CH709360B1 - Self-closing door hinge. - Google Patents

Abstract

The invention relates to a self-closing roller door hinge comprising a first band part (2) comprising an upper band roll (1a) and a lower band roll (1b) and a second band part (3) pivotable about a hinge axis (X). In this case, between the two tape rolls (1 a, 1 b) and the second hinge part (3) each have a reset group (7 a, 7 b) for generating a closing force directed towards the closing position effective. According to the invention, the upper restoring group (7a) has an upper pivoting cam (8a) connected to the second belt part (3) in a rotationally fixed manner and an upper sliding cam (9a) which is non-rotatable and slidable along the axis of rotation (X) in the upper belt roller (1a) and the upper one Sliding cam (9a) with an axial end face against an associated axial end face of the upper pivot cam (8) oppressive upper spring element (12a). Correspondingly, the lower restoring group (7b) has a lower swivel cam (8b) rotatably connected to the second band member (3), a lower sliding cam (9b) rotatable and slidable along the rotational axis (X) in the lower band roller (1b) and the lower one Sliding cam (9b) with an axial end face against an associated axial end face of the lower pivot cam pushing lower spring element (12b). At the axial end faces, the respective at least one bevel is provided for converting the linear spring forces generated by the spring elements (12a, 12b) into a closing force.

Description

Description: [0001] The invention relates to a self-closing roller door hinge with a first hinge part comprising an upper roll of tape and a lower roll of tape, and a second second hinge part pivotable about a hinge axis. In this case, in each case a restoring group for generating a closing position directed towards the closing force is effective between the two tape rolls and the second band part.

Such a generic roller door hinge is known for example from WO 2006/036 044. The restoring groups each have a sleeve-shaped body with a helical slotted guide arranged in its wall. In the assembled state, a pin engages in this slotted guide and forms in this way a cam gear for converting a linear spring tension into a closing force. Such closing mechanisms are expensive to manufacture and assemble.

Against this background, the invention has for its object to provide a self-closing roller door hinge with easy to produce and to be mounted locking mechanisms.

In the context of this patent application, the term "closing force" - unless explicitly stated otherwise - to be understood as acting between the band parts force that produce a torque acting in the closing direction.

The invention and solution to this problem is a self-closing roller door hinge according to claim 1 comprising an upper band roll and a lower band roll band part and a second, about a hinge axis from a closed position to an opening angle pivotable second band member. Between the upper tape roll and the second tape part is an upper reset group and between the lower tape roll and the second tape part, a lower reset group is effective. By the two restoring groups, a closing force directed towards the closing position is generated independently of each other. According to the invention, the upper restoring group has a rotationally fixed to the second band part associated upper pivot cam, a rotationally fixed and slidable along the axis of rotation in the upper band roll upper sliding cam and the upper sliding cam with an axial end face against an associated axial end face of the upper pivot cam pushing upper spring element. Correspondingly, the lower restoring group comprises a lower pivot cam rotatably connected to the second band member, a rotatably and slidable along the axis of rotation in the lower band roll lower sliding cam and the lower sliding cam with an axial end face against an associated axial end face of the lower pivot cam pushing lower spring element. At least one bevel for converting the linear spring forces generated by the spring elements into a closing force is provided on each of the axial end faces. In this case, bevel denotes a surface inclined in the direction of rotation relative to a rotational movement of the cams. This can be accomplished with a slope of the associated cam or a straight line, i. in the direction of rotation of the non-inclined surface, interaction. The forces between the individual components are transferred exclusively to pressure, so that the restoring groups for assembly can be assembled linearly without restriction.

Preferably, the upper sliding cam is rotationally fixed to at least one groove and slidably guided along the axis of rotation in the upper roll of tape and the lower sliding cam on at least one groove rotatably guided along the axis of rotation in the lower roll of tape. Each groove interacts with an associated bulge. The grooves can be arranged without restrictions on the sliding cam or on the inside of the associated tape roll. Advantageously, the interaction of several, preferably approximately evenly distributed over the circumference tongue and groove connections. These can also be arranged so that the sliding cams can be inserted into the tape rolls only in the correct orientation. Thus, a wrong assembly is excluded. To simplify manufacture, grooves milled into the upper roll of tape align with the grooves on the inner surface of the lower roll of tape so that they can be made in one operation.

Conveniently, at least one spring element is formed from disc springs. Disc springs are characterized by their compact design and can be produced with progressive, degressive and linear spring characteristics as required.

In a particularly preferred embodiment, the axial end faces of the cooperating upper and lower pivot cams and slide cams are formed so that the closing force generated is dependent on the opening angle. This can thus be adjusted as needed. For example, a large opening area with no or only a small closing force can be provided, a negative closing force for particularly large opening angles to stop the door or even a particularly large closing force at small opening angles to overcome the resistance of a latch.

Preferably, the closing force exerted by the upper restoring group and the closing force exerted by the lower restoring group have a different amount, at least in partial areas of the opening angle. If the two reset groups are active in different angular ranges - i. generate a closing force - and / or apply closing forces of different strengths, this allows a particularly simple adjustment of the closing force characteristic.

In a preferred embodiment, the sliding cam and the pivot cams of both restoring groups each have a hollow cylindrical concentric to the axis of rotation arranged portion. For the purpose of stabilization and / or guidance, the hollow-cylindrical section can be penetrated or filled on the inside by the same component or a further component.

Expediently, the axially abutting end faces of the sliding cam and the pivot cams are formed by annular end surfaces of the hollow cylindrical sections. The end surfaces may have any profile in the circumferential direction, but are generally not inclined in the radial direction. Preferably, the width of the circular ring in the radial direction is not greater than the radius of the cylindrical cavity remaining therein. Thus, in a pivoting movement, the relative speeds of the sliding cam and sliding cam sliding against each other inside and outside are approximately the same size, so that the abrasion phenomena occur approximately uniformly.

Conveniently, the annular end faces each have a profile in the circumferential direction with at least one slope with slope and at least one plateau without slope. This makes it particularly easy angle areas with restoring force - in which a slope is effective - and angle ranges without restoring force - in which a plateau is effective - set. If a swivel cam and an associated push cam are each provided with a bevel, they preferably have the same pitch, so that they can lie flat against one another during the effectiveness of the bevels. Such a profile can be produced easily in terms of manufacturing technology-for example by casting or milling from the full block of material.

Particularly preferably, the transitions between slope and plateau are rounded. This results in a pleasant continuous transition during operation. A sudden snapping of the reset groups is prevented.

Conveniently, at the pivot cam and on the sliding cam of the upper restoring group bevel and plateau in other angular ranges of the opening angle effective than on swing cams and sliding cam of the lower restoring group. As a result, the closing force profile can be adjusted more easily with simple means than with two identically effective restoring groups.

In a variant, the slope of the end face of a cam of the upper restoring group over a larger or smaller angular range of the opening angle is formed as a slope on the cam of the lower restoring group. For example, both slopes can be effective from the closed position with 0 °, wherein a first slope is steeper and already ends at a smaller angle. Due to the greater slope is exercised by this at identical spring tension and a larger closing force amount. From the end of the steep slope this is no longer effective and no longer contributes to the closing force. The second, flatter slope is effective over a larger angular range and exerts only a low closing force.

Alternatively, both the swivel cam of the upper restoring group and the swivel cam of the lower restoring group and the sliding cam of the upper restoring group and the sliding cam of the lower restoring group are each identical or mirror-symmetrical. The swivel cam of the upper restoring group is rotated by a displacement angle relative to the swivel cam of the lower restoring group rotatably fixed on the second band part. If the sliding cams are each aligned or symmetrically arranged, the restoring groups in different angular ranges are also effective in this variant. However, it is possible to resort to uniformly manufactured components. This can simplify and cheapen the manufacturing process. In order to arrange the two pivot cams against each other rotated by a constant displacement angle, there are several possibilities. For example. For example, the two pivot cams can be designed as end regions of an integrally formed hinge pin, which can be fastened in a rotationally fixed manner to the middle hinge part. Another possibility is that the two pivot cams are fastened by means of a spur toothing or toothed coupling to each other or to the second band part or an intermediate piece connected thereto. This would allow the displacement angle - even later - set variably.

Particularly preferably, in an opening angle range between 0 ° and 10 °, the cams of both restoring groups with bevels against each other and thus exert a restoring force. From a first angle - in particular 10 ° - lie the cam of one of the two restoring groups with plateaus together, so that they no longer exert restoring force. From a second opening angle - in particular 45 ° - the cams of both restoring groups with plateaus abut each other and exert no restoring force more up to a maximum opening angle - in particular 180 °. Alternatively, from a third angle, a negative restoring force can be exerted by at least one of the restoring groups, so that the door thereof is stopped in an open position.

Conveniently, the end face of the swing cam and the end face of the associated shift cam in the closed position in at least one restoring group circumferentially completely against each other. As a result, the restoring group is in a force-free rest position, which is particularly gentle on the material for storage.

Preferably, at least one bearing bush is arranged between the first band part and the second band part, which bushing is rotatable at least in relation to a band part. Such a bearing bush can absorb the forces of the belt connection and dissipate this friction. As a result, the return mechanism of the self-closing roller door hinge can work undisturbed. Alternatively or additionally, a rolling bearing may be provided. Optionally, the bearing bush can also be designed to provide a defined damping force. In this way, in particular an uncontrolled acceleration of the door leaf can be avoided by the restoring forces.

The invention will be explained in more detail with reference to the following, only one embodiment illustrative drawings. It shows schematically:

1 is a self-closing roller door hinge according to the invention with an exploded view of the ent restoring groups,

2 is a plan view of an inventive roller door hinge with indicated door frame and Türflü gel in different opening positions,

3 shows an inventive roller door hinge with broken tape rolls,

Fig. 4 detail view of Fig. 3 and

5A to 5D is a schematic functional view of the sliding cam as a function of the angle of rotation.

Fig. 1 shows an inventive self-closing roller door hinge in an exploded view. These include a first hinge part 2, which comprises an upper roll of tape 1 a and a lower roll of tape 1 b and a pivotable about a hinge axis X second hinge part 3. Both hinge parts 2, 3 each have fastening means 4 for fixing to a door or a door frame. In the plan view of FIG. 2, the first hinge part 2 is connected to an indicated door leaf 5 and the second hinge part 3 is connected to a door frame 6. The band parts 2, 3 are pivotable about an opening angle φ in an illustrated closed position. Dashed is an opening angle of about 60 ° and dash-dotted a maximum opening angle of about 180 ° shown.

Between the upper tape roll 1a and the second tape part 3, an upper reset group 7a and between the lower tape roll 1b and the second tape part 3, a lower reset group 7b is effective. According to the invention, the upper restoring group 7a has an upper swivel cam 8a connected in a rotationally fixed manner to the second swivel part 3, an upper sliding cam 9a displaceable in rotation along the axis of rotation X in the upper swath 1a, and an upper sliding cam 9a having an axial end surface 10a against an associated axial end surface 11a of the upper swing cam 8a pressing upper spring element 12a. Correspondingly, the lower restoring group 7b has a lower pivoting cam 8a, which is non-rotatably connected to the second belt part 3, a lower sliding cam 9b which is non-rotatably movable along the rotational axis X in the lower belt roller 1b and a lower sliding cam 9b with an axial end face 10b against an associated axial end face 11b of the lower swing cam 8b pushing lower spring element 12b. At least one bevel 13 for converting the linear spring forces generated by the spring elements 12a, 12b into a closing force (closing torque) is provided on each of the axial end faces. The upper swing cam 8 a and the lower swing cam 8 b are integrally formed as end portions of a hinge pin 14. The hinge pin 14 may be rotatably secured in the middle band roll 15 of the second hinge part 3 by means of a screwed into a threaded bore 16 grub screw 17. For this purpose, the hinge pin 14 in about the middle of a shallow recess 18. The width of the recess 18 in the direction of the pivot axis X is adapted to the diameter of the grub screw 17 so that the hinge pin 14 is automatically correctly centered during mounting.

The upper slide cam 9a and the lower slide cam 9b are each guided on two grooves 19 in the upper and in the lower roll of tape 1a, 1b rotatably along the axis of rotation X slidably. For this purpose, the sliding cams 9a, 9b each have two projections 20 on the wall side, which engage in the grooves 19.

The upper and the lower spring element 12a, 12b are formed from a stack of disc springs. These are each braced by means of a retaining screw 21a, 21b against the associated sliding cam 9a, 9b, wherein the retaining screw 21a, 21b are screwed with an externally mounted on the head thread in an associated internal thread of the upper and lower roll of tape 1a, 1b.

Fig. 3 shows an inventive self-closing roller door hinge in the assembled state, wherein the tape rolls 1a, 1b, 15 are broken. For better visibility of the remaining components, the inside spring elements 12a, 12b and the bearing bushes 22a, 22b arranged between the hinge pin 14 and the outer band rolls 1a, 1b are only indicated by dashed lines. Taking a comparative analysis with FIG. 4, which shows the lower restoring group 7b, one deduces that the sliding cams 9a, 9b are designed as hollow cylinders arranged concentrically with the pivot axis X. For stabilization they are penetrated on the inside by the retaining screws 21a, 21b. The pivot cams 8a, 8b have a hollow cylindrical section concentric with the pivot axis X, which is penetrated on the inside by a solid portion of the hinge pin 14. As can be seen in particular from FIG. 4, this inside massive section can also serve as a bearing for the sliding cam 9a, 9b, so that the roller belt is additionally stabilized. The axially abutting end faces 10a, 10b, 11a, 11b of the sliding cam 9a, 9b and the pivot cams 8a, 8b are formed by annular end surfaces of the hollow cylindrical sections. The annular end faces each have a profile in the circumferential direction with two bevels 13 with pitch and two intermediate plateaus 23 without gradients. The transitions 24 between the bevels 13 and the plateaus 23 are rounded. In addition, it can be seen particularly clearly in FIG. 4 that the hinge pin 14 has end sections formed as pivoting cams 8 a, 8 b relative to the sliding cams 9 a,

Claims (15)

9b has a reduced outer diameter, so that a clearance for a bearing bush 22a, 22b remains between the hinge pin 14 and the outer belt rollers 1a, 1b. This is at least opposite to the hinge pin 14 or the outer tape rolls 1a, 1b with little resistance rotatable and derives the holding forces of the roller door hinge safely. FIGS. 5A to 5D schematically show the kinematics of the restoring groups 7a, 7b. Shown are the circumferential profiles of the axially abutting end faces 10a, 10b, 11a, 11b of the outer sliding cam 9a, 9b and the integrally formed in the middle of a hinge pin 14 pivoting cams 8a, 8b. The profiles are shown as a solid line within the first 360 °. The sliding cam 9a, 9b are acted upon by the spring elements 12a, 12b with a spring force Fa, Fb, which is directed to the center. It can be seen that the profiles are each provided with bevels 13 for converting the linear spring forces Fa, Fb generated by the spring elements 12a, 12b into a closing force La, Lb. The slopes 13 connect to plateaus 23 without slope, the transitions 24 are rounded. The total closing force Lges, which results from the sum of the closing forces La, Lb generated by the upper restoring group 7a and by the lower restoring group 7b, depends on the opening angle φ. This is achieved by the special arrangement of the restoring groups 7a, 7b. The proposed arrangement results in that the closing force La exerted by the upper restoring group 7a and the closing force Lb exerted by the lower restoring group 7b have a different amount at least in partial areas of the opening angle φ. In Fig. 5A, which shows the kinematics for an opening angle φ of 0 °, the sliding cam 9a and the pivot cam 8a of the upper restoring group 7a exclusively with a bevel 13 each other, so that the spring force generated by the upper spring element 12a Fa in a upper restoring force La is converted. Swivel cams 8b and sliding cams 9b of the lower restoring group 7b are in a particular rest position, in which the end surfaces are circumferentially completely against each other. In this position, no restoring force Lb is generated. In the embodiments, the circumferential profiles of the axial end faces 10a, 10b, 11a, 11b of the upper and lower swing cam 8a, 8b and the upper and lower sliding cam 9a, 9b are each formed identically or mirror-symmetrically. The different amount of closing forces La, Lb generated by the restoring groups is achieved by arranging the upper and lower sliding cams 9a, 9b in symmetrical alignment, while the profiles of the end faces 11a, 11b of the two pivoting cams 8a, 8b are offset by an offset angle α twisted against each other are arranged. As a result, on the swing cam 8a and the shift cam 9a of the upper restoring group 7a, the slopes 13 and plateaus 23 are effective in other angular ranges of the opening angle φ than on the swing cams 8b and sliding cams 9b of the lower restoring group 7b. The kinematics of the restoring groups 7a, 7b will be explained below. If the roller door hinge is opened from the closing position shown in FIG. 5A-this is represented by a displacement of the profile 11a, 11b of the swivel cams 8a, 8b in a positive φ direction-the lower swivel cam 8b is at an opening angle φ greater than 0 ° exclusively with one Bevel 13 to an associated slope 13 of the lower sliding cam 9b, so that here also from the spring force Fb an additional closing force Lb is generated. In a first angular range both restoring groups 7a, 7b are effective. From an opening angle φ of 10 °, shown in FIG. 5B, the upper pivoting cam 8a comes into contact with an associated plateau 23 of the upper sliding cam 9a by means of a plateau 23. The closing force La generated by the upper restoring group 7a disappears. Meanwhile, the lower reset group 7b is still effective. From a second, shown in Fig. 5C opening angle φ of 45 °, the profiles of both restoring groups 7a, 7b each with plateaus 23 against each other. There are no restoring forces La, Lb, Lges. Fig. 5D shows the reset groups 7a, 7b in a maximum opening position with an opening angle φ of 180 °, in which still no restoring force Lges is exerted. It can be seen that at an even larger opening angle φ, the upper restoring group 7a becomes effective with a negatively inclined slope 13, so that a negative closing force La for holding a door can be generated. By suitably selecting the profiles of both restoring groups La, Lb, the closing force characteristic dependent on the opening angle φ can be flexibly adapted to the needs of the user. A particularly simple - even subsequently possible - setting can be to change the displacement angle α by turning at least one pivoting cam 8a, 8b relative to the second hinge part 3. claims 1. Self-closing roller door hinge with an upper band roll (1a) and a lower band roll (1b) comprising first band part (2) about a hinge axis (X) from a closed position by an opening angle (φ) ver-pivotable second band member (3 ) and a respective upper restoring group (7a) operative between the upper band roll (1a) and the second band member (3) and a lower restoring group (7b) operative between the lower band roll (1b) and the second band member (3), each for producing a closed position directed closing force, characterized in that the upper restoring group (7a) rotatably connected to the second band part (3) upper pivot cam (8a), a rotationally fixed and along the axis of rotation (X) in the upper band roll (1a) displaceable upper sliding cam (9a ) and an upper slide cam (9a) having an axial end face (10a) against an associated axial end face (11a) of the upper swing cam (8a) pushing upper spring element (12a), that the lower restoring group (7b) rotatably connected to the second band part (3) lower pivot cam (8b), a rotationally fixed and along the axis of rotation (X) in the lower belt roll (1 b) displaceable lower sliding cam (9b) and a lower spring element (12b) pushing the lower sliding cam (9b) with an axial end face (10b) against an associated axial end face (11b) of the lower pivot cam (8b) and that on the axial end faces (10a, 10b, 11a, 11b) is provided in each case at least one bevel (13) for converting the linear spring forces generated by the spring elements (12a, 12b) into a closing force. 2. self-closing roller door hinge according to claim 1, characterized in that the upper sliding cam (9a) on at least one groove (19) rotatably and along the axis of rotation (X) displaceably in the upper roll of tape (1a) is guided and that the lower slide cam (9b ) at least one groove (19) rotationally fixed and guided along the axis of rotation (X) displaceable in the lower roll of tape (1 b). 3. Self-closing roller door hinge according to claim 1 or 2, characterized in that at least one spring element (12a, 12b) is formed from disc springs. 4. Self-closing roller door hinge according to one of claims 1 to 3, characterized in that the axial end faces (10a, 10b, 11a, 11b) are formed so that the closing force is dependent on the opening angle (φ). 5. self-closing roller door hinge according to one of claims 1 to 4, characterized in that the closing force exerted by the upper restoring group (7a) and the closing force exerted by the lower restoring group (7b) closing force at least in partial areas of the opening angle (φ) have a different amount. 6. Self-closing roller door hinge according to one of claims 1 to 5, characterized in that the sliding cam (9a, 9b) and the pivot cams (8a, 8b) of both restoring groups (7a, 7b) each have a hollow cylindrical concentric with the axis of rotation (X) arranged portion , 7. self-closing roller door hinge according to claim 6, characterized in that the axially abutting end faces (10a, 10b, 11a, 11b) of the sliding cam (9a, 9b) and the pivoting cams (8a, 8b) are formed by annular end surfaces of the hollow cylindrical sections. 8. self-closing roller door hinge according to claim 7, characterized in that the annular end faces each have a profile in the circumferential direction with at least one slope (13) with slope and at least one plateau (23) without inclination. 9. self-closing door hinge according to claim 8, characterized in that the transitions (24) between the slope (13) and plateau (23) are rounded. 10. self-closing roller door hinge according to one of claims 8 or 9, characterized in that on the pivot cam (8a) and the sliding cam (9a) of the upper restoring group (7a) bevel (13) and plateau (23) in other angular ranges of the opening angle (φ ) are effective as on pivot cams (8b) and sliding cam (9b) of the lower restoring group (7b). 11. self-closing roller door hinge according to claim 10, characterized in that both the pivoting cam (8a) of the upper restoring group (7a) and the pivoting cam (8b) of the lower restoring group (7b) and the sliding cam (9a) of the upper restoring group (8a) and the sliding cam (9b) of the lower restoring group (7b) are identical or mirror-symmetrical and that the pivot cam (8a) of the upper restoring group (7a) rotated by a displacement angle (a) relative to the pivot cam (8b) of the lower restoring group (7a) rotatably on second band part (3) is fixed. 12. self-closing roller door hinge according to claim 10 or 11, characterized in that in the opening angle range between 0 ° and 10 °, the cams (8a, 9a, 8b, 9b) of both restoring groups (7a, 7b) with bevels (13) abut each other and so on Restoring force exert that from a first opening angle (φ), in particular 10 °, the cams (8a, 9a or 8b, 9b) of one of the two restoring groups (7a, 7b) with plateaus (23) abut each other and thus exert no restoring force in that, starting from a second opening angle (φ), in particular 45 °, the cams (8a, 9a, 8b, 9b) of both restoring groups (7a, 7b) bear against each other with plateaus (23) and both (7a, 7b) exert no restoring force until to a maximum opening angle (φ), in particular 180 °. 13. Self-closing roller door hinge according to one of claims 1 to 12, characterized in that the end face (11 a / 11 b) of the pivoting cam (8 a, 8 b) and the end face (10 a / 10 b) of the associated sliding cam (9 a / 9 b) in the Closing position at least one restoring group (7a, 7b) circumferentially completely abut each other. 14. Self-closing roller door hinge according to one of claims 1 to 13, characterized in that between the first band part (2) and the second band part (3) at least one bearing bush (22a, 22b) is arranged, at least with respect to a band part (2, 3) rotatable is. 15. self-closing roller door hinge according to one of claims 1 to 14, characterized in that the pivoting cam (8a) of the upper restoring group (7a) and the pivoting cam (8b) of the lower restoring group (7b) are designed as a continuous hinge pin (14) in one piece.