WO2016206871A1

WO2016206871A1 - Corner bearing for a tilt-and-turn window

Info

Publication number: WO2016206871A1
Application number: PCT/EP2016/061256
Authority: WO
Inventors: Hubert WEISSENBACHER
Original assignee: Maco Technologie Gmbh
Priority date: 2015-06-23
Filing date: 2016-05-19
Publication date: 2016-12-29
Also published as: DE102015110088A1; EP3314080B1; EP3314080A1

Abstract

The invention relates to a corner bearing (10) for a tilt-and-turn window or a tilt-and-turn door with a fastening portion (12), two spaced-apart cheeks (18) which project next to one another away from the fastening portion, wherein at least one of the cheeks (18) has a through-hole (20), and a pivot pin (22) having at least one external thread (32) which extends between the cheeks (18) and is screwed to at least one internal thread (28). The corner bearing is characterised in that the at least one internal thread (28) and the external thread (32) are not adapted to one another, in order to generate increased friction in comparison to internal and external threads (28, 32) which are adapted to one another.

Description

ECK BEARINGS FOR A TILT-TILT WINDOW

The present invention relates to a corner bearing for a turn-tilt window or a turn-tilt door with a mounting portion, two spaced, side by side protruding from the mounting portion cheeks, wherein at least one of the cheeks has a through hole, and a pivot pin with at least one External thread, which extends between the cheeks and is screwed with at least one internal thread.

Such a corner bearing is usually arranged at a lower corner of a window frame and is used, for example, in turn-tilt windows to allow both a complete opening and tilting of a window sash. For this purpose, a pivot pin is usually mounted on the axle, which is tiltably arranged. For complete opening of the window sash of the sash can be opened with the pivot pin as a rotation axis. In addition, the pivot pin allows tilting the window sash by its tilting mobility. The pivot pin may for example comprise the internal thread and be screwed to the external thread of the axle. Alternatively, the pivot pin may for example have a sliding bearing and sit with the plain bearing on the axle. To adjust a position of the sash in the associated window frame, the position of the pivot pin can be moved laterally between the two cheeks by means of the axle pin. Such a lateral adjustment by means of the axle pin is effected by the rotation of the axle pin, wherein the position of the pivot pin and possibly the axle pin is laterally adjusted by the screwed inner and outer threads. Due to this lateral adjustment, the pivot pin is displaced laterally. The axle can therefore also be referred to as adjusting screw.

Disadvantageously, during tilting movements of the window sash, the pivot pin can only turn the axle bolt in one direction of rotation and thus cause an undesired adjustment of the lateral position of the pivot pin between the cheeks. To counteract such an effect, for example, brake coatings may be attached to the external thread or to the internal thread. However, such brake coatings can lose their effect after repeated adjustment or adjustment of the position of the axle pin.

It is therefore the object underlying the invention to provide a corner bearing, which permanently suppresses an undesirable lateral adjustment. This object is achieved by a corner bearing according to claim 1 and in particular by the fact that the at least one internal thread and the external thread are not adapted to each other in order to produce an increased friction compared to matched inner and outer threads. In other words, the inner and outer threads are designed differently in such a way that, although the inner and outer threads can be screwed together, they produce a strong friction or a strong resistance during screwing. In this way, a required force or a required torque for rotating the axle bolt relative to the internal thread is achieved. increases, whereby a lateral adjustment when tilting the window is prevented.

An inventive corner bearing can also be referred to as a corner bearing block.

Matched internal and external threads are understood to mean threads that are commonly used together. This means that the internal and external threads are threads which are used according to a common standard and within the tolerances of the respective standard. For example, the inner and outer threads may be ISO ISO or ISO 4014 metric ISO threads, Whitworth threads, or UN threads (the Unified Thread Standard). Preferred embodiments of the invention are described in the description, the drawings and the dependent claims.

According to a first advantageous embodiment, the pitch of the at least one internal thread and the pitch of the external thread are different. Due to the different gradients, jamming or distortion between the inner and outer threads can occur, as a result of which a stiffness in the rotation of the axle pin relative to the inner thread is achieved. In particular, the pitch of the at least one internal thread and the pitch of the external thread differ by at least 5%, preferably by at least 10%. Thus, for example, when using a standard MG thread, the internal thread have the specified by the associated standard slope of 1, 0 mm. In contrast, the external thread of the axle pin can have a pitch of less than or equal to 0.9 mm or greater or less equal to 1, 1 mm. By such a choice of gradients unwanted adjustment of the axle by tilting movements of the pivot pin can be almost eliminated. According to a further advantageous embodiment, the flank angle of the at least one internal thread and the flank angle of the external thread are different, in particular the flank angle of the at least one internal thread differs from the flank angle of the external thread by at least 4 °, preferably by at least 6 °. The flank angles of the inner and outer thread can therefore not be adapted to one another, as a result of which point contact points of the inner and outer threads can occur together. In this way, an increased friction can also be generated.

The core diameter of the external thread is preferably at least 1.5%, preferably at least 2%, larger than the core diameter of an external thread adapted to the at least one internal thread and / or the core diameter of the at least one internal thread is at least 5%, preferably at least 7 % smaller than the core diameter of an internal thread adapted to the external thread. The core diameter of the external thread can therefore be larger and / or the core diameter of the internal thread may be smaller than specified by a respective standard. This also allows increased friction can be achieved.

According to a further advantageous embodiment, the flank diameter of the external thread is at least 3%, preferably at least 5%, larger than the flank diameter of an external thread adapted to the at least one internal thread and / or the flank diameter of the at least one internal thread is at least 3%, preferably around at least 5%, smaller than the pitch diameter of a matched to the external thread internal thread. Due to the thus changed pitch diameter, the flanks of the Internal and external thread press more strongly against each other or rub against each other and in this way also produce an increased compared to matched inner and outer threads friction. More preferably, the nominal diameter of the external thread is at least 3%, preferably at least 5%, larger than the nominal diameter of an external thread adapted to the at least one internal thread and / or the nominal diameter of the at least one internal thread is at least 3%, preferably at least 5%. , smaller than the nominal diameter of an internal thread adapted to the external thread. Such a choice of the nominal diameters can also result in the thread flanks being pressed against one another more intensively, whereby the friction between the inner and the outer thread is increased. According to a further advantageous embodiment, the external thread and / or the at least one internal thread has an oval or elliptical cross-section. In this context, the cross-section can be regarded as the surface which, viewed in the axial direction, is defined by the outer boundary of the external thread or the inner boundary of the internal thread.

The elliptical cross section may be selected such that the length of a semiaxis of the ellipse of the external thread is greater than the radius of the cross section of the adapted external thread and / or the length of a semi-axis of the ellipse of the internal thread smaller than that compared to round, matched threads Radius of the cross section of the adjusted internal thread is. In this way, in turn, increased friction can be generated in a relative movement of the inner and outer threads to each other. Preferably, the external thread and the at least one internal thread are directly adjacent to each other. This means that the material of the external thread bears directly against the material of the internal thread, that is, for example, a metal of the external thread contacts a metal of the internal thread. As a result, no brake coating is attached to one of the threads.

According to an advantageous embodiment, a pivot pin is provided which comprises the at least one internal thread and is screwed by means of at least one internal thread with the external thread of the axle. As a result, the pivot pin can be displaced axially along the axle pin by rotation of the axle pin, whereby lateral adjustment of the pivot pin is made possible. The pivot pin may have a U- or C-shaped area or a through hole in which the internal thread is mounted. In a preferred embodiment, the axle pin is rotatably mounted with respect to the cheeks but axially immovable, so that the axle pin retains its axial position with respect to the cheeks during rotation. This means that the axle pin is not axially displaceable between the cheeks. In particular, the axle bolt is e.g. stored in slide bearings in through holes of the cheeks. A torque required for a rotation of the at least one internal thread relative to the external thread is then higher than the torque required for the rotation of the axle bolt in the plain bearings. This ensures that the axle pin in the plain bearings is turned back and forth as the window tilts.

According to an alternative embodiment, the at least one internal thread is arranged in the through hole of the one cheek. In this embodiment, both cheeks may have a through hole with an internal thread. The through holes serve to receive the axle bolt, the external thread can be screwed in this way with the internal threads. The internal threads are preferably identical. An axial extension direction defined by the axle pin and axial directions defined by the internal threads may coincide. In this embodiment, an axial position of the axle between the cheeks can be changed by rotation of the axle. This allows the axle also move a pivot pin axially.

According to a further advantageous embodiment, the axle pin on a circumferential recess, which serves as a bearing seat for a pivot pin. The axle pin can thus have a tapered region without external thread, in which a pivot pin rests on the axle. The areas of the axle bolt with external thread can thus serve as a lateral guide and stop for the pivot pin, whereby the pivot pin is laterally displaceable by means of the axle bolt.

By not matched threads is a torque which is required for a rotation of the axle bolt in the internal thread or the internal threads, larger than a transferable from the pivot pin by means of the bearing seat on the axle bolt torque. Consequently, the axle can not be rotated by the pivot pin during tilting movements of the window. The axle bolt thus remains in tilting movements of the window in its position, whereby an undesirable lateral adjustment is prevented.

According to a further advantageous embodiment, a pivot pin is mounted tiltably on the axle. The pivot pin can for this purpose have two parallel, spaced-apart projections. The distance between the projections may correspond to the diameter of the axle pin in the tapered region, wherein end portions of the projections may be interconnected by means of a clamp to secure the pivot pin to the axle pin. By means of the pivot pin thus mounted can a tilting of the window or the door, which are provided with the corner bearing, are made possible.

It goes without saying that various changes to the at least one internal thread and to the external thread, which lead to threads which are not adapted to one another, can be combined with one another. Thus, for example, a deviating from the norm slope can be combined with a modified flank angle and / or a modified core diameter. The indicated values of the deviations (for example the slope, the flank angle, the core diameter, etc.) are each the deviations from the ideal values given by a respective standard, i. without tolerances. The terms pitch, flank angle, core diameter, pitch diameter and nominal diameter can be defined in particular according to the manner defined in DIN 13-19. Accordingly, the pitch can be the axial distance between two thread flanks. The flank angle can denote the angle defined by two adjacent, mutually facing flanks. The core diameter may be twice the radial distance between the axis of rotation and the point of a thread flank which is closest to a rotation axis or axis of symmetry. Accordingly, the pitch diameter may be the core diameter plus the radial height of a thread flank. The nominal diameter can be specified as the flank diameter plus the radial height of a thread flank.

Another object of the invention is a fitting arrangement with a corner bearing of the type described above. The fitting assembly also includes a Ecklagerband, which preferably comprises a sleeve. By means of the corner hinge For example, a door or window sash can be attached to a door or window frame in a rotatable or pivotable manner.

The invention will now be described purely by way of example with reference to the drawings. Show it:

FIG. 1A shows a corner bearing according to the invention in a front view; FIG.

Fig. 1 B, the corner bearing of Figure 1A in a side view.

Fig. 2 is an enlarged portion of the corner bearing of Fig. 1 A without

Axle bolt in a front view;

3 shows a pivot pin in a lateral sectional view; and

Fig. 4 is attached to a coupling piece Ecklager in a perspective view.

Figures 1A and 1B show a corner bearing 10 which includes a base plate 12 serving as a mounting portion. The base plate 12 includes four along a straight line arranged countersunk holes 14 for mounting screws.

In a lower region (in the figures), the base plate 12 widened, wherein from a widened portion 16 resulting therefrom, two cheeks 18 projecting from each other, projecting side by side from the base plate 12, each having a through-hole 20. The through holes 20 of the cheeks 18 are arranged axially aligned with each other.

An internal thread 28 is provided in each of the through holes 20 (FIG. 2) and an axle pin 22 is mounted with an external thread 32 (FIG. rum as a bearing seat for a pivot pin 24 is used. The pivot pin 24 has two spaced projections 25 which engage around the axle pin 22 and so store the pivot pin 24 on the axle 22. By rotation of the axle pin 22, the position of the axle pin 22 in the axial direction between the cheeks 18 can be changed. In this way, the pivot pin 24 can be moved laterally between the cheeks 18 and thus adjusted for example during assembly of a (not shown) window sash. On a cheeks 18 opposite side of the base plate 12 are protruding from the base plate 12 two alignment mandrels 26, which are respectively arranged in the upper and lower end portions of the base plate 12.

Fig. 2 shows the widened portion 16 of the corner bearing 10 without the axle pin 22. There are two arranged in the through holes 20 internal thread 28 can be seen. An axial distance between two thread flanks is marked as distance I. The internal thread 28 is an M6 thread in the example shown. Accordingly, the distance I between two thread flanks is 1, 0 mm.

In Fig. 3, the axle pin 22 is shown in more detail. The axle pin 22 has a substantially cylindrical shape, wherein in the end faces of the axle pin 22 respectively axially extending recesses 30 are introduced with engagement surfaces for a Allen tool, by means of which the axle pin 22 can be rotated. The axle pin 22 includes on its peripheral surface an external thread 32, which is also formed as M6 thread.

Centered with respect to the extension direction of the axle pin 22, a circumferential groove 34 is inserted into the outer surface of the axle pin 22, which serves as a seat for the pivot pin 24. An axial distance A between the thread flanks of External thread 32 does not conform to the standard of 1, 0 mm but is made smaller with 0.9 mm. This deviating from the norm distance A causes a sluggish rotatability of the axle pin 22 in the cheeks 18, more precisely a sluggish rotatability of the external thread 32 in the internal threads 28th

Fig. 4 shows a corner bearing 10 in a perspective view. The corner bearing 10 is in contrast to the corner bearing 10 of Fig. 1A by means of its base plate 12 attached to a coupling piece 36. The coupling 36 may be recessed into a door or window frame (not shown) and secure the corner support to the door or window frame.

If the corner bearing 10 attached to a window frame, a (not shown) window sash can be placed on the pivot pin 24 by means of a sleeve of a corner band attached to the wing. Thus, the window sash is rotatable and tiltable. Due to the stiff rotation of the axle pin 22, an unwanted rotation of the axle pin 22 and thus an unintentional adjustment of the lateral position of the pivot pin 24 can be prevented by tilting the window sash.

LIST OF REFERENCE NUMBERS

10 corner bearings

12 base plate

14 sinkhole

16 widened section

18 cheek

20 through hole

22 axle bolts

24 pivot pins

25 advantage

26 alignment mandrel

28 internal thread

30 deepening

32 external thread

34 circumferential groove

36 coupling piece

I pitch thread flanks internal thread A distance thread flanks external thread

Claims

claims

Corner bearing (10) for a turn-tilt window or a turn-tilt door with

a fixing portion (12),

two spaced, side by side of the mounting portion projecting cheeks (18), wherein at least one of the cheeks (18) has a through hole (20), and

an axle bolt (22) having at least one external thread (32) which extends between the cheeks (18) and is screwed to at least one internal thread (28),

By doing so, that is

the at least one internal thread (28) and the external thread (32) are not adapted to each other to produce increased friction compared to mating internal and external threads (28, 32).

Corner bearing (10) according to claim 1,

By doing so, that is

the pitch of the at least one internal thread (28) and the pitch of the external thread (32) are different.

Corner bearing (10) according to claim 1 or 2,

By doing so, that is

the pitch of the at least one internal thread (28) and the pitch of the external thread (32) differ by at least 5%, preferably by at least 10%.

Corner bearing (10) according to at least one of the preceding claims, characterized in that

the flank angle of the at least one internal thread (28) and the flank angle of the external thread (32) are different, in particular the flank angle of the at least one internal thread (28) differs from the flank angle of the external thread (32) by at least 4 °, preferably by at least 6 ° ,

Corner bearing (10) according to at least one of the preceding claims, characterized in that a

the core diameter of the external thread (32) is at least 1.5%, preferably at least 2%, larger than the core diameter of an external thread adapted to the at least one internal thread (28) and / or

the core diameter of the at least one internal thread (28) is smaller by at least 5%, preferably by at least 7%, than the core diameter of an internal thread adapted to the external thread (32).

the flank diameter of the external thread (32) is at least 3%, preferably at least 5%, larger than the flank diameter of an external thread (32) adapted to the at least one internal thread (28) and / or

the flank diameter of the at least one internal thread (28) is smaller by at least 3%, preferably by at least 5%, than the flank diameter of an internal thread (28) adapted to the external thread (32).

7. Corner bearing (10) according to at least one of the preceding claims, characterized in that it e e n e c e e s that

the nominal diameter of the external thread (32) is at least 3%, preferably at least 5%, larger than the nominal diameter of an external thread (32) adapted to the at least one internal thread (28) and / or

the nominal diameter of the at least one internal thread (28) is smaller than the nominal diameter of an internal thread (28) adapted to the external thread (32) by at least 3%, preferably by at least 5%.

8. corner bearing (10) according to at least one of the preceding claims,

By doing so, that is

the external thread (32) and / or the at least one internal thread (28) have an oval or elliptical cross-section.

9. corner bearing (10) according to at least one of the preceding claims,

By doing so, that is

the external thread (32) and the at least one internal thread (28) lie directly against each other.

10. corner bearing (10) according to at least one of the preceding claims,

By doing so, that is

a pivot pin (24) is provided which comprises the at least one internal thread (28) and by means of the at least one internal thread (28) with the external thread (32) of the axle bolt (22) is screwed.

11. corner bearing (10) according to claim 10,

characterized in that the axle pin (22) with respect to the cheeks (18) is rotatably mounted but axially immovable.

12. corner bearing (10) according to at least one of claims 1 to 9,

By doing so, that is

the at least one internal thread (28) is arranged in the through hole of the one cheek (18).

13. corner bearing (10) according to at least one of claims 1 to 9 and 12,

By doing so, that is

the axle pin (22) has a circumferential recess (34), which serves as a bearing seat for a pivot pin (24).

14. Corner bearing (10) according to at least one of claims 1 to 9, 12 and 13, characterized g e k e n e c i n e t that

on the axle pin (22) a pivot pin (24) is mounted tiltably.

15. fitting arrangement with a corner bearing (10) according to at least one of the preceding claims and a Ecklagerband.