DE102023201748A1 - Gear assembly for a vehicle window regulator - Google Patents

Abstract

The invention relates to a gear assembly (16) for a vehicle window lifter (2), comprising a worm gear (24) which can be driven by means of a worm shaft (28) of an electric drive motor (6) of the vehicle window lifter (2), and an output pinion (26) arranged concentrically in the worm gear (24) for a cable drum (18) of the vehicle window lifter (2), wherein the output pinion (26) has a number of radially oriented output extensions (50), wherein the worm gear (24) has a number of receptacles (38) corresponding to the number of output extensions (50), wherein the output extensions (50) engage in the receptacles (38) in such a way that each output extension (50) is seated in the tangential direction (T) between two approximately radially oriented side walls (40) of the respective receptacle (38), and wherein the output extensions (50) are designed to be elastically deformable in the tangential direction (T).

Description

The invention relates to a gear assembly for a vehicle window lifter, comprising a worm gear which can be driven by means of a worm shaft of an electric drive motor of the vehicle window lifter, and an output pinion arranged concentrically and in a form-fitting manner in the worm gear for a cable drum of the vehicle window lifter. The invention further relates to a vehicle window lifter with such a gear assembly.

Today, movable vehicle windows are usually moved between a closed position and an open position by electrically or electromotor-operated actuating devices as (vehicle) window lifters. Such a window lifter usually comprises an (electric) actuating or drive motor and an actuating mechanism that connects the drive motor to the window pane, i.e. couples it in terms of force transmission, which are assigned to a vehicle door or a vehicle body.

Such a window lifter is, for example, from the DE 10 2012 208 564 A1 Known window lifters of this type have a cable mechanism for raising and lowering the window pane, which, for example, in a two-strand or two-sided cable window lifter is held by means of drivers (rail sliders) along two guide rails that run parallel to one another. Cable window lifters typically have a cable pull that is guided on the one hand in a cable drum that winds it up and unwinds it and on the other hand is guided and fixed to one of the rail sliders with multiple deflections.

A (window lifter) gearbox is usually provided for the drive-technical coupling of the drive motor and the cable drum. The drive motor typically drives a worm shaft, which is in meshing engagement with a worm wheel. The worm wheel in turn drives an output pinion coupled to the cable drum. Since vibrations and/or undesirable shock loads can occur when the drive motor starts up or when it hits a (window) end position, damping is usually provided between the worm shaft and the output pinion.

When the worm gear formed by the worm shaft and the worm wheel exerts a torque on the output pinion, the teeth of the worm gear are evenly loaded. At high motor torques, for example more than 14 Nm (Newton meters), the worm gear is usually heavily worn, which has a detrimental effect on the acoustics and the performance curve of the vehicle window lifter. Furthermore, at high torques, axial relative movements can occur between the worm wheel and the output pinion. Such movements are reduced, for example, by means of a metal C-ring as a gear lock, so that the movement of the gear is kept within a small range. In order to avoid the disadvantages mentioned above, conventional window lifters are often limited in terms of motor torque.

The invention is based on the object of specifying a particularly suitable gear assembly for a vehicle window lifter. In particular, a particularly suitable damping between the gear components is to be realized, which enables the gear components to have the longest possible service life even at high torques. The invention is also based on the object of specifying a particularly suitable vehicle window lifter.

With regard to the gear assembly, the object is achieved according to the invention with the features of claim 1 and with regard to the vehicle window lifter with the features of claim 10. Advantageous embodiments and further developments are the subject of the subclaims. The advantages and embodiments mentioned with regard to the gear assembly can also be transferred to the vehicle window lifter and vice versa.

The gear assembly or gear arrangement according to the invention is intended in particular for a vehicle window lifter and is suitable and configured therefor. The gear assembly has two separate gear components.

The first gear component is designed in particular as a worm gear and is also referred to as such below. The worm gear can be driven or is driven, for example, by means of a helical worm shaft of an electric drive motor of the vehicle window lifter. The worm gear and the worm shaft form in particular a worm gear. The worm gear has a rotating gear ring with a central (gear ring/gear wheel) hub. The worm gear is designed, for example, as a one-piece, i.e. one-piece or monolithic, injection-molded part. The worm gear is made, for example, from polyoxymethylene (POM).

The second transmission component is preferably designed as an output pinion, and is subsequently also referred to as such. When used in a vehicle window lifter, the output pinion is coupled or can be coupled to a cable drum in terms of drive technology. The output pinion is designed, for example, as a one-piece, i.e. one-piece or monolithic, injection-molded part. The output pinion is made from POM, for example. The gear components or the worm gear and the output pinion are preferably made from the same plastic material, in particular POM.

The output pinion is arranged concentrically in the worm gear. This means that the output pinion is arranged within the circumference of the ring gear of the worm gear. The axes of rotation of the worm gear and the output pinion are preferably coaxial. The worm gear and the output pinion are essentially coupled in parallel.

Here and in the following, “axial” or an “axial direction” is understood to mean in particular a direction parallel (coaxial) to the axis of rotation of the first gear part, i.e. perpendicular to the front sides of the first gear part. Accordingly, here and in the following, “radial” or a “radial direction” is understood to mean in particular a direction oriented perpendicular (transverse) to the axis of rotation of the first gear part along a radius of the first gear part. Here and in the following, “tangential” or a “tangential direction” is understood to mean in particular a direction along the circumference of the first gear part (circumferential direction, azimuthal direction), i.e. a direction perpendicular to the axial direction and the radial direction.

According to the invention, the second gear component or the output pinion has a number of radially oriented output extensions. The output pinion therefore has at least two output extensions, preferably at least six output extensions, for example nine output extensions. The output pinion here has, for example, a toothed pinion, with the output extensions being formed in a star shape on one end face, axially spaced from the toothed ring of the pinion, projecting radially outwards. The output extensions are preferably formed integrally, i.e. one-piece or monolithic, onto the output pinion or the toothed pinion.

The first gear component or the worm gear has a corresponding number of receptacles. The receptacles are, for example, introduced into the hub body of the worm gear as pocket-like or chamber-like depressions or recesses. This creates a gear assembly with a particularly compact installation space.

The output extensions engage in the receptacles in such a way that each output extension is located in the tangential direction between two approximately radially oriented side walls of the respective receptacle. The phrase "approximately" is to be understood in this context in particular as a certain inclination or slant with respect to the radial direction. The side walls can therefore be arranged radially, or parallel to the radial direction, or deviate from the radial direction by an angle of inclination. The angle of inclination is in particular an acute angle between 0° and ± 45°, for example between 0° and ± 30°, in particular between 0° and ± 15°.

Each receptacle has two approximately radial side walls and an outer wall on the circumference or oriented towards the ring gear of the worm gear. The respective output extension is tangentially enclosed in a form-fitting manner by the side walls, with the outer wall providing a radial form-fitting arrangement. The output pinion thus engages in the worm gear in a form-fitting manner. When the worm gear rotates, the output extensions are supported on the side walls so that the output extensions are carried along by the receptacles of the worm gear, thus transferring the torque of the worm gear to the output pinion. The output extensions are designed to be flexible, particularly spring-elastic, and deformable in the tangential direction.

When a torque is applied via the worm gear, the output extensions experience at least a certain (elastic) deformation, which ensures that the gear assembly is dampened during load changes. This advantageously reduces or prevents reverse noise. Furthermore, the flexible output extensions of the output pinion improve the load-bearing capacity of the gear assembly and the associated window lifter components (e.g. the drive motor) at high torques. In particular, the service life of the worm gear, i.e. the worm gear and the worm shaft, is improved.

A “high torque” here and in the following is understood to mean in particular a torque greater than 14 Nm, for example greater than 50 Nm.

A “positive connection” or a “positive connection” between at least two interconnected parts is understood here and below in particular to mean that the cohesion of the interconnected parts is achieved at least in one direction by a direct interlocking of contours of the parts themselves or by an indirect interlocking via an additional connecting part is used. The “blocking” of a mutual movement in this direction is therefore due to the shape.

In an advantageous embodiment, the output extensions each have a ring contour as a bendable or spring-elastic deformable area. The ring contour creates a particularly advantageous geometry for the output extensions. In particular, in a one-piece design of the output pinion, it is possible to use a mechanically stable plastic for the output pinion, so that reliable power transmission is possible using the pinion. The bending flexibility of the output extensions is essentially realized by the ring contour.

In a practical further development, the ring contour is radially opened to form two flexible ring legs. In other words, the output extensions are designed as an open ring contour with an annular gap separating the ring legs. The ring legs rest in a substantially unbent (relaxed) state in a vertex area on the associated side wall. The ring legs are therefore supported on the side walls on the vertex side. The vertex area is arranged essentially centrally between a radially inner fixed end and a radially outer free end of the respective ring leg facing the annular gap. The annular gap or the open contour/structure advantageously and easily prevents damage (cracking or similar) to the output extensions due to excessive deformation.

In a suitable design, the ring legs each have a radially inward-facing contact surface on the free end, with the ring legs facing each other coming into contact with the contact surface facing each other in a bent (tensioned) state. This means that the ring legs rest against each other or support each other when deformed sufficiently, i.e. when torques are sufficiently high. This ensures that such torques can be transferred to the output pinion reliably and safely. The open ring contour and the contact surfaces make it possible to achieve a spring constant profile for the output extensions that is particularly advantageous in terms of torque transmission and can be easily and flexibly dimensioned for a particular application.

In one conceivable embodiment, the side walls of a receptacle are oriented at an angle to one another in the tangential direction. The side walls are therefore arranged at an angle to the radial direction, so that the tangential diameter of the receptacles tapers from the radial inside to the radial outside. As a result, the output extensions, in particular the ring legs, are held clamped in the receptacle by means of a certain preload.

An additional or further aspect of the invention provides that the worm gear and the output pinion are joined together in an axially positive manner by means of a joint connection. The joint connection blocks or impedes relative movement of the gear components along the axial direction. This means that a metallic C-ring for axially securing the gear components can be omitted. Furthermore, the noise generated by the gear assembly is reduced. In particular, the vibration frequency of the gear assembly is reduced.

The joint connection is, for example, a positive and/or non-positive joint connection, which can preferably be produced without tools. For example, the joint connection is designed for simple plug-in assembly of the transmission components.

The conjunction “and/or” is to be understood here and in the following in such a way that the features linked by means of this conjunction can be formed both together and as alternatives to one another.

A "frictional connection" or a "force-locking connection" between at least two interconnected parts is understood here and below to mean in particular that the interconnected parts are prevented from sliding off one another due to a frictional force acting between them. If there is no "connecting force" causing this frictional force (this means the force that presses the parts against one another, for example a screw force or the weight itself), the force-locking connection cannot be maintained and can therefore be broken.

In a practical embodiment, the joint is designed as a snap-in or clip connection. This enables particularly simple assembly of the gear assembly with fewer components.

In a preferred development, a flexible tab is formed on the output pinion between two adjacent output extensions, which tab is axially positively locked or can be locked or clipped to a radial projection (locking lug) of the worm gear. This enables a particularly A practical design of the joint is realized, which ensures a stable and reliable axial hold between the transmission components.

In one possible design, the side walls of adjacent receptacles are oriented in a roughly V-shape relative to one another, with the projection being molded onto the V-base. The side walls thus act as reinforcing struts for the projection, enabling a particularly stable locking connection.

The vehicle window lifter according to the invention is intended for a motor vehicle and is suitable and designed for this purpose. The vehicle window lifter is designed in particular as a cable window lifter with a cable actuator comprising an electric drive motor, a worm shaft, a cable drum and a gear assembly as described above. This creates a particularly suitable vehicle window lifter.

• 1 in schematischer Darstellung einen Fahrzeugfensterheber mit einer Getriebebaugruppe,
• 2 in perspektivischer Darstellung die Getriebebaugruppe mit einem Schneckenrad und mit einem Abtriebsritzel,
• 3 in perspektivischer Darstellung ausschnittsweise das Schneckenrad,
• 4 in perspektivischer Darstellung ausschnittsweise das Abtriebsritzel,
• 5 in Draufsicht die Getriebebaugruppe,
• 6 eine Schnittdarstellung der Getriebebaugruppe entlang der Schnittlinie VI-VI gemäß 5,
• 7 eine Schnittdarstellung der Getriebebaugruppe entlang der Schnittlinie VII-VII gemäß 5, und
• 8 in vergrößerter Darstellung den Ausschnitt A gemäß 6.

The invention is explained in more detail below with reference to a drawing. In it:

• 1 in schematic representation a vehicle window lifter with a gear assembly,
• 2 in perspective view the gear assembly with a worm gear and an output pinion,
• 3 in perspective view, part of the worm wheel,
• 4 in perspective view, part of the output pinion,
• 5 top view of the gearbox assembly,
• 6 a sectional view of the gearbox assembly along the section line VI-VI according to 5 ,
• 7 a sectional view of the gearbox assembly along the section line VII-VII according to 5 , and
• 8 in enlarged view the section A according to 6 .

Corresponding parts and sizes are always provided with the same reference symbols in all figures.

In the 1 In a simplified and schematic representation, an electric (vehicle) window lifter 2 is shown as an adjusting device for a (vehicle) window pane 4 of a vehicle door of a motor vehicle (not shown in detail).

The window lifter 2 has an electric drive motor (servomotor, window lifter motor) 6, which acts on the window pane 4 by means of an adjusting mechanism 8. The adjusting mechanism 8 has a guide rail 10 and a driver or rail slider 12 coupled to the window pane 4.

In the embodiment shown, the window lifter 2 is designed as a simply guided cable window lifter. The adjusting mechanism 8 has a cable pull 14 in addition to the guide rail 10.

The drive motor 6 of the window lifter 2 drives a cable drum 18 of the actuating mechanism 8 via a gear assembly 16. A traction cable of the cable pull 14 is arranged on the cable drum 18 in such a way that the traction cable is wound up and unwound when the cable drum 18 rotates as a result of the gear assembly 16.

An upper cable pulley or cable pulley 20 and a lower cable pulley 22 are attached to the guide rail 12 and are arranged on the opposite (rail) end faces. The traction cable of the cable pull 14 is guided around the cable pulleys 20, 22.

When the actuator 6 is actuated, the window pane 4 is moved to its (pane) position P. The window pane 4 can be moved reversibly between a closed position S, which represents the highest possible position P (upper end position), and an open position O, which represents the lowest possible position P (lower end position). In these positions S and O, the window pane 4 is in the 1 are indicated by dashed lines. The window pane 4 is shown in a half-open intermediate position with solid lines.

The following based on the 2 to 8 The gear assembly 16 explained in more detail has two coupled gear components (gear parts) 24, 26. The gear components 34, 36 are arranged concentrically and coaxially to one another and have a common (not shown in more detail) axis of rotation.

Here and in the following, “axial” or an “axial direction A” is understood to mean in particular a direction parallel (coaxial) to the axis of rotation. Accordingly, here and in the following, “radial” or a “radial direction R” is understood to mean in particular a direction oriented perpendicular (transverse) to the axis of rotation along a radius of the gear components 24, 26. Here and in the following, “tangential” or a “tangential direction T” is understood to mean in particular a direction along the circumference of the gear components. components 24, 26 (circumferential direction, azimuthal direction), i.e. a direction perpendicular to the axial direction A and the radial direction R.

The gear component 24 is designed as a worm gear and is also referred to as such below. The worm gear 24 is driven by means of a helical worm shaft 28 of the drive motor 6 and forms a worm gear with this. The worm gear is preferably designed as a one-piece, i.e. one-piece or monolithic, injection-molded part made of polyoxymethylene (POM).

The 3 The worm wheel 24 shown individually has a rotating gear ring 30 for meshing engagement with the worm shaft 28, and a hub body 32. The approximately ring-shaped hub body 32 has a central recess 34 for receiving a rotation axis (not shown in detail), which is enclosed by an axially upstanding ring collar 36.

In this embodiment, the ring collar 36 is surrounded by nine tangentially evenly distributed receptacles 38, which are provided with reference numerals in the figures only as examples. The chamber-like or pocket-like receptacles 38 are open radially on the inside and axially upwards (i.e. in the direction of the output pinion 26), and are enclosed radially on the outside and tangentially on three sides by two side walls 40 and an outer wall 42, wherein the axially oriented side walls 40 and outer walls 42 are provided with reference numerals in the figures only as examples. The outer walls 42 are essentially formed by the radial inside of the rotating gear ring 30.

The side walls 40 are oriented approximately radially and have a certain inclination or slant with respect to the radial direction R. In particular, the side walls 40 of the receptacles 38 are oriented inclined towards one another in the tangential direction T in such a way that the tangential diameter of the receptacles 38 tapers from radially inside to radially outside.

The side walls 40 of immediately adjacent receptacles 38 are arranged approximately in a V shape and have an acute opening angle W ( 5 ). In the embodiment shown, the opening angle W is dimensioned between 35° and 50°, for example at approximately 45°, in particular at 40°. The opening angle W of the side walls 40 is widened radially on the outside towards the ring gear 30, which means that the tangential diameter of the receptacles 38 is tapered more radially on the outside. On the V-base, i.e. on the radially inner end of the side walls 40, a radially inwardly projecting projection 44 is formed as an axial rear grip contour, which is provided with reference numerals in the figures merely as an example.

The 4 The gear component 26 shown individually is designed as an output pinion and is also referred to as such below. The output pinion 26 is coupled to the cable drum 18 via a rotating pinion 46. The output pinion is designed, for example, as a one-piece, i.e. one-piece or monolithic, injection-molded part made of POM.

In addition to the pinion 46, the output pinion 26 has a coupling or damping section 48 with nine output extensions 50 that protrude radially outwards in a star shape. The output extensions 50 are provided with reference numerals in the figures only as examples. The output pinion 26 has a central recess 52 for receiving the axis of rotation, which is arranged coaxially aligned with the recess 34. The coupling section 48 has a receiving seat 54 ( 6 , 7 ) for plug-in assembly with the ring collar 36. To form the receiving seat 54, the recess 52 is widened radially at the front end so that the annular receiving seat 54 is exposed as an axial stop surface for the ring collar 36.

The output extensions 50 each have an open ring contour as a bending or spring-elastically deformable area. The ring contour is separated by a radial ring gap 56 into two ring halves or ring legs 58, which can be elastically bent or deformed in the tangential direction T. The ring legs 56 each have a radially inward-facing contact surface 60 on the free end, wherein the mutually facing ring legs 60 come to rest on the mutually facing contact surface 60 in a bent (tensioned) state (not shown in more detail).

Between each two adjacent output extensions 50, a flexible (latching) tab 62 is formed for axially positive locking or clipping with the projections 44. The tabs 62 have in an axial-radial cutting plane ( 6 , 8 ) has an approximately V-shaped cross-sectional form, wherein the radially inner V-leg is designed to be essentially fixed, and wherein the radially outer V-leg is designed to be radially flexible. The V-base faces the worm wheel 24.

To assemble the gear components 24, 26, they are axially stacked and aligned concentrically and coaxially in such a way that the output sets 50 are arranged above the receptacles 38. The gear components 24, 26 are then axially plug-mounted. For this purpose, the ring collar 36 is inserted into the front opening of the coupling section 48 so that it sits on the receiving seat 54. The outside of the V-shaped tabs 62 slides along the respective projection 44 and is deformed and pre-tensioned radially inwards. As soon as the free ends of the tabs 62 have exceeded the projection 44, the tabs 62 are automatically moved outwards due to the (spring) pre-tension and thus axially engage behind the respective projection 44 in a form-fitting manner so that the gear components 24, 26 are axially secured or locked in a form-fitting and/or force-fitting manner.

In the plug-in state, the output extensions 50 engage in the receptacles 38 in such a way that each output extension 50 is seated in the tangential direction T between the two side walls 40 of the respective receptacle 38. In the essentially unbent (relaxed) state shown in the figures, the ring legs 58 each rest in a vertex area on the respective associated side wall 40. The ring legs 58 are therefore supported on the vertex side on the side walls 40, whereby the ring legs 58 have a certain prestress due to the opening angle W of the side walls 40.

The respective output extension 50 is tangentially enclosed in a form-fitting manner by the side walls 40, with the outer wall 42 and/or the radially outer widening of the opening angle W enabling a radial form-fitting arrangement. The output pinion 26 thus engages in a form-fitting manner in the worm gear 24. When the worm gear 24 rotates, the output extensions 50 are supported on the side walls 40, so that the output extensions 50 are carried along by the receptacles 38 of the worm gear 24, and thus transfer the torque of the worm gear 24 to the output pinion 26.

The claimed invention is not limited to the embodiments described above. Rather, other variants of the invention can also be derived from this by the person skilled in the art within the scope of the disclosed claims without departing from the subject matter of the claimed invention. In particular, all individual features described in connection with the various embodiments can also be combined in other ways within the scope of the disclosed claims without departing from the subject matter of the claimed invention.

List of reference symbols

2

Vehicle window regulator

4

window pane

6

Drive motor

8

Adjustment mechanism

10

Guide rail

12

Rail glider

14

Cable pull

16

Gearbox assembly

18

Rope drum

20

Pulley

22

Pulley

24

Gear component/worm wheel

26

Gearbox component/output pinion

28

Worm shaft

30

Sprocket

32

Hub body

34

Recess

36

Ring collar

38

Recording

40

Side wall

42

Exterior wall

44

projection

46

Pinion

48

Coupling section

50

Output extension

52

Recess

54

Recording seat

56

Annular gap

58

Ring leg

60

Contact surface

62

Tab

P

Disc position

S

Closed position

O

Disclosure

A

Axial direction

R

Radial direction

T

Tangential direction

W

Opening angle

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions.

Cited patent literature

• DE 102012208564 A1 [0003]

Claims (10)

Gear assembly (16) for a vehicle window lifter (2), comprising a worm gear (24) which can be driven by means of a worm shaft (28) of an electric drive motor (6) of the vehicle window lifter (2), and an output pinion (26) arranged concentrically in the worm gear (24) for a cable drum (18) of the vehicle window lifter (2), - wherein the output pinion (26) has a number of radially oriented output extensions (50), - wherein the worm gear (24) has a number of receptacles (38) corresponding to the number of output extensions (50), - wherein the output extensions (50) engage in the receptacles (38) in such a way that each output extension (50) is seated in the tangential direction (T) between two approximately radially oriented side walls (40) of the respective receptacle (38), and - wherein the output extensions (50) are designed to be elastically deformable in the tangential direction (T). Gearbox assembly (16) according to Claim 1 , characterized in that the output extensions (50) each have a ring contour as a flexurally elastically deformable region. Gearbox assembly (16) according to Claim 2 , characterized in that the ring contour is radially opened to form two flexurally elastic ring legs (58), wherein the ring legs (58) each rest in a vertex region on the respectively associated side wall (40). Gearbox assembly (16) according to Claim 3 , characterized in that the ring legs (58) each have a radially inwardly oriented contact surface (60) on the free end side, wherein the ring legs (58) facing each other come to rest on the contact surfaces (60) in a bent state. Gear assembly (16) according to one of the Claims 1 until 4 , characterized in that the side walls (40) of a receptacle (38) are oriented inclined towards each other in the tangential direction (T). Gear assembly (16) according to one of the Claims 1 until 5 , characterized in that the worm wheel (24) and the output pinion (26) are joined together in an axially positive-locking manner by means of a joining connection. Gearbox assembly (16) according to Claim 6 , characterized in that the joining connection is designed as a snap-in or clip connection. Gearbox assembly (16) according to Claim 6 or 7 , characterized in that between two adjacent output extensions (50) a flexible tab (62) is formed on the output pinion (26), which is or can be locked in an axially positive manner with a radial projection (44) of the worm wheel (24). Gearbox assembly (16) according to Claim 8 , characterized in that the side walls (40) of adjacent receptacles (38) are oriented approximately V-shaped relative to one another, wherein the projection (44) is formed on the V-base. Vehicle window lifter (2) for a motor vehicle, comprising an electric drive motor (6) with a worm shaft (28), a cable drum (18), and a gear assembly (16) according to one of the Claims 1 until 9 .

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