EP0279236B1 - Rotating actuating device for pivoting doors, especially vehicle doors - Google Patents

Abstract

A rotating drive mechanism for swinging doors, especially on vehicles, with a helical transmission consisting of a stator that is rigidly connected to the housing of the rotating drive mechanism, a rotor that can rotate but cannot move axially and that is rigidly connected to the driveshaft, a coupling component that moves axially to rotate the rotor in relation to the stator, and a pneumatic or hydraulic drive cylinder with a piston rod that is connected to the coupling component. The drive cylinder is an annular cylinder that has an outer and an inner jacket as well as an annular piston between the inner and the outer jacket. The coupling component is a nut that extends into the inner cylinder jacket and surrounds a rotor in the form of a threaded spindle. The rotor extends coaxially through the inside of the inner jacket and is, where it emerges from the housing, in one piece with the stub of the takeoff shaft. The coupling component is non-rotationally connected to an axial positioning mechanism that has rollers that travel in a positioning slot in the stator.

Description

The invention relates to a rotary drive for swinging doors, in particular on vehicles, with a screw gear consisting of a stator rigidly connected to the rotary drive housing, an axially non-displaceable, rotatably mounted rotor which is fixedly connected to the drive shaft, a coupling member which, by axial displacement, the rotation of the Rotor opposite the stator and a coaxial to the rotor arranged pneumatic or hydraulic drive cylinder, the piston rod is connected to the coupling member.

Such a rotary drive is known and described for example in DE-OS 29 19 435.

With the known rotary drive it should be achieved that the overall height can be significantly reduced. In order to achieve this, the piston rod in the known rotary drive is designed as a hollow body, the screw gear being arranged directly on the inside of the hollow body.

The object on which the present invention is based is to design a rotary drive with the features from the preamble of patent claim 1 in such a way that, compared to the known drive, further savings are achieved in terms of overall height, with sufficient guide length for the screw gear being to be retained and There should be a good separation between the pneumatic or hydraulic drive and the screw gear so that there are no sealing problems. Furthermore, it should be possible to accept the full drive torque at one or both ends of the output shaft without changes to the stator, rotor, coupling member and drive cylinder. Finally, it should be possible to carry out a variation of the translation of the screw mechanism in a simple manner.

This object is achieved according to the invention in that a double-acting ring cylinder, comprising parts of the rotor or the output shaft, serves as the drive cylinder, with an inner and an outer cylinder jacket, a cylinder base and a cylinder cover and an annular piston sealingly guided on the outer and inner cylinder jacket, the tubular piston rod is passed between the inner cylinder jacket and the cylinder cover and is connected to the coupling member outside the ring cylinder.

Advantageous developments of the rotary drive according to the invention are described in the subclaims.

A "ring cylinder" in the sense of the invention is understood to mean a drive cylinder whose working space has a circular cross section by being delimited on the outside by an outer cylinder jacket and on the inside by an inner cylinder jacket and the piston being an annular piston which is located between the outside and the inner cylinder jacket is sealingly guided. Both displaceable and rotatable components, namely both parts of the axially displaceable coupling member and parts of the rotatable rotor or the output shaft can then be arranged within the inner cylinder jacket. Since not only the rotor, but also the coupling member can extend far into the drive cylinder in this way, a considerable saving in overall height is achieved. The axial guides arranged outside the drive cylinder, which are preferably designed as roller guides, can be equipped with a variable pitch, which makes it possible to change the transmission ratio in the course of the axial movement.

Due to the special design of the drive cylinder, it is also possible to pass the output shaft through the entire housing of the rotary drive and to lead it out at both ends, so that the output torque can be taken off at both ends of the output shaft. Furthermore, it is possible to design the connection between the piston rod and the coupling member in such a way that the positive coupling between the coupling member and the piston rod takes place only in the axial direction, while a movement of these two components against one another is possible in the radial direction. In particular in embodiments with a two-sided decrease in the output torque Construction tolerances are compensated.

Three exemplary embodiments of the rotary drive according to the invention are explained in more detail below with reference to the accompanying drawings.

• Fig. 1 eine teilweise in axialer Richtung geschnittene Darstellung einer ersten Ausführungsform eines Drehantriebs;
• Fig.la die Form der Nutenführung des Drehantriebs nach Fig. 1;
• Fig. 2 eine Variante der Ausführungsform nach Fig. 1 in analoger Darstellung mit zwei Abtriebswellen;
• Fig. 2a in einer Darstellung analog Fig. 1a die Gestalt der Nutenführung bei der Ausführungsform nach Fig. 2;
• Fig. 3 in einer Darstellung analog Fig. 1 und 2 eine weitere Ausführungsform eines Drehantriebs;
• Fig. 3a in einer Darstellung analog Fig. 1a die Ausgestaltung der Nutenführung bei der Ausführungsform nach Fig. 3.

The drawings show:

• Figure 1 is a partially sectioned view in the axial direction of a first embodiment of a rotary drive.
• Fig.la the shape of the groove guide of the rotary drive according to Fig. 1;
• Fig. 2 shows a variant of the embodiment of Figure 1 in an analog representation with two output shafts.
• 2a in a representation analogous to FIG. 1a, the shape of the groove guide in the embodiment according to FIG. 2;
• Fig. 3 in a representation analogous to Figures 1 and 2, a further embodiment of a rotary drive.
• 3a shows the configuration of the groove guide in the embodiment according to FIG. 3 in a representation analogous to FIG. 1a.

The rotary drive according to FIG. 1, which is intended for swing doors, in particular on vehicles, for example public transport, has a rotary drive housing, which is designated overall by 1. The cylindrical housing has two end covers 1.1 and 1.3 and an annular intermediate flange 1.2 and a cylindrical jacket with grooves 5.2 forming the stator and a cover sleeve 1.4. The outer wall 4.1 in the lower part of the housing is also the outer cylinder jacket of a drive cylinder 4, which is described in more detail below. The entire drive housing is held together by axially guided screw connections 1.5.

The drive cylinder 4 consists of two coaxial cylinder jackets 4.1 and 4.2, the cylinder bottom 1.1 and the cylinder cover 1.2. The piston 4.3 of the cylinder is an annular piston which is guided in a sliding and sealing manner in the space between the outer cylinder jacket 4.1 and the inner cylinder jacket 4.2 and which is connected to a tubular piston rod 4.4 which is guided axially directly along the inner cylinder jacket 4.2. The piston rod 4.4 is sealingly led out of the drive cylinder 4 between the cylinder cover 1.2 and the inner cylinder jacket and connected to a coupling member 3, which in this embodiment is designed as a long nut extending into the interior of the inner cylinder jacket 4.2, which is the one Includes the rotor of a screw gear screw spindle 2, the upper end of which is supported by a ball bearing 2.3 on the rotary drive housing 1 and is integrally connected to an output shaft stub 2.1 guided to the outside.

Furthermore, the coupling member 3 is rotatably connected to a guide device 5 which determines the rotation of the coupling member when the piston 4.3 moves in the axial direction. The guide device 5 has rotatably mounted rollers 5.1 which run in the grooves 5.2 fixedly connected to the rotary drive housing 1. The guide device 5 is arranged on at least two sides of the coupling member 3 in a manner not shown in FIG. 1.

As can be seen from Fig. 1a, the groove guide can consist of two sections, namely a lower section 5.21 and a short upper section 5.22, which run helically with different pitch angles.

• Wird der Antriebszylinder 4 über die Einlaßöffnung 4.5 mit Druckmittel beaufschlagt, so bewegt sich der Kolben 4.1 in axialer Richtung und führt über die Kolbenstange 4.4 das Koppelglied 3 in axialer Richtung mit. Da dieses in die Schraubenspindel 2 eingreift und durch die Führungsvorrichtungen 5 geführt ist, hat dies zur Folge, daß die Schraubenspindel 2 und damit der Abtriebswellenstummel 2.1 in Drehung versetzt werden. Im letzten Abschnitt der Bewegung, wenn die Rolle 5.1 in den Teil 5.22 der Nutenführung 5.2 gerät, ändert sich das Verhältnis der Steigungswinkel, was zu einer Änderung des Übersetzungsverhältnisses des Schraubgetriebes im letzten Abschnitt der Bewegung führt.

The operation of the rotary drive shown in Fig. 1 is as follows:

• If the drive cylinder 4 is pressurized via the inlet opening 4.5, the piston 4.1 moves in the axial direction and carries the coupling member 3 in the axial direction via the piston rod 4.4. Since this engages in the screw spindle 2 and is guided by the guide devices 5, this has the consequence that the screw spindle 2 and thus the output shaft stub 2.1 are rotated. In the last section of the movement, when the roller 5.1 gets into the part 5.22 of the groove guide 5.2, the ratio of the pitch angle changes, which leads to a change in the gear ratio of the screw mechanism in the last section of the movement.

During the counter movement, pressure medium is supplied to the drive cylinder 4 via the inlet 4.6.

2 and 2a, a variant of the embodiment according to FIG. 1 is shown, which differs from the embodiment described above only in that two output shaft stubs 2.1 and 2.2 are present, the lower output shaft stub 2.2 via a ₁ - :; ger 2.4 is mounted in the rotary drive housing 1, while the upper output shaft stub 2.1 is mounted on a ball bearing 2.5. Furthermore, in this embodiment, the positive coupling between the piston rod 4.4 and the coupling member 3 takes place only in the axial direction. For this purpose, the piston rod 4.4 has an inwardly directed collar 4.41, which engages in an annular groove 3.1 on the outside of the coupling member 3, the inner diameter of the collar 4.41 being larger than the diameter of the annular groove 3.1, so that here a mutual displacement is possible in the radial direction. In this way it is achieved that structural tolerances in the radial direction cannot lead to an obstruction of the movement of the piston 4.3.

Otherwise, the design and mode of operation are exactly the same as in the embodiment according to FIG. 1 and the same reference numbers are also given for the same components.

A somewhat different embodiment of a rotary drive is shown in FIGS. 3 and 3a.

The rotary drive housing 6 has two end covers 6.1 and 6.3 on the two end faces and in the middle an annular intermediate flange 6.2 and a cylindrical jacket with grooves 8.4 forming the stator, which ends with the intermediate flange 6.2. The jacket is covered with a sleeve 6.4. The lower part between the end cover 6.1 and the intermediate flange 6.2 forms a hollow cylinder 9.1, which belongs to the drive cylinder 9 described below. The housing is in turn held together by screw connections 6.5.

The drive cylinder 9 consists of the outer cylinder jacket 9.1 and an inner cylinder jacket 9.2, the cylinder base 6.1 and the cylinder cover 6.6. In the space between the two cylinder jackets 9.1 and 9.2, the annular piston 9.3 is sealingly guided, the tubular piston rod 9.4 of which encompasses the inner cylinder jacket 9.2 and is sealingly guided out of the drive cylinder 9 on the cylinder cover. A coupling member 8 is attached to the end of the piston rod 9.4 that carries a pair of rollers 8.1-8.2 on two opposite sides. The coaxially arranged rollers 8.1 and 8.2 each run in groove guides 8.3 and 8.4. The groove guide 8.3 is located in a rotor 7.4, which is connected in a rotationally fixed manner to a shaft 7.3, which is guided coaxially through the rotary drive housing 6 and through the interior of the inner cylinder jacket 9.2. The ends of the shaft 7.3 are in one piece with the output shaft stubs 7.1 and out of the housing. 7.2 connected. The roller 8.2 of the coupling member 8 is guided in a second slot guide 8.4 of the stator, which is firmly connected to the end cover 6.3 and thus to the rotary drive housing 6. The slot guides 8.3 and 8.4 are helical with an opposite pitch angle. This is indicated in Fig. 3a.

The rotor 7.4 is rotatably mounted on the intermediate flange 6.2 via a ball bearing 7.5.

In the last part 8.42, the groove guide 8.4 has a slightly different slope than the part 8.41, which leads to a change in the gear ratio.

• Bei einer Zuführung von Druckmittel über den Einlaß 9.5 zum Antriebszylinder 9 bewegt sich der Kolben 9.3 im Raum zwischen den beiden Zylindermänteln 9.1 und 9.2 abwärts und dadurch werden über das Koppelglied 8 die beiden Rollen 8.1 und 8.2 in axialer Richtung mitgeführt. Die Bewegung der Rollen 8.1 und 8.2 in den Nutenführungen 8.3 und 8.4 ergibt infolge der gegensinnigen Steigung dieser Nuten eine Verdrehung des Rotors 7.4 gegenüber dem Stator bzw. dem Drehantriebsgehäuse 6. Die Welle 7.3 und mit ihm die Abtriebswellenstummel 7.1 und 7.2 werden verdreht. Das Übersetzungsverhältnis ist durch die Steigung der Nutenführungen 8.3 und 8.4 festgelegt, wobei im letzten Teil der Bewegungsbahn eine Änderung des Übersetzungsverhältnisses auftritt.
• Eine Umkehrung der Bewegungsrichtung wird durch Zuführung von Druckmittel zum Einlaß 9.6 erreicht.

The operating principle of the rotary drive according to FIG. 3 is as follows:

• When pressure medium is supplied via the inlet 9.5 to the drive cylinder 9, the piston 9.3 moves downward in the space between the two cylinder jackets 9.1 and 9.2 and as a result the two rollers 8.1 and 8.2 are carried along in the axial direction via the coupling member 8. The movement of the rollers 8.1 and 8.2 in the groove guides 8.3 and 8.4 results in a rotation of the rotor 7.4 with respect to the stator or the rotary drive housing 6 due to the opposite slope of these grooves. The shaft 7.3 and with it the output shaft stubs 7.1 and 7.2 are rotated. The transmission ratio is determined by the slope of the groove guides 8.3 and 8.4, with a change in the transmission ratio occurring in the last part of the movement path.
• The direction of movement is reversed by supplying pressure medium to the inlet 9.6.

Claims (9)

1. Rotating actuating device for pivoting doors, especially vehicle doors, with a helical gear unit, consisting of a stator rigidly connected to the rotating-actuating-device housing (1 and 6), of an axially undisplaceably, rotatably held rotor (2 and 7.3-7.4) rigidly connected to the output shaft (2.1-2.2 and 7.1-7.2), of a coupling link (3 and 8) - said coupling link affecting, by axial displacement, the rotation of the rotor in relation to the stator - and of a pneumatic or hydraulic actuating cylinder (4 and 9) disposed coaxially with respect to the rotor, the piston rod (4.4 and 9.4) of said actuating cylinder being connected to the coupling link, characterized in that the actuating cylinder is a double-acting annular cylinder embracing parts of the rotor (2) or of the output shaft (7.3), with an internal and an external cylinder jacket (4.1, 4.2 and 9.1, 9.2), a cylinder base (1.1 and 6.1) and a cylinder cover (1.2 and 6.2) and with an annular piston (4.3 and 9.3) sealingly guided on the external and internal cylinder jacket, the tube- shaped piston rod (4.4 and 9.4) of said annular piston passing between the internal cylinder jacket (4.2 and 9.2) and the cylinder cover (1.2 and 6.2) and being connected outside the annular cylinder to the coupling link (3 and 8).

2. Rotating actuating device according to claim 1, characterized in that the external cylinder jacket (4.1 and 9.1) forms a part of the rotating-actuating-device housing.

3. Rotating actuating device according to claim 2, characterized in that the output shaft (2.1-2.2 and 7.1-7.2) connected to the rotor (2 and 7.3-7.4) emerges at both end covers of the rotating-actuating-device housing.

4. Rotating actuating device according to any one of claims 1 to 3, characterized in that the piston rod (4.4) is positively coupled to the coupling link (5) merely in the axial direction.

5. Rotating actuating device according to any one of claims 1 to 4, characterized in that the rotor is a screw spindle (2) connected in one piece to the output shaft (2.1, 2.2) and in that the coupling link is in the form of an associated screw nut (3), with screw spindle and screw nut being embraced at least partially by the internal cylinder bracket (4.2) and with the screw nut (3) being axially guided in a guiding device (5) disposed outside the annular cylinder (4.1; 4.2).

6. Rotating actuating device according to claim 5 characterized in that the guiding device (5) comprises rotatably held rollers (5.1), said rollers running in grooves (5.2) rigidly connected to the rotating-actuating-device housing (1.2-1.3).

7. Rotating actuating device according to any one of claims 1 to 4, characterized in that the output shaft (7.3) is guided by the internal cylinder jacket (9.2), in that the rotor (7.4) is rigidly connected to the output shaft (7.1-7.3-7.2) and comprises a first groove guide (8.3) and in that axially movable roller pairs (8.1, 8.2) are rotatably held on the coupling link

(8), with, in each case, one roller (8.1) running in the first groove guide (8.3), while the second roller (8.2) runs in a second groove guide (8.4) rigidly connected to the rotating-actuating-device housing (6.2, 6.3) and the two groove guides (8.3, 8.4) each have different helix angles.

8. Rotating actuating device according to claims 6 or 7, characterized in that the helix angles of the groove guides are variable in order to vary the transmission ratio of the helical gear unit during the axial motion of the coupling link.

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