SCISSOR DRIVE

Abstract

A scissor drive includes two legs which can be pivoted relative to one another about a pivot axis, each having a longitudinal axis and designed to be connected to an external component, and a motor/gear assembly that drives the relative pivoting movement of the two legs. The first leg includes a housing that is hollow at least in portions, a cavity defined in the hollow housing extending at least in portions along the longitudinal axis of the first leg, and the motor/gear assembly being received in the housing of the first leg at least in portions in the portion of the cavity that extends along the longitudinal axis of the first leg.

Claims

1. Scissor drive, comprising: two legs which can be pivoted relative to one another about a pivot axis, each having a longitudinal axis and designed to be connected to an external component, and a motor/gear assembly that drives the relative pivoting movement of the two legs, wherein the first leg comprises a housing that is hollow at least in portions, a cavity defined in the hollow housing extending at least in portions along the longitudinal axis of the first leg, and the motor/gear assembly being received in the housing of the first leg at least in portions in the portion of the cavity that extends along the longitudinal axis of the first leg.

2. Scissor drive according to claim 1, wherein the motor/gear assembly comprises a rotary motor, the rotational axis of which extends substantially in parallel with the longitudinal axis of the first leg.

3. Scissor drive according to claim 1, wherein the motor/gear assembly comprises a reduction gear, which preferably has a reduction ratio of between 1:20 and 1:100, more preferably approximately 1:50.

4. Scissor drive according to claim 2, wherein it comprises a worm gear which is designed to convert a rotational movement of the rotary motor into a relative pivoting movement between the two legs.

5. Scissor drive according to claim 1, wherein it comprises a planetary gear train which is preferably designed having a reduction ratio of between 1:3 and 1:10, more preferably approximately 1:7.5.

6. Scissor drive according to claim 5, wherein the planetary gear train comprises two sets of concentrically arranged planet gears which are interconnected for conjoint rotation in pairs.

7. Scissor drive according to claim 1, wherein it also comprises an overload protection means.

8. Scissor drive according to claim 7, wherein the overload protection means is formed by a gearwheel and a hollow gearwheel which meshes therewith, the teeth of the gearwheel being arranged such that, when a predetermined maximum torque is exceeded, said teeth can slip over the teeth of the hollow gearwheel such that a reduced torque is transmitted between the hollow gearwheel and the gearwheel.

9. Scissor drive according to claim 1, wherein the worm gear and/or the planetary gear train and/or the overload protection means are also received at least in portions in the housing of the first leg.

10. Vehicle, for example a limousine, comprising at least one scissor drive according to claim 1, wherein one of the two legs is rigidly connected to the body of the vehicle and the other of the two legs is connected to an element which is pivotally attached to the body of the vehicle.

11. Vehicle according to claim 10, wherein the element which is pivotally attached to the body is a tailgate, a boot lid, a door or the like.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Additional features and advantages of the present invention will be described in detail in the following by way of example with reference to the accompanying figures, in which:

[0016] FIG. 1 is an exploded view of an embodiment of a scissor drive according to the invention;

[0017] FIG. 2 is a side view of the scissor drive from FIG. 1 in the assembled state; and

[0018] FIG. 3 is a section through the embodiment from FIGS. 1 and 2 along the arrows A in FIG. 2.

DETAILED DESCRIPTION

[0019] FIG. 1 is an exploded view of an embodiment of a scissor drive according to the invention, which is provided in a very general manner with reference numeral 10. The scissor drive comprises a first leg 20 and a second leg 30 which can be pivoted away from one another about a pivot axis 12 indicated by a dashed line and which each comprise a longitudinal axis L1 and L2, respectively, which is also indicated by a dashed line in FIG. 1. The two legs 20 and 30 each comprise, on the side thereof that is opposite the pivot axis 12, through-holes 22 and 32, by means of which said legs can be connected to external components using bolts or the like for example. The first leg 20 consists of a first housing part 24 and a second housing part 26 which are interconnected by means of a plurality of screws 40 when the scissor drive is assembled. Alternatively or additionally, however, other connection techniques known to a person skilled in the art can be used for the two housing parts, for example adhesion, welding, snap-fitting, etc.

[0020] The two housing parts 24 and 26 are hollowed in portions and, when assembled, form a housing in which there is defined a cylindrical first cavity 28a, which extends along the longitudinal axis L1 of the first leg 20, and a second cavity 28b which is connected to said first cavity and extends in a circle around the pivot axis 12. The connection between the first cavity 28a and the second cavity 28b is formed by a cylindrical portion 28c. When the scissor drive 10 is assembled, a motor/gear assembly 42 is mounted in the first cavity 28a, which motor/gear assembly comprises a rotary electric motor and a reduction gear on the output thereof.

[0021] When the scissor drive 10 is assembled, an output shaft 44 is fastened by a flange to the output of the reduction gear of the motor/gear assembly 42, which output shaft extends through the cylindrical portion 28c from the first cavity 28a into the second cavity 28. When the scissor drive 10 is in operation, the output shaft 44 rotates about an axis 46, which is also indicated by a dashed line, in a manner corresponding to the speed of the motor and the reduction ratio of the reduction gear. On the outer periphery of the output shaft 44, there is a set of angular teeth 44a which enables the output shaft to be used as a screw shaft in a worm gear. A worm gearwheel 48 meshes with this set of teeth 44a, has on its outer circumference a corresponding gear rim 48a and converts the movement of the output shaft 44 about the rotational axis 46 into a rotation about the pivot axis 12.

[0022] On the outer circumference of the worm gearwheel 48, there is also an inward-facing gear rim which is, however, hidden in the illustration in FIG. 1 but is provided with reference numeral 48b in FIG. 3. In turn, the toothed portions 50a of an overload protection gearwheel 50 mesh with this inward-facing gear rim 48b. Said toothed portions 50a are formed such that they comprise a projection which is part of the outer circumference of the overload protection gearwheel 50 and are undercut such that the teeth located on the relevant portion 50a can pivot radially inwards when there is an external torque which acts on the overload protection gearwheel 50 and exceeds a maximum torque, in order to thus pivot out of engagement with the inward-facing gear rim 48b of the worm gearwheel 48. In this way, the gearwheels 48 and 50 work together to provide overload protection, for example when an external torque acts on the second leg 30 in an inappropriate manner.

[0023] The hub of the overload protection gearwheel 50 extends through the hub of the worm gear 48, a toothed portion 50b being provided in this extension region. In turn, first planet gears 52a of a planetary gear train 52 mesh with this toothed region 50b. In this case, the planetary gear train 52 is formed as a stepped planetary gear train, the first planet gears 52a being rigidly connected in a coaxial manner to second planet gears 52b, the second planet gears 52b having a smaller diameter than the first planet gears 52a and thus a smaller number of teeth.

[0024] The second planet gears 52b run on the inner toothing of a hollow gearwheel 54 which is rigidly mounted in the cavity 28b and thus connected for conjoint rotation with the first leg 20. A gear rim 56a of an axle 56 acts as the sun gear in this planetary gear train 52 and also engages with the second planet gears 52b. As a result of the selected proportions of the toothing 56a, the hollow gearwheel 54 and the diameters of the planet gears 52a, 52b, respectively, the rotational movement is reduced further. When the scissor drive 10 is assembled, the axle 56 extends from the engagement region thereof with the toothing 56a between the first planet gears 52, through the hub of the worm gearwheel 48 and of the overload gearwheel 50 and exits the second cavity 28b of the first leg 20 via an opening 28d towards the outside. At this point, the second leg 30 can be attached to the second end 56b of the axle 56.

[0025] In the embodiment shown, the rotational moment of the motor gear assembly 42 is accordingly first reversed by the worm gear formed of the elements 44a and 48a, subsequently forwarded by the overload protection means formed of elements 48 and 50, geared down once again by the planetary gear train 52 and then transmitted to the second leg 30.

[0026] FIG. 2 is a side view of the scissor drive 10 from FIG. 1 in the assembled state. This figure shows a section plane which extends through the pivot axis 12 of the two legs 20 and 30, the view from FIG. 3 being understood to be in the direction of arrows A.

[0027] This view in FIG. 3 shows the elements arranged around the pivot axis 12 of the scissor drive 10 in the assembled state. The axle 56 is rigidly connected to the second leg 30 by its output end 56b. At its other end 56c, the axle 56 is rotatably received in a recess 28e in the first housing part 24 of the first leg 20. The gear rim 56a is also located on the axle 56, which gear rim meshes with the second planet gears 52b.

[0028] These second planet gears 52b also mesh at the other end with the hollow gearwheel 54 and are rotatably located on a planetary axle 52c, which is indicated by a dashed line and is connected to the planet carrier 52d of the planetary gear train. The planet gears 52a are also supported by the planetary axle 52c in a manner in which they are concentrically connected to the second gears 52b for conjoint rotation. The radially inner sides of these planet gears mesh with the set of teeth 50b of the overload protection gearwheel 50 which comprises the engagement portions 50a on the other end thereof. In the above-described manner, said engagement portions are in engagement with the inner toothing 48b of the worm gearwheel 48, whereas the outer toothing 48a of the worm gearwheel 48 meshes with the screw shaft 44 which is driven by the motor/gear assembly 42 in the above-described manner.