EP1645709B1 - Power door operator - Google Patents

Abstract

The door drive (12) has a drive motor (44) with an input shaft of epicyclical gear (48) connected to it. A displacing medium (40,42), for displacing the door (10) is also provided, which is connected to the first output shaft (58) of epicyclical gear. A swiveling medium (14) is provided for swiveling the door, which is connected to the second output shaft (64) of epicyclical gear.

Description

The invention relates to a drive for moving a door, in particular a motor vehicle, with a drive motor.

Such a door drive is basically known and is used in a motor vehicle, for example, to automatically open or close a sliding door of the motor vehicle.

A problem proves to be the drive of a sliding door, which should not only perform a sliding movement, but also a pivoting movement. It is desirable, for example, that the door initially pivots outward during opening and is then moved. To achieve this, the door drive is conventionally provided with two drive motors, one of which causes only a pivotal movement and the other only a sliding movement of the door. In addition to the increased costs caused by two separate drive motors, the movement of the door during the transition from the pivoting movement to the sliding movement or vice versa, i. when switching from one drive motor to the other drive motor, usually interrupted.

A door drive according to the preamble of claim 1 is in the DE-A-197 35 181 A1 discloses. Similar door drives are also from the US 4,461,182 and the EP-A-1 004 738 known.

The invention has for its object to provide a drive for moving a door, in particular a motor vehicle door, which is not only less expensive, but also allows a smooth transition from a pivoting movement to a sliding movement of the door or vice versa.

To solve the problem, a drive with the features of claim 1 is provided.

The drive according to the invention for moving a door, in particular of a motor vehicle, comprises a drive motor, which is connected to a drive shaft of a planetary gear, a displacement means for displacing the door, which is connected to a first output shaft of the planetary gear, and a pivoting means for pivoting the door, which is connected to a second output shaft of the epicyclic gear.

As is known, an epicyclic gearbox has three shafts, one of which is used according to the invention as a drive shaft and the other two as output shafts. Thus, it is possible according to the invention to effect both a pivoting and a displacement of the door by means of a single drive motor. Since the pivoting and moving of the door takes place by means of a single drive motor, according to the invention only one power supply, control and monitoring need to be provided for the drive. As a result, the cost of the door drive according to the invention over conventional door drives with two drive motors are significantly reduced.

Since the pivoting and the displacement of the door according to the invention are effected by one and the same drive motor, according to the invention also does not need to be switched between two drive motors. Rather, the change takes place from the pivoting movement to the displacement movement or vice versa by an optional blocking of one or the other output shaft. Since the drive shaft can be driven independently of the blocking of one or the other output shaft, it is possible to run continuously the drive motor regardless of the respective type of movement or regardless of a change in the type of movement. In this way, the change from the pivoting movement to the displacement movement or vice versa is substantially uninterrupted, i. It is achieved a particularly smooth opening or closing movement of the door.

According to the invention, a locking mechanism is provided which selectively allows pivoting or displacement of the door. In this case, the locking mechanism comprises a bearing pin provided on at least one pivoting arm of the pivoting means and a guide slot of the door, in which the bearing pin is selectively rotatable or displaceable.

The locking mechanism thus ensures that the door can either be pivoted or moved. In other words, a separation of the two types of movement of the door is achieved. In addition, the locking mechanism causes a blockage of either the first or the second output shaft. In this way, it is ensured that the power of the drive motor is always transmitted completely to either the pivot means or the shifting means.

Advantageous embodiments of the invention are described in the dependent claims, the description and the drawings.

According to a preferred embodiment, the planetary gear is a differential gear and in particular a planetary gear. In the latter gear, the drive shaft and the output shafts parallel to each other, whereby a particularly compact design of the door drive is achieved.

The configuration and in particular the translation of the planetary gear is advantageously adapted to the forces applied to the movement of the door. If the epicyclic gearing is a planetary gearing, the drive shaft can be connected, for example, to the sun gear of the gearing. Serves the pivoting movement to push a motor vehicle sliding door against a seal to the vehicle body and push away from this, so must be used for pivoting the door usually greater forces than the displacement of the door. In this case, it is appropriate to have the first output shaft, i. the displacement means, with the ring gear and the second output shaft, i. So the pivoting means to connect to the planet carrier of the transmission, as is achieved by the planet carrier a greater translation than by the ring gear.

According to a further embodiment, a coupling between the drive motor and the planetary gear is arranged. By the coupling of the drive motor can be decoupled from the epicyclic gear. This facilitates If necessary, a manual operation, ie pivoting and / or displacement of the door.

The pivot means may comprise at least one pivot arm, one end of which is movably, in particular rotatably and slidably connected to the door and whose other end is connected to the second output shaft. Such a pivot arm is a particularly simple means for pivoting the door and also allows a displacement of the door relative to the pivot arm.

Advantageously, the locking mechanism is designed so that when opening the door first a pivoting and then a displacement of the door takes place and / or when closing the door first a shift and then a pivoting of the door takes place. In the case of a motor vehicle sliding door, therefore, the door initially pivots outward during opening, whereby it is brought into a position which allows a displacement of the door relative to the vehicle body. The complete opening of the door opening is then carried out by the displacement of the door. The closing of the door takes place in the opposite direction.

Preferably, the locking mechanism is formed by the pivot means and a guide of the door, with which the pivot means cooperates. The locking mechanism thus requires no additional components, but is formed by such components, which includes the drive for moving the door anyway. This not only allows a particularly compact design of the door drive, but also leads to even further cost savings.

Preferably, the bearing pin has a non-circular and in particular semicircular cross-section, while the guide slot comprises a circular portion, whose diameter is adapted to a maximum cross-sectional dimension of the journal, and a straight portion whose width is adapted to a minimum cross-sectional dimension of the journal.

If the trunnion is in the circular portion of the guide slot, it can rotate relative to the guide slot, but not move along it, whereas a displacement of the trunnion relative to the guide slot possible, but a rotation is impossible when the trunnion in the straight section the guide track is located.

When the trunnion is in the circular guide track section and is aligned transversely to the straight guide track section, prior pivoting and proper alignment of the trunnion with the straight guide track section is a prerequisite for displacement of the trunnion in the guide track, i. for a displacement of the door relative to the pivot arm. By rotating the journal in the circular guide gate section, the journal can be aligned so that it can enter the straight guide gate section.

Depending on the position of the journal in the guide slot is thus optionally a rotation or displacement of the bearing journal with respect to the guide slot and thereby pivoting or displacement of the door relative to the pivot arm possible.

Advantageously, the bearing pin is arranged in the closed state of the door in the circular portion and aligned transversely to the straight guide portion. In the closed state of the door so only a rotation of the bearing pin relative to the guide slot and thus a pivoting of the pivot arm, i. So ultimately a pivoting of the door, possible. In this way, it is ensured that when opening the door, first a pivoting of the door and only then a shift takes place.

Fig. 1

eine Tür eines Kraftfahrzeugs mit einer ersten Ausführungsform eines erfindungsgemäßen Türantriebs;

Fig. 2

den Türantrieb von Fig. 1;

Fig. 3

einen Querschnitt durch ein Umlaufgetriebe einer zweiten Ausführungsform eines erfindungsgemäßen Türantriebs;

Fig. 4

eine Querschnittsansicht der Kraftfahrzeugtür und des Türantriebs von Fig. 1 im geschlossenen Zustand (durchgezogene Linien) und im offenen Zustand (strichpunktierte Linien); und

Fig. 5

einen Sperrmechanismus des Türantriebs von Fig. 1 in einem Zustand, in dem (a) eine Verschwenkung der Tür und (b) eine Verschiebung der Tür möglich ist.

The invention will now be described purely by way of example with reference to an advantageous embodiment with reference to the drawing. Show it:

Fig. 1

a door of a motor vehicle with a first embodiment of a door drive according to the invention;

Fig. 2

the door drive of Fig. 1 ;

Fig. 3

a cross section through a planetary gear of a second embodiment of a door drive according to the invention;

Fig. 4

a cross-sectional view of the motor vehicle door and the door drive of Fig. 1 in the closed state (solid lines) and in the open state (dash-dotted lines); and

Fig. 5

a locking mechanism of the door drive of Fig. 1 in a state in which (a) a pivoting of the door and (b) a displacement of the door is possible.

In Fig. 1 a sliding door 10 of a motor vehicle is shown, which is both by means of a door drive 12 with respect to a vehicle body, not shown, both pivotable and displaceable.

The door drive 12 is fixedly mounted on the vehicle body and comprises a pivoting arm 14, one end 16 of which is movably mounted in an upper guide 20 extending in the direction of displacement, in the present exemplary embodiment substantially horizontally, extending below the window 18 in the region of a door window 18 in that a bearing pin 19 connected in a rotationally fixed manner to the swivel arm 14 (FIG. Fig. 2 ) engages in a guide slot 21 of the guide 20. The other end of the pivot arm 14 is fixedly connected to an output shaft 64.

Below the pivot arm 14, a support arm 22 is provided approximately at the level of a door threshold, not shown, one end 24 is pivotally connected to the vehicle body and the other end 26 is pivotally and slidably mounted in a guide rail 28. The guide rail 28 is arranged in a lower edge region of the sliding door 10 and extends like the upper guide 20 in the direction of displacement, in the present embodiment, therefore, substantially horizontally.

In the area of the door sill, a slide guide 30 is also attached to the vehicle body, which also has a sliding direction extending main portion 32 and seen in the direction of travel front portion 34 which is angled toward the vehicle interior. In the carriage guide 30, a carriage 36 is guided, which is connected via an angle piece 38 with the sliding door 10.

By guided in the carriage guide 30 carriage 36, mounted in the guide rail 28 support arm 22 and mounted in the guide 20 pivot arm 14, the sliding door 10 is held on the vehicle body.

As in Fig. 1 and 2 is shown, the door operator 12 for moving the sliding door 10 on a cable mechanism comprising a drive roller 40 and a guided around the drive roller cable 42. The cable 42 extends at least in sections along the carriage guide 30 and is fixedly connected to the carriage 36. Upon rotation of the drive roller 40, the cable 42 is moved along the carriage guide 30 and the carriage 36 and thus the sliding door 10 is pulled in the direction of displacement. Instead of the cable mechanism may be provided for moving the sliding door 10, a gear / rack mechanism or a gear / timing belt mechanism.

For actuating the drive roller 40 and the pivot arm 14, a drive motor 44 is provided, for example, an electric motor, which is coupled via a coupling with a drive shaft 46 of a planetary gear 48. The planetary gear 48 is a differential gear and formed in the present embodiment as a planetary gear. The support arm 22 is in the in Fig. 1 and 2 embodiment shown not actively by the drive motor 44 pivotally.

Fig. 3 on the other hand shows a planetary gear 48, in which both the pivot arm 14 and the support arm 22 by the drive motor 44 are actively actuated. At the in Fig. 3 illustrated gear 48, the drive shaft 46 that shaft on which the sun gear 50 of the planetary gear 48 is seated. The sun gear 50 interacts with the ring gear 54 of the planetary gear 48 via a plurality of planet wheels 52. The ring gear 54 drives via a gear 56 to a first output shaft 58, on which the drive roller 40 of the cable mechanism sits.

The planet gears 52 are fixedly connected to a planetary carrier 60 which drives a second output shaft 64 via gears 62 ', 62 ".A gear 66 is attached to the output shaft 64 in the region of an end remote from the planetary gear 48 of the second output shaft 64, which with a Gear 68 of the pivot arm 14 cooperates to cause a rotation of the second output shaft 64, a pivoting of the pivot arm 14 about a pivot axis 70.

Between the gears 66 and 62 ", a further gear 72 is disposed on the second output shaft 64 which cooperates with a gear 74 connected to the carrier arm 74 to cause upon rotation of the second drive shaft 64, a pivoting of the support arm 22 about the pivot axis 70 ,

In Fig. 4 the sliding door 10 and the door drive 12 are shown in different closing or opening positions of the sliding door 10. In this case, the solid lines show the sliding door 10 in a position in which the door opening is completely closed by the sliding door 10.

An intermediate position of the sliding door 10 is shown in thin dashed lines, whereas the bold, dot-dash lines depict an opening end position of the sliding door 10.

In the closed position of the sliding door 10, the carriage 36 is in the front portion 34 of the carriage guide 30, while the bearing pin 19 of the pivot arm 14 is positioned in a rear end portion of the guide 20. The pivot arm 14 is aligned in this position at least approximately parallel to the guide 20.

As in Fig. 5 is to be recognized, the guide slot 21 has a straight portion 76 and a circular portion 78, wherein the bearing pin 19 is disposed in the closed position sliding door 10 in the circular portion 78. The bearing pin 19 has a semicircular cross-section, the maximum extent of which corresponds approximately to the diameter of the circular portion 78 and whose minimum extent corresponds approximately to the width of the straight guide slot portion 76. In the closed position of the sliding door 10, in which the pivot arm 14 is aligned approximately parallel to the guide 20, the semi-circular bearing pin 19 is oriented transversely to the straight guide slot portion 76 ( Fig. 5a ).

To open the sliding door 10, the drive motor 44 is activated and the sun gear of the planetary gear 48 is rotated by the drive shaft 46. Due to the orientation of the journal 19 transversely to the straight guide slot section 76 (FIG. Fig. 5a ) is a translation of the bearing pin 19 along the straight guide slot portion 76 and thus a displacement of the sliding door 10 initially not possible.

As a result, the second output shaft 64 is blocked. The entire force of the drive motor 44 is consequently transmitted via the planet carrier 60 to the second output shaft 64 and the pivot arm 14 is pivoted.

When opening the sliding door 10, the pivot arm 14 pivots by about 90 ° to the outside, in Fig. 4 so clockwise. The pivoting of the pivot arm 14 simultaneously causes a rotation of the bearing pin 19 in the circular guide slot section 78, whereby the bearing pin 19 is aligned with the straight guide slot section 76. Once the flat side 80 of the trunnion 19 is aligned parallel to the walls 82 delimiting the straight guide gate section 76, the trunnion 19 can move into the straight guide track section 76 and along the guide 20, thereby relieving the blockage of the first output shaft 58.

Once the first output shaft 58 is no longer blocked, the force of the drive motor 44 is no longer transmitted to the second output shaft 64, but to the first output shaft 58, since the displacement of the sliding door 10 requires less effort than the pivoting of the sliding door 10th the now taking place displacement of the sliding door 10, the bearing pin 19 moves into the straight guide slot section 76, so that the bearing pin 19 prevented from further rotation relative to the guide 24 and the second output shaft 64 is blocked. The orientation of the bearing pin 19 with the straight guide slot portion 76 thus ultimately causes a deflection of the power flow from the second output shaft 64 to the first output shaft 58 and thus a smooth transition from the pivoting movement to the sliding movement of the sliding door 10th

To close the sliding door 10 again, the drive shaft 46 of the planetary gear 48 need only be driven in the reverse direction of rotation. Since the bearing pin 19 is in the fully open sliding door section 10 in the straight guide slot section 76 ( Fig. 4 ), the second output shaft 64 is blocked and a pivoting of the sliding door 10 at the beginning of the closing movement is not possible. First, therefore, only a shift of the sliding door 10 can take place.

The sliding door 10 is displaced until the journal 19 enters the circular guide slot section 78 from the straight guide track section 76. Once this is the case, further translation of the trunnion 19 is impossible and the first output shaft 58 is blocked. This has the consequence that the force of the drive motor 44 is transmitted to the second output shaft 64 again. As a result, the pivot arm 14 inward, ie in Fig. 4 counterclockwise, pivoted until the sliding door 10 is fully pressed against the vehicle body. Here, the bearing pin 19 is again directed transversely to the straight guide slot section 76 ( Fig. 5a ).

LIST OF REFERENCE NUMBERS

10

sliding door

12

door drive

14

swivel arm

16

The End

18

window

19

pivot

20

guide

21

guide link

22

support arm

24

The End

26

The End

28

guide rail

30

carriage guide

32

main section

34

front section

36

carriage

38

elbow

40

capstan

42

rope

44

drive motor

46

drive shaft

48

epicyclic gear

50

sun

52

planet

54

ring gear

56

gear

58

drive shaft

60

planet carrier

62

gear

64

output shaft

66

gear

68

gear

70

swivel axis

72

gear

74

gear

76

straight section

78

circular section

80

plane side

82

wall

Claims (10)

1. A drive (12) for the moving of a door (10), in particular of a motor vehicle, comprising a drive motor (44) which is connected to a drive shaft (45) of an epicyclic transmission (48); a displacement means (40, 42) to slide the door (10) and connected to a first output shaft (58) of the epicyclic transmission (48); and a pivot means (14) for the pivoting of the door (10) and connected to a second output shaft (64) of the epicyclic transmission (48), wherein a blocking mechanism (14, 19, 20, 21, 76, 78) is provided which selectively permits a pivoting or a sliding of the door (10),
   characterised in that
   the blocking mechanism includes a support spigot (19) provided at at least one pivot arm (14) of the pivot means and a guide track (21) of the door (10) in which the support spigot (19) is selectively rotatable or slidable.
2. A drive (12) in accordance with claim 1, characterised in that the epicyclic transmission (48) is a differential transmission and in particular a planet gear.
3. A drive (12) in accordance with claim 1 or claim 2, characterised in that a coupling is arranged between the drive motor (44) and the epicyclic transmission (48).
4. A drive (12) in accordance with any one of the preceding claims, characterised in that the pivot means includes at least one pivot arm (14) whose one end (16) is movably in particular rotatably and slidably connected to the door (10) and whose other end is connected to the second output shaft (64).
5. A drive (12) in accordance with claim 4, characterised in that the one end (16) of the pivot arm (14) is supported in a guide (20) of the door (10) extending in the direction of sliding.
6. A drive (12) in accordance with any one of the preceding claims, characterised in that the blocking mechanism (14, 19, 20, 21, 76, 78) is made such that, when the door (10) is opened, a pivoting takes place first and then a sliding of the door and/ or, when the door (10) is closed, a sliding takes place first and then a pivoting of the door (10).
7. A drive (12) in accordance with any one of the preceding claims, characterised in that the blocking mechanism is formed by the pivot means (14) and by a guide (20) of the door (10) with which the pivot means (14) cooperates.
8. A drive (12) in accordance with any one of the preceding claims, characterised in that the support spigot (19) has an out-of-round and in particular semi-circular cross-section and the guide track (21) includes a circular section (78), whose diameter is matched to a maximum cross-sectional extent of the support spigot (19), and a straight section (76) whose width is matched to a minimal cross-sectional extent of the support spigot (19).
9. A drive (12) in accordance with claim 8, characterised in that the support spigot (19) is arranged in the circular section (78) and is aligned transversely to the straight guide section (76) in the closed state of the door (10).
10. A drive (12) in accordance with claim 8 or claim 9, characterised in that the support spigot (19) can be aligned with the straight guide section (76) by a pivoting of the pivot arm (14).

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