EP2510175B1 - Drive device for a deployment element of a motor vehicle - Google Patents

Description

The invention relates to a drive device for a between an open position and a closed position motor-adjustable release element, with an electric motor driven spur gear. In this case, in particular, a pivotable, i. one-sided hinged, exhibitable Verschließteil, for example, understood an opening window, a lifting roof or the like of a motor vehicle.

From the DE 197 57 346 C2 a drive device is known in which the driving force of an electric motor via a worm and spur gear on a one-piece with an output shaft first connecting member and a second link coupled thereto is transferable to a pivotable window. During an opening or closing movement of the windowpane, the joint between the two links moves along an arcuate path by about 180 ° while the junction between the second link and the windowpane moves back and forth along a straight path. The arcuate path of the connection point extends on the side opposite the pivoting hinge for articulation of the window pane side of the output shaft, which represents the center of the circle forming a semicircle path. The second connecting member between the connection point and the window pane is arc-shaped in one embodiment and thus surrounds the output shaft even when the opening window is closed.

At one of the DE 42 18 507 C2 known window actuator with an electric motor drive and multi-stage spindle gear and a similar pivot lever mechanism with two hingedly interconnected levers, the point of articulation for opening and closing the displayable side window in turn along a circular arc-shaped path about a rotational shaft axis is pivoted, the pivot point is in the closed position of the window on the opposite side of the window pane below the axis of rotation. As a result, the window is secured against unwanted (manual) opening.

If such drive devices are also operable in the so-called automatic run, they are in principle subject to the same legal requirements of window regulators for retractable windows in which a maximum pinching force of usually 100N in a so-called 4mm bar (upper nip limit) is allowed in the automatic direction in the closing direction ,

The invention has for its object to provide a particularly suitable drive device, which allows flexible installation with low space.

This object is achieved by the features of claim 1. For this purpose, a spur gear is provided, which comprises a driven gear with molded coupling lever for rotatable coupling of a deployment lever and a meshing with the driven spur gear (pinion) and a coaxial with the spur idler. The output gear, the spur gear and the intermediate gear are straight gears, ie gears with axially extending (axially) outer teeth. Such a display device is off DE 20 2008 170 U1 known. According to the invention, the output gear has an external toothing with a first toothed section and with a second toothed section adjoining it whose axial tooth width is smaller than the axial tooth width of the first toothed section.

The circumferentially different axial tooth width of the output gear on the one hand enables different power transmissions from the drive-side spur gear to the output gear and on the other hand ensures a particularly small overall axial width of the Strinradgetriebes including the intermediate gear. The different power transmission is used selectively by the comparatively large axial tooth width of the first toothed portion of the driven gear with the spur gear is engaged when the deployment element of the motor vehicle, in particular a Ausstellfenster, retracts during the closing operation with relatively high force in a closing seal and the spur gear is subjected to a correspondingly high load. In particular, the comparatively wide first toothed section engages with the associated spur gear when the opening element is in its closed position.

In contrast, the output gear with the second toothed portion with a comparatively small axial tooth width with the spur gear engaged when the deployment of the motor vehicle is moved outside the seal with relatively little effort and the spur gear is subjected to a correspondingly low load.

According to a further aspect of the invention, the lever pivotally connected to the coupling lever and transverse to the axes of rotation of the spur gear extending lever is arranged in the plane of symmetry of the spur gear including the coaxial with the spur gear intermediate gear. Due to this mirror symmetry, a left and right installation of the same drive unit is possible with at the same time the smallest possible axial installation width. For this purpose, the comparatively narrow second toothed section forms a corresponding free space for the extension lever coupled to the coupling lever during its adjusting movement. The intermediate gear is located on one side of the plane of symmetry, while the one toothed region of the first toothed section, which axially projects beyond the comparatively narrow second toothed section, is located on the other side of the plane of symmetry.

The spur gear and the intermediate gear are arranged on a common axis of rotation parallel to the axis of rotation of the driven wheel and expediently connected to one another. The Zwischenraddurchmesser is at least slightly smaller than the Abtriebsraddurchmesser and much larger than the spur gear diameter. The axial gear width of the spur gear is greater than or equal to the axial tooth width of the first gear portion. The pinion-like spur gear is aligned with the output gear on the side facing away from the intermediate gear.

The comparatively wide first toothed portion is suitably linear over a certain peripheral portion of the output gear in the relatively narrow second toothed portion over. To simplify and save material, the outer toothing of the drive wheel is expediently provided only on a relevant for the rotation angle outer circumference. Therefore, the output gear on a tooth-free peripheral portion on the opposite side of the two toothed portions on.

The coupling lever, which is suitably molded onto the output gear, has a receiving slot formed between two arms for a perforated lever head of the deployment lever. At the opposite end of the axis of rotation of the output gear free end, the coupling lever has a bearing lug for a fastening bolt for rotatably supporting the release lever on the coupling lever. In the assembly position, in which the fastening bolt is expediently locked or clipped with the coupling lever, the fastening bolt passes through the mutually aligned bearing eyelets of the deployment lever and the coupling lever. For this purpose, the bearing lug has a latching cam, which engages behind an annular groove in the bolt shank of the fastening bolt. As a result, a particularly simple assembly assembly is achieved. The gear-wheel side wall of the receiving slot of the corresponding Koppelhebelarms forms a plane in which the edge-side plane of the set back (second) toothing section. This level thus limits the free space of the deployment lever output side.

The coupling point between the coupling lever and the Ausstellhebel moves during an adjustment of the Ausstellelementes between its open position and its closed position on a semi-circular adjustment. The adjusting movement or the semicircular path expediently runs between two stops (stop points). These are preferably formed by mechanical damping elements. In the region which can be swept by the release lever between these stops, the comparatively narrow second toothed section of the driven wheel is set back relative to its first toothed section. The radial distance of the coupling point between the coupling lever and the release lever to the axis of rotation of the driven wheel is slight larger than the tip circle radius, so that the output gear abuts with its coupling point on the damping elements.

The spur gear with the output gear and with the spur gear and the intermediate gear are suitably part of a multi-stage reduction gear with a worm wheel. This is coupled on the one hand with the intermediate gear and meshes with the other hand, sitting on the drive shaft of an electric motor screw.

The external toothing of the output gear suitably covers a rotation angle of less than 200 °. Relative to an approximately horizontal displacement, which corresponds to an angle range of 0 ° in the open position and 180 ° in the closed position of the deployment, the adjustment of the coupling point expediently covers an angular range of about 180 °. In the locking position of the deployment element, a reliable blocking position of the lever mechanism and thus of the drive device is achieved with even a slight overshoot of the 180 ° dead center. Also, in the open position, a force-related dead center is reliably exceeded, if there the opening angle is at least slightly greater than 0 °.

The advantages achieved by the invention are in particular that by an external toothing of a driven gear of a Strinradgetriebes with at least two toothed sections of different axial tooth width on the one hand and by a symmetrical arrangement of a hinged to the driven gear Ausstellhebels along a transmission mirror axis or plane on the other hand left and right installation the same drive unit is possible at the same time particularly low axial installation width. As a result, an automatic closing of the raising element, in particular an automatic run for both fondseitigen opening window, achieved in the motor vehicle with low component diversity.

In addition, as a result of the targeted toothing use of the comparatively large tooth width of the driven wheel in the heavily loaded external gear area, ie when retracting a dial in a closing seal, a sufficient closing force when using an electric motor and comparatively low power possible. Furthermore, an embodiment of the output gear made of plastic is possible, which leads overall to a weight reduction of the drive device compared to a metal version.

Fig. 1

in perspektivischer Darstellung eine elektromotorische Antriebsvorrichtung mit einem aus einem Gehäuse herausragenden Ausstellhebel,

Fig. 2

in einer Seitenansicht ein Stirnradgetriebe der Antriebsvorrichtung gemäß Fig. 1 mit an ein Abtriebsrad mit unterschiedlicher axialer Zahnbreite angelenktem Ausstellhebel,

Fig. 3

in perspektivischer Darstellung das Stirnradgetriebe mit Blick auf das Stirnrad und Anschlag in einer ersten Verstellposition (Schließstellung),

Fig. 4

in einer Darstellung gemäß Fig. 3 das Stirnradgetriebe mit Anschlag in einer zweiten Verstellposition (Offenstellung),

Fig. 5

in perspektivischer Darstellung das Stirnradgetriebe mit Blick auf ein Zwischenrad und Anschlag in der Schließstellung,

Fig. 6

in einer Darstellung gemäß Fig. 4 das Stirnradgetriebe mit Anschlag in der Offenstellung,

Fig. 7

in einer perspektivischen Darstellung das Abtriebsrad mit angeformtem Koppelhebel und Lageröse, und

Fig. 8

in einer Schnittdarstellung das Abtriebsrad mit in die Lageröse eingeklipstem Befestigungsbolzen für den Ausstellhebel.

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

Fig. 1

a perspective view of an electromotive drive device with a protruding from a housing deployment lever,

Fig. 2

in a side view of a spur gear of the drive device according to Fig. 1 with an output shaft hinged to a driven wheel with different axial tooth width,

Fig. 3

in a perspective view of the spur gear with a view of the spur gear and stop in a first adjustment position (closed position),

Fig. 4

in a representation according to Fig. 3 the spur gear with stop in a second adjustment position (open position),

Fig. 5

in a perspective view of the spur gear with a view of an intermediate and stop in the closed position,

Fig. 6

in a representation according to Fig. 4 the spur gear with stop in the open position,

Fig. 7

in a perspective view of the output gear with molded coupling lever and bearing lug, and

Fig. 8

in a sectional view of the output gear with clipped into the bearing lug fixing bolts for the release lever.

Corresponding parts are provided in all figures with the same reference numerals.

Fig. 1 shows the drive device 1 with an example clam shell, closed housing in its installed position in a vehicle body 2, for example in the region of the C or D pillar, on a flange portion 3 of a side wall or a door frame in the rear of the motor vehicle. A deployment lever 4 of the drive device 1 is guided by a flange 5 to the outside to a display element 6, for example in the form of a hinged on one side to the vehicle body 2 Ausstellfensters, and there to a holding and / or Anlenkstelle 7. The drive device 1 comprises an in Fig. 1 Behind a housing contour hidden electric motor 8, which drives the release lever 4 between a closed position P _S and an open position P _{O of} the opening window 6 via a likewise concealed multi-stage reduction gear 9.

Fig. 2 shows a spur gear 10 and an intermediate gear (intermediate gear) 11 of the reduction gear 9 of the drive device 1. The idler gear 11 rotates about an axis of rotation 12, on which a pinion or spur gear (spur gear) 13 of the spur gear 10 is seated. The spur gear 13 is fixedly connected to the coaxial with this intermediate 11, in particular formed on this. An output gear (driven gear) 14 of the spur gear 10 rotates about a rotation axis 15, which is parallel to the axis of rotation 12 of the intermediate gear 11 and the coaxial with this spur gear 13. The release lever 4 extends in a plane perpendicular to the axes of rotation 12 and 15 extending plane of symmetry (mirror symmetry axis) 16 of the spur gear 10 and thus lies exactly in the middle of the axial transmission width b. The half axial transmission width b _{1 of} the spur gear 10 on the left side in the figure symmetry plane 16 is thus equal to half the axial transmission width b _{2 of} the spur gear 10 on the right side of the plane of symmetry 16. The idler 11 is located on the left side of the plane of symmetry 16, while the output gear 14 is located substantially on the right side of the plane of symmetry. On the side facing away from the intermediate wheel 11 side of the plane of symmetry 16, the output gear 14 is aligned with the spur gear 13, so this does not exceed.

As in connection with the Fig. 3 to 7 it can be seen, the output gear 14 has an external toothing with two toothed portions 14a and 14b different axial tooth width b ₃ and b ₄ on. In this case, the first toothed section 14a with the comparatively large tooth width b ₃ projects slightly beyond the plane of symmetry 16 to the intermediate gear wheel 11 on the left-hand side of the transmission. The second toothed section 14b with the comparatively small axial tooth width b ₄ is located completely on the right side of the plane of symmetry 16. The first toothed section 14a and the second toothed section 14b merge into one another via a third toothed section 14c whose axial tooth width is continuous from the first toothed section 14a (linear) to the second toothed portion 14b decreases.

In the representations according to the Fig. 2 . 3 and 5 is the output gear 14 with the first toothed portion 14a with a comparatively large axial tooth width b ₃ with the spur gear 13 in engagement and meshes with the outer toothing 17 over at least approximately its entire axial tooth width b ₅ (FIG. Fig. 3 ).

In this gear position is the coupled to a coupling lever 18 of the driven gear 14 adjusting lever 4 in a due to the comparatively narrow axial tooth width b _{4 of} the second toothed portion 14b of the driven gear 14 formed intermediate space 19 whose axial width by the difference of the two tooth widths b ₃ and b _{4 is} determined. As a result, at the same time mirror-symmetrical structure of the spur gear 10 - and thus the drive device 1 - the axial transmission width b of the spur gear 10 is particularly low and practically minimized. This in turn leads to a particularly small space requirement of the drive device. 1

Like from the Fig. 5 to 8 For this purpose, it passes through a bearing lug 21 of the coupling lever 18 and a hereby aligned, suitably designed as a slot bearing lug 22 of the release lever 4. The mounting bolt 20 forms in conjunction with the bearing lugs 21 and 22, the bearing or coupling point between the coupling lever 18 and the release lever 4. The radial distance r _{A of} the coupling point 20,21,22 to the axis of rotation 15 of the output gear 14 is greater than the tip circle radius r _K , so that the coupling point 20,21,22 and thus integrally formed on the output gear 14 coupling lever 18, the output gear 14 circumferentially at least slightly surmounted.

To accommodate the opening lever 4 and its free-end bearing head 23 with the bearing lug 22 of the coupling lever 18 is formed from a first Koppelhebelarm 18 a and this to form a receiving slot 24 for the release lever 4 opposite the second Koppelhebelarm 18 b. The second arm 18b is substantially integrally formed on a tooth-free peripheral portion 25 of the output gear 15. The first arm 18a is formed with its bearing end facing away from the retaining end 21 to a cylindrical bearing dome 26 for a bearing shaft of the output gear 14, not shown. The edge-side plane of the set back narrow toothed portion 14b of the output gear 14 is substantially in the plane which forms the slot-side Koppelhebel- or arm wall of integrally formed on the tooth-free peripheral portion 25 of the output gear 14 arm 18b of the coupling lever 18 ( Fig. 7 ). This level limits the intermediate space 19 on the in Fig. 2 right side of the drawing.

One of the coupling lever arms, in the exemplary embodiment the second coupling lever arm 18b of the coupling lever 18, has a trough 28 forming a clamping nose or locking cam 27. Im in Fig. 8 shown latched or clipped state of the fastening bolt 20 engages this locking cam 27 in an annular groove 29 of the fastening bolt 20 and engages behind a formed by the annular groove 29 shoulder or locking contour 30 of the mounting bolt 20. This locking or Klipsmechanismus allows a particularly simple installation of the deployment lever 4 in the coupling or articulation point produced by the eyelets 21,22 and the bolt 20 between the release lever 4 and the coupling lever 18. An integrally formed on the shoulder contour 30 of the annular groove 29 pin end integrally formed support collar 31 of the mounting bolt 20 is in its detent position at the opening edge of Bearing eye 21 and thus forms in addition to the rear grip of the locking cam 27 on the shoulder contour 30 of the annular groove 29 a second Lageroder Fixing point of the fastening bolt 20 in the bearing lug 21 of the coupling lever18.

In the Fig. 3 to 6 are rod or cylindrical mechanical damping elements 32,33 recognizable. The housing-fixed damping elements 32,33 attenuate a stop of the output gear 14 radially superior coupling lever 18 in the area defined by the fastening bolt 20 bearing 20,21,22 in the open position P _O or in the closed position P _{S of} the Ausstellfensters 6. The mechanical damping elements 32,33, for example, consist of a soft, elastic plastic material, thus allowing a noise-free installation of the deployment lever 4 in the end positions P _O and P _{S of} the opening window. 6

Due to the mirror-symmetrical structure of the spur gear 10 and the intermediate wheel 11 and the release lever 4 with its position within the plane of symmetry 16, the drive device 1 can be installed on both the left and on the right side of the vehicle to automatically actuate the corresponding Ausstellfenster 6 there. Its slot 20,21,22 on the coupling lever 18 passes during an adjustment between the open position P _O and the closed position P _S a circular path while sweeping over an angular range from greater than or equal to 0 ° to less than or equal to 200 °, preferably about 180 °.

Bezugszeichentiste

1 driving device 28 recess 2 vehicle body 29 ring groove 3 flange 30 Shoulder / latching contour 4 out lever 31 support collar 5 flange 32 damping element 6 Deployment element / window 33 damping element 7 articulation 8th electric motor b gear width 9 Reduction gear b _1,2 half gear width 10 Spur gears b _3,4,5 tooth width 11 idler 12 axis of rotation P _o open position 13 spur gear P _S closed position 14a first toothing section 14b second toothing section r _A radial distance 14c third toothing section r _K Tip circle radius 15 axis of rotation 16 Mirror / symmetry axis 17 external teeth 18 coupling lever 18a first clamping arm 18b second clamping arm 19 Between freedom 20 mounting bolts 21 clevis 22 slot-like eyelet 23 bearing head 24 receiving slot 25 tooth-free peripheral portion 26 bearing dome 27 Clamping lug / locking cam

Claims (13)

1. Drive device (1) for a vent element (6) of a motor vehicle, in particular for a rotatable vent window, which can be adjusted by a motor between an open position (P_O) and a closed position (P_s), having a spur gear unit (10) powered by an electrical motor, said spur gear unit (10) comprising an output gear (14), with a coupling lever (18) for the rotary coupling of a vent lever (4) of the drive device (1), and a spur gear (13), which meshes with the output gear (14), as well as comprising an idler gear (11), which is coaxial to the spur gear (13), for coupling with an electrical motor, characterised in that,

   - the output gear (14) has an outer gearing with a first gearing section (14a) and with a second gearing section (14b) that connects to it, the axial tooth width (b₄) of which is smaller than the axial tooth width (b₃) of the first gearing section (14a), and

   - that the vent lever (4) coupled to the coupling lever (18) is arranged in a plane of symmetry (16), which passes transversely to the axes of rotation (12, 15) of the spur gear unit (10).
2. Drive device (1) according to claim 1,
   characterised in that,
   the spur gear (13) and the idler gear (11) are connected with one another on a mutual rotation axis (12), which is parallel to the rotation axis (15) of the output gear (14).
3. Drive device (1) according to claim 1 or 2,
   characterised in that,
   the output gear (14) has a gear-free peripheral section (25).
4. Drive device (1) according to one of claims 1 to 3,
   characterised in that,
   the axial tooth width (b₅) of the spur gear (13) is larger than or equal to the axial tooth width (b₃) of the first gearing section (14a).
5. Drive device (1) according to one of claims 1 to 4,
   characterised in that,
   the spur gear (13) on the side facing away from the idler gear (11) aligns with the output gear (14).
6. Drive device (1) according to one of claims 1 to 5,
   characterised in that,
   the radial distance (r_A) of the coupling point (20, 21, 22) between the coupling lever (18) and the vent lever (4) for the rotation axis (15) of the output gear (14) is greater than the tip circle radius (r_K) thereof.
7. Drive device (1) according to one of claims 1 to 6,
   characterised in that,
   the coupling lever (18) has a first arm (18a), formed on the output gear (14) in the region of the rotation axis (15) of said output gear (14), and a second arm (18b), which is at a distance to the first arm (18a), forming a receiving slot (24) for the vent lever (4).
8. Drive device (1) according to one of claims 1 to 7,
   characterised in that,
   a mounting bolt (20) is provided for the rotary coupling of the vent lever (4) to the coupling lever (18), said mounting bolt (20) being locked in place in a bearing eye (21) of the coupling lever (18).
9. Drive device (1) according to claim 8,
   characterised in that,
   the coupling point (20, 21, 22) between the coupling lever (18) and the vent lever (4) is guided on a semi-circle-shaped circular path between a first stop (32) allocated to the open position (P_O) and a second stop (33) allocated to the closed position (P_s).
10. Drive device (1) according to claim 9,
    characterised in that,
    the stops are formed by mechanical damping elements (32, 33).
11. Drive device (1) according to claim 9 or 10,
    characterised in that,
    the second gearing section (14b) of the output gear (14) is set back in the region that can be covered by the vent lever (4) between the stops (32, 33), opposite the gearing section (14a).
12. Drive device (1) according to claim 11,
    characterised in that,
    the edge-side plane of the gearing section (14b) that is set back fundamentally lies in the plane which forms a wall of the receiving slot (24) of the arm (18b).
13. Drive device (1) according to one of claims 1 to 12,
    characterised in that,
    if the vent element (6) is situated in its closed position (P_s), the comparatively wide first gearing section (14a) engages with the allocated spur gear (13).

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