EP2126262B1 - Gear mechanism part for cable-controlled window lifter and drive unit for a cable window lifter - Google Patents

Abstract

The invention relates to a gear mechanism part (1, 2) for a cable-controlled window lifter, comprising a gear wheel (1) and a cable drum (2) that can be driven by the gear wheel (1). The gear wheel (1) and cable drum (2) are disposed on a common axis (52). The gear wheel (1) and the cable drum (2) are coupled by positive fit to outside gearing (5) disposed on an outside circumference projection (15). In the cable drum (2), a fitting chamber (40, 43) for cable end fastening is provided. The fitting chamber (40, 43) is disposed inside the outer circumference projection (15) on a cross-sectional plane projected perpendicular to the axis (52). In this way, a more compact design of the cable drum (2) and transmission of higher driving torque are achieved.

Description

The invention relates to a transmission part for a cable window lifter according to the preamble of claim 1 and to a drive unit for a cable window lifter. Such a transmission part is eg from the EP 1 514 989 A1 known.

A cable window lifter is used to raise and lower a window of a motor vehicle. Such a cable window lifter is for example from the EP 1 617 028 A1 known. The rope window lifter described therein has two guide rails, along which a respective driver is movably mounted. At the two drivers, the window pane is attached. In addition, a drivable by means of a drive unit cable is hinged to the drivers. The cable of the cable is partially wound on a drivable by the drive unit and provided with a cable drum rope drum. By means of the drive unit, either both drivers and thus the window pane are moved upwards or, with a reversal of the drive direction, both drivers and thus the window pane are moved downwards. There are also cable window lifter with only one guide rail and a driver known.

It is known to drive the cable drum by means of a driven by the drive unit gear. Here, gear and cable drum are arranged on a common axis. The gear wheel and the cable drum are coupled to one another by positive engagement of an outer toothing arranged on an inner circumferential projection with an inner toothing arranged on an outer circumferential projection. At least one nipple chamber is introduced into a rope end attachment in the cable drum. For this purpose, the end of the rope on a nipple, which is inserted during assembly in the nipple chamber. By means of the division of the gear part in the gear wheel and the cable drum, the installation of the wound on the cable drum cable is simplified. The cable drum with the cable attachment can be removed for mounting the gear wheel. The cable window lifter can be pre-assembled so far with drive unit, guide rail, pulley and driver. During final assembly, only the rope must be attached to the driver and the cable drum and the cable drum can be coupled to the gear wheel. In this way, a simple, trouble-free and quick replacement of a defective drive unit is also possible.

The separation of gear wheel and cable drum also makes it possible to use for the gear wheel and the cable drum different and optimized for the application materials. Thus, the gear can be made in particular of a tough, wear and lubricant resistant plastic, which has a long service life under mechanical stress. The cable drum is in particular made of a plastic with good static friction properties, so that the leadership of the rope is carried out with a high coefficient of friction and twisting or even jumping out of the rope from its rope is practically impossible.

The invention has for its object to provide an alternative transmission part for a cable window lifter with a gear and a gear driven by the gear drum. Furthermore, the invention has for its object to provide an alternative drive unit for a cable window lifter.

The first object is achieved by the characterizing part of claim 1.

In a first step, the invention is based on the consideration that the necessary nipple chamber influences the size of both components of the transmission part, in particular the cable drum. For easy accessibility, the nipple chamber was arranged in previously known transmission parts of the aforementioned in the radial direction outside of the tooth coupling. In order to obtain sufficient space for the introduction of the nipple chamber, the scope of the tooth coupling is reduced accordingly for a given circumference of the cable drum.

In a second step, the invention starts from the knowledge that with a small diameter of the toothing a lower drive torque can be transmitted than with a larger diameter.

Finally, in a third step, the invention recognizes that an enlargement of the toothing diameter can be achieved by arranging the nipple chamber in the radial direction outside the toothed coupling, in other words projecting onto a cross-sectional plane perpendicular to the axis, within the outer circumferential projection. Since the toothing carrying circumferential projections may not necessarily be configured circumferentially but also at least partially openwork, thereby the accessibility to the nipple chamber is not necessarily deteriorated.

This results in a total of a geometry of the transmission part, wherein the toothing of the gear is realized with the cable drum with an enlarged diameter to the previous design. Since the nipple chamber is introduced in a design-related anyway necessary space and thus no additional volume of the components is necessary for the introduction of the nipple chamber, the invention also opens up the possibility of making the overall volume of the gear unit also more compact. Compared to the previous embodiment of the coupling between gear and cable drum, the transmission of a higher torque is possible. The transmitted from the gear on the cable drum force is distributed over a larger circumference and a larger number of teeth. This reduces the mechanical load per tooth. The risk of failure of the coupling site due to breakage or deformation of one or more teeth is reduced. On the other hand, the lower load per tooth also allows the choice of simpler and thus cheaper materials.

Incidentally, it is irrelevant to the invention whether the outer peripheral projection is associated with the gear wheel and the inner circumferential projection of the cable drum or the inner peripheral projection with the gear wheel and the outer peripheral projection of the cable drum. The gearing itself can have a few to many teeth each. The circumferential projections can each be designed to be circumferential or single or multiple perforated. The circumferential projections are also not necessarily designed annular. Likewise, other wall forms for supporting the teeth are possible.

The outer peripheral projection additionally engages the corresponding component in an annular channel. The outer wall of the annular channel stabilizes the coupling point mechanically in addition. Thus, the risk of tilting the cable drum during operation of the cable window lifter is avoided. Furthermore, the annular channel is an insertion or assembly aid in coupling the gear wheel with the cable drum.

In a development, the teeth of the external toothing and / or of the internal toothing each have a substantially cuboidal structure. Such a geometry is made possible due to the increased circumference and allows a simplified coupling of the cable drum to the gear wheel, as compared to a tapered tooth geometry, a radial offset of the components is tolerated in the joining within certain limits. The risk of breakage of a cuboid tooth due to the tangential introduction of force is absorbed by its thickness. Also by the consequent reduction of the number of teeth, the assembly of cable drum and gear is simplified. Also, the production is simplified and therefore less expensive. In the usual embodiment of the gear wheel and / or the cable drum as a plastic injection molded part, for example, a cuboid tooth geometry is easier to introduce into a mold than a tooth geometry with pointed teeth. Furthermore, more material is arranged at the end surfaces of the cuboid teeth than pointed teeth. This ensures that an injection mold is better filled with the injected plastic, as is the case with tapered teeth. Thus, the gear wheel or rope drum can be mass-produced in a mass production at a lower reject rate. Next allows a rectangular toothing

In an advantageous development, the teeth of the external toothing and / or the internal toothing in the joining direction of the components are each chamfered, ie provided with a chamfer. The chamfer of the teeth may be provided on the external toothing and / or on the internal toothing. By chamfering the meshing of gear and cable drum to a positive coupling is easier to carry out. The chamfering of the teeth thus serves as an insertion or assembly aid. Conveniently, the outer peripheral projection of the internal toothing on the cable drum and the inner peripheral projection with the external toothing on the gear wheel is arranged. As a result, the space, which is greater in relation to the internal toothing projection, within the external toothing projection is available for receiving the nipple chamber. Thus gear and cable drum are executable in a particularly compact geometry.

In a further preferred variant, the drum circumference of the cable drum is smaller than the outer peripheral projection. In other words, the drum part of the cable drum is offset radially inwards relative to the outer peripheral projection. The transition between the outer peripheral projection and the cable drum is thus formed step-like. This step-like training serves, for example, as a guide for the wound on the cable drum rope of the cable. The risk of jumping out of the rope from the rope groove is thus low. Furthermore, this makes it possible to realize a particularly good lever arm for the cable, so that the cable window lifter can be operated with a drive motor of low power.

In an expedient development, the nipple chamber is aligned tangentially to the axis introduced into the cable drum. In other words, the nipple chamber is oriented such that the nipple of the rope with its longitudinal direction in the inserted state is tangent to the axis. Thus, a particularly simple insertion of the rope end with the nipple in the nipple chamber in the pulling direction can be achieved. After insertion into the nipple chamber, the nipple is pulled by the tensile force of the rope against a stop surface and thus securely held. The stop surface is aligned so that the tensile force acts perpendicular to this. Due to the tangential orientation of the nipple chamber, kinking of the cable or bending of the nipple relative to the cable direction is reliably avoided.

In an advantageous development, a cable groove connecting the drum circumference to the nipple chamber is introduced into the cable drum. In this way, a defined lead out of the rope from the nipple chamber is achieved. In particular, by a tangential lead out of the rope from the nipple chamber with a continuous curvature in the circumferential direction of the drum is a kinking of the rope at its end safe avoided. The rope is rather gently led out of the nipple chamber and nestles gently on its emergence from the rope groove to the cable drum.

Advantageously, two mutually offset in the axial direction nipple chambers are introduced with opposite orientation in the cable drum, which are both arranged on a cross-sectional plane perpendicular to the axis projected within the outer peripheral projection. In this way, in a cable window lifter with two drivers, the cables associated with the two drivers can both be connected to the cable drum in such a way that an equilibrium of forces results. Due to the opposing orientation of the nipple chambers, it is achieved that, during a rotation of the cable drum, one rope is unwound and the other rope is wound up and vice versa.

Advantageously, both nipple chambers are arranged one above the other in the axial direction of the cable drum and formed from a continuous channel. This allows a simple production of the cable drum, since the nipple chambers can be easily impressed in this way the component, in particular during production as a plastic injection molded part.

For coupling the gear with a drive a variety of configurations are possible. Thus, the coupling via a corresponding gear with parallel, intersecting or crossing transmission axes take place, which is a translation of the drive speed. Depending on the design of the transmission, this also allows a choice of the position of the drive motor and thus the position of the drive axle. The transmission can be designed both self-locking and not self-locking.

In an advantageous embodiment, the gear wheel is designed as a worm wheel meshing with a worm shaft. The worm shaft is in this case in particular attached to a shaft of a drive motor, so that the shaft of the drive motor is arranged perpendicular to the axis of the gear. This makes it possible to arrange the drive motor in a plane with the gear. In this way, a space-saving installation of a drive motor and the worm shaft comprehensive drive unit in the side panel of a motor vehicle is possible. In addition, can a realized by means of a worm shaft and a worm gear worm gear easily self-locking, so that the window pane is securely supported with its own weight in a de-energized state of the drive motor and held by the worm gear.

In an expedient variant, a wrap spring is arranged on the axis, the ends of which are in a releasing and with the cable drum in a releasing operative connection with the gear. An installation of a wrap spring is made possible by the enlarged circumference of the toothing. To the axis, both the gear wheel and the cable drum can be introduced into an approximately cylindrical recess into which the wrap spring is arranged arranged around the axis. The wrap spring is designed for example as a helical spring, the ends of which are bent radially outwards. The ends are in terms of power acted upon both by the gear, as well as by the cable drum. This application is realized, for example, by means of half-shells acting in opposite directions against the ends, which are arranged on the cable drum or on the gear wheel. Also, every other coupling element is conceivable. The arrangement is designed so that leads by a rotation of the gear in clockwise or counterclockwise to the solution of the wrap spring and a rotation of the cable drum to a blocking of the wrap. Accordingly, in the case of a helical spring, the gear wheel acts against the cable drum and in the winding direction. The drive-side torque is thus introduced without obstruction in the cable drum. However, if a torque is introduced via the cable drum, in particular due to the weight of the window, the wrap spring is pulled together about the axis. A force acting on the cable of the cable window lifter is not transmitted to the drive side.

By means of the wrap spring, a so-called wrap spring brake is realized, the use of which is particularly suitable when a non-self-locking gear is designed to drive the gear. The window is held securely in any position, even if the drive rotor is not energized. In this way, a saving of energy is possible. The wrap spring brake can of course also be used in a self-locking gear, for example, as an additional mechanical protection.

In an expedient development, the axis is metallized in the region of the wrap spring or made of metal. In this way, a favorable friction pairing between the axle and the wrap spring can be provided.

The second object is achieved by a drive unit for a cable window lifter with a drive motor, with a control unit and with a transmission part. The drive motor, the control unit and the transmission part are mounted here on a common housing.

Such a drive unit can be used both for a completely pre-assembled as well as for a locally configurable cable window lifters. The drive unit in this case forms an assembly unit, which is particularly easy to install due to the two-part design of the transmission part with a gear and a cable drum. The cable drum can be coupled by positive engagement in a simple manner to the driven by the drive motor gear. An exchange of the drive unit can be carried out in a simple manner in case of a defect. The housing forms in particular bearing shells for supporting the rotatable parts, in particular of transmission parts or the cable drum.

The directed to the gear unit embodiments with their advantages are to be transmitted to the drive unit mutatis mutandis.

If the gear wheel is designed as a worm wheel meshing with a worm shaft, then the worm shaft expediently sits directly on the shaft of the drive motor. Worm shaft and worm wheel form a worm gear. The result is a compact and flat mounting unit, wherein the drive motor is arranged in the plane of the gear. Such a drive unit is thus mounted in a simple manner in a side panel of a motor vehicle with limited installation depth. Furthermore, a drive unit with a worm gear is usually self-locking. In this way, the window pane is kept in the de-energized state. The worm wheel is supported on the worm shaft from. An energization of the drive motor in the case of holding the window is not necessary.

In an advantageous development, the axis of the gear unit is part of the housing. In other words, the axle is molded or formed on the housing. The gear part with the gear and the cable drum is thus simply pushed onto the axle. By integrating the axle into the housing, an assembly step can be saved. The total costs of production and assembly are thus reduced.

Advantageously, the housing is made of plastic. Thus, the housing can be produced, for example, in a simple manner in an injection molding process.

Fig. 1

das Getrieberad und die Seiltrommel einer Getriebeeinheit in einer pers- pektivischen Ansicht,

Fig. 2

die Seiltrommel gem. Fig. 1 in einer Draufsicht,

Fig. 3

die Seiltrommel gem. Fig 1 in einer perspektivischen Ansicht,

Fig. 4

das Getrieberad gem. Fig. 1 in einer Draufsicht,

Fig. 5

eine Antriebseinheit mit der verbauten Getriebeeinheit gem. Fig. 1 in einer perspektivischen Ansicht,

Fig. 6

die Antriebseinheit aus Fig. 5 in einer Draufsicht,

Fig. 7

die Antriebseinheit in einer geschnittenen Seitenansicht,

Fig. 8

eine Schnittzeichnung einer weiteren Getriebeeinheit in einer Antriebsein- heit,

Fig. 9

ein Detail aus Fig. 5, sowie

Fig. 10

eine schematische Schnittzeichnung einer weiteren Antriebseinheit in Querrichtung.

Embodiments of the invention will be explained in more detail with reference to a drawing. Show:

Fig. 1

the gear wheel and the cable drum of a gear unit in a perspective view,

Fig. 2

the rope drum gem. Fig. 1 in a plan view,

Fig. 3

the rope drum gem. Fig. 1 in a perspective view,

Fig. 4

the gear gem. Fig. 1 in a plan view,

Fig. 5

a drive unit with the installed gear unit acc. Fig. 1 in a perspective view,

Fig. 6

the drive unit off Fig. 5 in a plan view,

Fig. 7

the drive unit in a sectional side view,

Fig. 8

a sectional drawing of another transmission unit in a drive unit,

Fig. 9

a detail from Fig. 5 , such as

Fig. 10

a schematic sectional view of another drive unit in the transverse direction.

In Fig. 1 are shown as parts of a gear unit, a gear 1 and a cable drum 2. Both the gear 1 and the cable drum 2 are made of plastic and in particular produced as plastic injection molded parts. The gear wheel 1 essentially has a cylinder symmetry with an axial direction 3. Inside, an annular inner peripheral projection 4 with an external toothing 5 arranged thereon can be seen. The gear wheel 1 further has centrally a centrally extending in the axial direction 3 over the entire length bore 7 for rotatably receiving an axle. On the outer teeth 5 is followed in the radial direction to the outside of an outer wall 8 limited annular channel 9. The outer wall 8 is provided at its upper end with a flat support surface 10.

The gear wheel 1 is further designed to be coupled to a worm shaft as a worm wheel. To this end, the gear wheel 1 is provided with a helical toothing running around the outer circumference of the outer wall 8 and extending over part of the height of the outer wall 8 Fig. 1 not shown.

The cable drum 2 also essentially shows a cylindrical symmetry. The cable drum 2 is in the axial direction 3 in their gem. Fig.1 bottom third formed a substantially annular outer peripheral projection 15, which is provided with an internal toothing 16. Next, a centric bore 17 is centrally inserted into the cable drum 2. On the outer peripheral projection 15 is followed in the axial direction 3, a drum part 18 with a drum circumference, which is smaller than the circumference of the outer peripheral projection 15. On the lateral surface of the drum part 18 winds in the manner of a helix a cable groove 19 for guiding a wound rope in several turns from. Furthermore, in the outer peripheral projection 15, an opening 20 for performing a cable end of in Fig. 1 Not shown rope inserted into the interior of the outer peripheral projection 15. The internal toothing 16 of the outer peripheral projection 15 corresponds in a form-fitting manner to the external toothing 5 of the inner circumferential projection 4 of the gear wheel 1.

The external toothing 5 of the inner circumferential projection 4 of the gear wheel 1 has teeth 25 with a substantially cuboidal structure. At its upper end in the axial direction 3, the teeth 25 have a chamfer 26 for simplifying the joining with the cable drum 2. The teeth 27 of the internal teeth 16 have a substantially cuboid structure. At its lower end in the axial direction 3 is every 27 a bevel 28 introduced. Due to the cuboidal geometry of the teeth 25,27 a relatively large thickness is both a secure mechanical coupling and easy joining of the components 1 and 2 into each other possible. This is additionally supported by the bevels 26 and 28. The production of the components 1 and 2 is comparatively simple due to the cuboid shape of the teeth 25 and 27.

For a positive coupling of gear 1 and cable drum 2, the cable drum 2 is placed in the joining direction 32 on the gear so that the holes 7,17 are aligned with each other in the axial direction 3. In this case, the outer peripheral projection 15 engages with the teeth 27 of the internal teeth 16 in the teeth 25 of the external toothing 5 of the inner wall 4. In addition, while the outer peripheral projection 15 is inserted into the annular channel 9 of the gear 1. The bevels 26,28 of the teeth 25,27 serve as an insertion aid and facilitate placement. Furthermore, the placement is facilitated by a circumferentially introduced on the outside of the outer wall 15 chamfer 33, which simplifies the insertion into the annular channel 9. After placing the cable drum 2 on the gear wheel 1, the cable drum 2 is additionally supported by the outer wall 8 of the annular channel 9.

Fig. 2 shows the cable drum 2 gem. Fig. 1 seen in a plan view from the side of its outer peripheral projection 15 ago. The cable drum 2 has a nipple chamber 40 in its interior. In the illustrated plan view, it can be seen that the nipple chamber is projected in a cross-sectional plane perpendicular to the central bore 17 within the outer circumferential projection 15. In this nipple chamber 40 is in the Fig. 2 not shown, provided with a nipple end of a rope inserted. The nipple chamber 40 is introduced tangentially to the central longitudinal axis in the cable drum 2. Via a cable groove 41, the nipple chamber 40 is connected to the circumference of the drum part 18. The inserted rope is guided by means of the opening 20 to the outside and at least partially on the circumferential circumference of the drum circumference cable groove 19 gem. Fig. 1 wound. Since the cable is exposed to a tensile load, the nipple is pulled with its side facing the rope to a radially oriented nipple stop 42 and so securely held in the nipple chamber 40. The rope groove 41 is continuously curved, so that the inserted rope smoothly from the tangential direction inside the cable drum 2 is bent to the circumferential direction of the drum part 18. Thus, a kinking of the rope is certainly prevented.

Fig. 3 shows the axial direction 3 the outer peripheral projection 15 opposite end of the cable drum 2. Here, the cable drum 2, a further nipple chamber 43 in the nipple chamber 40 opposite orientation. It can be seen that the nipple chamber 43 is also projected within the outer circumferential projection 15 in a cross-sectional plane perpendicular to the central bore 17. In this nipple chamber 43 is in the Fig. 3 not shown, provided with a nipple end of another rope inserted. The nipple chamber 43 is also introduced tangentially to the cylinder symmetry in the cable drum 2. About a cable groove 41 and an opening 44 in the drum circumference 18, the rope is in turn outwardly feasible and partially wound on the circumferential circumference of the drum circumference cable groove 19. Both nipple chamber 40,43 are arranged one above the other in the axial direction 3 and formed in a continuous channel. In this way, a simple production is possible. Also, material can be saved.

By the opposite orientation of the nipple chambers 40,43 a rope is wound on a rotation of the cable drum 2, while the other rope is unwound and vice versa. The direction of rotation sets so in the case of a rotating rope, the ends of which are inserted into the nipple chambers 40,43, the direction of the rope as a whole and thus the adjustment of a connected to the rope window pane.

Fig. 4 shows for clarity again the gear 1 gem. Fig. 1 in a top view. It can be clearly seen the inner peripheral projection 4 with the external toothing arranged thereon 5. Also, the annular channel 9 is clearly visible.

From the Fig. 5 and Fig. 6 shows a drive unit 50 for a cable window lifter with a housing 51 made of plastic. The transmission part 1 and the cable drum 2 put together gear part is placed on an integrally formed on the housing 51 axis 52 and received by a cup-shaped gear receptacle 53. It can be seen the drum part 18 of the cable drum 2. The gear 2 is in the

Transmission mount 53 added. It can be seen only the support surface 10. Furthermore, the housing 51 receives a drive motor 54 for driving the gear 1 and a partially introduced control unit 55 for driving the drive motor 54. For mounting the cable window lifter whose rail guide is pre-assembled with the drivers and the rope on the inside of a motor vehicle door. Subsequently, the two nipples of the two cable ends are inserted into the nipple chambers 40,43 and the rope ends partially wound on the cable groove 19 of the drum circumference of the drum portion 18 of the cable drum 2 for mounting the rope on the cable window lifter. The cable drum 2 is placed on the axle 52 and positively connected via the corresponding toothing with the gear wheel 1. The housing 51 of the drive unit 50 can be screwed by means of three mounting holes 56 on the inside of the motor vehicle door.

Out Fig. 5 It will further be seen that the drive motor 54 is coupled to the gear wheel 1 via a worm gear. The drive motor 54 lies in a plane parallel to the gear 1. It can be seen the orientation of the drive shaft 57 of the drive motor 54, which is mounted in a shaft bearing 58 in the housing 51. On the drive shaft 57, a non-visible worm shaft is mounted, which meshes with the helical teeth of the gear 1.

The transmission side is held smoothly by means of a lubricant and sealed with a sealing ring 60 to the outside. The sealing ring 60 is adhesively bonded to the upper edge of the transmission receptacle 53 for this purpose. The configuration of the sealing ring 60 is in particular Fig. 7 to take the gem. Fig. 5 and 6 used sealing ring 60 in a cross section. For gluing, the upper edge of the gear housing 53 has an adhesive channel 61 with an inner wall 63 and an outer wall 64. The substantially cone-shaped sealing ring 60 is placed with a smaller diameter on the adhesive passage 61. Here, a circumferential groove 62 on the underside of the seal 60 surrounds the inner wall 63 of the adhesive channel 61. The outer wall 64 of the adhesive channel 61 has - as shown Fig. 5 and 6 visible - three in the radial direction outwardly extending pocket-like widenings 65, which from the axis 52 from an angular distance of about 120 ° to each other. By means of these widenings 65 is a simple supply of an adhesive 66 in the adhesive channel 61 possible. The adhesive 66 is distributed uniformly from the widenings 65 in the adhesive channel 61 and bonds the sealing ring 60 to the adhesive channel 61. Sealing of the gear wheel 1 now takes place by means of the two sealing lips 67 against the bearing surface 10. The outer wall 64 of the adhesive channel 61 also secures the sealing ring 60 in its position against impacts or shocks, which are unavoidable during assembly of the drive unit 50. Thus, it is reliably avoided that the sealing ring 60 changes its position, which would possibly lead to leaks.

In another, not shown in the figures variant 60 radially outwardly pointing nubs are formed on the outside of the sealing ring, which engage in the widening of the adhesive channel 61 and thus secure the sealing ring 60 against undesired rotation. This is important because the gear wheel 1 in the Fig. 1 shown formed bearing surface 10 rests on the sealing lip 67 and rubs in operation with its underside on the sealing lip 67 of the sealing ring 60. Thus, the sealing ring 60 is constantly subjected to shearing during the drive of the gear wheel 1.

The aspect described with regard to the use of a gluing channel 61 for gluing a sealing ring 60 is also inherently independent of the design of the gear part or of the other design of the drive unit.

Fig. 8 schematically shows in a sectional side view of an alternative embodiment of a drive unit 50 with a gear 1. The gear 1 is rotatably mounted on the central axis 51 and formed as a worm whose teeth mesh with a driven by the drive motor 54 screw shaft 72. The axis 52 has in the region of the gear wheel 1 on a metallic region, which is designed as a metallic sleeve 73. To this metallic sleeve 73 is formed as a spiral spring wrap 74 with several turns, so that the function of a wrap spring brake is made. Both the gear wheel 1 and the cable drum 2 have for this purpose in the interior a corresponding recess. For further embodiments, reference may be made to the previous figures.

The function of the wrap spring brake is the schematic Fig. 9 refer to. On the gear wheel 1 and on the cable drum 2, a half-shell 74 is integrally formed on the inner side facing the axis 52 for coupling to the wrap spring 74. In the sectional view transversely to the axial longitudinal direction of the axis 52, these two half-shells are shown as the only elements of the gear wheel 1 and the cable drum 2 for the sake of simplicity. The two loop spring ends 75 each engage in the gap-shaped intermediate space 76 between the two half shells. The gear wheel 1 is offset by means of the drive motor 54 in a rotational direction 77 clockwise or counterclockwise. The two radially bent loop spring ends 75 and thus the wrap spring 74 are acted upon by the formed on the gear wheel 1 half shell. This loading is in each case counter to the winding direction of the wrap spring designed as a spiral spring 74. The winding diameter of the wrap spring 74 is thereby increased, so that the axis 52 is released. The gear 1 and the form-fitting coupled cable drum 2 move freely on the axis 52. The drive torque of the drive motor 54 is transmitted to the cable drum 2.

If, however, an output-side attack of a force, in particular the weight of the window pane on the cable drum 2, the half-shell of the cable drum 2 with respect to the half shell of the gear wheel 1 is rotated clockwise or counterclockwise in the direction of rotation 78. Again, the two loop spring 75 are applied, but in this case in the winding direction of the wrap spring 72. The wrap spring 72 is pulled together in the manner of a rope and lies around the metallic sleeve 73. It comes to a frictional engagement between the inside of the wrap spring 72nd and the metallic sleeve 73. The metallic sleeve 73 ensures a defined frictional engagement. By contraction of the wrap spring 72 further rotation of the cable drum 2 and the coupled gear 2 is avoided. Both are supported against the drive axle 52. The drive side is thus protected against mechanical damage.

Fig. 10 shows in a schematic sectional view, the drive unit 50 in the transverse direction. The drive motor 54 drives the worm shaft 72 mounted thereon by means of a shaft 85. On the outside of the gear wheel 1 designed as a worm wheel a helical gear is arranged, which is in engagement with the worm shaft 72. With a movement of the worm shaft 72 about its longitudinal axis, the gear wheel 1 is rotated in a clockwise or counterclockwise direction. About the form-fitting connected to the gear 1 cable drum 2, this is set in a rotary motion. As a result, one of the two cables acting on the cable drum 2 is wound up and the other cable is unwound. The two drivers are moved along their guides for raising or lowering the window.

Since the shaft 85 is mechanically loaded from the output side, the shaft 85 is supported by means of two bearings 86. Furthermore, a connected to the control unit 55 Hall sensor 87 is provided for speed measurement. The speed measurement serves to control the drive motor 54 either to adjust the drive power and / or as anti-jamming. The gear and the worm shaft 85 are acted upon in the gear compartment with a lubricant for reducing the friction. The lubricant can pass through the shaft to electrical fittings such as the Hall sensor 87 or the control unit 55 and cause failures there. According to the prior art, a sealing washer has been provided in the shaft space 88 for sealing the electrical installations against the lubricant so far. However, this made of a plastic sealing disc, however, has no complete sealing effect.

According to an inventive inventive and not dependent on the invention described here approach is provided instead of the sealing washer a flexible sealing element 89 for sealing the electrical fittings against the lubricant.

The sealing element 89 has essentially the cross section of the shaft space 88. In addition, it has a cylindrical bore 90 for receiving the shaft 85. For assembly, the sealing element 89 is pushed onto the shaft, for example, prior to assembly of the worm shaft 72. However, it can also be slotted in the longitudinal direction 91 to be subsequently applied to the shaft 85. The flexible sealing element 89 has a slightly larger cross-section than the shaft space 88. As a result, it is held in position. Since the bore 90 is dimensioned so that the sealing element 89 rests against the shaft 85, a complete seal is achieved. Since the inner dimension of the bore 90 is only slightly smaller than the outer dimension of the shaft 85, a virtually unimpeded rotational movement of the shaft 85 is still possible. The sealing element is for example made of a rubber foam, a sponge rubber or other elastic sealing material. In particular, a slightly porous sealing material can absorb a larger amount of the sealant.

LIST OF REFERENCE NUMBERS

1

Pinion

2

cable drum

3

axially

4

Internal circumferential projection

5

external teeth

7

drilling

8th

outer wall

9

annular channel

10

bearing surface

15

Outer peripheral edge

16

internal gearing

17

drilling

18

drum part

19

cable groove

20

breakthrough

25

tooth

26

chamfer

27

tooth

28

chamfer

32

joining direction

33

chamfer

40

nipple chamber

41

cable groove

42

nipple stop

43

nipple chamber

44

breakthrough

50

drive unit

51

casing

52

axis

53

gearbox mount

54

drive motor

55

control unit

57

drive shaft

58

Achslager

60

seal

61

adhesive channel

62

groove

63

inner wall

64

outer wall

65

widening

66

adhesive

67

sealing lip

72

worm shaft

73

metallic sleeve

74

wrap

76

gap

77

direction of rotation

78

direction of rotation

85

wave

86

camp

87

Hall sensor

88

wave room

89

sealing element

90

drilling

91

Wave longitudinal direction

Claims (15)

1. Gear mechanism part (1, 2) for a cable-controlled window lifter, comprising a gear wheel (1) and a cable drum (2) which can be driven by the gear wheel (1),

   - the gear wheel (1) and cable drum (2) being arranged on a common shaft (52),

   - the gear wheel (1) and the cable drum (2) being coupled by the positive fit between an external gearing (5) arranged on an inner circumferential projection (4) and an internal gearing (16) arranged on an outer circumferential projection (15),

   - a fitting chamber (40, 43) being introduced into the cable drum (2) for fastening the cable ends, characterised in that

   - the fitting chamber (40, 43) is arranged within the outer circumferential projection (15) and outside the gearing coupling of the external and internal gearings (5, 16) projected on a cross-sectional plane perpendicular to the shaft (52) in the radial direction, and

   - in that the outer circumferential projection (15) on the corresponding component additionally engages with an annular channel (9).
2. Gear mechanism part (1, 2) according to Claim 1, characterised in that the teeth (25, 27) of the external gearing (5) and/or of the internal gearing (16) in each case have a substantially rectangular structure.
3. Gear mechanism part (1, 2) according to Claim 1 or 2, characterised in that the teeth (25, 27) of the external gearing (5) and/or of the internal gearing (16) respectively are bevelled in the joining direction (32).
4. Gear mechanism part (1, 2) according to any one of Claims 1 to 3, characterised in that the outer circumferential projection (15) with the internal gearing (16) is arranged on the cable drum (2) and the inner circumferential projection (4) with the external gearing (5) is arranged on the gear wheel (1).
5. Gear mechanism part (1, 2) according to Claim 4, characterised in that the drum circumference (18) of the cable drum (2) is smaller than the outer circumferential projection (15).
6. Gear mechanism part (1, 2) according to any one of Claims 1 to 5, characterised in that the fitting chamber (40, 43) is introduced into the cable drum (2) tangentially in relation to the shaft (52).
7. Gear mechanism part (1, 2) according to any one of Claims 1 to 6, characterised in that a cable groove (41) connecting the drum circumference (18) to the fitting chamber (40, 43) is introduced into the cable drum (2).
8. Gear mechanism part (1, 2) according to any one of Claims 1 to 7, characterised in that two fitting chambers (40, 43), which are offset in relation to one another in the axial direction, are introduced into the cable drum (2) aligned in opposite directions, both fitting chambers (40, 43) being arranged within the outer circumferential projection (15) projected on a cross-sectional plane perpendicular to the shaft (52).
9. Gear mechanism part (1, 2) according to Claim 8, characterised in that both fitting chambers (40, 43) are arranged one above the other in the axial direction and are formed from a continuous channel.
10. Gear mechanism part (1, 2) according to any one of Claims 1 to 9, characterised in that the gear wheel (1) is designed as a worm wheel which meshes with a worm shaft (72).
11. Gear mechanism part (1, 2) according to any one of Claims 1 to 10, characterised in that a wrap spring (74), the ends (75) of which are operatively connected to the gear wheel (1) in a detaching manner and operatively connected to the cable drum (2) in a restraining manner, is arranged on the shaft (52).
12. Gear mechanism part (1, 2) according to Claim 11, characterised in that the shaft (52) is metallised or manufactured from metal in the region of the wrap spring (74).
13. Drive unit (50) for a cable-controlled window lifter, having a drive motor (54), a control unit (55) and a gear mechanism part (1, 2) according to any one of Claims 1 to 12, wherein the drive motor (54), the control unit (55) and the gear mechanism part (1, 2) are mounted on a common housing (51).
14. Drive unit (50) according to Claims 13 and 10, characterised in that the worm shaft (72) rests on the shaft (85) of the drive motor (54).
15. Drive unit (50) according to Claim 13 or 14, characterised in that the shaft (52) of the gear mechanism part (1, 2) is part of the housing.

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