DE9413891U1 - Tape for doors, windows and the like - Google Patents

Abstract

The strip (100) has a disc (50) to limit the friction on the sliding surfaces (22',24'). The disc is of a material with good sliding properties arranged between an adjuster (22) and a counter bearing (24) which limits the contact pressure at the sliding surfaces. The screws to connect the adjuster and the counter bearing are headed screws (125) with a conical under-section (127) at the head (123).

Description

The invention relates to a tape of the type corresponding to the preamble of claim 1.

Such hinges are known in various designs. The abutment part is usually essentially plate-shaped and is fixed immovably to the mounting surface of the frame or sash by the fastening screws. The adjustment part comprises the hinge part that holds the hinge pin and is guided horizontally on the abutment part. The displacement is brought about by an adjustment element such as a horizontal threaded spindle parallel to the mounting surface or an eccentric.

Within the framework of these common features, there are different embodiments with regard to the mutual arrangement and connection of the abutment part and the adjustment part.

DE-GM 70 10 559 shows an embodiment in which a plate-shaped abutment part rests directly on the fastening surface of a sash frame and the adjustment part in the fastening area is above or, as seen from the observer standing in front of the frame, in front of the abutment part.
The fastening _screws extend through the adjustment part and the abutment part into the fastening surface of the sash and pull the adjustment part against the fixed abutment.

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D-45133 ESSEN ·

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bearing part.

In DE 34 12 953 C2, the arrangement is reversed. Here, the rear side of the adjustment part rests against the fastening surface and has a rectangular guide opening into which an abutment part with a T-shaped vertical cross-section engages, which rests with the undersides of the crossbar on the edges of the rectangular guide opening and pulls the adjustment part against the fastening surface when the fastening screws that pass through the abutment part are tightened.

In the DE-GM 93 17 065, the plate-shaped abutment part is again placed directly on the fastening surface of a sash and encompasses the front side of the sash with an angle. In addition to fastening screws, which in the fastening area pass through both the adjustment part and the abutment part and engage in the sash, additional connecting screws are provided which pass through the adjustment part and engage in threaded holes in the abutment part in order to pull the two parts together and connect them.

The adjustment part and the abutment part rest against each other on sliding surfaces in the fastening area. During adjustment, the adjustment part moves horizontally relative to the abutment part while sliding on the sliding surfaces. In doing so, friction must be overcome, which depends in particular on the magnitude of the force acting perpendicularly to the sliding surfaces, i.e. how tightly the screws connecting the two parts and in particular the fastening screws that pass through both parts are tightened.

One possibility would be to achieve the adjustment by loosening the fastening screws during the adjustment process. If the loosening is extensive, the wing adjusts itself under its own weight and requires support. Adjusting the wing is then laborious because it must be checked again and again whether the wing is still in the correct position after re-attaching.

tightening the fastening screws. A compromise would be to loosen the fastening screws only partially so that they can just about hold the sash without unwanted self-adjustment. However, this requires very sensitive work when tightening the fastening screws. The actual aim is to tighten the fastening screws to their final torque when installing the hinges and then to be able to adjust the hinge in the horizontal direction without having to partially loosen the fastening screws and then tighten them again.

This goal is achieved when the hinge parts are attached to a fixed frame or a sash frame made of hollow profiles using self-tapping screws. The tightening forces are automatically limited by the type of screws to a level that does not hinder the horizontal adjustment of a hinge part.

The situation is different, however, for hinge fastenings with threaded screws that engage in solid threaded parts, which are arranged inside the hollow profiles and form the support of the thread instead of their front wall. Examples of this are fastenings using expansion bushes according to DE-GM 73 17 785 or cuboid threaded pieces according to DE-GM 76 25 715. If the tightening torque of the fastening screws is not carefully calculated, tightening forces can be applied that make it difficult or even impossible to adjust the adjustable hinge parts.

The invention is based on the object of facilitating the adjustment of an adjustable strap part of the type in question when the fastening screws are tightened.

This object is achieved by the invention set out in claim 1. The sliding surfaces are formed on the mutually facing boundary surfaces of the abutment part and the adjustment part. In measures to limit the friction at this point, the fixing of the

The friction determining the hinge part on the fastening surface is not reduced. If the abutment part is in direct contact with the fastening surface, no friction-limiting means are provided on the contact surface. However, if the adjustment part is in direct contact with the fastening surface and the abutment part is above it, no friction-limiting measure is provided between the adjustment part and the fastening surface. This only happens on the sliding surfaces, where without such measures friction occurs which makes adjustment more difficult but does not affect the holding effect of the fastening arrangement. The friction is limited to such an extent that adjustment can still be carried out with the fastening screws tightened, so that the sash can be adjusted in the frame with the hinges fully installed.

Although the invention was based on problems that arise with a certain type of fastening with fastening screws engaging in solid threaded pieces inside the frame profiles, it is not limited to this type of fastening.

The friction during the movement of a body on a sliding surface depends in general on the friction coefficients between the two friction partners and the pressure force with which the body is pressed against the sliding surface.

Accordingly, a first embodiment of the invention consists in reducing the coefficient of friction on the sliding surfaces (claim 2), in particular by means of a disk made of a material with good sliding properties arranged between the adjustment part and the abutment part and essentially covering the sliding surfaces (claim 3).

The sliding surfaces could, for example, be specially lubricated or have a surface structure filled with lubricant. The disk could be made of a plastic with good sliding properties or of a porous sheet filled with lubricant.

The fastening screws can be tightened normally. However, the resistance to the mutual displacement of the adjustment part and the abutment part is reduced, so that adjustment is always possible.

An alternative embodiment of the invention consists in that the means to be provided limit the contact pressure of the abutment part and the adjustment part on the sliding surfaces (claim 4).

A practical embodiment of this idea is represented in claim 5.

The ring rests with its inner circumference on the conical lower part of the head of the respective screw, which means that only a component of the force transmitted by the conical lower part corresponding to the cone angle acts in the axial direction of the head screw and appears as contact pressure.

The preferred embodiment of such an arrangement is set out in claim 6.

The conical lower part of the screw head does not initially lie flat, but only in a ring-shaped zone on the inner circumference of the expansion ring. As tightening progresses, the conical lower part of the screw head slides into the expansion ring and pushes it apart radially until it lies flat over essentially the entire height of the inner circumference of the expansion ring. The resistance to the tightening torque then increases significantly and a natural limit to the tightening torque is given, with only a fairly precisely predeterminable component of the transmitted force in the axial direction of the screw.

In a specific embodiment of an adjustable band part, in which the adjusting part is arranged "above" the abutment part, the arrangement can be made in detail according to claim 7.

An important embodiment of an embodiment with an expansion ring is the grommet according to claim 8. Its length is such that the ring can simultaneously rest on the edges of the

-S-

long hole and is supported by the grommet in the axial direction of the screw. This creates a kind of stop when the screw is tightened, when the tightening torque increases significantly. By suitably coordinating the dimensions of the length of the grommet and the diameter of the expansion ring, it is possible to ensure that the expansion ring exerts a just acceptable contact pressure on the adjustment part, which does not yet hinder the adjustment, but is sufficient to securely fix the band part on the fastening surface.

According to claim 9, the grommet and ring can be a one-piece separate part, which has manufacturing advantages.

But the ring can also be a separate part that is pushed onto the screw like a washer.

A third possible embodiment of the invention is the subject of claim 11. Even with a disc spring, it is possible to ensure that only a limited force is exerted in the axial direction of the screw, which produces a correspondingly limited contact pressure.

The prerequisite for this is that the disc spring is not completely flattened.

This requirement can be supported by the design according to claim 12. The grommet helps to limit the further tightening of the screw before the disc spring is completely flattened and, without spring action, transfers the tightening force of the screw directly in the manner of a washer.

For manufacturing reasons, the grommet can be a separate part of both the expansion ring and the disc spring (claim 13) and, for reasons of clean concentric guidance, can engage in a recess in the abutment part (claim 14).

Alternatively, however, it is also possible to form the grommet by an extension of the abutment part {claim 15).

The drawing shows embodiments of the invention.

Fig. 1 shows a front view of a hinge, partially in section, in a plane passing through the axis of the hinge pin and parallel to the fastening surface:

Fig. 2 shows a horizontal section through the adjustable hinge part to be attached to the sash:

Fig. 3 shows a section along the line III - III in Fig. 1;

Fig. 4 shows a view of a friction reducing disc:

Fig. 5 shows a view corresponding to Fig. 2 of another embodiment of the band;

Fig. 6 and 7 show enlarged sections of Fig. 5 in two different tightening phases of the fastening screw.

Fig. 8 shows a third embodiment in a section corresponding to Fig. 2;

Fig. 9 shows a fourth embodiment in a section corresponding to Fig. 2;

Fig. 10 shows a section of Fig. 9 on an enlarged scale.

In Fig. 1, a fixed frame 1 and a casement frame 2 can be seen, which can consist of aluminum profiles, for example, and are only indicated schematically. They are pivotally connected to one another by a hinge 100. The hinge 100 contains a frame hinge part 10 and a casement hinge part 20, which are pivotally connected to one another by a hinge pin 30 with a hinge axis 7 that is vertical in the operating position. As can be seen from Fig. 1, the casement hinge part 20 is supported on the frame hinge part 10 via a weight-transferring friction-reducing disk 41. The hinge pin 30 is mounted in the frame hinge part 10 in a non-rotating hinge pin bushing 40 and continues into the casement hinge part 20 and is held there in a rotationally fixed manner.

The frame band part 10 holds a

vertical flat boundary surface of the fixed frame 1, which has a rear flat contact surface that rests on the fastening surface. A hinge part 6 is connected in one piece to the fastening part 4, which is horizontally offset from the fastening part 4 and has a cylindrical recess for receiving the hinge pin bushing 40. This is eccentric, i.e. the cylindrical outer peripheral surface and the cylindrical inner peripheral surface of the hinge pin bushing 40 have axes that are laterally offset from one another by the amount of eccentricity. Depending on the rotational position of the hinge pin bushing 40, the position of the hinge pin 30 relative to the hinge part 10 can be adjusted.

The band part 10 is fastened by fastening screws 15 screwed vertically into the fastening surface of the frame 1, which penetrate the fastening part 4 from the front. The fastening area is covered by a cover 12, so that the screw heads can no longer be reached after the fastening screws 15 have been tightened.

The hinge part 20 to be fastened to the wing 2 also comprises a fastening part 14 with a laterally offset hinge part 16 in which the hinge pin 30 is held in a rotationally fixed manner. The fastening area of the fastening part 14 can be covered by a cover 21 which, after fastening and adjustment, makes the fastening screws 25 of the hinge part 20 inaccessible. The cover 21 is designed as an angle piece in the manner shown in Fig. 2, which with its right leg 21' directed towards the fastening surface 3 in Fig. 2 overlaps the right side of the fastening part 14 and is fixed at the free end of the leg 21' by a tongue and groove arrangement 13. The other leg 21" of the cover 21 extends in front of the front side 11 of the fastening part 14 which is parallel to the contact surface 5 and has an approximately

triangular cross-section rising towards the hinge part 16, which engages with its edge on the free leg under a projection 18 of the hinge part 16. It is secured by a screw 17 which is accessible when the wing is open.

In addition to the cover 21, the hinge part 20 comprises an adjustment part 22, which comprises the fastening part 14 and the hinge part 16, as well as an essentially plate-shaped abutment part 24 with the dog-bone-like outline shown in Fig. 1. The abutment part 24 is arranged in a recess 23 of the fastening part 14 of the adjustment part 22 and faces the flat bottom 22' of the recess 23 with its flat underside 24'. The abutment part 24 is penetrated by two fastening screws 25, which engage vertically into the fastening surface 3 through an elongated hole 26 in the adjustment part 22. On the back of the wall of the frame of the wing 2 forming the fastening surface 3, a solid threaded piece is provided, into which the fastening screws 25 can be screwed.

The abutment part 24 has a sleeve-like projection 36 on the back, through which the fastening screw 25 extends and which engages in a corresponding hole in the fastening surface 3 in order to fix the abutment part 24 to the fastening surface 3.

A head screw 27 perpendicular to the hinge axis 7 is arranged in the recess 23, which is supported on both sides in the recess 23 in its axial direction and passes through a threaded hole 28 of the abutment part 24 horizontally and parallel to the fastening surface 3. The head of the screw 27 is accessible through an opening 29 in the right wall in Figs. 1 and 2 of the fastening part 14 of the adjustment part 22 and can be rotated, by means of which the position of the adjustment part 22 can be adjusted relative to the abutment part 24 fixed on the fastening surface 3.

This attitude requires a shift in the

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Adjusting part 22 on the one hand against the fastening surface 3, on the other hand against the flat underside 24' of the abutment part 24. Without special measures, the mutually facing surfaces 22', 24' of the adjusting part 22 and the abutment part 24 form sliding surfaces with considerable friction. In order to reduce the friction at this point, a disk 50 is inserted between the sliding surfaces 23', 24', the outline of which can be seen in Fig. 4 and corresponds to the outline of the abutment part 24. The projections 36 of the abutment part 24 pass through the holes 51 of the disk 50. The disk 50 is made of a material with good sliding properties, i.e. of a suitable plastic or a sheet metal which has at least one lubricant-filled porous surface.

With the same tightening force of the fastening screws 25, which clamp the fastening part 14 of the adjustment part 22 between the abutment part 24 and the fastening surface 3, the friction is not reduced between the fastening part 14 and the fastening surface 3, but rather between the abutment part 24 and the adjustment part 22, so that the adjustment by means of the screw 27 is made easier and can also be carried out when the fastening screws 25 are fully tightened.

Where functionally identical parts are present in the other embodiments, the reference numbers are the same.

In the band part 120 of Fig. 5, the abutment part 124 is arranged directly on the fastening surface 3 and engages with the sleeve-like centering or fixing projections 136 surrounding the fastening screws 125 in corresponding holes in the fastening surface 3.

The adjustment part 122 lies on or in front of the abutment part 124 and is pulled down onto the abutment part 124 by the fastening screws 125, which pass through the adjustment part 122 and the abutment part 124. The parts 122,124 lie against each other via sliding surfaces 122',124'. The adjustment screws 125, which, like

in the band part 20 of Fig. 1 to 4, two are present one above the other, each of which passes through an elongated hole 115 of the adjustment part 122. A transmission piece 116 is provided, which consists of a grommet 117, which is seated with the foot part in a recess 118 of the abutment part 124, and an expansion ring 119, which in this embodiment is integral with the grommet 117 and projects radially from its outer circumference in order to lie axially on the top of the edges of the elongated hole 115 and to transfer the tightening force of the screw 125 to the adjustment part 122 and to press it against the abutment part 124.

In Fig. 6 and 7, the design in the area of the fastening screws 125 is shown enlarged. The fastening screws 125 have a head 123 with a conical lower part 127, the cone angle of which in the embodiment is approximately 60°, so that the half cone angle 128 indicated in Fig. 6 is approximately 30°.

The transfer piece 116 encloses the shaft of the fastening screw 125 with its sleeve 117 with a small amount of play. The expansion ring 119, which in the exemplary embodiment is one piece with the sleeve 117, has a conical inner circumference 129 which widens towards the conical lower part 127 of the head 123, but has a smaller cone angle of approximately 45° in the exemplary embodiment, so that the half cone angle 130 indicated in Fig. 6 is approximately 22.5°. If the fastening screw 125 is therefore pushed further downwards from above according to Fig. 6, it initially comes to rest on the edge 131 with the conical lower part 127 of the head 123. When the fastening screw 125 is tightened, the conical lower part 127 slides further into the expansion ring 119 and pushes it radially apart at the edge 131 until the state shown in Fig. 7 is reached, in which the conical lower part 127 and the inner circumference 129 of the expansion ring 119 are in flat contact. When this state is present, the pressure for further turning the fastening screw 125 increases.

required tightening torque very strongly, so that this tightening torque is limited. Only one component of the axial force of the fastening screw 125 is transferred to the adjustment part 122 via the expansion ring 119, which can be determined not only by the cone angle on the lower part 127 but also by the length of the grommet 117, the depth of the recess 118 and the expansion ring 119. In this way it is ensured that, despite the fastening screw 125 being fully tightened, the adjustment part 122 is not clamped so tightly onto the abutment part 124 that adjustment by means of the screw 27 (Fig. 1) or by means of a similar element is no longer possible.

The expansion ring 119 would also function without the grommet 117. However, the grommet 117 provides additional support, which at the moment of full engagement according to Fig. 7 results in an even greater increase in the tightening torque required to further turn the fastening screw 125.

The design of the inner circumference of the expansion ring 119 could also be different, e.g. by the expansion ring 119 having a cylindrical inner circumference with a diameter that only slightly exceeds the diameter of the screw shaft. Even then, the expansion ring 119 with an upper edge corresponding to the edge 131 first comes into contact with the conical lower part 127 and when tightened, the conical lower part 127 works its way into the expansion ring to a point where the tightening torque increases very sharply.

The cover 121 is held in place at the band part 120 by means of a screw 109.

In the embodiment according to Fig. 8, the cover 221 is also fixed by means of a screw 109. The adjustment part 222 is again arranged on or in front of the abutment part 224. The parts 222, 224 lie against one another via sliding surfaces 222', 224'. The abutment part 224 lying directly on the fastening surface 3 has

a one-piece projection that passes through an elongated hole 115 of the adjustment part 222 and forms the grommet 217, which extends just to the top of the adjustment part 222. The expansion ring 229 is a separate ring that functions in the same way as the expansion ring 119 when the fastening screw 125 is tightened and only transfers part of the tightening force of the fastening screw 125 in its axial direction to the adjustment part 222.

In Fig. 9, a further band part 320 is shown, which in its construction essentially corresponds to the band part 220 of Fig. 8, but has a fastening screw 25 with a flat underside of the head, which corresponds to the fastening screw 25 of Figs. 1 to 3.

In further contrast to the band part 220, no expansion ring 219 is provided, which is radially expanded when the fastening screw 125 is tightened, but rather a disk spring 319, which in its concave curvature points downwards towards the abutment part 224. The grommet 317, which, as shown, is a separate part, but can also be integral with the abutment part 224, is dimensioned in such a way that it protrudes slightly over the top of the adjustment part 222, as can be seen from Fig. 10.

When the fastening screw 25 is tightened, the disc spring 319 is deformed until the area adjacent to the hole comes into contact with the front side of the sleeve 317. The edge of the disc spring 319 protrudes radially outwards and rests resiliently on the top of the adjustment part 222. The extent of the spring effect and thus the force transmitted to the adjustment part 222 depends on the dimensioning of the disc spring 319 and the dimensioning of the length of the sleeve 317. The lower the sleeve 317 is, the more the disc spring 319 is deformed and the greater the force transmitted. The end of the sleeve 317 must always be slightly above the top of the adjustment part 222 so that the disc spring 319 is not completely flattened and the force transmission is still achieved by its spring effect.

When the front side of the grommet 317 is reached, there is a sharp increase in the necessary tightening torque, which prevents or makes it difficult to turn the fastening screw 25 any further, thereby limiting the tightening of the fastening screw 25.

It is understood that friction-reducing means such as the disk 50 of Figs. 1 to 4 and means for limiting the pressure force according to Figs. 5 to 10 can also be implemented simultaneously on one band part.

Claims (15)

1. Belt (100) for doors, windows and the like,
with a strap part (10) which can be fastened to a front fastening surface of the fixed frame (1), with a hinge part (20, 120, 220, 320) that can be fastened to a front fastening surface (3) of the wing (2), with a hinge part (6,16) of both band parts
(10;20,120,220,320) passing through a vertical hinge pin (30) around which the two hinge parts (10;20,120,220,320) can be pivoted against each other, with an abutment part (24,124,224) forming part of one band part (20) which is fastened to the fastening surface (3) by fastening screws (25,125) screwed into the fastening surface (3) perpendicularly to the latter, with an adjusting part (22, 23) comprising the hinge part (6, 16) of one (20, 120, 220, 320) of the band parts and forming a further part of the band part (20, 120, 220, 320)
122,222), wherein the abutment part (24,124,224) and the adjustment part (22,122,222) are arranged on top of one another, connected by means of the fastening screws (25,125) and can be displaced against one another horizontally by means of an adjustment element while sliding against one another along sliding surfaces (22',24';122',124';222',224'), D-40239DÜSSaJDOR*f»»M&V*NYSTfiASSSV fit&öti iä /Z1J /98 145 -0 · TELEFAX 49 /211 /38 145-20 characterized, that means are provided for limiting the friction on the sliding surfaces (22',24';122',124';222 ^f ,224'). 2. Belt according to claim 1, characterized in that the means reduce the coefficient of friction on the sliding surfaces (22', 24'). 3. Belt according to claim 2, characterized in that the means comprise a disk (50) made of a material with good sliding properties, arranged between the adjustment part (22) and the abutment part (24) on the sliding surfaces (22', 24') and transmitting the system pressure. 4. Belt according to claim 1, characterized in that the means limit the contact pressure on the sliding surfaces (22', 24'; 122', 124'; 222', 224'). 5. Band according to claim 4, characterized in that the screws for connecting the adjustment part (122, 222) and the abutment part (124, 224) are exclusively head screws (125) with a conical lower part (127) of the head (123), which are arranged with the conical lower part (127) in a ring that transmits the tightening force of the head screws (125). 6. Band according to claim 5, characterized in that the ring is an expansion ring (119,219) which can be expanded radially by the conical lower part (127) of the head (123) until its inner circumference (129) rests flat against the conical lower part (127) of the head (123). 7. Band according to claim 5 or 6, characterized in that the abutment part (124,224) rests on the fastening surface (3) and the adjustment part (122,222) is arranged above the abutment part (124,224), that the respective fastening screw (125) has an elongated hole (115) of the adjustment part (122,222) and the abutment part (124,224) and engages in the fastening surface (3) and that the ring rests with its underside on the edges of the long hole (115) when the fastening screw (125) is tightened. 8. Band according to claim 7, characterized in that a grommet (117,217) is provided which surrounds the fastening screw (125) under the head (123) and passes through the elongated hole (115), which is supported in the axial direction of the fastening screw (125) on the one hand on the ring and on the other hand on the abutment part (124,224) and the length of which is dimensioned such that at the latest when the conical lower part (127) of the head (123) is in full contact with the inner circumference (129) of the ring, the underside of the ring rests on the edges of the elongated hole (115). 9. Band according to claim 8, characterized in that the grommet (117) and the ring (119) are a one-piece separate part (116). 10. Band according to claim 8, characterized in that the ring (219) is a separate part. 11. Band according to claim 4, characterized in that the abutment part (224) rests on the fastening surface (3) and the adjustment part (222) is arranged on the abutment part (224), that the fastening screw (25) passes through an elongated hole in the adjustment part (222) and the abutment part (224) and engages in the fastening surface (3) and that the fastening screw (25) has a flat underside of its head and a disc spring (319) is arranged on it, the edge of which rests on the edges of the elongated hole (115). 12. A band according to claim 11, characterized in that a fastening screw (25) under the head surrounding grommet (317) passing through the elongated hole (115) is provided, the length of which is such that, when the disc spring (319) is not yet completely flattened, it is supported on the one hand against its underside and on the other hand against the abutment part (224). 13. Band according to one of claims 8 to 12, characterized in that the grommet (317) is a separate part. 14. Band according to one of claims 8 to 13, characterized in that the grommet (117) engages in a recess (118) of the abutment part (124). 15. Band according to one of claims 8 to 14, characterized in that the grommet (217) is formed by an extension of the abutment part (224).