WO2006063565A1

WO2006063565A1 - Blind for a vehicle window

Info

Publication number: WO2006063565A1
Application number: PCT/DE2005/002225
Authority: WO
Inventors: Harald Krüger; Werner Stammberger; Sebastian Schnetter
Original assignee: Brose Fahrzeugteile Gmbh & Co. Kg, Coburg
Priority date: 2004-12-17
Filing date: 2005-12-05
Publication date: 2006-06-22
Also published as: DE202004019844U1; DE112005002702A5

Abstract

The invention relates to a blind for a vehicle window that is delimited by a peripheral window frame with a bottom, top, and lateral window frame edge. Said blind comprises a web whose continuous edge is provided with a section that is fixed to a rotatably mounted winding shaft and a section which is located at a distance from the winding shaft, as well as two substantially parallel guide rails within which sliding elements that are joined to the section of the blind edge located at a distance from the winding shaft are guided in a longitudinally movable manner with the aid of pressure-resistant and/or bending-resistant actuating means, said actuating means being connected to a drive unit. According to the invention, a device which is connected to the drive unit is provided for compensating the length of the pressure-resistant and/or bending-resistant actuating means (11, 12).

Description

Window roller blind for a vehicle window

description

The invention relates to a window roller blind for a vehicle window according to the preamble of claim 1.

From EP 1 123 824 A2 a side window roller blind for motor vehicles is known, which has a winding shaft, which is rotatably mounted behind the side panel of the door or the B-pillar. On the winding shaft a roller blind is wound up, which can be deducted for complete or partial covering of the window of the winding shaft. To the side window roller blind includes a guide rail which is fixed to the door in the region of the front window frame portion and extends from the upper window frame portion to the inside of the door. In the guide rail, a carriage runs with a through a slot of the guide rail projecting outward strip-shaped flange which is connected to a mounted on the upper edge of the roller blind edge reinforcing strip. The carriage is connected via a pressure-resistant, linear element in the form of a flexible metal or plastic wire, the soul of a Bowden cable or a shear-stiff, stranded strand of wire with a reduction gear, which is driven by a drive motor. To wind the roller blind onto the winding shaft, a spring motor arranged in the winding shaft is provided which, together with the drive motor, forms part of the drive device of the side window roller blind and has a pretensioning force in the sense of winding the roller blind web onto the windscreen. generated ckelwelle.

At rest, the roller blind is wound up under the action of the spring motor on the winding shaft and the slot in the guide rail down. To drive out the side window roller blind, the drive motor is set in motion and the pressure-tight guided linear element is displaced via the reduction gear, so that the roller blind is unwound over the strip-shaped flange and the edge reinforcement strip from the winding shaft and pulled upwards in the door. In this case, the roller blind can be kept stretched next to the window by means of the guide rail or additional pressure or rigid actuator.

If, in this known side window roller blind, one of the two carriages guided in the guide rails and connected to the winding shaft opposite section of the roller blind edge reaches its end position defined by a stop or the upper window frame edge, this is not necessarily the case with the other carriage as well a corner of the window pane is not covered by the window blind. This vacancy is in the range of the upper end stop of the window blinds and thus at head height of the vehicle occupants, where it is particularly disturbing because of the risk of glare from incident sunbeams.

To solve this problem also known in cable winches for motor vehicles, it is known from DE 39 25 864 C2 to connect the window with two guided in guide rails sliders, which are connected via a cable with a self-locking drive device. To limit the disc movement upwards a stop is attached to a slider or an associated portion of the rope, while another stop is connected via a spring element with the other slider or the associated portion of the rope and is effective when cranking the disc as a first stop, so that when the spring-loaded stop at the upper end position abutting the window lifter rope against the resistance of the Federele- element can be moved by a certain amount until the other, fixed stop abuts.

From US Pat. No. 6,668,902 B2, a window roller blind is known which has a motor which can be driven in both directions of rotation and is connected to a cable drum, two cables wound around the cable drum, two cables connected to the two cables and by the rotation of the cable

Cable drum sliding slider, two at one end pivoting with the gliders connected rods, whose other ends are connected to a one end of a Roliobahn receiving tension bow, and a winding shaft, which is connected to the other end of the blind sheet, and winds the roller blind resiliently. The cables are provided with a cable sheath which, on the one hand, is connected to the cable power! receiving attachment and on the other hand attached to a body-mounted stop. The connection with the body-fixed stop via axially offset circumferential grooves, so that the respective cable length and thus the tension can be adjusted by connecting the body-fixed stop with one of the circumferential grooves.

From DE 100 57 762 A1 discloses a window blind for regulating the light entry through a window in an interior of a motor vehicle is known, which has a rotatably mounted winding shaft and a roller blind, which is fixed with an edge on the Wickewelle and their parallel edge with a Tension rod is connected. The winding shaft is associated with a winding shaft in the Aufwickelsinn the roller blind vorspannender spring motor. In addition to the lateral longitudinal edges of the roller blind guide rails extend with therein guide grooves in which the tension rod is guided end. The ends of the tension rod are connected to flexurally elastic push members, which are connected to a drive device for adjusting the tension rod along the guide rails.

Since the bending elastic thrust members are to be adjusted only with great effort so that they move the pull rod of the roller blind exactly parallel to the winding shaft, it comes because of the lack of parallelism of the trigger pull rod to a diagonal train in the blind, resulting in obliquely extending waves in the extended roller blind leads. In addition, tolerances in the production of the roller blind can produce parallelism errors, which, in conjunction with unequal withdrawal of the roller blind from the winding shaft, reinforce the obliquely extending undulations or folds in the roller blind.

In addition, it may come with partially or completely deducted from the winding roller blind web to flutter and move the roller blind due to shock during travel when the roller blind is not kept sufficiently tight.

To avoid distortion in the roller blind due to improperly adjusted Schubglie- the known window blind has a compensation device through which the winding shaft with respect to a perpendicular to the longitudinal axis of the winding shaft extending Axis is limited pivoting. The compensation device consists, inter alia, of a bearing bracket, which receives the winding shaft and is supported at the ends of the body via springs and thus biased elastically in a centered position.

However, the elastic support of the winding shaft ends to compensate for not exactly parallel displacement of the tension rod, but also to keep the roller blind and thus avoiding a Schiefziehenens and Faltenwurfes the blind sheet is connected to a considerable space especially in the vertical direction, the arrangement of the retaining bracket and the spring supports is required. In a larger required travel this place in a door sill of a motor vehicle door but is often not available, especially in the door sill further door units such as a window, a door lock and the like are to be accommodated.

Object of the present invention is to provide a window blind for vehicles of the type mentioned, in which a uniform system of the winding shaft opposite roller blind section is ensured at the upper edge of the window frame with low manufacturing and assembly costs.

This object is achieved by the features of claim 1.

The solution according to the invention, when the roller blind is pulled off the winding shaft, ensures simultaneous abutment of both sliding elements at the upper end or in a stop of the guide rails and thus uniform contact of the roller blind section opposite the winding roller section at the upper edge of the window frame with low material and production costs.

The solution according to the invention shifts the adjustment of the lifting height of the pressure- and / or bending-resistant actuating elements and thus the simultaneous application of the pressure- and / or bending-resistant actuating elements and adjustable sliding elements on a stop or at the upper end of the guide rails in the region of Drive device, so that the setting of the lifting height of the pressure and / or rigid actuating elements made centrally and in particular can be automatically adjusted. Since the drive device is usually arranged in the door shaft in the case of a window roller blind for a vehicle door, the arrangement of setting devices directly on the vehicle window or in the area of the door sill also lapses, so that a length compensation of the pressure-resistant and / or bending-resistant actuating means during assembly of the window blind be made and no unintentional adjustment when using the window blinds can occur. In addition, the length compensation is laid in a covered by a body or door trim area, so that no visually disturbing adjustment means are provided in the window area.

The solution according to the invention, for setting a simultaneous stop of both sliding elements in the upper end position to provide a length compensation device for the pressure and / or rigid actuating means and to connect them to the drive means, can be realized with different means.

A first embodiment is characterized in that the position of the drive device with respect to the pressure-resistant and / or bending-resistant actuating means is preferably modifiable in that the effective length of the pressure-resistant and / or bending-resistant actuating means is shortened and the effective length of the other pressure and / or rigid actuating means is extended.

As a result of the positioning of the drive device which can be varied with respect to the pressure-resistant and / or bending-resistant actuating means, a greater length compensation of the pressure and / or bending-resistant actuating means is achieved with minimal changes in position of the drive device. At the same time a simple adjustment during assembly of the window blinds is ensured in which, for example, in preassembled window blind the drive means is actuated until one of the two sliding elements has reached its upper end position. Subsequently, the fastening of the drive device to the vehicle body is released and adjusted by moving or pivoting the drive means an equal distance between the two sliding elements from the upper end position, so that when repeated operation of the drive device in the closing direction of the window blinds a simultaneous stop of both sliding elements at the upper end position is ensured.

By subsequently fixing the drive device to the vehicle body, the thus set length of the two pressure and / or bending-resistant actuating means between the sliding elements and the connection with the drive device is fixed and thus permanently ensuring a simultaneous stop of both sliding elements in the upper end position.

A second embodiment is characterized in that the drive device has a with a drive motor and the pressure and / or rigid actuating means connected differential gear.

By arranging a differential between a drive motor of the drive device and the pressure and / or rigid actuating means, a length compensation between the pressure and / or rigid actuating means via the drive gear is achieved, so that after striking one of the two sliding elements at the upper end stop and the resulting fixed standing of this sliding element adjusting pressure and / or rigid actuating means the other pressure and / or bending rigid actuating means and thus the associated sliding element is further adjusted until this has reached the upper end position. This embodiment thus requires no adjustment of the drive and actuating means of the window blind during assembly and, accordingly, no readjustment due to wear or other stresses of the window blinds.

In a first variant, the differential gear has at least one length compensation element between the drive side connected to the drive motor and the output side connected to the pressure and / or bending-resistant actuating means.

The length compensation element may for example be resilient and consist of a between a drive side and an output side, meshing with the pressure and / or rigid actuating means toothed elements, acting as a torsion spring coil spring or compressible in the circumferential direction of a toothed rubber elements, wherein the coil spring or rubber elements is preferably arranged in a first, a hollow cylindrical inner space having toothed element or are and thus allow a space-saving arrangement.

Alternatively, the length compensation element may consist of a ratchet arranged between a drive-side and an output-side, meshing with the pressure and / or rigid actuating means toothing elements, which has a pawl which on the front side of a receiving the toothed elements Worm wheel is arranged and is in engagement with a ratchet wheel, which is arranged on the end face of a first toothed element.

In a second alternative, the differential gear consists of a differential differential gear, which is coupled to the pressure and / or rigid actuating means coupled Achswellenkegelräder and with the Achswellenkegelrädern, mounted in a differential case bevel gears, the differential differential preferably arranged in a drive worm or with This is connected, which meshes with a drive shaft connected to the motor shaft of the drive screw, so that also an extremely space-saving design and arrangement of the differential gear is ensured.

In a third alternative, the differential gear consists of a self-locking viscous coupling with a transmission of the driving force to the pressure and / or bending rigid actuating means or a force transmission element connected to the pressure and / or rigid actuating means via a viscous silicone oil.

In this differential gear connected to a drive motor drive shaft of the roller blind on steel plates, which are arranged in a hermetically sealed clutch drum with a silicone filling, which is brought by the steel blades in rotary motion, so that due to the high viscosity of the silicone oil, a high entrainment effect with the pressure and / or rigid actuating means connected drive plates is achieved. If there is a difference in rotational speed between the drive shafts connected to the pressure- and / or bending-resistant actuating means, this entrainment effect automatically increases, so that a drive axle becomes stationary as a result of reaching the upper limit stop of the actuating element connected to this drive axle via the pressure-resistant and / or bending-resistant actuating means Sliding the other drive axle is further moved until the connected to this drive axle via the corresponding pressure and / or rigid actuating means sliding member has also reached the upper stop.

In all variants of the solution, the pressure-resistant and / or bending-resistant actuating means can be arranged in a sheath, which are preferably supported on the drive device and on the guide rails, which receive the sliding element connected to the pressure and / or bending-resistant actuating means. Due to the additional arrangement of a spring element between a connected to the pressure and / or rigid actuating means stop on the one hand and in particular the lower end of the guide rails on the other hand, both a damping when reaching the upper stop and a compensation of minor height differences, so that the accuracy requirements of the Length compensation between the actuating means are kept low and readjustments are not required or only at longer intervals.

Embodiments of the solution according to the invention illustrated in the drawing are intended to explain the idea underlying the invention in more detail. Show it:

Figure 1 is a side view of a vehicle door with a schematic representation of a window blinds with partially extended roller blind, pressure and / or rigid actuating means and equipped with a length compensation device drive means.

FIG. 2 shows a schematic illustration of a length compensation device with an adjustable or pivotable drive device; FIG.

3 is a perspective view of a length compensation device with a coil spring acting as a torsion spring;

4 is a perspective view of a length compensation device with rubber elements.

5 is a perspective view of a length compensation device with a ratchet.

Fig. 6 is a perspective view of a length compensation device with a differential differential and

7 is a partially sectioned plan view of the length compensation device with differential differential gear according to FIG. 6.

FIG. 1 shows schematically a side view of a vehicle door 1 with a door cut-out 2 which extends from an upper window frame edge 21, a lateral window frame edge 22 and a lower, substantially horizontally extending and the upper end of a door shaft forming window frame edge 23 is limited and can be closed by a liftable and lowerable window 3.

To cover the disc surface of the window pane 3 is a vertically adjustable in the direction of the double arrow A window blind 7 with a roller blind 8, the up on a winding shaft 9 and to cover the window 3 and the door opening 2 of the winding shaft 9 can be unwound.

The rotatably mounted winding shaft 9 is arranged between an inner panel and an inner lining of the vehicle door 1 and a parapet reinforcement provided below the door opening 2 door parapet in the door shaft and has for winding the blind sheet 8, a spring motor or a torsion spring, the 8 when unwinding the blind sheet the winding shaft 9 is tensioned, so that the roller blind 8 is wound in the opposite direction on the winding shaft 9 with a reduction of the roller blind 8 of the winding shaft 9 subtractive force.

The roller blind 8 has one of the shape of the liftable and lowerable window pane 3 corresponding blank with a circumferential roller blind edge, which includes a fixed to the winding shaft 9 section and an opposite portion 10 which is connected directly or via a pull with sliding elements or slide 15, 16 is, which are guided in lateral guide rails 13, 14, so that the roller blind 8 is withdrawn along the guide rails 13, 14 of the winding shaft 9 and wound onto the winding shaft 9.

To remove the roller blind 8 from the winding shaft 9 is a roller transport mechanism, the pressure and / or rigid actuating means 11, 12, for example in the form of flexible push rods, pressure-resistant toothed belt, spindles, pitch cable or the like, which are actuated by a drive device 4 and guided in the guide rails 13, 14 and connected to the upper roller blind edge 10 sliding elements or carriages 15, 16 along the guide rails 13, 14 adjust. The pressure and / or rigid actuating means 11, 12 are arranged in sheaths 110, 120, which are supported on the one hand on the drive means 4 and on the other hand on the guide rails 13, 14. If one of the two sliding elements 15 or 16 connected to the upper roller blind edge 10 of the roller blind 8 reaches the upper edge of the window frame 21 in front of the other sliding element 15, 16, a wedge-shaped gap between the upper roller blind edge 10 and the upper edge of the window frame 21 results, which covers the covering effect of the Fens terrollos 7 diminished and is generally perceived as disturbing.

In order to ensure an exact lifting height of the sliding elements 15, 16 connected to the upper roller blind edge 10 in accordance with the predetermined contour of the upper window frame edge 21 or of the upper roller blind edge 10, at least one of the two pressure-resistant and / or bending-resistant actuating elements 11, 12 is at an elastic and / or adjustable length compensation device, by means of which the lifting height of the sliding elements 15, 16 can be compensated and / or precisely adjusted in a spring elastic manner. This spring-elastic length compensation or the exact adjustment of at least one of the two pressure and / or rigid actuating means 11 and 12 and thus a contour of the upper window frame edge 21 and the upper roller blind edge 10 adapted lifting height of the sliding elements 15, 16 can be realized by different length compensation devices become.

2 shows in an enlarged schematic plan view the region V according to FIG. 1 with the drive device 4 arranged on a mounting or carrier plate 100, which usually consists of a drive motor 5 and a drive gear 6, which are connected to drive means 111, 121 of the pressure and / or rigid actuating means 11, 12 is coupled, so that upon actuation of the drive motor 5, the pressure and / or rigid actuating means 11, 12 are moved via the connected to the drive motor 5 drive gear 6 in opposite directions, so that with the ends of the pressure and / or rigid actuating means 11, 12 connected sliding elements 15, 16 are raised or lowered together on their associated guide rails 13, 14.

In the embodiment shown in FIG. 2, the drive elements 111, 121 of the pressure and / or bending-resistant actuating means 11, 12 are formed as flexible tooth elements in the form of spindles, pressure-resistant toothed belt or the like, which engage in drive gears of the drive gear 6. The envelopes 110, 120 of the pressure and / or rigid actuating elements 11, 12 are supported on the support plate 100 via stops 112, 122. By adjusting the drive means 4 in one of the two indicated by the double arrow B directions, the position of the drive means 4 with respect to the pressure and / or rigid actuating means 11, 12, ie the respective distance between the connection of the drive gear 6 with the drive elements 111 , 121 of the pressure and / or rigid actuating means 11, 12 and thus the distance to the sliding elements 15, 16 shown in FIG. 1, changed, so that the effective length of the one actuating means 11 and 12 is shortened, while the effective length of the other actuating means 11 and 12 is extended. The length compensation effected thereby ensures simultaneous reaching of the upper end position of both sliding elements 15, 16 connected to the actuating means 11, 12, so that the section 10 of the roller blind edge opposite the winding shaft 9 rests flush against the upper edge of the window frame 21.

The housing of the drive motor 5 is connected to two slotted guides, which have elongated holes Verstellaufnahmen 51, 52, in the two associated with the support plate 100 Verstellführungen 53, 54 engage, so that the lateral adjustment of the drive motor 5 is limited in the direction of the double arrow B. ,

For reasons of space, the sheaths 110, 120 of the actuating means 11, 12 can be formed in the shape of a blade and, correspondingly, the actuating means 11, 12 can be brought into arcuate running with their drive elements 111, 121 into engagement with the drive gear 6. By pivoting the drive device 4 about an axis forming the center point of the curved shape of the sheaths 110, 120, a corresponding length compensation is likewise achieved between the pressure-resistant and / or bending-resistant actuating means 11, 12.

The length compensation device shown in perspective in FIG. 3, connected to the drive device 4, shows the drive motor 5, a drive worm 60 connected to the drive shaft of the drive motor 5, and a worm wheel 61 which meshes with the drive worm 60 and is non-rotatably connected to two gear elements 62, 63. The first toothed element 62 has a hollow-cylindrical interior, in which a helical spring 31 acting as a torsion spring is arranged, whose bent spring ends engage on the one hand with a stop in the hollow-cylindrical interior of the first toothed element 62 and on the other hand with a stop of the worm wheel 61. The toothed elements 62, 63 in turn mesh with formed as spindles, for example, pressure and / or rigid actuating means 11, 12th

The torque transmission from the drive motor 5 to the toothed elements 62, 63 and thus to the roller blind 8 via the sliding elements 15, 16 and optionally a pull bar adjusting pressure and / or rigid actuating means 11, 12 thus takes place via the drive screw 60 and the worm wheel 61 directly to the second toothed element 63, while the torque is transmitted from the worm wheel 61 to the first toothed element 62 via the helical spring 31 acting as a helical spring, so that a relative movement between the two pressure and / or bending-resistant actuating means 11, 12 is made possible. As a result, a length compensation depending on the force acting on the pressure and / or rigid actuating means on the part of the sliding elements 15, 16 and ensures that both sliding elements 15, 16 can move into the respective end positions, even if the pressure and / or rigid actuating means 11, 12 are not precisely adjusted and thus have a length which ensure a synchronous movement of the sliding elements 15, 16.

4, the helical spring 31 of the length compensating device according to FIG. 3 is replaced by rubber elements 32, which are arranged in the force flow between the worm wheel 61 and the first toothed element 62. For this purpose, the worm wheel 61 can be provided with radially extending cylindrical cutouts 610, which are divided by webs 611 corresponding to the number of rubber elements 32. The three rubber elements 321, 322, 323 shown in this embodiment are inserted into the radially extending cutouts 610 in the worm wheel 61 and have bores 324 for transmitting power to the first toothed element 62, into which one end face of the first toothed element 62 in the hollow cylindrical interior intervene protruding pins.

Alternatively, a corresponding receptacle can be provided in the first toothed element 62 into which the rubber elements 321, 322, 323 are inserted, in the bores 324 of which pins 61 projecting from the end face of the worm wheel 61 engage.

In the length compensation device shown in perspective in FIG. 5, a ratchet is used for length compensation between the pressure and / or bending-resistant actuations

11, 12. In an analogous version to the length compensation devices according to FIG. 3 and 4, a drive motor 5 drives, via a drive worm 60, a worm gear 61 which is directly connected to a second gear element 63 and via the ratchet to the first gear element 62. The ratchet consists of a pawl 33 arranged on the front side of the worm wheel 61, which is aligned with a pawl wheel 34 arranged on the front side of the first toothed element 62, so that in the manner of a pawl for locking a gear part, for example the handbrake of a motor vehicle, under the action of a force or a torque between the worm gear 61 and the first gear member 62, a relative movement between the worm gear 61 and the first gear element 62 takes place until a predeterminable maximum torque occurs and the power transmission from the worm gear 61 to the first gear element 62 directly he follows.

By applying the ratchet principle, a self-adjusting system for length compensation of non-synchronously moved sliding elements 15, 16 is thus made possible.

In Fig. 6 designed as a differential differential gear differential or length compensation device is shown in a perspective view. Like the embodiments described above, the drive device 4 consists of a drive motor 5 whose motor shaft is connected to a drive worm 60 which meshes with a worm wheel 61. The worm wheel 61 contains in its interior the differential differential gear 40 which is connected to two toothed elements 62, 63, whose teeth engage in the corresponding counter-toothing of two pressure and / or rigid actuating means 11, 12.

By applying the principle of operation of a differential differential gear ensures that when reaching the end position of one of the two with the pressure and / or rigid actuating means 11, 12 connected sliding elements 15, 16 the respective pressure and / or rigid actuating means 11 and 12 stopped is, while the other sliding member 15, 16 or pressure and / or rigid actuating means 11, 12 is further moved to reinforced until this has reached the end position.

7 shows a partially sectioned plan view of the length compensation device with differential differential gear according to FIG. 6. The drive motor 5 of the drive device 4 is connected via the drive worm 60 with the worm wheel 61 in which four intermeshed bevel gears 42 to 45 are arranged. Two opposing Ausgichskegelräder 42, 43 are mounted with their axes in the differential housing 41 of the worm wheel 61, while the two perpendicular thereto and opposite each other Achswellenkegelräder 44, 45 are connected to the toothing elements 62, 63, with the pressure and / or rigid actuating elements 11, 12 mesh and, depending on the direction of rotation of the drive motor 5, lift or lower the sliding elements 15, 16 connected to the pressure-resistant and / or rigid actuating elements 11, 12 on the guide rails 13, 14, so that the roller blind 8 according to FIG 1 unwound from the winding shaft 9 for covering the window pane 6 according to FIG. 1 or wound on the winding shaft 9 to release the window pane 6.

When lifting the sliding elements 15, 16 drives the drive motor 5 via the drive screw 60, the drive worm wheel 61, the bevel gears 42, 43 do not rotate on their shafts and take the Achswellenkegelräder 44, 45 in effect equal to a rigid connection, so that the two connected to the Achswellenkegelrädern 44, 45 toothing elements 62, 63 rotate at the same speed and thus the pressure and / or rigid actuating means 11, 12 move uniformly in opposite directions, so that the sliding elements 15, 16 on the guide rails 13, 14 are raised uniformly.

If one of the two sliding elements 15, 16, for example, the sliding element 15 reaches the upper end stop, the associated toothed element 62 and the axle bevel wheel 44 connected thereto can not rotate due to the connection via the pressure and / or bending actuating means 11. However, the drive worm wheel 61 is rotated by the drive screw 60 further from the drive motor 5 in the same direction of rotation and takes with their shafts in the differential housing 41 mounted bevel gears 42, 43 with it. Because of the fixed axle shaft gear 44, the differential bevel gears 42, 43 entrained by the differential gear housing 41 must turn about their own axis and thus roll on the stationary axle bevel gear 44. As a result, due to the sliding element 16, which is not yet in its upper end position, the axle bevel wheel 45, which likewise engages with the differential bevel gears 42, 43, receives an additional drive and causes, via the toothed element 63 and the pressure element 63 and / or rigid actuating means 12 an accelerated adjustment of the Gleitele- element 16 until this has reached the upper end position.

Owing to the additional drive of the axle bevel wheel 45 coupled to the "trailing" sliding element 16, the time delay with which one of the two sliding elements 15, 16 reaches the upper end position is so minimal that the impression of simultaneously abutting both sliding elements 15 for the user , 16 in the upper end position with flush contact of the winding shaft 9 opposite portion 10 of the roller blind edge on the upper edge of the window frame 21 is formed.

Since the differential differential gear length differences of the two pressure and / or rigid actuating means 11, 12 regardless of which of the two sliding elements 15, 16 reaches the upper end position first, is during assembly of the window blinds no adjustment of the sliding elements 15, 16 by appropriate Längenein- positions of the pressure and / or rigid actuating means 11, 12 required. As a result of the additional drive of coupled to the trailing sliding axle Achswellenkegelrads each fixed to the other Achswellenkegelrad occurs no significant difference in the end position positioning of the sliding elements 15, 16, even with larger ^' length differences.

The possible embodiments of the solution according to the invention are not limited to the embodiments shown in the drawing and described above. Thus, for example, instead of pivoting the drive device 4 according to FIG. 2, only the drive gear 6 or individual gear parts for length compensation of the pressure and / or rigid actuating means 11, 12 are adjusted.

A variant of the embodiment shown schematically in Fig. 3 consists in an insert of the above-described self-locking viscous coupling or a similar differential gear.

By adjusting the drive device, arrangement of a differential gear or a length compensation system thus a simple and centrally applicable tolerance compensation of manufacturing and setting tolerances is made possible and damped retraction of the sliding elements in the blocking state when reaching the upper and lower end position. Furthermore, switching noises when changing the Verstellrich- tion of the window blinds and the occurrence of Einklemmkräften when closing the window blinds reduced. Finally, the use of adjusting devices and accordingly a costly adjustment of the window blinds to achieve a synchronous movement of the sliding elements can be dispensed with.

LIST OF REFERENCE NUMBERS

1 vehicle door

2 door opening

3 window pane

4 drive device

5 drive motor

6 drive gear

7 window blind

8 roller blind

9 winding shaft

10 of the winding shaft opposite portion of the roller blind edge 11, 12 pressure and / or rigid actuating means

13, 14 guide rails

15, 16 sliding elements

18, 19 spring elements 1 upper edge of the window frame 2 side edge of the window frame 3 horizontal edge of the window frame 1 coil spring 2 rubber elements

33 pawl

34 Ratchet wheel 0 Differential differential 1 Differential gear case 2, 43 Compensating bevel gears 4, 45 Axle bevel gears

51, 52 adjustment shots

53, 54 Adjustment guides

60 drive screw

61 drive worm wheel

62 first toothing element

63 second toothing element 100 carrier plate

110, 120 Enclosure of the pressure and / or bending-resistant actuating means

112, 122 strokes

Claims

claims

1. Window roller blind for a vehicle window, which is delimited by a peripheral window frame with a lower, upper and side edge of the window frame, with a roller blind whose circumferential roller blind edge has a fixed to a rotatably mounted winding shaft portion and a remote from the winding shaft portion, with two in the Essentially parallel to each other guide rails, in which with the remote from the winding shaft portion of the

Roller blind edge associated sliding elements are guided longitudinally displaceable by means of pressure and / or rigid, connected to a drive means actuating means,

marked by

a device (31-34; 40; 51-54) connected to the drive device (4) for length compensation of the pressure- and / or bending-resistant actuating means (11, 12).

2. Roller blind according to claim 1, characterized in that the position of the drive device (4) with respect to the pressure and / or bending-resistant actuating means (11, 12) is variable.

3. Roller blind according to claim 1 or 2, characterized in that the drive device (4) is adjustable such that the effective length of a pressure and / or rigid actuating means (11 or 12) shortened and the effective length of the other pressure and / or rigid actuating means (12 or 11) is extended.

4. Roller blind according to claim 3, characterized in that the drive device (4) is linearly adjustable or pivotable about an axis.

5. Roller blind according to claim 1, characterized in that the drive device (4) with a drive motor (5) and the pressure and / or rigid actuating means (11, 12) connected to the differential gear (31 - 34, 40).

6. Roller blind according to claim 5, characterized in that the differential (31 - 34, 40) at least one length compensation element (31 - 34) between the drive motor (5) connected to the drive side and the pressure and / or bending-resistant actuating means ( 11, 12) connected output side up.

7. Window roller blind according to claim 6, characterized by a spring-elastic length compensation element (31, 32).

8. Roller blind according to claim 7, characterized in that the spring-elastic length compensation element of a between a drive-side and an output side, with the pressure and / or rigid actuating means (11, 12) meshing toothing elements (62, 63) arranged acting as a torsion spring coil spring (31) exists.

9. Roller blind according to claim 7, characterized in that the spring-elastic length compensation element from between a drive-side, with the pressure and / or rigid actuating means (11, 12) meshing toothing elements (62, 63) arranged in the circumferential direction of the one toothed element (62) compressible rubber elements (32).

10. Roller blind according to claim 5, characterized in that the helical spring (31) or rubber elements (32) in a first, a hollow cylindrical interior having toothing element (61) is arranged or are.

11. Window roller blind according to claim 10, characterized in that the length compensation element from a between a drive side and a driven side, with the pressure and / or bending-resistant actuating means (11, 12) meshing toothing elements (62, 63) arranged ratchet (33, 34).

12. Window roller blind according to one of the preceding claims 5 to 11, characterized in that the ratchet has a pawl (33) which on the end face of the toothed elements (62, 63) receiving worm wheel (61) is arranged and with a ratchet wheel (34 ) is engaged, which at the

Front side of a first toothed element (62) is arranged.

13. Window roller blind according to claim 5 or 6, characterized in that the compensation gear is designed as differential differential gear (40), with the pressure and / or bending-resistant actuating means (11, 12) coupled Achswellenkegelräder (44, 45) and with the Achswellenkegelrädern (44, 45) meshing, in a differential housing (41) mounted bevel gears (42, 43).

14. Roller blind according to claim 13, characterized in that the differential differential (40) in a drive worm wheel (61) is arranged or connected to a Antriebschneckenrad (61) connected to a with the motor shaft of the drive motor (5) drive screw (60 ) combs.

15. Window roller blind according to claim 5 or 6, characterized in that the differential gear as a self-locking visco-coupling with a transmission of the drive force on drive elements of the pressure and / or bending-resistant actuating means

(11, 12) is formed via a viscous silicone oil.

16. Window roller blind according to at least one of the preceding claims, characterized in that the pressure and / or rigid actuating means (11, 12) in sheaths (110, 120) are arranged, which are supported at least on the drive means (4).

17. Roller blind according to claim 16, characterized in that the sheaths (110, 120) on the guide rails (13, 14) are supported.

18. Roller blind according to claim 16 or 17, characterized in that the LJm hüllungen (110, 120) end, on the guide rails (13, 14) adjacent

Have stops (112, 122).

19. Roller blind according to claim 18, characterized in that between the stops (112, 122) and the guide rails (13, 14) spring elements (18,

19) are arranged.