EP2620583B1 - Raising/pivot bearing for blinds with switchable intermediate position - Google Patents

Description

The present invention is concerned with an elevator / reversible bearing for a sunshade system with a Lamellenbehang which can be coupled with a drive shaft and an elevator bearing with a winding spool and a spiral bearing for adjusting the slat tilt of the curtain, wherein a support member or one with the upper End connected turning tape is guided over a turning disc which can be coupled via a friction clutch to the drive shaft and rotatable between two end positions, wherein the turning disc is blocked in an intermediate position by means of a switchable locking device.

There is a need to adjust the slats already in a certain inclination position when descending sun protection systems with a slat hanging. This prevents, for example, that a room is first completely darkened, before the desired slat inclination can then be set in the extended final state. Depending on the design, there are already such bearings in which the previously known as working position fixed intermediate position but can only be extended in the lower hanging position. Closing the fins at e.g. half blinded curtain is then not possible.

The lamellae are suspended on the supporting member, which is e.g. can be designed as a ladder cord or loop cord.

There are also embodiments in which the so-called working position can be canceled, but this requires always complicated traversing movements, in which the slats have to be adjusted back and forth.

In known work camps, the problem is that they are active in each new deep driving and dominate only one angular position, the angular position can only be changed by costly conversion measures and not influenced by the user.

Examples of known bearings with a switchable intermediate position are from the EP 2211012A2 , of the EP 2348188A2 and the DE 3718513A1 is known. An example of a bearing in which the lamellar position is switchable only with completely unwound Behang, is in the CH700451A1 shown.

The object of the present invention is to provide an elevator / reversible bearing for a sun protection system with Lamellenbehang, which makes it possible to specify between the end positions of the reversible bearing at any Behangstellung any slat inclination when deep drawing.

According to the invention the object is achieved in that in an elevator / spiral bearings of the type described above, the locking device comprises at least one axially or radially movable locking element which rotates with the turning disc, and at least one stationary, distributed over the circumference locking element, in which the locking element in a freely selectable angular position of the turning disc is engageable, wherein the movable and / or the stationary locking element has a plurality of circumferentially distributed notches.

Due to the rotating with the turning disc detent disc in conjunction with the variable locking positions in a fixed position, it is possible to block the turning disc in any intermediate position, the friction then slippage of the drive shaft when deep driving in a relation to the end position further open slat position allows. The locking element can be triggered by any suitable switching mechanism, depending on the configuration and nature, this may for example also be an electric actuator.

Particularly preferred is an embodiment in which the movable locking element is an axially movable disc having at least one locking lug which engages through a recess of the turning disc, wherein it is engaged in the blocking position in a toothed disc, which distributed over the circumference fixed locking elements forms.

In a further preferred embodiment of the invention, a mechanical release of the locking disk is provided, wherein a control disk is provided which is rotatable between stops relative to the movable locking disk, wherein on the control disk at least one switching element, preferably at least two uniformly distributed over the circumference switching elements, is movably mounted against a return spring which radially deflects in a relative direction of rotation of a ramp on the locking disk and axially presses in the opposite direction of relative rotation by means of this ramp the locking disk in the blocking position.

This embodiment makes it possible to move by a simple reverse rotation of the drive shaft, which can also be made selectively by an electronic control, the locking disc and thus the coil bearings in a blocked position between the two end stops, so that a further deep driving then in an intermediate position Slats is possible. The ramps have a height such that they lie in the blocking position out of engagement of the switching element.

In yet another preferred embodiment of the invention it is provided that at least one rocker is provided on the latching element, which is pivotally mounted, wherein it is pivoted in the blocking position into a position in which a first arm of the rocker projects into the path of movement of a reset element, so that the rocker can be folded by the reset element, wherein a second arm of the rocker disengages the locking disk from the stationary locking elements. The design as a rocker ensures that when disengaged locking element, the reset elements can pass in the area of the rocker. In the locked position, the rocker then flips out, so that its now projecting into the movement path of the reset element arm forms an attack point to cancel the blocking position by appropriate rotation of the formed on the control disk reset element.

An expedient embodiment provides that the rocker protrudes in the blocking position in the movement path of the switching element, so that this assumes the function of the reset element in the blocking position. For this variant, the simpler substructure speaks, while by separate Reset elements if necessary, the necessary switching paths can be positively influenced.

The friction clutch is preferably provided between a spiral bearing drive and the control disk, wherein the friction clutch preferably has a wrap spring, which wraps around a cylindrical friction surface, and has bent spring ends, which engage through radial recesses in the control disk and take them rotatably, wherein radially outside the control disk stationary stops are provided which limit the Verdrehweg the wrap spring and thus the control disc and the turning disc and widen the wrap under plant.

In this way, the rotation stops can be realized directly in the region of the friction clutch, these stops then also limit the pivot angle of the slats on the turning disc. The formation of the friction clutch by means of a wrap spring has the advantage that the friction torque can be considerably reduced by the widening, so that the wear and the power losses are reduced at further rotating drive shaft. This is advantageous because at a complete shutdown of the curtain, the friction clutch is in the slipping state over the largest distance.

In a preferred embodiment, it is provided that the latching element facing the bent end of the wrap engages in its blocking position against a raised rocker. In this way, the friction clutch is relieved even when switched intermediate position and correspondingly reduces the friction torque.

Preferably, the turning disc is mounted via a second friction clutch on a stationary cylindrical surface. The additional friction clutch prevents inadvertent adjustment of the inclination of the slats in the event that a force is applied to the ladder cord from the outside, which may for example be the case under wind action.

For this purpose, the second friction clutch preferably has a wrap spring, which wraps around the cylindrical surface, with its ends lying between the turning disk and an adapter disk, which are rotatable relative to one another in a narrow angular range, wherein a rotation on the adapter disk, which is rigidly connected to the locking disk is a reduction in the wrapping force of the wrap spring and turning on the turning disc causes an increase in the wrapping force of the wrap spring. When pulled on the ladder cord stiffened according to the wrap spring and secures the turning disk against rotation, while the desired drive causes a reduction in the entangling force and thus allows easy adjustment.

In a particularly preferred embodiment of the invention, the spiral bearing is coupled via a reduction gear with a drive shaft which reduces the rotational speed of the spiral bearing relative to the drive shaft. Such a transmission, which may be formed as a planetary gear, eccentric, cycloidal or helical gear, has the advantage that even at high speed of the drive shaft for a quick adjustment of the extension length of the curtain Nevertheless, a precise adjustment of the slat inclination is possible. In addition, the switching angle in the elevator / Wendelager can better comply, which is also in an electronic control of the intermediate position of advantage to avoid switching errors.

A constructive embodiment provides that the planetary gear consists of a sun gear, which can be coupled to the drive shaft, a stationary ring gear and a plurality of planetary gears, which are mounted on a rotating planetary carrier on which a friction surface is formed for the first friction clutch.

• Fig. 1 ein Explosionsschaubild eines Aufzugs-/Wendelagers;
• Fig. 2 eine gedrehte Perspektivansicht des Explosionsschaubilds nach Fig. 1;
• Fig. 3 eine Stirnansicht des Wendelagers aus Fig. 1 mit seiner Reibkupplung;
• Fig. 4 eine teilgeschnittene Schrägansicht des Wendelagers nach Fig. 3;
• Fig. 5 eine Schrägansicht der Rastscheibe aus Fig. 1 mit eingeklappten Wippen;
• Fig. 6 eine Rückansicht der Rastscheibe nach Fig. 5;
• Fig. 7 eine Rückansicht der Rastscheibe mit ausgestellten Wippen entsprechend der Blockierstellung;
• Fig. 8 eine Frontansicht der Rastscheibe in der Blockierstellung mit ausgestellten Wippen;
• Fig. 9 eine Schrägansicht der Steuerscheibe nach Fig. 1;
• Fig. 10 ein Explosionsschaubild einer weiteren Ausführungsform der Erfindung;
• Fig. 11 eine Stirnansicht der Rastscheibe aus Fig. 10;
• Fig. 12 eine Stirnansicht der Steuerscheibe aus Fig. 10.

Hereinafter, reference will be made to embodiments of the invention with reference to the drawings. Show it:

• Fig. 1 an exploded diagram of an elevator / reversing bearing;
• Fig. 2 a rotated perspective view of the explosion diagram after Fig. 1 ;
• Fig. 3 an end view of the spiral bearing Fig. 1 with its friction clutch;
• Fig. 4 a partially cut oblique view of the spiral bearing after Fig. 3 ;
• Fig. 5 an oblique view of the locking disk Fig. 1 with folded rockers;
• Fig. 6 a rear view of the locking disk after Fig. 5 ;
• Fig. 7 a rear view of the locking disc with flared rockers according to the blocking position;
• Fig. 8 a front view of the locking disc in the blocking position with flared rockers;
• Fig. 9 an oblique view of the control disk after Fig. 1 ;
• Fig. 10 an exploded view of another embodiment of the invention;
• Fig. 11 an end view of the locking disk Fig. 10 ;
• Fig. 12 an end view of the control disc Fig. 10 ,

In Fig. 1 an elevator / Wendelager is shown, as it is installed in the upper rails of external venetian blind or venetian blinds. The bearing is driven by a polygonal drive shaft (not shown), which will be discussed in more detail later. The elevator / spiral bearing has a housing 12 which can be closed by a cover 14. The housing 12 has at the passage openings bearing surfaces 16, 18 (see Fig. 2 ) on which the drive shaft is mounted on parts of the bearing 10. This will be discussed later.

The bearing 10 has an elevator bearing 20 with a reel 22 on which a textile belt or the like can be wound, which is connected to the lower rail of a Lamellenbehangs (not shown), so that the extension length is adjustable by winding and unwinding of the tape. The coil 22 is laterally by a rotating wall 24 and on the other side by a stationary, in the housing 12th fixed wall 26 limited. The tape reel 22 is hollow on the inside with a polygonal opening, which is adapted to the cross section of a drive shaft to be inserted, so that a positive rotational driving can take place. A first cylindrical bearing surface 28 is supported on the bearing surface 18 of the housing 12, while a second cylindrical bearing surface 30 is rotatably mounted in a corresponding inner cross section 35 of the bearing wall 26. The elevator bearing thus also forms a bearing point of the drive shaft on the housing 12.

On the bearing wall 26, a toothed disc 34 is fixed, which has a plurality of circumferentially uniformly distributed teeth as stationary latching elements 36. The toothed disc 34 is arranged by a suitable resilient mounting 38 on the bearing wall 26, which holds a certain path compensation in the circumferential direction, if it should come to a tooth collision when engaging.

The bearing 10 also has an integrated helical bearing 40, which has a turning disc 42, a friction clutch formed by a wrap spring 44 on a cylindrical friction surface 32 on the bearing wall, an adapter disc 46 for driving the friction clutch 44, a locking disc 48 with pivotable rockers 50 attached thereto a control disk 52 with radially pivotally mounted thereon switching elements 54 which are held by springs 56 in a rest position, and another formed by a wrap 57 friction clutch, which sits on a cylindrical friction surface 59 of a spiral bearing drive. Via the turning disc 42, a turning belt 58 is guided, which is connected to the upper ends of a ladder cord (not shown) is on whose ladders the individual slats are suspended. The turning belt 58 is guided in a groove 60 of the turning disc 42, wherein balls 62 which engage in recesses 64 at the edges of the groove 60, ensure a positive entrainment of the turning belt through the turning disc.

The friction surface 59 is formed on a planet carrier 66 of a planetary gear 68, the bearing pin 70 has, on which planetary gears 72 are rotatably mounted in a sun gear 74, whose inner cross section is formed as a polygon corresponding to the drive shaft, and a stationary in the housing ring gear ( not shown). The sun gear 74 has a first friction surface 78 which rests on the bearing surface 16 of the housing 12 and thus supports the drive shaft, which is seated in the polygonal socket 76, on the housing. The sun gear 74 also has a second cylindrical bearing surface 80 on which the planet carrier is rotatably mounted.

The task of the planetary gear 68 is to reduce the rotational speed of the planet carrier and thus the driven parts of the spiral bearing in rotation of the drive shaft in their speed with respect to this, so that upon rapid actuation of the elevator bearing 20 still fine adjustment of the setting of the fin angle on the turning disc 42nd and the turning belts 58 is enabled. The cylindrical friction surface 59 of the planet carrier 66 takes the wrap spring 57, whose ends 82, 84 are bent radially outwardly. The ends 82, 84 engage through radial recesses 86, 88 of the control disk 52 and project radially beyond them, so that they end with stops (not shown) in the region of the housing 12 and its cover 14th interact. These end stops limit the angle of rotation of the turning bearing 40, wherein a start to a stop causes the wrap spring 57 is widened and correspondingly reduces its frictional torque on the friction surface 59. As a result, when the end stop is reached, the drive shaft can be further rotated under reduced frictional torque in order to raise or lower the curtain and to minimize the power losses and wear occurring during this process.

Normally, the control disc 52 takes over driver 90,92 the locking disc 48 (see Fig. 5 to 8 ) on this provided with driver elements 94,96. The locking disk 48 is in turn connected in a torsionally rigid manner to the adapter disk 46, which in turn entrains the turning disk 42 in a manner described in greater detail below, so that the adjustment of the disk inclination can take place.

As already mentioned, the turning disc 42 is rotatably mounted on the friction surface 32, which cooperates with the wrap spring 44. (please refer FIG. 3 and FIG. 4 ) For this purpose, the turning disc 42 has an axially projecting dome 98, which is arranged with a small play between the two bent spring ends 100, 102 of the wrap spring 44 in the mounted state. The spring extends from the spring ends 100, 102 respectively initially under the dome 98 therethrough.

The adapter disc 46 is in turn formed with radial stops 104,106, which are at a comparable distance to the bent spring ends 100,102 as the flanks of the dome 98. Well recognizable in FIG. 3 and FIG. 4 also connecting elements 108, by means of which the adapter plate 46th with the turntable 42 co-rotating but slightly rotatably connected.

How out Fig. 4 becomes clear, causes a rotation of the adapter plate relative to the wrap spring 44, as is the case with a normal driving the helical bearing 42, regardless of the direction of rotation inevitably widening of the wrap spring 44, so that reduces the friction torque and the coil bearings adjusted under low friction torque can be. On the other hand, if a rotation of the turning disc 42 without intentional drive influences, for example by train on the turning belts, as may be the case with a gust of wind, the dome sets depending on the direction of rotation of one of the two spring ends 100,102 and pulls the wrap spring 44 in both cases to, so that the friction torque of the friction clutch is increased and blocked the turn plate, and no unintentional adjustment of the slat inclination can occur.

The shown elevators / spiral bearings 10 also offers the possibility to lock the turning disc in any intermediate position between the two end stops of the spring ends 82,84 of the wrap 57, wherein by an axial adjustment of the locking disc 48 in the direction of the bearing wall 26 locking lugs 110 (FIGS. see on Fig. 5 to 8 ) engage in the stationary locking elements 36 of the toothed disc 34. The locking lugs 110 protrude through openings in the adapter disk and the turning disc 42, wherein they take the latter in the unlocked state in the direction of rotation. While FIGS. 5 and 6 show the locking disc 48 in a state in which the locking elements 110 are disengaged, so that the turning plate 42 is rotatable show FIGS. 7 and 8 the State in which the locking element is engaged. First arms 112 of the rockers 50 lie down when adjusting the locking disk 48 in the blocking position of the adapter disk 46 and pivot in the in FIGS. 7 and 8 shown position in which second arms 114 of the rockers protrude axially in the direction of the control disk 52. This switching process is triggered by the switching elements 54 (see Fig. 9 ) over active surfaces 116 on ramps 118 (see Fig. 5 ) Act on the locking plate and with appropriate rotation of the control disk 52 relative to the locking disc 48 moves this axially which can be achieved by a reverse rotation of the drive shaft.

How out Fig. 9 can be seen, the switching elements 54 are pivotally mounted about pivot axes 120 so that they favored against the restoring forces of the compression springs 56 by a curve edge 122 when hitting the ramps 118 of the locking disk 48 can escape radially outward when the drive shaft rotates forward, where They are then pushed back by the compression springs 56 in its radially inner position. This means that the actuation of the locking element 48 is possible only in one direction of rotation.

The ramps 118 pass through the axial displacement of the locking disk 48 in the blocking position of the engagement region of the switching elements 54. At the same time, however, the second arms 114 of the rockers 50 are placed in the path of movement of the switching elements 54, so that in the case of a corresponding reverse rotation of the control disk 52 by correspondingly actuating the drive shaft and thus of the planet carrier 66, the active surfaces 116 of the control elements 54 strike the second arms 114 of the rockers. Starting from the blocking position are the switching elements 54 at a corresponding relative rotation, the rockers 50 back into the in Fig. 5 and Fig. 6 shown position, wherein the first arms 112 of the rockers press the locking disk accordingly from the adapter disk 46, so that the locking disk axially removed and the locking elements 110 disengage from the stationary toothed disk 34. The blocking position is thus canceled.

The blocking position can be approached starting from any angular position of the slats, since the toothed disc 34 allows a locking in any position. Therefore, the bearing shown has the advantage that the user can set individually or by default of an electrical control when driving a Lamellenbehang specifically an intermediate position, so that on the one hand when driving already targeted blackout occurs, on the other hand, a complete darkening of the room is avoided.

In Fig. 10 another embodiment of an elevator / helical bearing 210 is shown. This in turn consists of a housing 212 with bearing surfaces 216,218, an elevator bearing 220 with a tape reel 222, a bearing wall 226, a stationary toothed disc 234, a turning disc 242 with a circumferential groove 260 through which a turning belt 258 is guided, a detent disk 248 and a planetary gear 268, the constructive of the embodiment described above is substantially identical and therefore will not be explained in more detail here.

A significant constructive difference is the formation of friction clutches, here by spring tongues 244 in the region of the turning plate 242, slide on a friction surface 232 on the bearing wall 226, and are formed by spring tongues 257, which are formed on the inner periphery of the control disk 252 and on a friction surface 256 of the planet carrier 266 slide. The disadvantage of this simplified embodiment is that the friction torque of the friction clutches is always constant, so that when starting against a stop no reduction of the friction torque is possible. In the area of the turning disk 242, it is also not possible to increase the frictional torque in the event of an introduction of force on the turning belts 258 in order to avoid an adjustment of the angle inclination of the disks.

Structurally very similar to the locking disc 248 opposite to the previously described embodiment (see Fig. 11 ). It has latching elements 310 and rockers 250, which correspond in their function to the rockers 50 described above completely. Well recognizable in Fig. 11 also the ramps 318, which with switching elements 254 (see Fig. 11 ) interact. These switching elements 254 are again against the action of a return spring (not shown) radially outwardly adjustable, wherein in the in Fig. 12 As shown in the embodiment shown, the switching elements 254 are pivotally mounted about a tangential pivot axis, while in the previously described embodiment (see Fig. 9 ) are formed pivotable about an axial axis of rotation. In the same way, the switching elements 254 cooperate with the ramps 318 to engage the locking disc 248 with its locking elements 310 in the toothed disc 234 and thereby the turning plate 242 in a desired arbitrary Lock intermediate position. The provision via the rockers takes place at the in 10 to 12 shown embodiment by firmly on the control disk 252 integrally formed reset elements 255th In Fig. 12 is shown in the lower part of the illustration, the control 254 in the non-pivoted position, in which it cooperates with the Rampem 318 in reverse rotation, while it is shown deflected radially outwards in the upper part of the illustration, a position which it in the radial deflection in the forward direction assumes when it runs against the backs of the ramps 318.

Claims (13)

1. A lifting and tilting bearing for a sun protection unit with a slatted curtain, which slatted curtain can be coupled with a drive shaft and comprises a lifting bearing (12; 212) with a winding spool (22; 222) and a tilting bearing for adjusting the slat angle of the curtain, whereby a carrying means or a turning band (58) connected with the upper end of the carrying means, is guided over a tilting disk (42; 242), which disk can be coupled via a friction coupling with the drive shaft and can be turned between two end positions, whereby the tilting disk (42; 242) can be blocked in an intermediate position by means of a locking device, characterized in that the locking device comprises at least one axially or radially moveable locking element, which rotates with the tilting disk (42; 242), and comprises at least one locationally fixed locking element (36), into which the moveable locking element can be inserted at a freely selectable angular position of the tilting disk (42; 242), whereby the moveable and/or the locationally fixed locking element (26) comprises several locking teeth distributed around the perimeter.
2. A lifting and tilting bearing according to claim 1, characterized in that the moveable locking element is an axially moveable locking disk (48; 248), which comprises at least one locking lug (110; 310), which extends through a recess in the tilting disk (42; 242), whereby it is engaged with a toothed disk (34; 234) in the blocked position, which forms the locationally fixed locking elements (36) distributed around the perimeter, or other locationally fixed locking elements.
3. A lifting and tilting bearing according to claim 2, characterized in that a control disk (52; 252) is provided, which can be turned between stops relative to the moveable locking disk (48; 248), whereby at least one switching element (54; 254) is arranged on the control disk (52; 252) moveable against the returning force of a spring (56), which switching element moves radially away in a relative rotational direction of an associated ramp (118; 318) and presses the locking disk (48; 248) into the blocking position in the opposite relative rotational direction via the ramps (118; 318).
4. A lifting and tilting bearing according to claim 3, characterized in that at least one rocker (50; 250) is pivotably arranged on the locking disk (48; 248), whereby the rocker is pivoted into a position in the blocking position of the tilting disk (42; 242), in which a first arm (114) of the rocker (50; 250) protrudes into the movement path of a restoring element (255), such that the rocker (50; 250) can be flipped by the restoring element (255), whereby a second arm (112) of the rocker (50; 250) disengages the locking disk (48; 248) from the locationally fixed locking elements (36).
5. A lifting and tilting bearing according to claim 4, characterized in that the rocker (50) protrudes into the movement path of the switching element (54) in the blocking position, so that the switching element assumes the function of the restoring element in the blocking position.
6. A lifting and tilting bearing according to one of the previous claims, characterized in that a first friction coupling is provided between a tilting bearing drive and the control disk (52; 252).
7. A lifting and tilting bearing according to claim 6, characterized in that the first friction coupling comprises a wrap spring (57), which wraps around a cylindrical friction surface (59) and possess bent spring ends (82, 84), which engage through radial recesses (86, 88) in the control disk (52) and take these along in a rotational manner, whereby locationally fixed stops are provided radially outside of the control disk (52), which limit the turning path of the control disk with the spring ends (82, 84) and expand the wrap spring (57) upon contact.
8. A lifting and tilting bearing according to claim 7, characterized in that the bent end (82) of the wrap spring (57) facing the locking disk (48) contacts an erected rocker (50) in the blocking position of the tilting disk (42) and locking disk (46), said rocker (50) defining the rotational stop in the blocking position.
9. A lifting and tilting bearing according to one of the previous claims, characterized in that the tilting disk (42; 242) is arranged on a locationally fixed, cylindrical surface (32; 232) via a second friction coupling.
10. A lifting and tilting bearing according to claim 9, characterized in that the second friction coupling comprises a wrap spring (44), which wraps around the cylindrical surface (32), whereby its spring ends (100, 102) lie between the tilting disk (42) and an adapter disk (46), which can be pivoted relative to each other in a narrow angular range, whereby turning the adaptor disk (46), which is connected to the locking disk (48) in a rotationally fixed manner, effects a reduction of the wrap-around force of the wrap spring (44) and turning the tilting disk (42) effects an increase of the wrap-around force of the wrap spring (44).
11. A lifting and tilting bearing according to one of the previous claims, characterized in that the tilting bearing can be coupled with a drive shaft via a reduction gearing, which reduces the rotational speed of the tilting bearing relative to the drive shaft.
12. A lifting and tilting bearing according to claim 11, characterized in that the reduction gearing is formed as a planetary gearing (68; 268), an eccentric gearing, a spur gearing or a cycloidal gearing.
13. A lifting and tilting bearing according to claim 12, characterized in that the planetary gearing (68) comprises a sun gear (74) that can be coupled with the drive shaft, a locationally fixed hollow wheel and several planetary wheels (72), which are arranged on a rotational planetary carrier (66) on which the friction surface (59) for the first frictional coupling is formed.

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