuating element and thus to the extension arm. As a further advantage, the assembly is simplified with regard to the connection between the drive element and the actuation element that is effective for the actuation of the actuation element, since a pin or rivet connection or the like between the actuation element and the drive element can be omitted due to the toothed sections.

The drive element can have a toothed rack section which meshes with a toothed sector of the actuating element, which is mounted on the wing so as to be rotatable about an axis which is essentially parallel to the axis of rotation when the wing is closed. As a result, a large angle of rotation can be achieved without difficulty and, accordingly, a large tilt opening width.

In this connection it is preferred that the axis of the actuating element is offset relative to the first axis in the direction perpendicular to the sash frame plane and, in the case of the sash frame being tilted open, to the fixed frame, and that Rack section is offset from the first axis in the opposite direction.

In this way, a reduction effect is achieved which amplifies the torque acting on the actuating element and thus on the extension arm when the driving element is actuated. Even heavy sashes can be pressed on or off (if necessary manually) via the drive unit. The reduction is determined by the distance between the axis of the actuating element and the rack section; this distance can be selected according to the requirements with regard to the respective wing and the type of actuation provided (manual and / or motorized).

The actuating element is preferably designed as a separate element which is pivoted at a third wing pivot point on the wing about a fourth axis which is substantially parallel to the axis of rotation when the wing is closed. The second wing articulation point and, with the wing closed, the pivot arm articulation point can thus be arranged independently of the actuating element in the same plane parallel to and possibly coinciding with the casement plane, and it can simultaneously be used in the direction perpendicular to the casement plane with little installation space required achieve high reduction. The support arm and the actuating element can each be optimized in their shape and in their arrangement on the wing or on the raising arm with regard to their respective function (carrying the wing weight when the wing is tilted open together with the raising arm or pressing and pushing the wing).

The actuating element can engage the support arm via a bolt-bolt guide connection. This design has the advantage that only one articulation point is provided on the extension arm, which prevents the extension arm from being weakened by an elongated hole or the like.

The second wing articulation point is preferably offset relative to the third wing articulation point in the direction parallel to the tilt axis toward the first wing articulation point. The support arm and the portion of the actuating element engaging the support arm are thus inclined in the same direction in each tilt-open position of the wing with respect to the sash frame plane, and the pin guide of the pin-pin guide connection, which is preferably formed on the support arm, can accordingly be relatively short.

The actuating element and the support arm can overlap in the region of the second wing articulation point, wherein the actuating element can have an arc-shaped elongated hole into which a hinge pin or the like defining the second wing articulation point engages. The wing pivot points for the support arm and the actuating element can thus be arranged independently of the dimensions of the support arm or the actuating element in order to achieve the desired reduction on the wing with a small installation space requirement. The relationship between the displacement of the drive element and the resulting change in the tilt opening angle can be set by appropriate arrangement of the articulation points and by appropriate design of the actuating element and the bolt-bolt guide connection. In particular, a substantially linear relationship between the displacement of the drive element and the tilt opening angle can be achieved over a large part of the tilt opening angle range.

It is preferred that the first, second and third wing articulation points are formed on a faceplate section which is fixed on the wing in a wing rebate groove and is essentially parallel to the tilt axis, and that the drive element is arranged below the faceplate section in the rebate groove, with the above being above the faceplate section Gear section.

With this design, the extension arm, the support arm and the actuating element can be preassembled on the faceplate section, so that only the faceplate section together with the drive element must be mounted in the sash groove for final assembly on the wing. The installation effort is significantly reduced.

In combination with or also independently of the actuating element described above, the opening device according to another aspect of the invention can have a catch arm which can be actuated by the drive element and which at a first catch arm end at a fourth wing articulation point on the wing about an essentially closed axis to the axis of rotation parallel fifth axis is rotatably articulated and the catch arm end section comprising the second catch arm end can be brought into engagement with a driving element of the deployment arm in a first tilt angle range of smaller tilt angles for pressing on or pushing off the wing, and the rest of the tilt opening angle range is out of engagement with the Take-away element stands.

The catch arm relieves the actuating element or the support arm, if any, acted upon by the actuating element in the first tilt angle range from at least part of the forces required for pressing on or pushing off in the first tilt angle range. Relief during the transition from the tilt-open position to the closed position of the sash is of particular importance, since this may require relatively large pressing or pulling forces of the sash against the fixed frame.

If the driving element is closer to the first extension arm end than the extension arm articulation point, there are much more favorable power transmission ratios for pressing on or pushing down the wing in the first tilting angle range due to a longer lever arm than if the pressing or pushing off were done solely via the actuating element. Pressing or pressing is the easier or the more effective, depending the driving element is arranged closer to the first extension arm end. By means of the catch arm, the extension arm can be reliably brought into an essentially parallel orientation to the tilt axis during the transition from the tilt opening position to the closing position, whereby malfunctions are reliably avoided.

It is preferred that the catch arm also serves to hold the extension arm at least in the ready-to-rotate position in a substantially parallel orientation to the tilt axis. Separate locking elements for locking the extension arm in a substantially parallel orientation to the tilt axis, for example by means of separate locking elements on the faceplate section actuated by the driving element, can thus be dispensed with.

It is particularly expedient if the end of the tentacle arm is fork-shaped, in particular with two fork tines. In this context, it is preferred that the second fork tine closer to the sash frame when the sash is tilted open is shorter than the first fork tine. As a result, when the tilt-open wing is closed, the preferably essentially bolt-shaped entrainment element can be reliably "caught" by the fork-shaped end arm section in order to produce the engagement between the end arm section and the entrainment element, the tilting angle range over which the catch arm can press the wing, is larger than the tilt angle range over which it can push the wing. Malfunctions are thus reliably avoided.

When the wing is closed, the fourth wing articulation point can lie in the direction parallel to the tilt axis between the engagement bolt and the first wing articulation point. This design is advantageous because the extension arm and the catch arm are thus inclined in the same direction relative to the wing plane (in each tilt angle opening position with engagement between the catch arm end section and the driving element). The dimensions of the tentacle end section in the longitudinal direction of the catch arm can thus be relatively small and the entrainment element can be arranged relatively close to the first end of the extension arm, which results in the aforementioned favorable power transmission conditions (long lever arm).

It is preferred that the catch arm can be actuated by a separate guide lever which is pivoted at a first guide lever end at a fifth wing pivot point on the wing about a sixth axis which is substantially parallel to the axis of rotation when the wing is closed, the guide lever being actuatable by the drive element is.

By this measure, the power transmission via the tentacle to the extension arm can be optimized regardless of the shape of the tentacle and the position of the fourth wing pivot point, and it can be the desired relationship between the displacement of the driving element and the resulting pivoting movement of the tentacle according to the requirements , especially with regard to interaction with the actuating element. The fourth wing articulation point and, when the wing is closed, the driving element can be arranged in the same plane as the first wing articulation point, regardless of the desired reduction ratio, in the plane parallel to the wing frame plane.

The guide lever preferably has a cam pin guide, in which a guide pin which is coupled to the drive element engages. The required relationship between the displacement of the driving element and the resulting swiveling movement of the catch arm can be selected by appropriate design of the cam pin guide.

It is particularly preferred that the sixth axis is offset from the fifth axis in the direction perpendicular to the sash frame plane and, with the sash open, from the fixed frame, and that the guide pin is offset from the fifth Axis is offset in the opposite direction. As a result, a torque gain is achieved by a corresponding reduction of the actuating movement of the drive element via the guide lever. As already mentioned, the shape of the tentacle is not determined by the reduction function. Without the guide lever, the catch arm would have to be made very wide in order to achieve a corresponding reduction, which would be unfavorable in terms of the material expenditure and the required, but limited installation space.

The guide lever can engage the catch arm via a pin-pin guide connection. For this purpose, the catch arm preferably has an elongated hole extending in the longitudinal direction of the catch arm.

It is preferred that the fifth wing articulation point lies in the direction parallel to the tilt axis between the fourth wing articulation point and the first wing articulation point. By this measure, the guide lever and the catch arm are inclined in each pivot position of the catch arm in the same direction relative to the wing plane, so that the bolt guide or the elongated hole on the catch arm only has to have small dimensions in the longitudinal direction of the catch arm. It is more important, however, that this results in favorable power transmission conditions (long lever arm) on the catch arm or on the extension arm.

The fourth and fifth wing pivot points can be formed on the faceplate section. The guide bolt, which preferably shifts essentially parallel to the tilting axis when the driving element is displaced, is then arranged next to the faceplate section. This results in the advantages already mentioned in connection with the actuating element according to the invention with regard to a simplified assembly of the opening device on the wing.

To coordinate the movement of the actuating element and the movement of the catch arm with one another when the driving element is displaced and for decoupling the guide lever from the movement of the drive element outside the first tilt angle range and at least in the ready-to-turn position, it is preferred that the cam pin guide has a first rectilinear section, into which the guide pin engages if the catch arm end section does not engage with the driving element in Engagement is, wherein the first rectilinear section extends in the associated rotational position of the guide lever in the direction of movement of the guide pin that adjoins the first rectilinear section not extending in the direction of movement of the guide pin actuating portion of the cam pin guide into which the guide pin Actuation of the guide lever engages, and that the cam pin guide has a second rectilinear section adjoining the actuating section, into which the guide pin is in a substantially parallel orientation of the Ausstella rms engages to the tilt axis, wherein the second straight section extends in the assigned rotational position of the guide lever in the direction of movement of the guide pin.

The display device according to the invention with an actuating element according to the invention can be designed such that the toothed sections of the actuating element and the drive element mesh with one another over the entire tilt opening angle, regardless of whether a catch arm according to the invention is provided or not. If a catch arm according to the invention is provided, it is also possible, however, for the toothed sections to mesh with one another only in a second tilt opening angle range of larger tilt angles, the first and second tilt opening angle ranges overlapping at least slightly and the first and second tilt opening angle ranges together comprising all tilt opening angles. In this case, the movement of the actuating element and the catch arm need only be coordinated with one another in the transition region between the first and the second tilt opening angle region. Mechanical tension in the opening device are thus reliably avoided and the function of the actuating element and the function of the catch arm can be optimized largely independently of one another.

According to another aspect, the invention relates to a turn-tilt fitting for windows, doors or the like, which turn-tilt fitting comprises an opening device according to the invention with an actuating element according to the invention and / or a catch arm according to the invention.

The other fitting parts can essentially be normal fitting parts, which can also be used in turn-tilt fittings without an opening device. The hardware parts can thus be manufactured in large numbers, which reduces the manufacturing costs and storage costs.

According to a further aspect, the invention relates to a window, a door or the like with an opening device according to the invention or with a turn-tilt fitting according to the invention.

Figur 1

eine erfindungsgemäße Ausstellvorrichtung in Draufsicht mit einem für den maximalen Kippöffnungswinkel ausgestellten Ausstellarm;

Figur 2

in den Teilfiguren a bis c die Ausstellvorrichtung der Figur 1 mit variierender Stellung des Ausstellarms entsprechend unterschiedlicher Kippöffnungswinkel bzw. (Figur 2c) einem bezüglich der Kippfunktion geschlossenen Flügel, wobei die Figuren 1, 2a, 2b und 2c eine Sequenz von aufeinanderfolgenden Stellungen beim Übergang vom maximalen Kippöffnungswinkel zum geschlossenen Flügel zeigen; und

Figur 3

in einer Detailvergrößerung den Stützarm und das Betätigungselement der erfindungsgemäßen Ausstellvorrichtung in der in Figur 1 gezeigten Stellung des Ausstellarms.

In Figur 1 ist zusätzlich ein feststehender Rahmen und ein sich in Kipplage entsprechend dem maximalen Kippöffnungswinkel befindender Flügel angedeutet, die in den Figuren 2 und 3 der Einfachheit halber weggelassen sind.The invention is explained below with reference to an embodiment shown in Figures 1 to 3. In the figures shows

Figure 1

a stay device according to the invention in plan view with a stay arm extended for the maximum tilt opening angle;

Figure 2

in the sub-figures a to c, the opening device of FIG. 1 with a varying position of the opening arm corresponding to different tilt opening angles or (FIG. 2c) a wing closed with respect to the tilting function, FIGS. 1, 2a, 2b and 2c being a sequence of successive positions point at the transition from the maximum tilt opening angle to the closed wing; and

Figure 3

in a detail enlargement the support arm and the actuating element of the deployment device according to the invention in the position of the deployment arm shown in FIG.

In FIG. 1, a fixed frame and a wing that is in a tilted position corresponding to the maximum tilting opening angle are additionally indicated, which are omitted in FIGS. 2 and 3 for the sake of simplicity.

According to the exemplary embodiment shown in the figures, the opening device according to the invention has a so-called three-point or opening scissors which holds the sash 1 in the tilting position relative to the fixed frame 2 when it is tilted. The stay scissors comprises a stay arm 4, which is pivoted at a first stay arm end at a frame pivot point 6 on the fixed frame 2, the frame pivot point 6 together with another frame pivot point, not shown, defining an axis of rotation about which the rotation -Tilting sash swivels when the sash is opened. When the wing is rotated, the opening arm 4 assumes the position shown in FIG. 2c.

At its second extension arm end, the extension arm 4 is rotatable and displaceable on a faceplate section 8 fixed in a sash groove on the wing 1 in a manner known per se by means of an elongated hole 10 extending in the longitudinal direction of the faceplate section 8 and an articulated bolt or the like engaging in the elongated hole 10 articulated. The bolt engaging in the elongated hole 10 forms a displaceable first wing articulation point 12, at which the extension arm 4 is pivoted about a first axis which is essentially parallel to the axis of rotation when the wing is closed. The elongated hole 10 extends substantially parallel to the Rotation axis essentially orthogonal tilt axis of the turn-tilt wing.

The stay scissors further comprises a support arm 14, which is rotatably articulated with a first support arm end 14a at an extension arm articulation point 16 between the first 4a and the second 4b extension arm end in the form of an articulated bolt or the like, with the rotary movement being activated by a when closed Wing is characterized to the axis of rotation substantially parallel second axis. The support arm 14 is pivotally articulated on its second support arm end 14b at a second wing articulation point 18, formed by a hinge pin or the like, on the faceplate section 8 and thus on the wing 1, the rotary movement being characterized by a third axis which is essentially perpendicular to the axis of rotation when the wing is closed .

The first and second wing articulation points 12 and 18 and the extension arm articulation point 16 form the end points of a triangle when the wing is open, the longest side of which is from the faceplate section between the first and second wing articulation points 12 and 18 and the other sides thereof are formed by the extension arm section between the first wing pivot point 12 and the extension arm pivot point 16 or the support arm 14. When the wing is closed, the first and second wing pivot points 12 and 18 and the extension arm pivot point 16 lie in a plane E which is essentially parallel to the axis of rotation and the tilt axis.

For the implementation of the pressing or push-off function, a separate actuating element 20 is provided which is rotatably articulated on a third wing articulation point 22 formed by a hinge pin or the like on the faceplate section 8 and thus on the wing 1, the rotary movement being effected by a when the wing is closed fourth axis which is essentially parallel to the axis of rotation. The second wing pivot point is opposite the third wing pivot point in Offset towards the first wing pivot point. The arm 20b of the actuating element 20 is thus inclined in every tilt opening angle position in the same direction as the support arm 14. The third wing pivot point is closer to the fixed frame 2 than the second wing pivot point 18 or the first wing pivot point when the wing is open 12th

The actuating element 20 has an arm 20b projecting from a substantially sector-shaped section 20a, which engages via a bolt 24 with an elongated hole 26 in the support arm 14 for producing a bolt-bolt guide connection. The actuating element 20 and the support arm 15 are thus motionally coupled, with a rotary or pivoting movement of the actuating element 20 about the third wing pivot point 22, a pivoting movement of the support arm 14 with simultaneous pivoting movement of the deflecting arm 4 about the continuously shifting first wing pivot point 12 Consequence.

In the embodiment shown, the actuating element 20 or the sector-shaped section 20a of the actuating element 20 and the second wing pivot point overlap. For this purpose, the actuating element has an arcuate elongated hole 34 into which the hinge pin forming the second wing pivot point 18 engages.

The actuating element 20 has on its sector-shaped section 20a on the side facing away from the fixed frame a toothed sector 28, which with a rack section 30 of a drive element which can be displaced below the faceplate section 8 essentially parallel to the tilt axis in the form of a drive rod section 32 over the entire tilt opening angle range (in which shown embodiment) combs. The drive rod section 32 and the actuating element 20 are thus positively coupled in motion over the entire tilt opening angle range.

As already mentioned, the third wing articulation point 22 is shifted relative to the first wing articulation point 12 or the second wing articulation point 18 when the sash 1 is open in the direction of the fixed frame 2, while the toothed sector 28 is on the side of the frame facing away from the frame 2 sector-shaped section 20a of the actuating element 20 is arranged with a correspondingly arranged toothed rack section 30, which stands to the side of the faceplate section 8 on the side of the faceplate section 8 facing away from the fixed frame when the sash is open. This results in particularly favorable power transmission ratios, namely a reduction effect which amplifies the torque acting when the drive rod section is actuated on the actuating element and thus on the support frame or on the extension arm.

In order to enlarge the lever arm or for a stronger reduction, the third wing articulation point 22 is formed on a bracket 22a projecting from the side of the faceplate 8 on the side closer to the fixed frame 2 from the faceplate section 8 when the wing 1 is open. The lever arm which is effective with respect to the fourth axis when the actuating element 20 is actuated by means of the toothed rack section 30 is therefore longer than the width of the faceplate section 8.

The drive rod section 32 can be displaced in a manner known per se manually and / or in a motorized manner parallel to the tilt axis or parallel to the faceplate section 8, in particular for actuating the actuating element 20 and thus for pressing on or pushing off the wing 1 with respect to the fixed one Frame 2. A corresponding sequence of tilt opening angle positions is shown in Figures 1 and 2a to c.

Starting from the tilt opening position with the maximum tilt opening angle as shown in FIG. 1, there has been a displacement of the drive rod section 32 and thus of the rack section 30 in the direction facing away from the first wing articulation point 12 (to the right in the figures) by 9 length units results in a relative approximation of the frame articulation point 6 to the wing 1 by about 56 length units. The resulting position of the extension arm 4 is shown in Figure 2a. If the drive rod section 32 and thus the rack section 30 is displaced by a further 4.5 length units in the same direction, the frame pivot point 6 approaches the wing 1 by a further approx. 41 length units. The corresponding position of the extension arm 4 is shown in Figure 2b. After a total displacement of approx. 18 length units, the final state shown in FIG. 2 c is reached with the wing 1 closed and the extension arm 4 extending parallel to the faceplate section 8 or to the tilt axis, for which purpose the frame pivot point relative to the wing 1 extends by a further approx. 53 length units moved perpendicular to the sash level. One unit of length corresponds to 1 mm, for example.

When the state shown in FIG. 2 c is reached, the toothed sector 28 disengages from the toothed rack section 30. To hold the raising arm 4 in parallel to the faceplate section 8, separate locking cams that can be actuated by the connecting rod section 32 and lock the raising arm 4 on the faceplate section 8 could be provided. Instead of such locking cams, the embodiment shown in the figures has a catch arm 40, which holds the extension arm 4 in the ready-to-turn position and with the wing 1 closed and locked on the frame 2 in a parallel orientation to the faceplate section 8, as in the following together with further functions of the catch arm 40 is explained in more detail.

The catch arm 40 is rotatably articulated on a first catch arm end 40a by means of a hinge pin forming a fourth wing articulation point 42, the pivoting or pivoting movement of the catch arm 40 being essentially parallel to the axis of rotation when the wing is closed fifth axis is characterized. The catch arm 40 has at its other end 40b a fork-shaped catch arm end section 44 with two fork tines 44a and 44b.

The catch arm 40 can be pivoted about the fifth axis by means of a separate guide lever 46, the guide lever 46 being actuable by the drive rod section 32. The guide lever 46 is rotatably articulated with a first guide lever end 46a at a fifth wing pivot point 48 in the form of a hinge pin on the faceplate section 8, the rotary movement of the guide lever 46 being characterized by a sixth axis which is essentially parallel to the axis of rotation when the wing is closed. The fifth wing articulation point 48 is offset in relation to the fourth wing articulation point 42 in the direction of the first wing articulation point 12, the fourth wing articulation point 42 being closer to the fixed frame 2 than the fifth wing articulation point 48 when the sash is open in a tilted manner.

The guide lever 46 has at its second end 46b an articulated bolt 50 which engages in an elongated hole 52 in the catch arm 40 for producing a bolt-bolt guide connection which couples the guide lever 46 and the catch arm 40.

The guide lever 46 has a cam pin guide 54, in which a guide pin 56, which is coupled to the drive rod section 32, engages. When the drive rod element 32 is displaced, the side of the faceplate section 8 on the side (with the sash opened) closer to the fixed frame, the upstanding guide pin 56 parallel to the faceplate section 8, 50, so that when the middle curved guide curve section is reached, a controlled pivoting of the guide lever 46 and thus the catch arm 40 takes place. Due to the arrangement of the fourth wing articulation point 42, the fifth wing articulation point 48 and the curved pin guide 54 or the guide pin 56, favorable power transmission ratios again result in relation to one another when the catch arm 40 is actuated, namely a long, effective lever arm or a torque-increasing reduction.

For pressing or pushing the wing 1 with respect to the fixed frame 2 or also for holding the raising arm 4 in a parallel orientation to the faceplate section 8 with the wing closed, as shown in FIG. 2c, the raising arm 4 has a driving element in the form of a driving pin 58 , which is in a first tilt angle range smaller tilt angle with the fork-shaped arm end section 44 in engagement. Since the fork tine 44a which is closer to the fixed frame when the sash is tilted open is longer than the fork tine 44b which is more distant from the fixed frame 2, the engagement between the driving pin 58 and the catch arm end section 44 is only in relation to the pressing, but still in a portion of the larger tilting angle range of the former tilting angle range not effective in pushing off the wing 1 with respect to the fixed frame 2. Such a situation is shown in FIG. 2b. An intervention that is also effective with regard to the pulling-off only exists at even smaller tilting angles, including the parallel position of the raising arm 4 with respect to the faceplate section 8 shown in FIG. 2c. From this it becomes clear that in the exemplary embodiment shown the main function of the catching arm 40 is to reliably "catch" the raising arm 4 , with subsequent pressing of the wing 1 on the fixed frame 2.

When the wing is closed, the fourth wing articulation point 42 and the fifth wing articulation point 48 are closer to the first wing articulation point 12 than the driving pin 58. When the wing 1 is tilted open, the deployment arm 4, the catch arm 40 and the guide lever 46 are accordingly with respect to the faceplate section 8 inclined in the same direction. The dimensions of the tentacle end section, in particular the length of the fork tine 44a, can thus be relatively short and, moreover, there are more favorable ones Power transmission ratios to the extension arm 4, namely a long effective lever arm.

The interaction of the actuating element 20 according to the invention and the catch arm 40 according to the invention according to the embodiment shown will now be explained in more detail below with reference to FIGS. 1 and 2. In Figure 1, the position of the extension arm 4 is shown at the maximum tilt opening angle. The bolt forming the first wing articulation point 12 strikes the right end of the elongated hole 10, the arm 20b of the actuating element 20 and the support arm 15 are pivoted out of the plane E with the maximum possible swivel angle, the bolt 24 on the closer to the fixed frame 2 End of the slot 26 stops. The drive rod section 32 assumes its left-most possible position in the arrangement shown, the rack section 30 and the toothed sector 28 being in engagement with one another.

The catch arm 40 and the guide lever 46 are also pivoted from the plane E to the fixed frame 2 with a maximum pivoting angle. The guide pin 56 stops at the left end of the cam pin guide 54 and the hinge pin 50 stops at the end of the elongated hole 52 closer to the second catch arm end 40b.

A displacement of the drive rod section 32 to the right by approximately 9 length units leads to the position of the extension arm shown in FIG. 2a. The pivot position of the catch arm 40 and the guide lever 46 has not yet changed, since the guide pin 56 moves in a straight line section 54a of the cam pin guide 54 which extends parallel to the direction of movement of the guide pin 56. The driving pin 58 is not yet within reach of the end section 44, in particular the fork prong 44a.

The swivel angle of the extension arm 4 and the swivel angle of the support arm 14 are now significantly reduced, the first wing pivot point 12 has moved to the left within the elongated hole 10 and now occupies approximately a central position with respect to the elongated hole 10. The bolt 24 and the bolt forming the second wing articulation point 18 now each take approximately a central position with respect to the elongated hole 26 and the arcuate elongated hole 34, respectively. The rack section 30, which has moved to the right together with the drive rack section 32, is still in engagement with the toothed sector 28.
The position of the catch arm 40 is unchanged since the guide pin 56 has only moved within a straight section 54a of the cam pin guide 54, which, in the position of the guide lever 46 shown in FIGS. 1 and 2a, extends in the direction of movement of the guide pin 56.

A further movement of the drive rod section 32 to the right by a further approx. 4.5 length units leads to the position of the extension arm 4 and the other components shown in FIG. 2b. The displacement of the rack section 30 triggered by the displacement of the drive rod section 32 caused a further rotation of the actuating element 20 via the toothed sector 28 meshing with the rack section 30, so that the arm 20b of the actuating element 20 is now only relatively slightly inclined with respect to the plane E. The same applies to the support arm 14, the bolt 24 with respect to the elongated hole 26 further approaching the end of the elongated hole 26 closer to the pivot arm 16. The hinge pin forming the second wing articulation point 18 has further approached the end of the arcuate elongated hole 34 closer to the arm 20b. The hinge pin forming the first wing articulation point 12 has within the elongated hole 10 further approximated the left end of the elongated hole 10, which is widened like a keyhole for assembly purposes. The rack section 30 and the toothed sector 28 continue to mesh with each other.

During the transition to the position shown in FIG. 2b, the driving pin 58 is in the catching area of the end arm section 44, more precisely the longer fork 44a, whereupon a pivoting movement of the catch arm 40 to the plane E began. This pivoting movement was triggered by the guide pin 56 entering an actuating section 54b of the cam pin guide 54 which adjoins the rectilinear region 54a and does not extend in the direction of movement of the guide pin 56. By striking the guide pin 56 on the pin guide edge delimiting the actuating section 54b in the direction of movement of the guide pin 56, the movement of the guide pin 56 calls for a pivoting movement of the guide lever 46 and thus, via the pin-pin guide connection 50, 52, a corresponding pivoting movement of the catch lever 40 in the same direction. Because of the arrangement of the fifth wing pivot point 48 and the guide pin 56 already described, a relatively long lever arm is effective, so that the torque causing the pivoting movement is increased. The fork tine 44a engages on the driving pin 58 of the raising arm 4, so that the raising arm 4 is used not only by the actuating element 20, but also by the catch arm 40 to the wing 1. The movement of the actuating element 20 and the guide lever 46 and thus the catch arm 40 must be coordinated with one another so that there is no tension in the mechanism. This can be achieved by appropriate design of the actuating section 54a of the cam pin guide 54.

After displacement of the drive rod section 32 and thus of the rack section 30 to the right by a further approx. 4.5 length units, the end position shown in FIG. 2c is reached. The extension arm 4 now extends essentially parallel to the faceplate section 8. The same applies to the support arm 14 and the arm 20b of the actuating element 20 as well as for the catch arm 40 and the guide lever 56. The guide pin 56 is now out of the actuating section 54b of the cam pin guide 54 emerged and into a rectilinear section 54c of the cam pin guide, which in this position of the guide lever extends parallel to the direction of movement of the guide pin 56 occurred. Also, the rack section 30 is now out of engagement with the toothed sector 28. The drive rack section 32 can now be moved further to the right without the actuating element 20 or the guide lever 46 being affected, for. B. to control other functions of the connecting rod section 32 associated fitting parts, in particular locking the wing 1 on the fixed frame 2 or selecting the ready-to-turn position.

During the transition from the position shown in FIG. 2b to the end position shown in FIG. 2c, the catch arm 40 and the actuating element 20 and thus the support arm 14 have moved in a coordinated manner and have pulled the catch arm 4 together on the wing 1. The second extension arm end or the hinge pin forming the first wing articulation point 12 now take their leftmost position with respect to the elongated hole 10. The bolt 24 has arrived at the end of the elongated hole 26 closer to the second wing pivot point 18, while the bolt forming the second wing pivot point 18 has arrived at the end of the arcuate elongated hole 34 closer to the arm 20b of the actuating element 20.

An unintentional swiveling out of the extension arm 4 is prevented by the guide pin 56 being located in the straight section 54c of the cam pin guide 54, so that the guide lever 46 fixes the catch arm 40 and the latter via the fork-shaped end section 44 the drive pin 58. The extension arm 4 is thus securely held in parallel to the faceplate section 8. A well-defined position of the extension arm is given by a stop 60, on which the longer fork 44a strikes. The driving pin 58 engages on both sides with the catch arm end section 44, that is to say with the longer fork 44a and the shorter fork 44b.

If the sequence of FIGS. 1 and 2a, b, c is viewed in the reverse order, it shows the opening of a wing. Starting from FIG. 2c, the drive rod section is displaced 32 by moving the guide pin 56 into the actuating section 54b, a pivoting movement of the guide lever 46 and thus the catch arm 40 from the parallel position to the faceplate section 8. Due to the engagement of the shorter fork prong 44b on the driving pin 58, the deployment arm 4 is thereby pivoted out. At the same time, engagement is again established between the toothed rack section 30 and the toothed sector 28, so that the displacement of the connecting rod section 32 also results in the arm 20b of the actuating element 20 and thus the support arm 14 being pivoted out. The actuating element 20 and the catch arm 40 thus press the extension arm 4 away from the wing 1, which causes the wing 1 to be pressed off the fixed frame 2.

When the drive rod section 32 is moved further to the left, the driving pin 58 disengages from the shorter fork prong 44b, so that subsequently only the actuating element 20 presses the wing 1 from the fixed frame 2 via the support arm 14 and the extension arm 4. This tilt opening movement may also be supported by gravity.

In the position shown in FIG. 2b, the driving pin 58 is still in the catching area of the longer fork tine 44a. A further movement of the drive rod section to the left causes the driving pin 58 to emerge from the catch area of the longer fork prong 44a. A further pivoting movement of the catch arm 40 is therefore unnecessary and is terminated when the guide pin 56 enters the straight section 54a of the cam pin guide 54 (cf. FIG. 2a). The drive rod section 32 can be shifted further to the left until the tilt opening position shown in FIG. 1 is reached with the maximum tilt opening angle.

In summary, the invention relates to an opening device for windows, doors or the like with a tilt and turn sash, which comprises a three-point scissors from a raising arm and a support arm. The wing can be pressed or pressed by means of an actuating element acting directly or indirectly on the raising arm, the actuating element being actuatable by a drive element. According to the invention, the actuating element and the driving element each have a toothing section through which the actuating element and the driving element can be coupled in motion. According to another aspect, it is proposed to design the opening device with a catch arm which can be actuated by the drive element and which can be brought into engagement with the opening arm in a tilting angle range of smaller tilting angles in order to press or depress the wing.

Claims (24)

Opening device for windows, doors or the like with a tilt and turn sash (1) having an axis of rotation and an essentially orthogonal tilt axis, comprising: - A extending arm (4) defining a maximum tilt opening angle, which is articulated at a first extending arm end (4a) at a frame pivot point (6) lying on the axis of rotation on the fixed frame (2) about the axis of rotation, and at its second extending arm end (4b) is articulated at a first wing articulation point (12), which can be displaced essentially parallel to the tilt axis, about a first axis which is essentially parallel to the axis of rotation when the wing (1) is closed; - A support arm (14) which, at a first support arm end (14a) at an extending arm articulation point (16) between the first (4a) and the second (4b) end of the extending arm (16) on the extending arm (4), has a closed wing (1) is rotatably articulated to the axis of rotation substantially parallel to the second axis,
and which is articulated at its second support arm end (14b) at a second wing articulation point (18) on the wing (1) so as to be rotatable about a third axis which is substantially parallel to the axis of rotation when the wing (1) is closed,
the extension arm articulation point (16) being arranged when the wing (1) is closed between the first (12) and the second (18) wing articulation point; - A couplable with a manually and / or motor-operated drive unit, essentially drive element (32) parallel to the tilt axis and displaceable parallel thereto, in particular drive rod section; and - An actuating element (20) which acts directly or indirectly on the raising arm (4) and can be actuated by the driving element (32), for pressing on or pushing off the wing (1), characterized,
that the actuating element (20) and the driving element (32) each have a toothed section (30 or 32) or the like, which for pressing or pressing the wing (1) by the actuating element (20) at least in a partial range of the maximum tilt opening angle comb together. Display device according to claim 1, characterized in that the drive element (32) has a rack section (30) which is rotatably mounted with a toothed sector (28) on the wing (1) about an axis substantially parallel to the axis of rotation when the wing (1) is closed Actuating element (20) combs. Display device according to claim 2, characterized in that the axis (wing articulation point 22) of the actuating element (20) with respect to the first axis (wing articulation point 12) in the direction perpendicular to the sash frame plane and, in the case of a tilt-open sash frame, towards the fixed frame (2) is offset, and that the rack section (30) is offset in relation to the first axis (wing pivot point 12) in the opposite direction. Display device according to one of the preceding claims, characterized in that the actuating element is designed as a separate element (20) which is at a third wing articulation point (22) is pivoted on the wing (1) about a fourth axis which is essentially parallel to the axis of rotation when the wing (1) is closed. Display device according to claim 2, characterized in that the actuating element (20) engages on the support arm (14) via a bolt-bolt guide connection (24, 26). Display device according to claims 4 or 5, characterized in that in the direction parallel to the tilt axis the second wing articulation point (18) is offset relative to the third wing articulation point (22) towards the first wing articulation point (12). Display device according to one of the preceding claims and according to claim 2, characterized in that the actuating element (20) and the support arm (14) overlap in the region of the second wing articulation point (18) and in that the actuating element (20) has an arcuate elongated hole (34 ) into which a hinge pin or the like engaging the second wing articulation point (18) engages. Display device according to one of the preceding claims, characterized in that the first (12), second (18) and third (22) wing articulation point are formed on a faceplate section (8) which is fixed to the wing in a sash groove and is essentially parallel to the tilt axis, and that the drive element (32) is arranged below the faceplate section (8) in the rebate groove, with the toothed section (30) projecting above the faceplate section (8). Display device according to one of the preceding claims or according to the preamble of claim 1, characterized in that a catch arm (40) which can be actuated by the drive element (32) is provided and which at a first catch arm end (40a) at a fourth wing articulation point (42) on the wing (1) by one when the wing (1) is closed The axis of rotation, which is essentially parallel to the fifth axis, is rotatably articulated and can be brought into engagement with a catch arm end section (44) comprising the second catch arm end (40b) with a driving element (58) of the deployment arm (4) in a first tilt angle range for smaller tilt angles or pressing the wing (1) and which is out of engagement with the driving element (58) in the rest of the opening tilt angle range. A raising device according to claim 9, characterized in that the catch arm (40) also serves to hold the raising arm (4) at least in the ready-to-turn position in a substantially parallel orientation to the tilt axis. Display device according to claims 9 or 10, characterized in that the end arm section (44) is fork-shaped, in particular with two fork tines (44a, 44b), the driver element (58) preferably being essentially bolt-shaped. Display device according to claim 11, characterized in that the second fork tine (44b) which is closer to the sash frame when the sash (1) is opened is shorter than the first fork tine (44a). Display device according to one of claims 9 to 12, characterized in that in the direction parallel to the tilt axis the fourth wing pivot point (42) at closed wing (1) between the driving element (58) and the first wing pivot point (12). Display device according to one of claims 9 to 13, characterized in that the catch arm (40) can be actuated by a separate guide lever (46) which is attached to a fifth wing articulation point (48) on the wing (1) at a first guide lever end (46a). is pivoted about a sixth axis which is essentially parallel to the axis of rotation when the wing (1) is closed, the guide lever (46) being actuatable by the drive element (32). Display device according to claim 14, characterized in that the guide lever (46) has a curved pin guide (54) into which a guide pin (56) which is coupled to the drive element (32) engages. Display device according to claim 15, characterized in that the sixth axis (wing articulation point 48) is offset relative to the fifth axis (wing articulation point 42) in the direction perpendicular to the sash frame plane and, in the case of the sash opened, from the fixed frame, and in that the guide pin is offset in relation to the fifth (wing pivot point 42) axis in the opposite direction. Display device according to one of claims 14 to 16, characterized in that the guide lever (46) acts on the catch arm (40) via a pin-pin guide connection (50, 52). Display device according to one of claims 14 to 17, characterized in that in the direction parallel the fifth wing articulation point (48) lies between the fourth wing articulation point (42) and the first wing articulation point (12) to the tilt axis. Display device according to claim 17 or 18, characterized in that the fourth (42) and fifth (48) wing articulation points are formed on the faceplate section (8), and in that the guide bolt (56) is arranged next to the faceplate section (8) and moves substantially parallel to the tilt axis when the driving element (32) is displaced. Display device according to one of claims 17 to 19, characterized in that the cam pin guide (54) has a first rectilinear section (54a) into which the guide pin (56) engages when the end arm section (44) does not engage the driving element (58) is engaged, the first rectilinear portion (54a) extending in the assigned rotational position of the guide lever (46) in the direction of movement of the guide pin (56),
that the first straight section (54a) is followed by an operating section (54b) of the cam pin guide (54) which does not extend in the direction of movement of the guide pin (56) and into which the guide pin (56) engages to actuate the guide lever (46) , and
that the cam pin guide (54) has a second rectilinear section (54c) adjoining the actuating section (54b), into which the guide pin (56) engages when the extension arm (4) is oriented essentially parallel to the tilt axis, the second rectilinear section (54c) in the assigned rotational position of the guide lever (46) extends in the direction of movement of the guide pin (56). Display device according to one of claims 1 to 8, in particular also according to one of claims 9 to 20, characterized in that the toothed sections (28, 30) mesh with one another over the entire tilt opening angle. Display device according to one of claims 1 to 8 and according to one of claims 9 to 20, characterized in that the toothing sections (28, 30) mesh with one another only in a second tilting opening angle range of larger tilting angles, the first and the second tilting opening angle range overlapping at least slightly and the first and second tilt opening angle ranges together comprise all tilt opening angles. Turn-tilt fitting for windows, doors or the like, with an opening device according to one of the preceding claims. Window, door or the like, with an opening device or a turn-tilt fitting according to one of the preceding claims.

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