DE3201098C2 - Cable window regulators, in particular for motor vehicles - Google Patents

Abstract

In the case of a cable window lifter for motor vehicles with a pull cable (14) which is guided over a deflection (32) and engages the window pane, it is proposed that a curved helical spring (38) which is under compressive prestress is installed between the deflection roller (36) and the bearing part (34). to be provided which pretensions the displaceably mounted deflection roller (36) in direction (C) and in this way enables automatic tensioning of the rope. In addition, the axis of rotation of the deflection roller (36) can be pivoted to adapt to changing inclinations of the pull rope (14). A retaining bolt (41) attached eccentrically to the bearing part (34) facilitates assembly.

Description

The invention relates to cable window regulators, in particular for motor vehicles, according to the preamble of Claim 1.

Such a cable window regulator is known from DE-OS 27 50 904. The pulley is here on one Intermediate carrier mounted rotatably, which in turn is attached eccentrically to a carrier so as to be pivotable and is pretensioned by means of a helical spring in the sense of tensioning the rope.

Furthermore, from DE-OS 28 02 563 a cable window regulator with a cable deflection is known in which the rope rests directly on a semicircular segment of an intermediate carrier. The intermediate carrier is in turn pivotably attached to a carrier and by means of a leg spring in the sense of tensioning the rope biased. The disadvantage is the increased traction cable friction compared to a deflection with a deflection pulley.

In a cable window regulator described in DE-GM 79 16 177, a preloaded compression spring is provided, which acts between the carrier and a Bowden cable sheath for the pull rope and in this way for it ensures that the pull rope is always under tension, regardless of manufacturing and assembly inaccuracies as well as regardless of dimensional changes occurring during operation, in particular Rope elongations. The pull rope must be under tension in order to reverse the direction without problems to ensure the window regulator and to prevent the openly guided Zugeil from his Guides jumps. The disadvantage of the known arrangement is that it requires the use of a Bowden cable sleeve presupposes. In addition to the increase in manufacturing and assembly costs due to this additional part Another disadvantage is that the pull rope is only accessible to a limited extent, which, for example, requires changing the rope difficult.

The object of the invention is to further simplify the deflection of a cable window regulator of the type mentioned at the beginning with a relatively large stroke and low deflection pulley friction.
The task is identified by the characteristic features

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Male of claim 1 solved in connection with the features of the preamble Advantageous embodiments of the cable window regulator according to the invention are the subject of the subclaims.

Because the coil spring not only has the preload function, but also by supporting the pulley takes on the intermediate girder function in the middle area, the intermediate carrier hinged to the actual carrier is omitted. If the tension in the rope is reduced urges the central part of the helical spring outwards, taking the pulley with it. This leads to the desired post-tensioning of the pull rope. Since the coil spring always has several of its coils the friction between the helical spring and the surrounding area is in contact with the inner circumferential surface of the deflection roller swivel castor comparatively small. Since a relatively long coil spring can be used, can also achieve a relatively large stroke.

To guide the coil spring on the bearing part and subsequently to guide the pulley over the Helical spring on the bearing part is proposed that the bearing part and / or the deflection roller with a guide groove for the coil spring are provided.

To simplify assembly, it is proposed that the two ends of the helical spring be matched Grooves of the bearing part are used.

When using pulleys, which are arranged in the area of the ends of a curved guide rail are, the problem arises that the inclination between the pulley and the driver extends Cable section changes relative to a plane perpendicular to a rigid pulley axis

This has the result that the flank surfaces of a cable guide groove of the deflection pulley are worn out in a short time. The wear of the pivot bearing of the deflecting pulley, which is now also loaded with tilting, also increases. In order to avoid these disadvantages, it is proposed that the deflecting roller about a to the axis of curvature of curved guide rail parallel pivot axis on the rigidly connected to the guide rail Carrier is stored. The inclination of the pulley axis therefore changes according to the inclination of the aforementioned Pull rope section, so that forces always act on the deflection pulley, which in a to the pivotable Deflection roller axis lie vertical plane. The two rope sections leading to the pulley are lying always on this level.

This pivot bearing is achieved with simple means in that the deflection roller with one of these Pivoting movements permitting game is mounted on the bearing part attached to the carrier.

In order to allow the deflection roller to migrate under an inclined tensile load with simple means to avoid, is attached to the bearing part in all shifting or pivoting positions of the Deflection roller proposed holding and guide tabs resting on a side surface of the deflection roller.

In order to minimize the friction between the bearing part and the deflection roller even when the deflection roller is pivoted to hold (when using the helical spring: in that the bearing part with a to the plane of the deflected Pull rope perpendicular to the contact surface of the pull rope on the deflection eccentric bearing pin rotationally fixed connected is the pivotable in a bolt opening of the carrier and in different rotational positions is fixable During assembly, the bearing part can therefore be pivoted towards the rope so far that this can easily be placed over the pulley. Then the bearing part is so far back pivoted until the desired preload is achieved and then fixed on the carrier. The setting the desired rotational position is simplified in that the bearing pin and the bolt opening with form-fitting interlocking serrations or serrations are provided, in the latter case by training with saw teeth that yield elastically in the radial direction, the possibility is given that the bearing pin is rotated in a single direction with intermeshing saw teeth can.

To fix the bearing part on the carrier in a desired rotational position, the bearing pin with the Carrier be riveted. In a further embodiment of the invention, the bearing pin is with the carrier star riveted. In this case, the serrations or saw teeth can be omitted, since the star riveting for a non-rotatable connection between the bearing pin and the carrier ensures that there is no axial displacement either required for turning adjustment.

A safe entrainment of the pull rope is guaranteed if the Umienkrolle with a receiving the pull rope wedge or trapezoidal rope groove is provided.

Simple, inexpensive production is guaranteed if, as suggested, the deflection roller and / or the bearing part is made of plastic, preferably injection-molded plastic.

The invention is explained below using an exemplary embodiment with reference to the drawing. It shows

F i g. 1 is a schematic front view of a cable window regulator;

F i g. 2 shows a partial view of the arrangement according to FIG. 1 in the direction of arrow II;

F i g. 3 ene front view of a rope deflection according to the invention as detail A of FIG. 1;

F i g. 4 shows a sectional view of the cable deflection according to FIG. 3 in section along the line IV-IV;

F i g. 5 is a sectional view according to FIG. 4, however, with the deflection pulley shifted upwards for tensioning the rope; and

F i g. 6 shows an individual front view of a bearing part of the deflection according to FIG. 3 to 5.

In the F i g. 1 and 2, a cable window regulator 10 for installation in a motor vehicle door is shown roughly schematically. This comprises a hand crank-driven or electric motor-driven drive unit 12, which drives a pull cable 14 guided along a closed loop via a cable drum (not shown). The pull rope 14 is used to move up and down (double arrow B in FIG. 1) a window pane, not shown, which is via a U-rail indicated in FIG. 2

γ Aar I ItniAnb-rr »!! *» with crr / \ Rtm / \ crli / * hpn Ifi an ihrpm iintprpn Onprrnnri with pinpm driver '

Hub), it is proposed to make the contact surfaces spherical. When using the aforementioned holding and guide tabs, the convex contact surfaces are provided in the area of the inner circumferential edge of the deflection roller remote from the holding and guide tabs.
In order to facilitate assembly, it is proposed that the window regulator 10 be connected in a non-positive manner. In Fig. 1, fastening holes 20 for fastening the U-rail 16 to the driver plate 19 of the driver 18 are indicated. A driver block 22, likewise only indicated schematically, which is fastened to the underside of the driver plate 19, receives a cable nipple 24 of the traction cable 14, so that the driver 18

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is taken from the pull rope 14.

The driver 18 is attached to a guide rail with an L-shaped cross-section via guide holes (not shown) 26 can be moved back and forth along this. At the two ends of the guide rail 26 are holding plates 28 attached, on the one hand the attachment of the guide rail 26 to a motor vehicle door panel serve (fastening holes 30) and, on the other hand, each have a carrier for each deflection 12 form for the pull rope 14. In the F i g. 3 to 6 is that in FIG. 1 upper rope deflection 3 shown in detail (in Scale approx. 2: 1).

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

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

The carrier section 40 in the form of a general prism, that is to say with mutually parallel side surfaces 42 and 44, is rounded on its downwardly directed side (surface 46) in such a way that in the position shown in FIG. 5 shown uppermost position of the guide roller 36, this with its inner circumference on the support portion 40 abuts the surface 46 is therefore a partial cylinder peripheral surface with a horizontal cylinder axis and an inner radius Rj corresponding to the deflection roller 36 is substantially cylindrical radius. Since the sector angle oc (see FIG. 6) which is located in a plane perpendicular to the cylinder axis and defines the partial cylinder is less than 180 ° at approx. 140 ° and thus the in FIGS. B. from left to right running width i / of the carrier section 40 is accordingly smaller than the inner diameter Rj of the deflection roller 36 and also the height of the carrier section 40 including that on it in the position according to FIG. 4 applied helical spring 38 is smaller than the inner diameter Rj, the deflection roller 36 can in the direction of arrow B by the distance a according to FIG. 3 are moved back and forth between the in F i g. 4 shown lower end position and the upper end position according to F i g. 5. The tab 43 serves as a holding and guide tab for the deflection roller 36, which prevents the deflection roller 36 from being lifted off and thus removed from the bearing part 34 in the direction away from the retaining plate 28, as shown in FIG. 5 shows, the area of the deflection roller 36 located at the top is arranged between the tab 43 and the holding plate 28 with little lateral play and is thus safely guided in all positions

The play a enables the rope 14 to be re-tensioned, with a change in the rope length of almost twice the play a being able to be compensated due to the approximately 180 ° deflection of the rope 14 around the deflection rings 36. In order to achieve automatic tensioning of the rope, the deflection pulley 36 is pretensioned with the help of the helical spring 38 in the direction of the arrow C. For this purpose, the helical spring 38 is attached to the support section 40 under axial compressive pretension, with both helical spring ends being supported on inclined surfaces 47 which are attached to the lower surface 46 and are inclined to one another, forming an angle β of approximately 170 °. A partial cylinder jacket surface 48 extends between these surfaces 47, against which all turns of the helical spring 38 rest in the lower end position of the deflecting roller 36 according to FIGS. 3 and 4. The helical spring axis 50 indicated by dotted lines is subsequently also approximately in the shape of a part of a circle (see FIG. 3). In this position, however, the helical spring can only remain if it is prevented from dodging with its middle part upwards, i.e. in direction C, which is achieved by the deflection roller 36, on the inner circumference of which the helical spring 38 in the area of its outer curvature with all Turns, provided that the pulley 36 is held by the correspondingly short pull rope 14 in its lower end position. However, as soon as the tension of the pull rope 14 decreases, for example due to rope elongation during operation, the central area of the helical spring 38 pushes upwards, taking the pulley 36 with it
To fasten the ends of the helical spring 38, receiving grooves 52 are provided on the carrier section 40 in the area of the inclined surfaces 47. In order to prevent the helical spring 38 from deflecting to the side, the inner circumference of the deflection roller 36 is designed with a correspondingly designed guide groove 54. In the lower end position (FIGS. 3 and 4), the helical spring 38 also rests against the inside of the tab 45.

The in F i g. The guide rail 26 shown in FIG. 2 is curved about a horizontal axis of curvature with a radius λ2. During the displacement of the driver 18 along the guide rail, the inclinations ö \ and 02 of the rope sections 55 and 57 leading from the driver 18 to the rope deflectors 32 change to a rope loop plane defined by the rope sections 59 and 61 between the deflectors 32 and the drive unit 12 . This change in angle when the power windows are operated can be around 10 ° to 15 °. If deflection pulleys with a rigid deflection roller axis are used in this case, there is increased wear on the deflection pulley and the pull rope due to the inclined approach of the rope on the guide pulley. In order to enable pivoting of the deflection roller axis 63 (see FIG. 4) as an alternative or in addition to the described tensioning of the rope, the deflection roller 36 on the bearing part 34 is by one in FIG. 3, e.g. B. pivot axis running from left to right. In the in Figs. 3 and 4, the lower end position of the guide roller 36 shown this lies with a contact surface 56 on a contact surface 58 at the free upper end of the

so flap 45, the inner peripheral edge 62 of the deflection roller 36 remote from the contact surface 56 touching the vertical inner surface 64 of the long flap 43. Since the deflection roller 36 decreases in width radially outward (with inwardly curved side surfaces 60) there is the possibility of the deflection roller 36 in the direction of the arrow D in its in FIG. 4 to pivot position indicated with dashed circumferential surface (with deflection roller axis 63 '). In this case, the mutually adapted, convex (contact surface 58 concave) contact surfaces 56 and 58 slide off one another; the in F i g. 4 left inner peripheral edge 62 slides on the inner surface 64 of the nose 43 upwards. The in F i g. 4 is again an end position, since the right outer peripheral edge 66 of the deflection roller 36 now rests against the holding plate 28 and prevents further pivoting of the deflection roller 36.

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the contact surfaces 56 and 58 away from each other. However, this does not affect the ability to pivot the deflection roller 36, which then rests on the outer curvature of the helical spring 38 and between the nose 43 and holding plate 28 is pivotably guided. Only in the in F i g. 5 shown upper end position lies down the contact surface 56 of the deflection roller 36 on a correspondingly curved contact surface 65 in the area of FIG F i g. 5 right edge of the lower partially cylindrical surface 46 of the bearing part 34. The pulley 36 is formed symmetrically to its axis-normal center plane, so that its spherical contact surface 56 opposite a further spherical contact surface 67 is arranged, which in the position according to FIG Shaped surface 69 of the carrier section 40 rests (see also FIG. 6). In the in F i g. 5 position shown the deflection roller 36 can therefore no longer be pivoted, but this is no longer problematic is because this position is practically never reached while the built-in window regulator is in use, but only represents a transport position of the preassembled window regulator.

So that the pivoting movement is not hindered by the fact that the in F i g. 4, the inner peripheral edge 62 on the left collides with the radially outwardly extending side edges 70 of the nose 43, the nose 43 is kept relatively narrow with one in FIG. 3 horizontally extending mean width b, which corresponds to approximately 0.4 times the inner diameter R \ of the deflecting roller 36. The deflection roller 36 is adequately secured against a tilting movement perpendicular to the tilting movement in the direction of arrow D , since at the beginning of the displacement movement from the lower end position according to FIG. 3 and 4, the helical spring 38 rests essentially over its entire length in the guide groove 54 formed between the curved surfaces 56 and 67 on the inner circumference of the deflecting roller 36 and, with increasing upward displacement, the number of adjacent turns decreases, but the tab 43 due to its increasing width ensures adequate guidance of the deflection roller 36. Here, the play between the deflecting roller 36, the holding plate 28 and the nose 43 is just large enough that the deflecting roller 36 does not jam between the holding plate 28 and the nose 43 in all of its shifting and pivoting positions.

Due to the pivoting possibility described, the deflection roller 36 follows the different inclination of the rope section 57 coming from the driver 16, so that the rope 14 is always at the groove bottom of a V-belt groove-like Cable groove 72 runs on the outer circumference of the deflection tube and does not rub against the groove flanks 74 in the process. The wear of the rope 14 and the rope groove 72 is therefore low and the run of the pulley 32 is also low therefore smooth.

The already mentioned bearing pin 41, which protrudes perpendicularly from the side surface 44 of the carrier section 40 on the side of the shorter lug 45, is arranged eccentrically with respect to a vertical central plane 79 parallel to the pin axis with an eccentricity forming distance c between the pin axis and the central plane. For assembly, the bearing part 34 can now be pivoted about this eccentric bolt 41, for example into the position shown in FIG. 3 with a dotted outline indicated by 34 'designated position, in which the nose 43 is horizontal. It can be seen 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 FIG. 3 and 4 lies. The pulley 36 provided with the pull rope in the intended length can therefore be pushed comfortably over the bearing part 34 into its intended position and then the bearing part 34 can be rotated into the final position with the nose pointing upwards or in the direction of arrow c; the direction C according to FIG. 1 lies approximately on the bisector between the cable sections 57 and 61.

Since it is not necessary to align the nose 43 exactly parallel to the direction C , a basic adjustment can already be made according to the respective rope length by a corresponding more or less strong deviation from this orientation. In order to facilitate this, the end of the bearing pin 41 on the carrier section side is provided with a circumferential serration 76, as in FIG. 6 indicated, formed. This engages positively in a corresponding inner circumferential serration of a receiving opening 78 of the holding plate 28. In order to adjust the rotation of the bearing part 34, it is thus corresponding to the width of the serration 76 in FIG. 4 and 5 shifted to the left, then twisted in the desired manner and finally pushed back to the right into mutual engagement of the serrations.

Instead of the serration, however, saw teeth can also be used in which the teeth are radially elastically resilient in such a way that with intermeshing saw teeth (i.e. without the must be moved axially) the bearing part 34 for tensioning the pull rope 14 in the counterclockwise direction F i g. 3 can be rotated, but a blockage occurs in the opposite direction.

In order to prevent unintentional adjustment of the bearing part 34 when the window lifter 10 is fully assembled, the bearing part 34 riveted to the driver plate 22 after adjustment, for example by means of a 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 shift distance a of the deflection roller 36 is 7.5 mm, about one-third of the inner diameter R \ of the deflection roller 36. It is also possible, the axis 63 of the guide pulley 36 by an angle γ (see Figure 4) of about 10 ° to 15 To pan. In addition or as an alternative to the possibility of displacement and swiveling, the fastening of the bearing part 34 via an eccentric bearing pin 41 (eccentricity c about 4 mm) achieves a simplified assembly, since the deflection roller 36 is shifted in the direction of the center point of the rope loop by corresponding pivoting of the bearing part 34 . The formation of the bearing pin 41 with serration 76 (or saw teeth) allows easy adjustment of the bearing part 34 depending on the respective rope length, the bearing part 34 being fixable in the respectively selected rotational position.

The deflection roller 36 and possibly also the bearing part 34 can be injection-molded from plastic, so that only low manufacturing costs are incurred.

For this purpose 2 sheets of drawings

Claims (13)

32 Ol 098 claims: 1. Cable window lifter, especially for motor vehicles, with at least one pulley (36) a deflector (32) mounted on a carrier (28), guided to a window pane, possibly via a driver (16) that is displaceable on a guide rail (26), engaging the pull rope (14), a bearing part which acts between the carrier and the deflection roller and is attached to the carrier (34) supporting spring (38) the roller that can be moved relative to the carrier in the sense of tensioning the rope prestressed, characterized in that one which is under axial compressive prestress Helical spring (38) is provided which is supported at both ends on the bearing part (34) and a curved, preferably approximately partially circular shape Has helical spring axis (SO), and that the ring-like deflection roller (36) with an inner circumferential surface (54) rests against the outer curvature of the helical spring (38) 2. Cable window regulator according to claim 1, characterized in that the bearing part and / or the pulley (36) is provided with a guide groove (54) for the helical spring (38) 3. Cable window regulator according to claim 1 or 2, characterized characterized in that the two ends of the helical spring (38) in adapted receiving grooves (52) of the bearing part (42) are used. 4. Cable window regulator, in particular according to one of claims 1 to 3, characterized in that the with a deflection roller (36) formed deflection (32) around an aclise of curvature of the curved Guide rail (26) parallel pivot axis pivotable on the one with the guide rail (26) rigidly connected carrier (retaining plate 28) is mounted. 5. Cable window regulator according to claim 4, characterized in that the deflection roller (36) with a this pivoting movement permitting play on one or the bearing part (34) attached to the carrier is stored. 6. Cable window lifter according to one of claims 1 to 5, characterized by a retaining and guide tab (43) attached to the bearing part (34) and resting on one side of the deflecting roller (36) in all shifting or pivoting positions of the deflecting roller (36) ), whose width / ^ extending in the circumferential direction of the adjacent deflecting roller (36) is preferably smaller than the inner diameter R \ of the deflecting roller and is therefore best about to V2 of the inner diameter R] . 7. Cable window lifter according to claim 5 or 6, characterized in that the bearing part (34) and pulley (36) rest against one another on matched, convex contact surfaces (56, 58). 8. Cable window lifter according to claim 7, characterized in that the contact surface (56) of the pulley (36) in the area of the inner circumferential edge further away from the shape-retaining and guide tabs (43) the deflection roller (36) is provided. 9. Cable window regulator according to one of claims 1 to 8, characterized in that the deflection or the bearing part (34) with a perpendicular to the plane of the deflected pull rope (14), to the contact surface of the pull rope (14) is rotatably connected to the deflection eccentric bearing pin (41), the pivotable in a bolt opening (78) of the carrier (retaining plate 28) and in different rotational positions is determinable 10. Cable window lifter according to claim 9, characterized in that the bearing pin (41) and the Bolt opening (78) formed with interlocking serrations or serrations (76) are. 11. Rope window regulator according to claim 9 or 10, characterized in that the bearing pin is riveted to the carrier, preferably star riveted, is 12. Cable window lifter according to one of claims 1 to 11, characterized in that the pulley (36) is formed with a wedge-shaped or trapezoidal rope groove (72) which receives the pull rope (14) 13. Cable window lifter according to one of claims 1 to 12, characterized in that the pulley (36) and / or the bearing part (34) are formed from plastic, preferably injection-molded plastic.