DE3201098A1 - Cable-type window lifter, especially for motor vehicles - Google Patents

Abstract

In a cable-type window lifter for motor vehicles, having a pull cable (14) guided via a deflection (32) and engaging on the window pane, it is proposed to provide between the deflection pulley (36) and the bearing part (34) a curved helical spring (38) which is under compression prestress and which prestresses the displaceably mounted deflection pulley (36) in the direction C and thus allows an automatic cable retensioning. Furthermore, the axis of rotation of the deflection pulley (36) can be pivoted in adaptation to changing inclinations of the pull cable (14). A holding bolt (41) attached eccentrically to the bearing part (34) makes mounting easier. <IMAGE>

Description

Cable window regulators, in particular for motor vehicles

The invention relates to a cable window regulator, in particular for motor vehicles, with a guided over at least one deflection mounted on a carrier a window pane, possibly via a driver that can be displaced on a guide rail attacking, driven pull rope, which by means of at least one elastic The tensioning element is pre-tensioned. In known cable window regulators of this type (e.g. DE-GM 79 16 177 Fig. 1) is a pretensioned compression spring.

see which one between the carrier and a Bowden cable cover for the Pull rope acts and in this way ensures that the pull rope is always under one Preload is independent of manufacturing and assembly inaccuracies as well as independently changes in dimensions occurring during operation, in particular rope elongations. The pull rope must always be under tension to ensure a smooth reversal of direction to ensure the window regulator and to prevent the open run Pull rope jumps out of its guides. The disadvantage of the known arrangement is that they requires the use of a Bowden cable cover. In addition to the Increase in manufacturing and assembly costs due to this additional part is also disadvantageous that the pull rope is only accessible to a limited extent, which for example it is difficult to change the rope.

In contrast, the object of the invention is to provide a cable window regulator of the type mentioned at the outset to be provided, regardless of the use a Bowden cable sleeve, the rope can be tensioned or retensioned automatically.

This object is achieved in that at least one of the deflections designed to be displaceable and / or pivotable relative to the carrier and by the Tensioning element acting between the carrier and the deflection in the sense of a tensioning of the rope is biased.

The rope tension or tensioning of the rope is accordingly determined by the corresponding Shifting the deflection causes the need for the use of a Bowden cable cover is not required.

Even a relatively small shift in the deflection is already achieved a relatively large rope length compensation is achieved. For example, with a 1800 diversion corresponds to a shift of the deflection taking place in the longitudinal direction of the rope Rope shortening by twice the length.

It is proposed that the deflection comprises a deflection roller, which is preferably attached to a carrier with play in a radial direction Bearing part is stored with the interposition of the clamping element. By using The pulley reduces the friction of the pull rope at the deflection, making it easier Running and less wear. The structure is still simple, there only a total of three parts, namely the pulley, the Bearing part as well as the clamping element are required, it is further proposed that as elastic Biasing element a helical spring is used, which is under axial compressive bias standing is supported with both ends on the bearing part and a curved one, preferably has approximately part-circular helical spring axis and that the ring-shaped Deflection pulley with an inner circumferential surface on the outer curvature of the coil spring is present.

In this embodiment, the outer curvature of the helical spring thus forms the movable pivot bearing for the pulley.

When the tension in the rope is released, the helical spring presses with it its middle part to the outside, taking the pulley with it. this leads to for the desired tensioning of the pull rope. Since the coil spring always has several of its turns rests against the inner circumferential surface of the deflection roller, is the friction comparatively low between helical spring and pulley. Because a relative long coil spring can be used, can also have a relatively large stroke achieve.

For guiding the coil spring on the bearing part and subsequently for It is suggested to guide the pulley via the helical spring on the bearing part, that the bearing part and / or the pulley with a guide groove for the helical spring are provided.

To simplify assembly, it is proposed that the two ends the coil spring are used in adapted grooves of the bearing part.

When using pulleys, which in the area of the ends of a curved guide rail are arranged, there arises a problem that the inclination of the rope section extending between the pulley and the driver opposite a changes to a rigid pulley axis perpendicular plane.

This leads to the fact that the flank surfaces of a cable guide groove Deflection pulley can be worn out in a short time. The wear and tear of the now also loaded on tilting pivot bearing of the pulley. To these disadvantages to avoid it is proposed that the deflecting roller about an axis of curvature the curved guide rail parallel pivot axis pivotable on the one with the Guide rail is mounted rigidly connected carrier. The inclination of the pulley axis therefore changes according to the inclination of said pull rope section, so that forces always act on the deflection roller, which in a pivotable deflection roller axis vertical plane. The two rope sections leading to the pulley are lying always on this level.

This pivot bearing is achieved with simple means by that the pulley with a game that allows these pivoting movements on the Support attached bearing part is stored.

In order to allow the pulley to move under a To avoid inclined tensile loads, a in all displacement or. Pivoting positions of the pulley on one side surface the deflection roller adjacent holding and guide tabs proposed.

In order to reduce the friction between the bearing part even when the deflection roller is pivoted and pulley as small as possible (when using the helical spring: in the starting position of the pulley with the largest possible stroke), it is suggested to form the contact surfaces convex. When using the aforementioned holding and guiding flap are the convex contact surfaces in the area of the holding and guide tabs distant inner circumferential edge of the deflection roller seen.

To facilitate assembly, it is proposed that the bearing part with a perpendicular to the plane of the deflected pull rope, to the contact surface of the pull rope is rotatably connected to the deflection eccentric bearing pin, which is in a Bolt opening of the carrier pivotable and in different rotational positions is determinable. During assembly, the bearing part can therefore be pivoted towards the rope as far as possible that this can be easily placed over the pulley. Afterward the bearing part is swiveled back until the desired preload is achieved is and then fixed on the carrier. The setting of the desired rotational position is simplified by the fact that the bearing pin and the pin opening are positively locked interlocking serrations or saw teeth are provided, in the latter Trap by training with saw teeth that yield elastically in the radial direction there is the possibility that the bearing pin with interlocking saw teeth can be twisted in a single direction.

To fix the bearing part on the carrier in a desired rotational position the bearing pin can be riveted to the carrier. In another embodiment the invention, the bearing pin is star riveted to the carrier. In this case the serrations or saw teeth can be omitted, since the star riveting for a provides a non-rotatable connection between the bearing pin and the carrier. It is therefore not a axial shift required for rotary adjustment.

A safe transport of the pull rope is guaranteed when the pulley is provided with a wedge-shaped or trapezoidal rope groove that receives the pull rope.

Simple, inexpensive production is guaranteed, if how proposed the pulley and / or the bearing part made of plastic, preferably Injection plastic, are formed.

The invention is based on an exemplary embodiment below the drawing explained.

1 shows a schematic front view of a cable window regulator; FIG. 2 shows a partial view of the arrangement according to FIG. 1 in the direction of arrow II; Fig. 3 shows a front view of a cable deflection according to the invention as detail A of FIG. 1; FIG. 4 shows a sectional view of the cable deflection according to FIG. 3 in section the line IV-IV; FIG. 5 shows a sectional view according to FIG. 4, but with the rope tensioning pulley moved upwards; and FIG. 6 is a single front view of a bearing part the deflection according to FIGS. 3 to 5.

In Figs. 1 and 2, a cable window regulator 10 is roughly schematically for Installation in a motor vehicle door shown. This includes a hand crank driven or electric motor-driven drive unit 12, which has a not shown Rope drum drives a pull rope 14 guided along a closed loop. The pull rope 14 is used to move up and down (double arrow B in Fig. 1) one not window pane shown, which via a U-rail 16 indicated in FIG its lower transverse edge with a driver 18 the window regulator 10 is positively connected. In Fig. 1 there are fastening holes 20 for fastening the U-rail 16 indicated on a driver plate 19 of the driver 18.

A driver block 22, also only indicated schematically, which is attached to the underside of the driver plate 9, takes a cable nipple 24 of the pull rope 14 so that the driver 18 is taken along by the pull rope 14.

The driver 18 is on a guide blocks, not shown Cross-sectionally L-shaped guide rail 26 displaceable back and forth along this. At the two ends of the guide rail 26 holding plates 28 are attached which on the one hand, the attachment of the guide rail 26 to a motor vehicle door panel serve (mounting holes 30) and on the other hand each have a carrier for each form a deflection 32 for the pull rope 14. In FIGS. 3 to 6, the one shown in FIG. 1 upper rope deflection 32 shown in detail (on a scale of approx. 2: 1).

The rope deflection 32 consists only of three parts, namely one Bearing part 34 shown individually in FIG. 6, one encompassing the bearing part 34 Deflection roller 36 and a helical spring 38 between bearing part 34 and deflection roller 36.

The bearing part 34 consists of a carrier portion 40, one in the 4 and 5 to the right from the support section 40 projecting bearing bolts 41 and of two lobes protruding upwards in FIGS. 3 to 6, of which the longer, namely the left in FIGS. 4 and 5, denoted by 43 and the shorter by 45 is.

The carrier portion 40 in the form of a general prism, so with mutually parallel side surfaces 42 and 44, is on its downwardly directed Side (surface 46) rounded in such a way that in the uppermost shown in FIG Position of the deflection roller 36, this rests with its inner circumference on the carrier section 40.

The surface 46 is accordingly a partial cylinder circumferential surface more horizontal Cylinder axis and an inner radius R1 of the deflection roller 36 substantially corresponding Cylinder radius.

Since the part of the cylinder located in a plane perpendicular to the cylinder axis defining sector angle a (see Fig.

6) with approx. 1400 is less than 1800 and thus din in FIGS. 3 and 6, e.g. the width d of the support section 40 running from left to right accordingly is smaller than the inner diameter R1 of the pulley 36 and also the height of the Carrier section 40 including those resting against it in the position according to FIG. 4 Helical spring 38 is smaller than the inner diameter R1, the pulley can 36 are moved back and forth in the direction of arrow B by the distance a according to FIG. 3 namely between the lower end position shown in Fig. 4 and the upper one End position according to FIG. 5. The tab 43 here serves as a holding and guide tab for the deflection roller 36, the lifting and thus removal of the deflection roller 36 prevented by the bearing part 34 in the direction away from the holding plate 28. As Fig. 5 shows, the area of the guide roller 36 which is located above is between the tabs 43 and the holding plate 28 arranged with little lateral play and on this Way safely guided in all positions.

The movement play a makes it possible to re-tension the rope 14, wherein due to the approximately 1800 deflection of the rope 14 around the deflection pulley 36 compensates for a change in rope length of almost double the play a can be. The deflection pulley is used to achieve automatic tensioning of the rope 36 biased in the direction of arrow C by means of the helical spring 38. For this is the helical spring 38 under axial compressive prestress standing on the support section 40 attached, with both coil spring ends supported on inclined surfaces 47, which adjoin the lower surface 46 and against each other forming an angle ß are inclined by approximately 1700. Between these surfaces 47 extends a Partial cylinder jacket surface 48 on which the deflection roller is in the lower end position 36 3 and 4, all turns of the helical spring 38 are in contact. The dotted indicated helical spring axis 50 is also approximately part-circular in the sequence (see Figure 3). However, the coil spring can only remain in this position if this is prevented from dodging with its middle part upwards, that is, in direction C, which is achieved by the deflecting roller 36, on its inner circumference the coil spring 38 rests in the area of its outer curvature with all turns, provided that the pulley 36 is of the correspondingly short pull rope 14 in their held lower end position. However, as soon as the tension of the pull rope 14 decreases, For example, due to rope elongation during operation, the helical spring urges 38 with its middle area upwards, taking the pulley 36 with it.

To fasten the ends of the coil spring 38 are on the support section 40 in the area of the inclined surfaces 47 receiving grooves 52 are provided. To a side Preventing the coil spring 38 from swerving is the inner circumference of the pulley 36 formed with a correspondingly formed guide groove 54. In the lower End position (Fig. 3 and 4) the coil spring 38 is also on the inside of the Lobe 45.

The guide rail 26 shown in Fig. 2 is around a horizontal Curvature axis curved with radius R2. During the movement of the carrier 18 The inclinations 61 and 62 of the driver therefore change along the guide rail 18 leading to the rope deflections 32 rope sections 55 and 57 to a through the cable sections 59 and 61 between the deflections 32 and the drive unit 12 defined rope loop plane. This change in angle when the power windows are operated can be about 100 to 150. In this case, pulleys with more rigid Deflection pulley axis used, it occurs as a result of the inclined feed of the rope on the Leading role to increased wear of unsteering roller and Pull rope. To pivot the deflection roller axis 63 (see FIG. 4) alternatively or In addition to the described tensioning of the rope, the deflection pulley is necessary 36 on the bearing part 34 about a pivot axis running from left to right in Fig. 3, for example pivoted. In the lower end position shown in FIGS. 3 and 4 of the deflection roller 36, this lies with a contact surface 56 on a contact surface 58 at the free upper end of the tab 45, the inner surface of the contact surface 56 distant Circumferential edge 62 of the pulley 36 is the vertical inner surface 64 of the long lobe 43 touched. Since the deflection roller 36 decreases in width radially outwards (with inwardly curved side surfaces 60) there is the possibility of the pulley 36 in the direction of arrow D in its circumferential surface indicated by dashed lines in FIG. 4 Pivoting position (with deflection roller axis 63 ') - to be pivoted. Here the slide matched, convex (contact surface 58 concave) contact surfaces 56 and 58 against each other; the left in Fig. 4 inner peripheral edge 62 slides on the Inner surface 64 of the nose 43 upwards. The pivot position shown in FIG is again an end position, since the right outer peripheral edge 66 of the pulley 36 now rests on the holding plate 28 and the deflection roller is pivoted further 36 prevented. When the rope tension decreases and as a result when there is a movement the deflection roller 36 upwards, the contact surfaces 56 and 58 are removed from one another. However, this does not affect the pivotability of the deflection roller 36, the then rests on the outer curvature of the helical spring 38 and between the nose 43 and the retaining plate 28 is pivotably guided. Only in the upper end position shown in FIG The contact surface 56 of the deflection roller 36 rests against a correspondingly curved one Contact surface 65 in the area of the right edge in FIG. 5 of the lower, partially cylindrical Surface 46 of the bearing part 34. The deflection roller 36 is symmetrical to its axis normal Middle plane formed so that their spherical contact surface 56 opposite a further convex contact surface 67 is arranged, which is in the position 5 rests against a correspondingly shaped surface 69 of the carrier section 40 (see also Fig. 6). In the position shown in Fig. 5, the pulley 36 can therefore no longer be pivoted, which, however, is no longer problematic is practical because this position is useful when using the built-in window regulator is never reached, but only a transport position of the preassembled window regulator represents.

So that the pivoting movement of the pulley is not hindered is that the left in Fig. 4 inner peripheral edge 62 with the radially external side edges 70 of the nose 43 collides, the nose 43 is relative kept narrow with a horizontal average width b in FIG. 3, which corresponds to approximately 0.4 times the inner diameter R1 of the deflection roller 36. The deflection roller 36 is against a perpendicular to the tilting movement in the direction of arrow D Tilting movement sufficiently secured because at the beginning of the sliding movement from the 3 and 4, the helical spring 38 is substantially above the lower end position according to FIGS their entire length between the curved surfaces 56 and 67 on the inner circumference the guide roller 36 formed guide groove 54 rests and with increasing displacement The number of adjacent turns decreases towards the top, but the tab 43 does ensures adequate guidance of the deflection roller 36 due to its increasing width. Here, the play between the pulley 36, the holding plate 28 and the Nose 43 just big enough that the pulley 36 in all of its displacement and Pivot positions not jammed between holding plate 28 and nose 43.

Due to the pivoting option described, the pulley follows 36 of the different inclinations of the cable section 57 coming from the driver 16, so that the rope 14 is always on Groove bottom of a V-belt groove-like Cable groove 72 runs on the outer circumference of the deflection pulley and not on the groove flanks 74 scrubs. The wear of the rope 14 and the rope groove 72 is therefore low and the run of the deflection roller 32 therefore also runs smoothly.

The already mentioned bearing pin 41, which is on the side of the shorter Nose 45 protruding perpendicularly from the side surface 44 of the carrier section 40 is related arranged eccentrically on a vertical center plane 79 parallel to the bolt axis with a distance c between the bolt axis and the center plane, which forms the eccentricity. For assembly, the bearing part 34 can now be pivoted about this eccentric bolt 41 are, for example, indicated in Fig. 3 with a dotted outline 34 'designated position in which the nose 43 is horizontal. You can see that the now highest point of the bearing part 34 due to the eccentricity below the outer curvature of the helical spring 38 in the starting position according to FIGS. 3 and 4 lies.

It can therefore be provided with the pull rope in the intended length Deflection roller 36 conveniently pushed over the bearing part 34 into its intended position and then the bearing part 34 in the final position with upwards or in the direction of the arrow C pointing nose; the direction C is 1 approximately on the bisector between the cable sections 57 and 61.

Since it is not necessary, the nose 43 is exactly parallel to the direction Aligning C can be done by deviating more or less from this orientation already requires a basic adjustment according to the respective rope length be made. To make this easier, the end is on the carrier section side of the bearing pin 41 with a circumferential serration 76, as indicated in Fig. 6, educated. This engages positively in a corresponding one Internal circumferential serration a receiving opening 78 of the holding plate 28. For rotational adjustment of the bearing part 34 this is therefore the width of the serration 76 in Fig. 3 and 4 shifted to the left, then twisted in the desired way and finally pushed back to the right into mutual engagement of the serrations.

Instead of the serration, however, saw teeth can also be used be, in which the teeth are so radially resilient that when interlocking Saw teeth (i.e. without having to move axially) the bearing part 34 are rotated in the counterclockwise direction of FIG. 3 to tension the pull cord 14 can, however, a blockage occurs in the opposite direction.

To prevent unintentional adjustment of the bearing part 34 when it is fully assembled To prevent window lifter 10, the bearing part 34 with the driver plate 22 riveted after adjustment, for example by means of star riveting 82 of the free end 80 of the bearing pin 41 (see Fig.

5). This prevents axial displacement of the bearing pin 41, so that the serrations always remain in mutual engagement.

The above-described rope deflection 32 is characterized in that it ensures automatic tensioning of the rope over a relatively large stroke. The displacement distance a of the deflecting roller 36 is approximately one third at 7.5 mm of the inside diameter R1 of the deflection roller 36. In addition, there is the possibility of the axis 63 of the deflection roller 36 by an angle y (see Fig. 4) of about 100 to Pan 150. Additionally or alternatively to the possibility of shifting and swiveling is achieved by fastening the bearing part 34 via an eccentric bearing pin 41 (eccentricity c about 4 mm) a simplified assembly achieved, since by corresponding pivoting of the bearing part 34, the deflection roller 36 in the direction is shifted towards the center of the rope loop. The training of the bearing pin 41 with serration 76 (or saw teeth) allows easy adjustment of the Bearing part 34 as a function of the respective rope length, the bearing part 34 can be fixed in the selected rotational position.

The deflection roller 36 and possibly also the bearing part 34 can be made of plastic are injected, so that only low manufacturing costs are incurred.

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Claims (16)

Cable window lifters, especially for motor vehicles patent claims 1. Cable window lifters, especially for motor vehicles, with one over at least a deflector (32) mounted on a carrier and guided to a window pane possibly engaging via a driver (16) which is displaceable on a guide rail (26) Pull rope (14) which is pretensioned by means of at least one elastic tensioning element is, characterized in that at least one of the deflections (32) opposite the Carrier is designed to be displaceable and / or pivotable and by the between Carrier and deflection (32) acting tensioning element in the sense of a rope re-tensioning is biased. 2. Cable window regulator according to claim 1, characterized in that the deflection (32) comprises a deflection roller (36) which preferably with play in a radial direction (C) on a bearing part (34) attached to the carrier Between circuit of the clamping element is stored. 3. Rope window regulator according to claim 2, characterized in that the resilient biasing element comprises a coil spring (38). 4. Rope window regulator according to claim 3, characterized in that the helical spring (38), which is under axial pressure pretension, engages with both Ends on the bearing part (34) supported and a curved, preferably approximately part-circular Has helical spring axis (50), and that the ring-like deflection roller (36) rests with an inner circumferential surface on the outer curvature of the helical spring (38). 5. Rope window regulator according to claim 4, characterized in that the bearing part and / or the pulley (36) with a guide groove (54) for the helical spring (38) is provided. 6. Cable window regulator according to claim 4 or 5, characterized in that that the two ends of the helical spring (38) in adapted receiving grooves (52) of the Bearing part (34) are used. 7. Rope window regulator, in particular according to one of claims 1 to 6, characterized in that the deflection (32) formed with the deflection roller (36) about a pivot axis parallel to the axis of curvature of the curved guide rail (26) pivotable on the support rigidly connected to the guide rail (26) (holding plate 28) is stored. 8. Rope window regulator according to claim 7, characterized in that the deflection roller (36) with a play that allows this pivoting movement on one or the bearing part (34) attached to the carrier is supported. 9. Cable window regulator according to one of claims 2 to 8, characterized by one attached to the bearing part (34) in all shifting or pivoting positions the deflecting roller (36) on one side of the deflecting roller (36) holding and Guide tab (43), which extends in the circumferential direction of the adjacent pulley (36) extending width (b) is preferably smaller than the inner diameter R1 of the pulley and preferably about 1/4 to 1/2 of the inner diameter R1 amounts to. 10. Cable window regulator according to claim 8 or 9, characterized in that that the bearing part (34) and the deflection roller (36) are formed on matched, convex Contact surfaces (56, 58) bear against one another. 11. Rope window regulator according to claim 10, characterized in that the contact surface (56) of the deflection roller (36) in the area of the shape holding and guide tabs (43) more distant inner peripheral edge of the deflection roller (36) is provided. 12. Cable window regulator, in particular according to one of claims 1 to 11, characterized in that the deflection or the bearing part (34) with a to the plane of the deflected pull rope (14) perpendicular to the contact surface of the pull rope (14) on the deflection eccentric bearing pin (41) is non-rotatably connected, which is in a bolt opening (78) of the carrier (retaining plate 28) pivotable and fixable in different rotational positions. 13. Rope window regulator according to claim 12, characterized in that the bearing bolt (41) and the bolt opening (78) with interlocking interlocking Notch or Saw teeth (76) are formed. 14. Cable window regulator according to claim 12 or 13, characterized in that that the bearing pin is riveted, preferably star riveted, to the carrier. 15. Cable window regulator according to one of claims 2 to 14, characterized in that that the deflection pulley (36) with a wedge-shaped or trapezoidal shape which receives the pull rope (14) Cable groove (72) is formed. 16. Cable window regulator according to one of claims 2 to 15, characterized in that that the pulley (36) and / or the bearing part (34) made of plastic, preferably Injection plastic, are formed.