EP2510175A1

EP2510175A1 - Drive device for a deployment element of a motor vehicle

Info

Publication number: EP2510175A1
Application number: EP10720995A
Authority: EP
Inventors: Uwe Sommer
Original assignee: Brose Fahrzeugteile SE and Co KG
Current assignee: Brose Fahrzeugteile SE and Co KG
Priority date: 2009-12-11
Filing date: 2010-05-06
Publication date: 2012-10-17
Anticipated expiration: 2030-05-06
Also published as: US20120234116A1; JP2013513739A; US8607656B2; JP5597720B2; CN102449256B; RU2483183C1; EP2510175B1; WO2011069565A1; DE202009016813U1; CN102449256A

Abstract

The invention relates to a drive device (1) for a deployment element (6) of a motor vehicle, in particular for a pivotable hinged window, which can be moved between an open position (Po) and a closed position (Ps) in a motorized manner. A spur gear transmission (10) driven by an electric motor comprises an output gear (14) having a coupling lever (18) for coupling a deployment lever (4) in a rotationally movable manner, a spur gear (13) that meshes with the output gear (14), and an intermediate gear (11) that is coaxial with the spur gear (13). The output gear (14) has outer teeth having two teeth sections (14a, 14b) of different axial tooth width (b₄). The deployment lever (4) that is coupled to the coupling lever (18) extends in a plane of symmetry (16) perpendicular to the rotational axes (12, 14) of the spur gear transmission (10).

Description

description

Drive device for a display element of a motor vehicle

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 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.

In one known from DE 42 18 507 C2 window actuator with an electric motor drive and multi-stage spindle gear and a similar pivot lever mechanism with two hinged interconnected levers, the pivot point for opening and closing the side window can turn turn along a circular arc path around a rotary shaft Axis is pivoted, the pivot point is in the closed position of the window on the opposite side of the window glass below the axis of rotation. As a result, the window is secured against unwanted (manual) opening.

If such drive devices are to be operated also in the so-called automatic run, they are in principle subject to the same statutory requirements of window regulators for retractable windows, in which a maximum pinching force of usually 100N in a so-called 4mm rod (upper Einklemmspaltgrenze) 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 installation 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, i. Gears with in the axial direction (axially) straight outer teeth. The output gear has an external toothing with a first toothed section and with a second toothed section adjoining thereto 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 allows on the one hand 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 section of the output gear is in engagement with the spur gear when the deployment element of the motor vehicle, in particular a special opening window, during the closing process with comparatively high force enters a closing seal and the spur gear is exposed 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 order, in which the fastening bolt is expediently locked or clipped with the coupling lever, the fastening bolt passes through the mutually aligned bearing eyes of the raising lever and of 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 closing position of the deployment element, a reliable blocking position of the lever mechanism and thus of the drive device is achieved with only 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.

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

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

2 is a side view of a spur gear of the drive device according to FIG. 1 with an output wheel articulated to a driven wheel with a different axial tooth width,

3 is a perspective view of the spur gear with a view of the

Spur gear and stop in a first adjustment position (closed position),

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

5 is a perspective view of the spur gear with a view of a

Intermediate wheel and stop in the closed position,

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

7 is a perspective view of the output gear with integrally formed coupling lever and bearing lug, and

8 shows a sectional view of the output gear with fastening bolts clipped into the bearing lug for the deployment 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 opening 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 guided to a holding and / or An steering point 7. The drive device 1 comprises a concealed in Fig. 1 behind a housing contour electric motor 8, via a likewise concealed multi-stage reduction gear 9, the release lever 4 between a

Closed position P _s and an open position Po of the Ausstellfensters 6 drives.

Fig. 2 shows a spur gear 10 and an intermediate gear (idler 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 bi 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 16th 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 can be seen in connection with FIGS. 3 to 7, the output gear 14 has an external toothing with two toothed portions 14a and 14b. Licher axial tooth width b ₃ and b ₄ on. In this case, the first toothed section 14a with the comparatively large tooth width b3 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 illustrations according to FIGS. 2, 3 and 5, the output gear 14 with its first toothed portion 14a with a comparatively large axial tooth width b ₃ engages with the spur gear 13 and meshes with its external toothing 17 over at least approximately its entire axial tooth width b ₅ < (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

As can be seen comparatively clearly from FIGS. 5 to 8, the coupling of the deployment lever 4 to the coupling lever 18 takes place by means of a fastening bolt 20. For this purpose, it passes through a bearing lug 21 of the coupling lever 18 and a bearing lug 22, which is suitably aligned as a slot of the raising 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 lever 4. The radial distance r _{A of} the coupling point 20,21, 22 to the axis of rotation 15 of the driven gear 14 is larger as its head circle radius r _K , so that the coupling point 20,21, 22 and thus the 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 return of the narrow toothed section 14b of the output gear 14 lies essentially in the plane forming the slot-side coupling lever or arm wall of the arm 18b of the coupling lever 18 formed on the tooth-free peripheral section 25 of the output gear 14 (FIG. 7). This level limits the intermediate space 19 on the right in FIG. 1 drawing page.

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. In the locked or clipped state of the fastening bolt 20 shown in FIG. 8, this locking cam 27 engages in an annular groove 29 of the fastening bolt 20 and engages behind a shoulder or locking contour 30 of the fastening bolt 20 formed by the annular groove 28. This locking or clip mechanism permits a Particularly simple assembly of the deployment lever 4 in the coupling or articulation point between the release lever 4 and the coupling lever 18 produced by the bearing lugs 21, 22 and the bolt 20. A support collar 31 of the fastening bolt 20 formed on the shoulder contour 30 of the annular groove 29 lies in its latching position at the opening edge of the bearing lug 21 and thus forms in addition to the rear grip of the latching cam 27 on the shoulder contour 30 of the annular groove 29 a second bearing or fixing point of the fastening bolt 20 in the bearing lug 21 of the coupling lever 18.

In FIGS. 3 to 6, rod-shaped or cylindrical mechanical damping elements 32, 33 can be seen. The housing-mounted 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 ₀ or in the closed position Ps of the opening window 6. The mechanical damping elements 32nd , 33, which consist for example of a soft, elastic plastic material, thus allowing a noise-free installation of the deployment lever 4 in the end positions Po and Ps 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 ₀ 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 °.

LIST OF REFERENCE NUMBERS

1 drive device 28 recess

2 vehicle body 29 annular groove

3 Flange area 30 Shoulder / latching contour

4 deployment lever 31 support collar

5 flange opening 32 damping element

6 Display element window 33 Damping element

7 articulation point

8 electric motor b transmission width

9 reduction gear bi _{, 2} half gear width

10 helical gearbox b3 _, 4.5 tooth width

11 intermediate wheel

12 rotation axis P ₀ open position

13 spur gear P _{s closed position}

14a first gear section

14b second gear portion r _A radial distance

14c third toothing section r _K tip circle radius

15 axis of rotation

16 mirror / symmetry axis

17 external toothing

18 coupling levers

18a first clamping arm

18b second clamping arm

19 intermediate clearance

20 fastening bolts

21 bearing lug

22 slothole bearing lug

23 bearing head

24 receiving slot

25 tooth-free peripheral portion

26 Lagerdom

27 Clamping nose / locking cam

Claims

claims

First drive device (1) for a display element (6) of a motor vehicle, in particular for a pivotable Ausstellfenster, which is motor-adjustable between an open position (Po) and a closed position (Ps), with an electric motor driven spur gear (10), which is a Abtriebsrad (14) with a coupling lever (18) for the rotationally movable coupling of a deployment lever (4) and a with the output gear (14) meshing spur gear (13) and a spur gear (13) coaxial idler (11),

wherein the output gear (14) has an outer toothing with a first toothed section (14a) and with a second toothed section (14b) adjoining thereto whose axial tooth width (b ₄ ) is smaller than the axial tooth width (b ₃ ) of the first toothed section ( 14a), and

- Wherein the coupling lever (18) coupled to the deployment lever (4) arranged in one of the axes of rotation (12,15) of the spur gear (10) transversely extending plane of symmetry (16).

2. Drive device (1) according to claim 1,

characterized,

the spur gear (13) and the intermediate gear (11) are connected to one another on a common rotational axis (12) parallel to the axis of rotation (15) of the output gear (14).

3. Drive device (1) according to claim 1 or 2,

characterized,

the output gear (14) has a tooth-free peripheral section (25).

4. Drive device (1) according to one of claims 1 to 3,

characterized,

the axial tooth width (b ₅ ) of the spur gear (13) is greater than or equal to the axial tooth width (b ₃ ) of the first toothed portion (15a).

5. Drive device (1) according to one of claims 1 to 4,

characterized,

the spur gear (13) on the side facing away from the intermediate gear (11) is aligned with the output gear (14).

6. Drive device (1) according to one of claims 1 to 5,

characterized,

the radial distance (r _A ) of the coupling point (20, 21, 22) between the coupling lever (18) and the extension lever (4) to the axis of rotation (15) of the driven wheel (14) is greater than its tip circle radius (r _K ).

7. Drive device (1) according to one of claims 1 to 6,

characterized,

in that the coupling lever (18) has a first arm (18a) formed in the region of the axis of rotation (15) of the driven wheel (14) and a second arm (18b) spaced therefrom to form a receiving slot (24) for the opening lever (4). having.

8. Drive device (1) according to one of claims 1 to 7,

characterized,

in that a fastening bolt (20) is provided for the rotationally movable coupling of the opening lever (4) to the coupling lever (18), which is latched in a bearing lug (21) of the coupling lever (18).

9. Drive device (1) according to claim 8,

characterized,

that the coupling point (20,21, 22) between the coupling lever (18) and the deployment lever (4) on a semicircular circular path between one of the Open position (Po) associated with the first stop (32) and one of

Closed position (Ps) associated second stop (33) is guided.

10. Drive device (1) according to one of claims 1 to 9,

characterized,

the stops are formed by mechanical damping elements (32, 33).

11. Drive device (1) according to claim 9 or 10,

characterized,

in that the second toothed section (14b) of the driven wheel (14) is set back in relation to the toothed section (14a) in the area which can be painted over by the opening lever (4) between the stops (32, 33).

12. Drive device (1) according to claim 11,

characterized,

in that the edge-side plane of the set-back toothing section (14b) lies substantially in the plane forming a wall of the receiving slot (24) of the arm (18b).

13. Drive device (1) according to one of claims 1 to 12,

characterized,

in that the comparatively wide first toothed section (14a) engages with the associated spur gear (13) when the opening element (6) is in its closed position (Ps).