Actuator device for automatically activating the vehicle door of a motor vehicle

Abstract

An actuator device for automatically activating the vehicle door of a motor vehicle, in particular the tailgate, includes an electromotive drive and a radially extending arm. The radially extending arm is attached either to the vehicle door or to a vehicle bodywork and is set in motion by the electromotive drive. The electromotive drive has an electrical motor and a gearbox driven by the motor. The gearbox has a wobble mechanism.

Claims

1. An actuator device for automatically activating a vehicle door of a motor vehicle, comprising: an electromotive drive and an arm attached to either the vehicle door or a vehicle bodywork and wherein the arm is configured to be set in motion by the electromotive drive to open or close the vehicle door, wherein the arm extends radially with respect to a rotation axis of the electromotive drive, said electromotive drive comprising an electrical motor and a gearbox driven by the motor, wherein the gearbox comprises a wobble mechanism, wherein the gearbox is coupled directly to an overload shaft, wherein the overload shaft is rotationally attached to an output shaft via a friction ring inserted between the output shaft and the overload shaft, the output shaft being coupled directly to the arm, and wherein when torque values of the actuator device, which are exerted on either the overload shaft or the output shaft, are beyond a predetermined value, the friction ring slides in rotation with one of the overload shaft and the output shaft.

2. The actuator device according to claim 1, wherein the wobble mechanism comprises an excenter shaft, an oscillating front wheel, and a fixed planetary wheel, the excenter shaft is rotationally driven by the electrical motor and supports the oscillating front wheel, the oscillating front wheel having outer teeth and the fixed planetary wheel having inner teeth meshing with the outer teeth of the front wheel, the front wheel having less teeth than the planetary wheel.

3. The actuator device according to claim 2, wherein the gearbox further comprises an Oldham coupling, and the front wheel is coupled to the overload shaft via the Oldham coupling.

4. The actuator device according to claim 3, wherein the Oldham coupling comprises an Oldham disc having first diametrically opposed recesses and second diametrically opposed recesses, shifted by 90? with respect to said first recesses, said first recesses engage with two diametrical projections of said front wheel and said second recesses engage with projections carried by said overload shaft.

5. The actuator device according to claim 4, wherein said excenter shaft supports rotationally the front wheel and the Oldham disc.

6. The actuator device according to claim 2, wherein the gearbox comprises a tubular retaining element in which the planetary wheel is fixed.

7. The actuator device according to claim 1, further comprising a brake device located between the electrical motor and the gearbox.

8. The actuator device according to claim 7, wherein the brake device is a permanent-magnet-excited hysteresis brake.

9. The actuator device according to claim 1, further comprising a first reduction device located between the electrical motor and the gearbox.

10. The actuator device according to claim 1, wherein the wobble mechanism comprises a gearbox excenter shaft rotationally supported by radial bearings, and wherein the excenter shaft comprises: a rotational axis; and an excenter mass that outbalances oscillations of the excenter shaft when the excenter shaft rotates around the rotational axis of the excenter shaft.

Description

(1) Further details and advantages of the invention emerge from the following exemplary embodiments explained with reference to figures, in which:

(2) FIG. 1 is a schematic perspective view of the rear region of a motor vehicle with the tailgate opened and a laterally arranged actuator device according to the invention;

(3) FIG. 2 shows partially the actuator device of FIG. 1 in an explosion view;

(4) FIG. 3 shows more in detail a longitudinal section through the actuator device of FIG. 1;

(5) FIG. 4 shows a longitudinal section through the gearbox excenter shaft shown in FIGS. 2 and 3.

(6) In all figures, the same reference numbers designate the same elements.

(7) In FIG. 1, the numeral 1 designates a motor vehicle which has a tailgate 2 which can be pivoted by an actuator device 3 from a closed position into the opened position illustrated in FIG. 1, and if appropriate in turn into the closed position. The actuator device 3 is connected here to the bodywork of the motor vehicle 1 via a radial arm 6 and to the tailgate 2 by being connected to a tailgate hinge.

(8) In particular, the actuator device 3 may comprise connection means to the associated vehicle door hinge.

(9) As an alternative, the actuator device may be integrated in a driver or even passenger door of the vehicle, and/or the arm 6 may be attached to the mobile door, or tailgate 2.

(10) Reference is now made to FIGS. 2 and 3 for the description of the inner parts of the actuator device 3.

(11) The actuator device 3 comprises a tubular housing 5, in which the mechanism is contained. The tubular housing comprises a first tubular portion 7 and a second tubular portion 8, rotationally driven by the motor (not represented) with respect to the first one 7, and forming a support for the arm 6.

(12) At the opposite end of the one carrying the arm 6 supporting tubular base 8 of the tubular housing 5, a cover disc 9 closes the tubular housing 5. A retaining bracket 10 surrounds the tubular housing 5 for attaching the actuator device 3 to the vehicle bodywork, with a rubber ring 11 placed between said housing 7 and said bracket 10 to reduce vibration transmission.

(13) The retaining bracket 10 may in particular be attached to the vehicle bodywork, if the arm 6 is attached to the door 2, or to the vehicle door 2, if the arm 6 is attached to the bodywork.

(14) Adjacent to the cover disc 9 is fixed into the first tubular housing portion 7 a motor damper 12 made of an elastic material, for example made of rubber.

(15) On the other side of the motor damper 12 is fixed with one end an electrical motor 14. The motor damper 12 is here a rubber tube, part of which surrounds the one end of the motor 13 which has a roughly cylindrical shape.

(16) The electrical motor 14 has an output shaft 16 coupled to a brake device 18.

(17) More in detail, the brake device 18 is a hysteresis brake as described for example in EP1 940 012 the content of which is hereby incorporated by reference.

(18) The brake device 18 is coupled to a first reduction device 19.

(19) More in detail, the first reduction device 19 may for example be a two stepped epicyclic gearing.

(20) The first reduction device 19 comprises essentially a first planet gear attached in rotation with the output shaft of the motor. The first planet gear meshes with satellite gears which comprise two radial segments with different diameters. The first planet gear meshes with the larger radius segment. The smaller radius segment meshes with a second planetary gear which is attached to the output shaft 30 of the first reduction device 19.

(21) The ratio of the radii between first and second planetary gears corresponds to the reduction ratio of the first reduction device 19. Other reduction device types known from the state of art are also usable as first reduction device 19. If the door is light enough or if support elements such as one or more telescopic gas springs are implemented, no first reduction device 19 may be necessary.

(22) The output shaft 30 of the first reduction device 19 is connected to the gearbox 20 of the actuator device 3, which comprises a wobble mechanism.

(23) In particular, the wobble mechanism comprises a gearbox excenter shaft 34 rotationally supported by radial bearings 36.

(24) As can be seen in detail, in particular in FIGS. 3 and 4, the gearbox excenter shaft 34 has at one end facing the electrical motor 14 and the brake device 18, an engagement portion 38 engaging into the tubular output shaft 30 of the first reduction device 19.

(25) Two supporting portions 40 are held in radial bearings 36 that are supported fixed by a rotationally fixed, housing forming tubular retainer element 42 in contact with the brake device 18. In particular, the retainer element 42 is attached to the first tubular housing portion 7 by means of an annular portion 43 of larger diameter, forcefully inserted into the first tubular housing portion 7.

(26) The supporting portion 40 farthest from the electrical motor 14 is adjacent to an excenter shaft portion 44 which rotationally supports via radial bearings 36 an oscillating front wheel 46. Between the excenter shaft portion 44 and the front wheel 46 is placed an annulus 47 rotating freely with respect to either one or both of the excenter shaft portion 44 and/or the front wheel 46.

(27) As can be seen in particular on FIG. 4, the excenter shaft portion 44 has a smaller diameter than portions 38 and 40 with a center axis 48 that is eccentric with respect to the rotational axis 50 of the excenter shaft 34 which is concentric and in line with the output shaft 16 of the electrical motor 14.

(28) On FIG. 4 is also represented an inertial mass 52 extending radially from the excenter shaft 34. This inertial mass 52 is used to outbalance the oscillations of the excenter shaft 34 when it rotates around its axis 50.

(29) On the axial side that faces the arm 6 of the front wheel 46 is an Oldham coupling 56 that will be described more in detail later on.

(30) When the excenter shaft 34 rotates, the oscillating front wheel 46 describes therefore an oscillating motion.

(31) The oscillating front wheel 46 has outer teeth 58 that mesh with the inner teeth 60 of a planetary wheel 62 fixed in rotation with respect to the first tubular housing portion 7.

(32) In order to make a gear reduction, the front wheel 46 has fewer teeth than the planetary wheel 62. As an example, the front wheel has 38 teeth whereas the planetary wheel has 40 teeth. In such a way a reduction ratio of 19:1 can be achieved.

(33) As can be seen on FIG. 3, the planetary wheel 62 is fixed in rotation and held in position in particular by the retainer element 42.

(34) Therefore, the reduction is achieved through the cooperation of the oscillating front wheel 46 and the planetary wheel 62.

(35) In order to drive the arm 6, the output of the oscillating rotation of the front wheel 46 has two diametrical projections 64 for engagement with the Oldham coupling 56.

(36) These projections 64 engage in correspondent diametrically opposed first recesses 66 of an Oldham disc (also called cross disk) 68 rotationally carried by the front wheel 46 of the gearbox 20.

(37) The Oldham disc 68 has second recesses 70 that are also diametrically opposed, but 90? shifted with respect to the first recesses 66.

(38) These second recesses 70 receive projections 71 of an overload shaft 72. This overload shaft 72 is rotationally attached to an output shaft 73 by means of a friction ring 74, inserted between the output shaft 73 and the overload shaft 72.

(39) The material, dimensions and form of the friction ring 74 are selected so that when torque values corresponding to normal operation of the actuator device 3 are exerted either on the output shaft 73 or the overload shaft 72 the friction ring 74 maintains said shafts 72, 73 solidly attached in rotation, and so that in case of torque values higher than a predetermined value being applied, the ring 74 slides in rotation with one of the shafts 72, 73.

(40) Thus, when the door 2 is blocked or when an important force is applied on said door 2, the torque between the output and overload shafts 72, 73 increases until a predetermined value where the shafts 72, 73 are frictionally unclutched. Therefore, the abnormally high torque values are not transmitted to the gearbox 20, the vehicle structure (door 2 or bodywork) and/or the motor 14 where harm might occur.

(41) The output shaft 73 is attached by means of a bearing 75 and form fit 76 to the arm 6 support forming second tubular housing portion 8 and thus drives said second tubular housing portion 8 and the supported arm 6 in rotation at the reduced speed and with increased torque.

(42) Due to the presence of the annular portion 43 on one end and of the motor damper 12, a gap G (see FIG. 3) is created between the motor 14, the braking device 18 and the first reduction device 19, on one hand and the first housing portion 7 on the other hand. Thus the motor 14, the braking device 18 and the first reduction device 19 are suspended, and only a minor portion of their vibrations is transmitted to the first housing portion 7 and resulting in noise.

(43) In this way, only the gearbox 20 with the wobble mechanism, that generates fewer vibrations, is directly transmitting vibrations to the housing 5.

(44) Furthermore, it is clear that in this way, the gearbox 20 together with the brake device 18 (and possible first reduction stage 19) may be assembled separately since forming a closed module.

(45) Then this gearbox/brake unit 18, 20 can be assembled directly with the electrical motor 14, and then inserted in the housing 7.

(46) In functioning, the shaft 16 of the electric motor 14 rotates and drives the excenter shaft 34 in motion. This causes the front wheel 46 to mesh with the teeth of the planetary wheel 62.

(47) Therefore the front wheel 46 describes an oscillating movement at a speed corresponding to the rotational speed of the output shaft of the motor 14, reduced by the first reduction stage 19. In addition, the front wheel 46 rotates around the shaft 34 at a reduced speed which corresponds to the reduction value of the gearbox.

(48) This reduced rotational speed of the front wheel 46 is fed to the Oldham coupling 56 that suppresses the oscillating movement and causes the output shaft 73 to rotate at the reduced rotational speed of the front wheel 46.

(49) As shown above, the use of a wobble mechanism which comprises a shaft 34, a front wheel 46, a planetary wheel 62, and an Oldham coupling 56, as a gearbox 20 results in a very compact gearbox with reduced number of parts.

(50) The reduced number of parts means a reduced susceptibility to failures and an easier and cheaper assembling.

(51) Also, the obtained electromotive drive comprising the motor 14, brake device 18, first reduction stage 19 and gearbox 20 is potentially smaller and fitting in a smaller and easily concealed housing 7 while having similar efficiency in the torque exerted on the arm 6 than state-of-art drives.

(52) In addition, as fewer teeth are meshing at the same time together than in gearboxes of known actuator devices with planetary construction, contact noise, and therefore overall noise can be reduced in an important way. In particular, in a standard epicyclic reduction gear device, six teeth contacts are meshing per reduction stage, considering three planet gears per stage, while in a wobble mechanism only one teeth set is meshing at every time.

(53) Moreover, a wobble mechanism allows a better reduction rate per implemented stage, here as described about 19:1, when compared to a single epicyclic reduction stage, usually about 6:1.

(54) In addition, such a wobble mechanism may be very compact. Therefore the wobble mechanism may be built shorter than the multiple epicyclic reduction stages needed to reach an equivalent reduction rate.

(55) Furthermore, at equivalent torque value ranges, the average diameter of the considered reduction device may be reduced.

(56) It has also been shown that the assembling of the gearbox is quite easy and may be robotized, contributing to reduce costs furthermore.