DE102013100002B4 - Drive device for a gullwing door of a bus - Google Patents

Abstract

The invention relates to a drive device (1) for at least one wing door (6a, 6b) of a bus. According to the invention, the movement of the wing door (6a, 6b) in a longitudinal direction x and a movement of the wing door (6a, 6b) in a transverse direction y are effected by means of a single actuator (3a). For this purpose, the movements mentioned are mechanically coupled to one another in a partial stroke of the longitudinal stroke of the actuator.

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a drive device for at least one wing door of a vehicle, in particular a bus.

STATE OF THE ART

Buses have entry-level openings for the driver and passengers, in which a door frame is closed by one or two counter-opening and closing folding door (s). From a sealed closed position of the gullwing doors, in which the hinged door is arranged flush with an outer skin of the bus, the hinged door is first moved transversely to the longitudinal axis of the bus to be moved thereafter parallel to the longitudinal axis of the bus, in which case the gullwing outside can be passed on the outer skin of the bus until an open position of the wing door is reached, in which the door frame is released. For the generation of the transverse movement on the one hand and the longitudinal movement on the other hand usually separate actuators are used. It is also known that the transverse movement is caused by the rotation of a rotary column with this held and pivoted to the rotary armature swingarm, which is coupled via a guide unit with an associated wing door. It is also possible to generate the transverse movement by an electric spindle drive with a supplementary use of a pneumatic actuator. Furthermore, a coupling of the movement of two wing doors of the bus via a cable is known. Finally, drive devices are known in which via a single actuator and coupled to this rotary column, a pure pivoting of an associated hinged door.

Prior art relating to fluidic drive devices for gullwing doors of a vehicle are in particular the patent applications DE 10 2012 107 527 A1 . DE 10 2012 103 638 A1 . DE 10 2011 001 003 A1 . DE 10 2010 002 625 A1 . DE 10 2008 011 315 A1 and DE 10 2006 031 477 A1 as well as the DE 10 2008 034 994 B3 Applicant can be seen in which in particular measures relating to a cushioning for the actuating movement, constructive embodiments of fluidic actuators, sensor devices for detecting a travel of the actuators, fluidic circuits for controlling the actuation of the actuators, manual override devices and valves for manual emergency opening of the wing doors and security measures are disclosed for a closed position of the gullwing doors.

DE 24 27 334 A1 discloses a swing-sliding door for a railroad car or a bus. A front edge of the swing-sliding door is guided over a roller in a vehicle-fixed backdrop. For a partial lift, in which the swing-sliding door is moved only parallel to the vehicle longitudinal axis, the scenery is rectilinear. By contrast, the scenery in the partial stroke, in which the pivot sliding door is closed and moved transversely to the vehicle longitudinal axis, curved in the direction of the vehicle interior. The movement of the swing-sliding door along the gate is permanently mechanically coupled to a pair of pivot arms, which hold a parallel to the vehicle longitudinal axis and oriented by the pivoting of the pivot arms transversely to the vehicle longitudinal axis moving T-beam. On the T-beam, a roller is held, which can roll along a guide rail extending at the top of the swing-sliding door. For closed swing-sliding door, this role is in the rear edge of the swing-sliding door. With the opening of the swing-sliding door, the leading edge of the swing-sliding door moves along the curved portion of the gate, which also has the consequence that the roller with the trailing edge moves transversely to the vehicle longitudinal axis as a result of the coupling via the pivot arms. Following this, both the roller held on the front edge of the pivoting sliding door roll along the rectilinear part of the slide as well as the roller arranged in the closed state in the region of the rear edge of the pivoting sliding door along the guide rail, so that this role in the direction of the front edge of the Swing-sliding door moves. Since in the course of this movement the support distance of the two rollers is reduced with a concomitant reduced support function, a supplementary support of the swing-sliding door is required.

OBJECT OF THE INVENTION

• – eines aktuatorischen Aufwands,
• – einer Koordination einer Bewegung der Flügeltür in Längsrichtung und Querrichtung,
• – einer Verriegelung einer eingenommenen Betriebsstellung der Flügeltüren,
• – eines gemeinsamen Antriebs von zwei Flügeltüren,
• – einer Ermöglichung einer Einzeltürsteuerung und/oder einer Doppeltürsteuerung,
• – einer Gewährleistung einer synchronen Bewegung der Flügeltüren,
• – eines rotatorischen Antriebs einer Drehsäule,
• – einer Ausbildung des fluidischen Aktuators und/oder
• – einer manuellen Notbetätigung

verbessert ist.The present invention has for its object to provide a drive device for folding doors of a bus, which in particular with regard to

• - an actuarial effort,
• A coordination of a movement of the hinged door in the longitudinal and transverse directions,
• A locking of a assumed operating position of the gullwing doors,
• - a common drive of two double doors,
• An enabling of a single door control and / or a double door control,
• - ensuring a synchronous movement of the gullwing doors,
• A rotary drive of a rotary column,
• - An embodiment of the fluidic actuator and / or
• - a manual emergency operation

is improved.

SOLUTION

The object of the invention is achieved with the features of the independent claim. Further preferred embodiments according to the invention can be found in the dependent claims.

DESCRIPTION OF THE INVENTION

The invention proposes a drive device for at least one hinged door, in particular a pair of gullwing doors, of a vehicle such as a bus. In the drive device, an actuator is used. By means of the actuator, a movement of at least one wing door in a longitudinal direction over a longitudinal stroke can be brought about. This movement in the longitudinal direction is used for the actual opening movement, so that in the case of the use of two hinged doors correlates with a movement of the wing doors away from each other or towards each other.

According to the invention, an additional actuator is not used to bring about the required additional movement of the at least one wing door in the transverse direction. Rather, the movement of at least one hinged door in a longitudinal direction over the longitudinal stroke (and thus also the movement of the actuator) is mechanically coupled to the movement of the at least one hinged door in a transverse direction. This transverse movement is primarily used to attach or remove the hinged door from the vehicle frame, door frame or gasket. According to the invention thus finds one and the same actuator use both for the generation of the movement in the longitudinal direction and the movement in the transverse direction.

In the context of the invention, the longitudinal direction and the transverse direction are understood to mean not only a pure movement in the mentioned directions, but also any other movement which has an essential component in said direction. Thus, for example, bringing about the movement in the transverse direction by the pivoting of a rocker with the movement of a pivot point for the hinged door on a circular arc, which is primarily oriented in the transverse direction, take place.

• a) In dem genannten Teilhub erfolgt veranlasst durch den Aktuator sowohl die Bewegung der Flügeltür über eine geeignete Halteeinrichtung zwischen Aktuator und Flügeltür in eine Längsrichtung als auch in eine Querrichtung, womit sich eine unter Umständen komplexe Bewegungsform der Flügeltür ergeben kann.
• b) Außerhalb des genannten Teilhubs erfolgt keine wesentliche Bewegung in Querrichtung. Vielmehr ist außerhalb des genannten Teilhubs die Bewegung der Flügeltür durch die Bewegung in Längsrichtung geprägt.

According to the invention, the movement in the longitudinal direction is mechanically coupled only in a partial stroke of the longitudinal stroke with the movement in the transverse direction, so that two different phases of movement are to be distinguished:

• a) In said partial stroke is caused by the actuator both the movement of the hinged door via a suitable holding device between the actuator and gullwing in a longitudinal direction and in a transverse direction, which may result in a possibly complex movement of the gullwing door.
• b) Outside the said sub-stroke no significant movement takes place in the transverse direction. Rather, the movement of the hinged door is characterized by the movement in the longitudinal direction outside of said sub-stroke.

The two mentioned forms of movement correlate on the one hand with the movement of the hinged door in the direction of the door frame or away from it (see a)) (possibly also with a superimposed longitudinal movement) and on the other hand with the pure opening or closing movement of the wing doors towards each other or away from each other (see b)).

There are many possibilities for the type of coupling of the movements in the two forms of movement. To name just one example, the needs-based coupling of movements only in the partial stroke via a drive mechanism, a linkage, a gear o. Ä. Take place, the decoupling outside of the sub-hub via a game, a loose, a telescopic outside of the sub-stroke Drive connection, an effective outside the sub-stroke slot, a motion-controlled switching element or even an electrically or electropneumatically controlled and switchable coupling element takes place.

There are many possibilities for the actuator design. While according to the prior art fluidic actuators often find use in which a fluidly acted on both sides actuating piston forms a spindle nut of a spindle drive or in which a cylinder housing is held on the vehicle frame, while in the cylinder housing a movable actuator piston drives an actuating plunger, the invention proposes in particular Design before that a cylinder housing of the actuator is moved with the movement of the hinged door. This represents a reversal of the principle of action of various fluidic actuators used in the prior art in which the actuating piston is moved relative to the stationary cylinder housing. For this embodiment of the invention, a separating body or separating piston which is not moved with the actuation of the actuator is used. In this case, the movement of the cylinder housing on the one hand with a holding device for the hinged door and on the other hand with the other kinematics for Generation of movement of the hinged door in the transverse direction coupled in said partial stroke.

In a further embodiment of the invention, the drive device has a holding device on which a hinged door can be held. By means of a longitudinal guide device are / is the cylinder housing and / or the holding device guided with respect to the movement in the longitudinal direction. In order to ensure the degree of freedom in the transverse direction, the longitudinal guide device is supported by support means. The support means are guided movable in the transverse direction. By means of the actuator are / a movement of the holding device and / or the cylinder housing along the longitudinal guide device in the longitudinal direction over the longitudinal stroke can be brought about. Only in the partial stroke of the longitudinal stroke is the movement in the longitudinal direction coupled with the movement of the support device in the transverse direction.

For a particular proposal of the invention, the coupling of the movement of the holding device and / or the cylinder housing with the movement of the support device via an arbitrarily designed driver unit. This driver unit mechanically couples the holding device and / or the cylinder housing with the support device only for the partial stroke.

To allow, for example, an adjustment of the partial lift to different installation conditions or to different manufacturing tolerances, the invention proposes in a further embodiment, that the position of the driver unit and thus the size of the partial stroke is adjustable. This setting can be made in steps or steplessly.

Also for the design of the support means there are many possibilities, provided that they have the degree of freedom of movement in the transverse direction. For a proposal of the invention, the support means are designed as support carriages, which are guided by a transverse guide device in the transverse direction.

For a particularly simple embodiment of the invention, the transverse guide device is formed with a guide rail or guide rod. For example, the support carriage may have a recess or bore through which the guide rail or guide rod extends. The support carriage can then be slidably moved along the guide rail or guide rod.

As mentioned above, there are many possibilities for coupling the movements in the longitudinal direction and in the transverse direction. For a proposal according to the invention, the support means are supported via a toggle mechanism on a support device. A coupling of the movement of the holding device and / or the cylinder housing in the longitudinal direction with the movement of the support means in the transverse direction then takes place via the toggle mechanism. It has been found that such a toggle mechanism can be advantageous in terms of power development. In the following, a possible, not limiting the invention advantageous design of such a toggle mechanism is explained: If, for example, the toggle mechanism in the closed position close to the extended position, with large forces applied to the toggle mechanism forces large closing forces can be generated, creating a tight and tight application of the hinged door is guaranteed to a door frame and a seal carried by it. Also can then be secured with small holding forces, the closed position of the hinged door. On the other hand, for a knee angle away from the extended position, a change Δα of the knee angle results in a change in the distance Δx _{1 of} the two opposite end portions of the toggle, while near the extended position the same change in the knee angle Δα to another change in the distance Δx ₂ of said end points Toggle leads. By choosing the traversed during the coupling sub-knee knee angle of the toggle mechanism thus a movement characteristic of the hinged door can be specified, whereby a change in the speed of movement of the movement in the transverse direction over the partial stroke can be selectively brought about.

There are many possibilities for generating the change in the knee angle of the toggle mechanism. For a proposal according to the invention, a coupling rod is articulated to a toggle of the toggle mechanism or to the knee joint, which is coupled in the partial stroke on the driver unit with the holding device or the cylinder housing. Thus, in the partial stroke with the coupling of the movements in the longitudinal and transverse directions of the flow of force from the actuator via the cylinder housing or the holding device, the coupling rod and the toggle mechanism to the support means, in particular the support carriage.

In addition to the connection of the hinged door via the holding device to the cylinder housing, a further holding device can be used to hold the hinged door at least at two points or in two areas. Here, the connection between a holding device and the gullwing door can be rigid, elastic, via a joint or a coupling device, in order to allow a relative movement or pivoting in the connection region allow or also to bring about a complex kinematics of the gullwing door.

For one embodiment of the invention, the movement of the support means, the guide carriage and / or the toggle mechanism via a rotary column with the movement of a second holding device, on which the hinged door is held in addition to the first-mentioned holding device coupled. This coupling can be done arbitrarily. For an embodiment of the invention, the rotary column is coupled to the pivoting column (and rotated therewith) via a pivoting arm and a coupling rod with the movement of the support device, the guide carriage or the toggle mechanism. For this purpose, an end portion of the coupling rod is hinged to the rocker, while another end portion of the coupling rod is articulated to the toggle mechanism, the guide carriage or the support means.

While in principle any actuator (in particular also an electrically actuated actuator) can be used within the scope of the invention, a fluidically actuated actuator is preferably used. This may be a pneumatic or a hydraulic actuator.

For a particular embodiment of the drive device according to the invention this has a movable cylinder housing. A longitudinal guide device extends between two support devices. The cylinder housing is guided relative to the longitudinal guide device. A separator carried by the longitudinal guide means (which may be formed separately from or integral with the longitudinal guide means) separates two pressure chambers formed in the cylinder housing. Channels are provided, via which the pressure chambers can be acted upon by the fluid. The cylinder housing form piston surfaces for this embodiment.

It is entirely possible in the context of the present invention for the channels to be formed outside the components mentioned or at least partially in one of the components mentioned. For a particular proposal of the invention, the channels are at least partially formed in the longitudinal guide means, so that this longitudinal guide device is designed to be multifunctional.

It is further possible within the scope of the invention that the pressure chambers are decoupled from each other, so that the fluidic loading of the pressure chambers in addition to the targeted pressure change by the fluidic control circuit can only change by a largely to be reduced by suitable sealing elements leakage. In one embodiment of the invention, the pressure chambers are coupled to each other via at least one throttle or at least one check valve. On the one hand, a manual change of the operating position of the hinged door may be effected via this coupling under certain circumstances even without actuation of the fluidic control circuit by applying hand forces to the hinged door and thus the cylinder housing, which ultimately have the consequence that fluid from a pressure chamber via the throttle or the Check valve is led to the other pressure chamber, which then a (slow) manual door opening is possible. Alternatively or cumulatively, the coupling of the pressure chambers via the throttle or the check valve can be used to compensate for any leakage. If, for example, the drive device reaches an end stop, the targeted pressure equalization via the throttle or the check valve can be brought about in the area of the end stop. Preferably, according to the invention, two non-return valves opening in different directions are interposed between the pressure chambers. For a compact design, the throttles or check valves may also be integrated in the separating body.

It is entirely within the scope of the present invention that the support device maintains a once activated and occupied operating position by fluidic backup, which is particularly the case when forming the actuator as a hydraulic actuator. If an alternative or additional securing of an operating position is desired, the invention proposes that at least one support device can be locked or locked in the transverse direction via a latching or locking device. (Alternatively or cumulatively, it is also possible for a latching or locking device to perform a locking or detenting in the longitudinal direction, for example of the cylinder housing relative to the longitudinal guide device.)

It is also possible that the support means in the transverse direction have no "preferred position". According to a particular embodiment of the invention, however, the support means are supported via a spring element on a support means, wherein the spring element is acted upon by a movement of the support means in the transverse direction. For example, the spring element can act on the support device away from the door frame, with the result that in a short circuit of the pressure chambers via a bypass line, in particular after actuation of a manual emergency valve, the spring element, the support device (and thus the hinged door) moves away from the door frame, which then a further opening of the hinged door by movement in the longitudinal direction is made possible for a Handnotöffnung.

In principle, it is possible that the drive device has only the explained degree of freedom in the transverse direction and in the longitudinal direction. This is particularly advantageous if only a double door control is desired. In a further embodiment of the invention, in particular for enabling a single door control, the invention proposes that the transverse guide device is supported with at least one degree of freedom relative to a support device. A movement along this degree of freedom then results in a change in the orientation of the longitudinal guide device. This is used in particular if only a hinged door is to be opened. In this case, the oblique position of the longitudinal guide device, which per se does not lead to an opening of the hinged door takes place. Upon actuation of an actuator of a hinged door, the movement of the holding device then takes place along the oblique longitudinal guide device, whereby it can be removed from the door frame and guided past the outer skin of the bus.

For an embodiment of the invention, two hinged doors can be opened and closed synchronously by means of the drive device, this synchronous movement comprising both the movement in the longitudinal direction and the movement in the transverse direction synchronously. Here, the coupling of the movement of the wing doors preferably takes place fluidically, for example by the fluidic actuators for the two wing doors are arranged in fluidic series connection, in which case an actuator acts as a master cylinder, while the other actuator acts as a slave cylinder.

In a particular embodiment, two gullwing doors can be opened and closed synchronously by means of the drive device, or only one gullwing door can be opened or closed while the other gullwing door remains closed or opened.

Advantageous developments of the invention will become apparent from the claims, the description and the drawings. The advantages of features and of combinations of several features mentioned in the description are merely exemplary and can take effect alternatively or cumulatively, without the advantages having to be achieved by embodiments according to the invention. Without thereby altering the subject matter of the appended claims, as regards the disclosure of the original application documents and the patent, further features can be found in the drawings, in particular the illustrated geometries and the relative dimensions of several components and their relative arrangement and operative connection. The combination of features of different embodiments of the invention or of features of different claims is also possible deviating from the chosen relationships of the claims and is hereby stimulated. This also applies to those features which are shown in separate drawings or are mentioned in their description. These features can also be combined with features of different claims. Likewise, in the claims listed features for further embodiments of the invention can be omitted.

BRIEF DESCRIPTION OF THE FIGURES

In the following the invention will be further explained and described with reference to preferred embodiments shown in the figures.

1 shows a highly schematic drive device for two wing doors of a bus with the fluidic control circuit.

2 shows very schematically the drive device for folding doors according to 1 with an alternative embodiment of the fluidic control circuit.

3 shows in a spatial representation obliquely from above a suspension with drive means for two wing doors, the wing doors are here in an open position.

4 shows in a perspective view obliquely from above the suspension with drive device for two wing doors according to 3 , here are the gullwing doors in a partially closed position.

5 shows in a perspective view obliquely from above the suspension with drive device for two wing doors according to 3 and 4 , here are the gullwing doors in a closed position.

6 shows a horizontal section through parts of the suspension and drive device for two wing doors according to 3 to 5 ,

7 shows a detail VII of the horizontal section according to 6 ,

8th shows a detail VIII of the horizontal section according to 6 ,

9 shows a detail of the suspension with drive device for two wing doors in a spatial representation obliquely from below, in which case the drive device and suspension are shown in an operating position in which the gullwing doors have a maximum distance in the transverse direction of a door frame.

10 shows a detail of the suspension with drive device for two wing doors in a spatial representation obliquely from below, here the drive device and suspension are shown in an operating position in which the wing doors are applied to the door frame, whereby a closed position is reached.

11 shows in a detailed spatial view obliquely from above the suspension and drive device in a partially disassembled state.

12 shows in a detailed spatial view obliquely from above the suspension and drive device in a partially disassembled state.

13 shows a detail of the drive device and suspension when looking in the transverse direction of the vehicle to the outside.

14 shows a section XIV-XIV according to 13 by the drive device and suspension.

15 shows in a spatial detail view obliquely from below a drive device with a holding device for the folding doors.

16 shows a spatial view obliquely from below a drive device with the holding devices for the folding doors.

17 shows a highly schematic drive device for folding doors with an alternative embodiment of the fluidic control circuit.

DESCRIPTION OF THE FIGURES

1 shows a highly schematic drive means 1 with fluidic control circuit 2 for actuating the drive device 1 , Here is the control circuit 2 designed in particular as a pneumatic or hydraulic control circuit.

The drive device 1 is formed with two actuators 3a . 3b , The fluidic loading of the actuators 3a . 3b has opening and closing movements 4a . 4b (and corresponding opening and closing forces) of cylinder housings 8a . 8b the actuators 3a . 3b result in which over 1 strongly schematically illustrated holding devices 5a . 5b each to an associated hinged door 6a . 6b (in 1 not shown). In this case, the opening and closing movements take place 4a . 4b in opposite directions, in order to open the two hinged doors 6a . 6b away from each other and for a closing movement the two double doors 6a . 6b to move towards each other. The movement of the cylinder housing 8a . 8b the actuators 3a . 3b takes place in a longitudinal direction of the vehicle, which is marked in the figure with "x".

The following is the structure and operation based on the actuator 3a explained, wherein for the actuator 3b the corresponding applies. The actuator 3a is as a double-acting cylinder unit 7a educated. The cylinder unit 7a owns the cylinder housing 8a which has an interior 9a has. The cylinder housing 8a is in the two end areas via sealing and guide units 9a . 10a opposite a longitudinal guide device 11a , which here as a guide tube 12a is formed, guided under seal in the direction x. An interior 13a of the cylinder housing 8a is through one of the guide tube 12a carried piston-like separator 24a divided into two pressure chambers 14a . 15a , The cylinder housing 8th forms end opposite piston surfaces 16a . 17a out, which each have a pressure chamber 14a . 15a assigned. By generating a pressure difference in the pressure chambers 14a . 15a can different pressure forces on the piston surfaces 16a . 17a be brought about, the resultant results in an opening or closing force. Outside the range of movement of the cylinder housing 8a opposite the guide tube 12a owns the guide tube 12a connections 18a . 19a , These connections 18a . 19a are each via channels 20a . 21a the longitudinal guide device 11a , in particular in the interior of the guide tube 12a , with an associated pressure chamber 14a . 15a connected. In addition, the two pressure chambers are an optional feature 14a . 15a coupled together via throttle valves or two mutually parallel, acting in different directions check valves 22a . 23a ,

• – der während der Stellbewegung der Aktuatoren 3a, 3b nicht bewegten Längsführungseinrichtung 11a, 11b und dem ebenfalls nicht mitbewegten Trennkörper 24, welcher einen ruhenden Trennkolben zwischen den beiden Druckräumen 14, 15 bildet, sowie
• – den während der Stellbewegung bewegten Zylindergehäusen 8a, 8b.

The actuators 3a . 3b are thus each formed with

• - During the adjustment movement of the actuators 3a . 3b non-moving longitudinal guide device 11a . 11b and also not moved along separating body 24 , which a stationary separating piston between the two pressure chambers 14 . 15 forms as well
• - The moving during the adjusting cylinder housings 8a . 8b ,

The fluidic control circuit 2 has a pump 25 , The pump 25 is driven by a drive unit 26 in which it is the drive unit of the vehicle or a separate for the operation of the control circuit 2 competent drive unit, for example. An electrically operated pump, can act. The pump 25 is designed for example as a pump with switchable conveying direction and controllable or adjustable output pressure and / or flow rate. By doing control circuit 2 is a primary page 27 the pump 25 with the connection 18a of the actuator 3a connected. The connection 19a of the actuator 3a is a preferably electrically controllable valve, here a 3/2-way solenoid valve 28 (in 1 in a passage position) connected to the port 18b of the actuator 3b , The connection 19b of the actuator 3b is connected to the secondary side 29 the pump 25 , For a changeover of the conveying direction of the pump 25 the secondary side of the pump becomes the primary side (and vice versa).

1 shows the 3/2-way solenoid valve 28 in a passage position in which this the connections 19a . 18b connects with each other. A bypass line 30 in which a manually operated emergency valve 31 is arranged, connects directly in parallel with the pump 25 the primary side 27 with the secondary side 29 when the emergency valve 31 is open. The bypass line 30 has a branch 32 which is between the emergency valve 31 and the primary side 27 is arranged. The branch 32 is with a connection of the 3/2-way solenoid valve 28 connected, which in the in 1 ineffective bypass position of the 3/2-way solenoid valve 28 with the connection 18b of the actuator 3b is connected while in this switch position of the connection 19a via the 3/2-way solenoid valve 28 is locked.

• a) Ohne Betrieb der Pumpe 25 und für geschlossenes Handnotventil 31 erfolgt eine fluidische Sicherung einer eingenommenen Position der Aktuatoren 3a, 3b und damit der Flügeltüren 6a, 6b. (Im Folgenden wird noch erläutert, dass auch eine zusätzliche Sicherung durch eine Rast- oder Sperreinrichtung erfolgen kann.) Ohne die Rückschlagventile 22a, 23a kann (unter Vernachlässigung einer Leckage) auf diese Weise eine fluidische Fixierung der Flügeltüren 6a, 6b erfolgen. Hingegen wird mittels der Rückschlagventile 22, 23 bei Ausübung von insbesondere manuellen Kräften auf die Flügeltüren 6a, 6b eine Öffnungs- oder Schließbewegung grundsätzlich ermöglicht. Die Öffnungs- oder Schließbewegung bzw. die für die Veranlassung derselben erforderliche manuellen Kräfte werden vorgegeben durch die Drosselcharakteristik der Rückschlagventile 22, 23. Alternativ oder kumulativ möglich ist, dass mittels der Rückschlagventile 22a, 23a ein fluidischer Ausgleich von Leckageströmen, bspw. im Bereich einer Endlage, erfolgen kann.
• b) Erfolgt eine Förderung des Fluids von der Sekundärseite 29 durch die Pumpe 25 zur Primärseite 27, erfolgt eine Erhöhung des Drucks in dem Druckraum 14 des Aktuators 3a. Diese Erhöhung des Drucks hat an der Kolbenfläche 16a eine Druckkraft zur Folge, welche bestrebt ist, das Zylindergehäuse 8a in 1 nach links zu bewegen. Diese Beaufschlagung des Zylindergehäuses 8a nach links hat wiederum zur Folge, dass auch der Druck in dem Druckraum 15a ansteigt. Der Aktuator 3a wirkt in diesem Fall als eine Art ”Geberzylinder”, da angesichts der Beaufschlagung des Zylindergehäuses 8a in 1 nach links auch der Druck in dem Druckraum 15a ansteigt. Dieser ansteigende Druck in dem Druckraum 15a wird über den Kanal 21a, den Anschluss 19a, das 3/2-Wege-Magnetventil 28 in seiner Durchlassstellung, den Anschluss 18b, den Kanal 20b zu dem Druckraum 14b des Aktuators 3b übertragen, welcher somit als eine Art ”Nehmerzylinder” dient. Diese Druckbeaufschlagung führt infolge der wirksamen Kolbenfläche 16b zu einer Beaufschlagung des Zylindergehäuses 8b des Aktuators 3b in 2 nach rechts. Diese Beaufschlagung des Zylindergehäuses 8b nach rechts hat wiederum eine Druckerhöhung an der Kolbenfläche 17b zur Folge. Auf diese Weise wird Fluid aus dem Druckraum 18b über den Kanal 21b und den Anschluss 19b herausgepresst und der Sekundärseite 29 zugeführt. Durch die erläuterte fluidische Wirkkette wird eine Schließbewegung für Flügeltüren 6a, 6b erzeugt.
• c) Für eine Umkehrung der Förderrichtung der Pumpe 25 gilt das unter b) Gesagte entsprechend (mit Umkehrung der Beaufschlagungsrichtungen und der Bewegungsrichtungen).
• d) Wird das 3/2-Wege-Magnetventil 28 in die Bypassstellung umgeschaltet, erfolgt eine Umgehung des Aktuators 3a über eine Umgehungsleitung 33, welche von dem 3/2-Wege-Magnetventil 28 über die Verzweigung 32, den Teil der Bypassleitung 30 ohne Handnotventil 31 zu der Primärseite 27 führt. Da über das 3/2-Wege-Magnetventil 28 in der Bypassstellung der Anschluss 19a abgesperrt ist, ändert sich für diesen Schaltzustand des 3-2/Wege-Magnetventils unabhängig vom Betriebszustand der Pumpe 25 die Stellung des Zylindergehäuses 8a des Aktuators 3a nicht. Hingegen kann je nach Betrieb der Pumpe 25 die Erzeugung einer Öffnungs- und Schließbewegung 4a für das Zylindergehäuse des Aktuators 3b erfolgen. Letztendlich kann je nach Schaltzustand des 3/2-Weg-Magnetventils 28 über die Pumpe 25 alternativ
• – eine Doppeltürsteuerung mit gemeinsamer gegenläufiger Ansteuerung der Öffnungs- und Schließbewegungen 4a, 4b der Zylindergehäuse 8a, 8b der Aktuatoren 3a, 3b erfolgen oder
• – ausschließlich eine Einzeltürsteuerung über die Steuerung der Öffnungs- und Schließbewegung 4b des Zylindergehäuses 8b des Aktuators 3b erfolgen.
• e) Schließlich ist über das Handnotventil 31 (und Überführung des 3/2-Wege-Magnetventil 28 in die in 1 Bypassstellung) ein Kurzschluss der beiden Druckräume 14b, 15b ermöglicht, so dass eine manuelle Öffnung oder Schließung der Flügeltür 6b, welche dem Aktuator 3b zugeordnet ist, ermöglicht ist.

The operation of the drive device 1 is as follows:

• a) Without operating the pump 25 and for closed manual emergency valve 31 there is a fluidic securing a assumed position of the actuators 3a . 3b and thus the gullwing doors 6a . 6b , (In the following, it will be explained that an additional securing can also take place by means of a latching or locking device.) Without the check valves 22a . 23a can (neglecting a leak) in this way a fluidic fixation of the wing doors 6a . 6b respectively. On the other hand, by means of the check valves 22 . 23 when exercising particular manual forces on the gullwing doors 6a . 6b basically allows an opening or closing movement. The opening or closing movement or the manual forces required for the same are predetermined by the throttle characteristic of the check valves 22 . 23 , Alternatively or cumulatively, it is possible that by means of the check valves 22a . 23a a fluidic compensation of leakage currents, for example. In the range of an end position, can take place.
• b) If the fluid is delivered from the secondary side 29 through the pump 25 to the primary page 27 , there is an increase in the pressure in the pressure chamber 14 of the actuator 3a , This increase in pressure has on the piston surface 16a a compressive force result, which endeavors, the cylinder housing 8a in 1 to move to the left. This admission of the cylinder housing 8a Turning left again results in pressure in the pressure chamber 15a increases. The actuator 3a acts in this case as a kind of "master cylinder", since in view of the loading of the cylinder housing 8a in 1 to the left also the pressure in the pressure room 15a increases. This rising pressure in the pressure chamber 15a is over the channel 21a , the connection 19a , the 3/2-way solenoid valve 28 in its passage position, the connection 18b , the channel 20b to the pressure room 14b of the actuator 3b transferred, which thus serves as a kind of "slave cylinder". This pressurization results due to the effective piston area 16b to a loading of the cylinder housing 8b of the actuator 3b in 2 to the right. This admission of the cylinder housing 8b to the right again has an increase in pressure on the piston surface 17b result. In this way, fluid from the pressure chamber 18b over the canal 21b and the connection 19b squeezed out and the secondary side 29 fed. The illustrated fluidic chain of action is a closing movement for folding doors 6a . 6b generated.
• c) For a reversal of the conveying direction of the pump 25 the statement under (b) applies accordingly (with reversal of the directions of action and directions of movement).
• d) Will the 3/2-way solenoid valve 28 switched to the bypass position, there is a bypass of the actuator 3a via a bypass 33 that of the 3/2-way solenoid valve 28 over the branch 32 , the part of the bypass line 30 without manual emergency valve 31 to the primary page 27 leads. Because of the 3/2-way solenoid valve 28 in the bypass position the connection 19a is shut off, changes for this switching state of the 3-2 / way solenoid valve regardless of the operating state of the pump 25 the position of the cylinder housing 8a of the actuator 3a Not. On the other hand, depending on the operation of the pump 25 the generation of an opening and closing movement 4a for the cylinder housing of the actuator 3b respectively. Ultimately, depending on the switching state of the 3/2-way solenoid valve 28 over the pump 25 alternative
• - A double door control with common opposite control of the opening and closing movements 4a . 4b the cylinder housing 8a . 8b the actuators 3a . 3b done or
• - Only a single door control via the control of the opening and closing movement 4b of the cylinder housing 8b of the actuator 3b respectively.
• e) Finally, about the emergency valve 31 (and transfer of the 3/2-way solenoid valve 28 in the in 1 Bypass position) a short circuit of both pressure chambers 14b . 15b allows, allowing a manual opening or closing the double door 6b which is the actuator 3b is assigned, is possible.

A single door control for the cylinder housing 8a of the actuator 3a is for the design of the fluidic control circuit 2 according to 1 not possible.

2 shows an alternative embodiment of the drive device 1 with a fluidic control circuit 2 , which also alternatively a single control of both actuators 3a . 3b (So both double doors 6a . 6b ). Here are the actuators 3a . 3b yourself accordingly 1 educated. According to 2 is also the pump 25 through a bypass line 30 with integrated manual emergency valve 31 bridged, but here no branching 32 is available. Between the pump 25 facing connections 18a . 19b the actuators 3a . 3b and the primary or secondary side 27 . 29 and the bypass line 30 each is a 3/2-way solenoid valve 34 . 35 interposed, which in 2 each in their passage position. In the passage position connect the 3/2-way solenoid valves 34 . 35 the respective assigned connection 18a . 19b of the actuator 3a . 3b with the bypass line 30 and the primary or secondary side 27 . 29 , In addition, have the 3/2-way solenoid valves 34 . 35 a bypass position, in which the with the bypass line 30 and the primary or secondary side 27 . 29 connected connection of the 3/2-way solenoid valve 34 . 35 about this with a bypass line 36 are connected. The bypass line 36 connects on the one hand the two connections of the 3/2-way solenoid valves 34 . 35 together. In addition, the bypass line 36 over a branch 37 with a connection line 38 which directly (without integration of the 3/2-way solenoid valve 28 ) the connections 19a . 18b connected, connected.

• a) bis c) Befinden sich beide 3/2-Wege-Magnetventile 34, 35 in ihrer Durchlassstellung, wie dies in 2 dargestellt ist, ist eine Betriebsweise gemäß a) bis c), wie diese zu 1 beschrieben worden ist, möglich.
• d) Wird das 3/2-Wege-Magnetventil 34 in seine Durchlassstellung geschaltet, während sich das 3/2-Wege-Magnetventil in seiner Bypassstellung befindet, ist mittels des Betriebs der Pumpe 25 eine Einzeltürsteuerung mit einer Ansteuerung nur des Aktuators 3a ermöglicht, während über die Absperrung des mit dem Anschuss 19b des Aktuators 3b verbundenen Anschlusses des 3/2-Wege-Magnetventils 35 keine Änderung der Betriebssituation des Aktuators 3b erfolgt.
• e) Wird umgekehrt das 3/2-Wege-Magnetventil 35 in seine Durchlassstellung überführt, während das andere 3/2-Wege-Magnetventil 34 in seiner anderen Schaltstellung ist, ist eine Einzeltürsteuerung mit einer Ansteuerung nur des Aktuators 3b über den Betrieb der Pumpe 25 möglich, während der Aktuator 3a durch Absperrung des Anschlusses 18a seinen Betriebszustand nicht ändert.
• f) Befinden sich beide 3/2-Wege-Magnetventile 34, 35 in ihrer Durchlassstellung und ist das Handnotventil 31 geöffnet, kann eine gemeinsame manuelle Öffnung oder Schließung der Flügeltüren 6a, 6b erfolgen, wobei das Fluid zwischen den Druckräumen 14a, 15b über das Handnotventil 31 in seiner Öffnungsstellung umgewälzt wird.
• g) Befindet sich hingegen eines der 3/2-Wege-Magnetventile 34, 35 in seiner Durchlassstellung, während das andere 3/2-Wege-Magnetventil 34, 35 in seiner Umgehungsstellung ist, kann bei geöffnetem Handnotventil 31 eine manuelle Öffnung oder Schließung lediglich einer Flügeltür 6a, 6b erfolgen.

The operation of the drive device 1 according to 2 is as follows:

• a) to c) Are both 3/2-way solenoid valves 34 . 35 in their Durchlassstellung, as in 2 is shown, is a mode of operation according to a) to c), as these too 1 has been described, possible.
• d) Will the 3/2-way solenoid valve 34 is switched to its passage position while the 3/2-way solenoid valve is in its bypass position, by means of the operation of the pump 25 a single door control with a control of the actuator only 3a allows, while over the barrier of the with the Anschuss 19b of the actuator 3b connected connection of the 3/2-way solenoid valve 35 no change in the operating situation of the actuator 3b he follows.
• e) Conversely, the 3/2-way solenoid valve 35 transferred to its forward position, while the other 3/2-way solenoid valve 34 in its other switching position is a single door control with a control of the actuator only 3b about the operation of the pump 25 possible while the actuator 3a by blocking the connection 18a does not change its operating state.
• f) Both 3/2-way solenoid valves are located 34 . 35 in their passage position and is the emergency valve 31 open, can be a common manual opening or closing the double doors 6a . 6b take place, the fluid between the pressure chambers 14a . 15b via the manual emergency valve 31 is circulated in its open position.
• g) If, on the other hand, one of the 3/2-way solenoid valves is located 34 . 35 in its forward position, while the other 3/2-way solenoid valve 34 . 35 is in its bypass position, can with open manual emergency valve 31 a manual opening or closing only a hinged door 6a . 6b respectively.

For the control of the 3/2-way solenoid valve 28 according to 1 as well as the 3/2-way solenoid valves 34 . 35 according to 2 Preferably, a strategy is chosen such that even at the onset of electrical power supply (and thus break the possibility of electrical control), the desired manual override by manual operation of the emergency valve 31 remains possible. For 1 this means that via a return spring, the 3/2-way solenoid valve 28 is de-energized in its bypass position. Is a manual override operation at break in the electrical power supply according to 2 for both double doors 6a . 6b desired, should the 3/2-way solenoid valves 34 . 35 be de-energized in its passage position. Is, however, only a manual override a gullwing door 6a . 6b desired, the associated 3/2-way solenoid valve 34 de-energized to its forward position, while the other 3/2-way solenoid valve 35 then it must take its bypass position without current.

• – Weitere Steuerungs- und Regelungsmaßnahmen,
• – eine Berücksichtigung beliebiger Betriebssituationen,
• – Notfallmaßnahmen,
• – eine Beeinflussung der Öffnungs- und Schließgeschwindigkeiten,
• – die Herbeiführung einer Endlagendämpfung für die Bewegung der Aktuatoren und Flügeltüren,
• – die Ausgestaltung der fluidischen Kreisläufe mit Verwendung unterschiedlicher Verbindungs- und Umgehungsleitungen,
• – der Einsatz von schaltbaren Ventilelemente, Drosseleinrichtungen und/oder Entlüftungseinrichtungen, Schutzmaßnahmen gegen das Einklemmen von Personen zwischen den Flügeltüren und/oder
• – Maßnahmen zur Überwachung der Öffnungs- und Schließbewegungen

u. ä. sind dem Fachmann an sich bekannt oder für diesen aus dem Stand der Technik zu diesem Technologiefeld entnehmbar und lassen sich mit den erfindungsgemäßen Ausgestaltungen kombinieren.The control of both the pump 25 as well as the 3/2-way solenoid valves 28 . 34 . 35 via an electronic control unit or CPU, which is not shown in the figures. This control is carried out depending on the respective operating situations, wherein the opening or closing movement can be brought about centrally by the driver and / or accessible to the passengers inside and / or outside of the vehicle actuators, which, for example, adjacent the gullwing doors 6a . 6b can be arranged. In the figures, only the actuators are simplified 3a . 3b for a pair of double doors 6a . 6b shown. It is understood that several such pairs of gullwing doors have multiple pairs of actuators can be controlled. This can be done via one and the same pump 25 take place, which then acted on parallel or serial line branches a plurality of actuators, or via a plurality of pumps, which then each a pair of actuators 3a . 3b (or multiple pairs of actuators) may be associated with multiple circuits in this case 2 ,

• - other control and regulatory measures,
• - a consideration of any operating situations,
• - emergency measures,
• An influence on the opening and closing speeds,
• The achievement of a cushioning for the movement of the actuators and gullwing doors,
• The configuration of the fluidic circuits using different connection and bypass lines,
• - the use of switchable valve elements, throttling devices and / or venting devices, protective measures against the entrapment of persons between the gullwing doors and / or
• - Measures to monitor the opening and closing movements

u. Ä. Are known to those skilled in the art or for this from the prior art to this technology field and can be combined with the embodiments of the invention.

To simplify the illustration is in 1 and 2 only a movement of the cylinder housing 8a . 8b in a direction x, which for one embodiment correlates with the movement of the gullwing doors 6a . 6b in the direction of the vehicle's longitudinal axis. It is possible that additional actuating devices or coupling devices or degrees of freedom are used, via which additionally a pivoting movement of the wing doors 6a . 6b about a vertical axis (axis z) can be brought about. Depending on the pivoting about the axis z, the actuating direction x of the actuator with respect to the longitudinal axis of the vehicle can then also change. It is also possible that the holding devices 5a . 5b with the movement of the actuators 3a . 3b in the direction of the X-axis only with a point of the hinged door 6a . 6b be coupled articulated so that the movement of the hinged door on a circular path then in addition to the translational movement of the cylinder housing 8a . 8b of the actuator 3a . 3b depends on the said additional coupling device and / or a further actuator, as will be explained in more detail below.

As a special feature is the 1 and 2 to see that the cylinder housing 8a . 8b the actuators 3a . 3b are not fixed to the vehicle frame, but about their adjusting movement along the longitudinal guide devices 11a . 11b to be moved. Here, the movement of the cylinder housing 8a . 8b be fluidly coupled together, in which case a cylinder housing 8a . 8b as a kind of "master cylinder" acts, while the other cylinder housing 8b . 8a then serves as a "slave cylinder". But this fluidic coupling is via valve elements, here the 3/2-way solenoid valves 28 . 34 . 35 canceled. For the embodiment according to 1 and 2 are the longitudinal guidance devices 11a . 11b vehicle frame fixed, but this is not mandatory, as will be explained below.

In the 3 to 15 is in further constructional detail and with expanded possibilities a drive device 1 exemplified, in which, for example, a fluidic control circuit 2 according to 1 or 2 can be used.

3 shows the parallel to each other and to the x-direction oriented longitudinal guide devices 11a . 11b , which are here as guide tubes 12a . 12b are formed. Opposite these in the direction of the X-axis are the cylinder housing 8a . 8b which the holding devices 5a . 5b for the double doors 6a . 6b wear. While 3 the drive device 1 in an open position with maximum distance of the wing doors 6a . 6b shows are in the 4 and 5 different closing positions of the hinged doors 6a . 6b shown.

• – das Dichtelement 43,
• – ein Dichtelement 52, welches zwischen Kopf 48 und Grundkörper 68 verspannt ist, sowie
• – ein Dichtelement 53, welches zwischen der Durchgangsbohrung der Kopplungshülse 44 und einer Mantelfläche der Kopplungsschraube 46 eingespannt ist,

abgedichtet sein.The structure of the longitudinal guide devices 11a . 11b as well as the cylinder units 7a . 7b are in detail in the 6 to 8th to recognize:
The guide tubes 12a . 12b are rigid in their end areas and parallel to each other on supporting devices 39 . 40 held. As exemplified by the support device 39 according to 7 is shown, the support means 39 . 40 each with a body 68 educated. The main body 68 has two stepped through holes 41 . 42 , in which under radial sealing by a sealing element 43 a coupling sleeve 44 extending, which frontally into the guide tube 12a . 12b is screwed with a tension of the front side of the guide tube 12a . 12b against a covenant 45 the coupling sleeve 44 , Through the passage recesses 41 . 42 through a coupling screw extends 46 whose threaded portion with an internal thread of the coupling sleeve 44 is screwed. By screwing in the coupling screw 46 in the coupling sleeve 44 becomes a cylindrical tapered heel 47 the through-hole 41 . 42 braced between a head 48 the coupling screw 46 and a frontal or blind 45 the coupling sleeve 44 , The coupling screw 46 has an inner channel 49 , which on the one hand into an interior 50 of the guide tube 12a . 12b flows and on the other hand via a radial branch channel communicates with a supply line, not shown in the figures or bore in the body 68 which with a connection 18 . 19 connected is. A crossover cross section between the tap hole 51 and the supply line can over

• - The sealing element 43 .
• - A sealing element 52 which between head 48 and basic body 68 is tense, as well
• - A sealing element 53 , which between the through hole of the coupling sleeve 44 and a lateral surface of the coupling screw 46 is clamped,

be sealed.

As in particular from the detail VIII according to 8th it can be seen, are the guide tubes 12a . 12b two-piece design with guide tube parts 12-1 and 12-2 , The guide tube parts 12-1 and 12-2 are rigidly connected with each other via the separating body 24 , The separating body 24 has a ring body 54 of which pins equipped with an external thread in the x-direction 55 . 56 extend. The external threads of the pins 55 . 56 are screwed with internal threads of the guide tube parts 12-1 and 12-2 , whereby the associated end faces of the guide tube parts 12-1 and 12-2 be clamped against annular end faces of the ring body 54 so that the separating body 24 and the guide tube parts 12-1 and 12-2 form a rigid entity. The ring body 54 forms radially outward a cylindrical sealing and guiding surface 57 , In the sealing and guiding surface 57 is radially a circumferential groove 58 introduced, in which a sealing element 59 is arranged. The interiors 50-1 and 50-2 the guide tube parts 12-1 and 12-2 are over channels formed with longitudinal bores 60 . 61 of the separating body 24 connected with each other. In the channels 60 . 61 are the throttles or check valves that open in the opposite direction 22 . 23 arranged. In the opening direction upstream of the check valves 22 . 23 flows into the channels 60 . 61 one radial tap hole each 62 . 63 ,

The cylinder housing 8th are here with a cylinder housing tube 64 formed, which in both end regions with a sealing and guiding unit 9 respectively. 10 is screwed. At the sealing and guiding units 9 are in this case the holding devices 5 directly attached. The cylindrical inner surface of the cylinder housing tube 64 slides for the adjusting movement along the sealing and guiding surface 57 the separating body 24 , wherein a seal by the sealing element 59 he follows. Between the inner surface of the cylinder housing tube 64 and the lateral surface of the guide tube parts 12-1 and 12-2 a radial gap is formed, in the area of the two pressure chambers 14 . 15 be formed. Thus, the pressure chamber 14 radially inwardly limited by the lateral surface of the guide tube 12 and radially outboard through the inner surface of the cylinder housing tube 64 , In one end area is the pressure chamber 14 axially limited by an end face of the annular body 54 , In the other axial end region is the pressure chamber 14 axially limited by an annular inner end face of the sealing and guiding unit 9 , which thus the piston surface 16 forms. The same applies to the pressure chamber 15 Here, the one axial limitation and the formation of the piston surface 17 not through the sealing and guiding unit 9 takes place, but by the sealing and guiding unit 10 , A fluidic connection of the interiors 50-1 and 50-2 with the associated pressure chambers 14 . 15 takes place via the channels 60 . 61 and the tap holes 62 . 63 ,

In 6 It can be seen that for a closed position of the wing doors, the cylinder housing 8th with the sealing and guiding unit 10 immediately adjacent to the support device 39 is arranged, wherein an end face of the sealing and guiding unit 10 can also come to the support device to the plant. On the other hand, the sealing and guiding unit moves away 10 with the opening movement of the hinged doors 6a . 6b increasingly from the support device 39 , The cylinder housing 8th is preferably more than half as long as the longitudinal guide device 11 , whereby a good support and absorption of a tilting moment about an axis transverse to the longitudinal axis of the longitudinal guide device 11 is guaranteed.

Ultimately, depending on the pressurization of the supply lines in the support devices 39 . 40 the fluidic loading of the pressure chambers 14 . 15 be changed, bringing a movement of the cylinder housing 8a . 8b in opening and closing direction 4a . 4b can be brought about. The movement of the double doors 6a . 6b This is preferably done parallel to the vehicle longitudinal axis and in the direction indicated by x in the figures. The of the sealing and guiding units 9 . 10 trained piston surfaces 16 . 17 Here are annular surfaces with diameters corresponding to the annular gaps between the inner surface of the cylinder housing tube 64 and the lateral surface of the guide tube 12 ,

• – nach Bewegung der Flügeltüren 6a, 6b in einer ersten Bewegungsphase in x-Richtung parallel zu dem Fahrzeug mit dem erforderlichen Abstand von einer äußeren Wandung und einem Türrahmen des Fahrzeugs ohne Nutzung des zusätzlichen Freiheitsgrads
• – in einer zweiten Bewegungsphase die Flügeltüren 6a, 6b in ihre Schließstellung zu bewegen, wobei die Flügeltüren dann (zumindest auch) in Querrichtung y des Fahrzeugs auf einen Türrahmen mit geeigneter Dichtung zu bewegt werden.

It is quite possible that the support device 1 exclusively has the explained degree of freedom in the direction x. For that in the 3 to 15 illustrated embodiment has the support device 1 about a further degree of freedom in a transverse direction, which is referred to here as direction y. This additional degree of freedom is ensured by using the guide tubes 12 formed longitudinal guide devices 11 together with the support facilities 39 . 40 in the direction of y opposite a vehicle frame or a door frame are movable. This extra degree of freedom can serve

• - after movement of the double doors 6a . 6b in a first movement phase in the x-direction parallel to the vehicle with the required distance from an outer wall and a door frame of the vehicle without the use of the additional degree of freedom
• - In a second phase of movement, the double doors 6a . 6b to move into its closed position, the wing doors are then (at least) in the transverse direction y of the vehicle to a door frame with a suitable seal to be moved.

Especially in the 12 and 14 It can be seen that such an additional degree of freedom in the y-direction is ensured via a transverse guiding device 65 , This has a oriented in the direction of the Y-axis guide rod 66 , which on a vehicle frame fixed or door frame fixed support 67 is held.

The main body 68 is in this case as a kind of guide slide 69 educated. For this purpose, the guide carriage has 69 a continuous recess 70 , in which end two guide bushes 71 . 72 are used, which sliding and as free of play on the guide rod 66 are supported. Between the guide carriage 69 and the guide rod 66 acts a spring element 73 which urges the guide carriage away from the door frame in the y-direction.

The movement of the cylinder housing 8th along the longitudinal guide means 11 in the x-direction is only a partial lift, namely the last part of the closing stroke or the first part of the opening stroke, coupled with the movement of the guide carriage 69 opposite the guide rods 66 in the direction of y. This coupling is done mechanically. The cylinder housings have this feature 8th , here the sealing and guiding units 9 , via a driver unit 74 , which only for the partial stroke of the cylinder housing 8th be effective. For the illustrated embodiment, the driver unit 74 formed by an extension 75 the sealing and guiding units 9 , Through a continuous recess 76 of the extensions 75 extends a coupling rod 77 , For the partial stroke, for which the movement of the cylinder housing 8th with the movement of the guide carriages 69 is coupled and thus a coupling of the movement of the cylinder housing 8th in the longitudinal direction x with the movement of the support means 39 . 40 takes place in the transverse direction y, is a driver 78 the coupling rod 77 one-sided to the extension 75 with which the mechanical coupling between the movement of the cylinder housing 8th with the movement of the coupling rods 77 created and effective. For the illustrated embodiment, the driver 78 with a plugged onto the coupling rod sleeve 79 formed, which end by a nut 80 is secured.

In the supporting devices 39 . 40 facing end areas are the coupling rods 77 on a toggle mechanism 81 hinged, which is movable in a plane xy. The toggle mechanism 81 has a first toggle 82 and a second toggle 83 which has a knee joint 84 connected to each other. The knee joint 84 remote end portion of the first toggle lever 82 is at the guide slide 69 hinged. The knee joint 84 remote end portion of the second toggle lever 83 is on the carrying device 67 hinged. The coupling rod 77 acts on the first toggle 82 which is preferably approximately midway between the two articulation points of the first toggle lever 82 he follows.

• – In der Öffnungsstellung der Antriebseinrichtung 1 und der Flügeltüren 6 gemäß 3 befindet sich das Zylindergehäuse 8a maximal nach links verschoben. In dieser Öffnungsstellung hat sich der Fortsatz 75a gegenüber der Stellung in 8 ebenfalls weit nach links bewegt, so dass der Mitnehmer 78a den Fortsatz 75a nicht kontaktiert.
• – Mit Betätigung der Aktuatoren 3a, 3b bewegen sich die Flügeltüren 6a, 6b aufeinander zu bis zu der Stellung gemäß 4. In dieser besitzen die Flügeltüren 6a, 6b noch einen kleinen verbleibenden Spalt. In der Stellung gemäß 4 beginnt der Teilhub, für welchen eine Kopplung der Bewegung der Flügeltüren 6a, 6b und der Bewegung der Zylindergehäuse 8 mit der Bewegung der Führungsschlitten 69 einsetzt. In der Betriebsstellung gemäß 4 ist somit gerade der Fortsatz 75 zur Anlage an den Mitnehmer gekommen.
• – Eine weitere Druckbeaufschlagung der Aktuatoren 3a, 3b hat zur Folge, dass die Zylindergehäuse 8 weiter aufeinander zu bewegt werden, was auch zur Folge hat, dass die Koppelstangen 77a, 77b aufeinander zu gezogen werden. Mit der Fortführung der Schließbewegung betätigen die Koppelstangen 77 den Kniehebelmechanismus 81. Der Kniehebelmechanismus 81 wird aus der abgewinkelten Betriebsstellung gemäß 9 (Kniewinkel bspw. ca. 70° ± 20°) gemäß 9 in Richtung seiner Strecklage (10, Kniewinkel bspw. ca. 80° ± 8°) bewegt. Die Veränderung des Kniewinkels hat zur Folge, dass sich der Abstand des Anlenkpunkts des Kniehebelmechanismus 81 an der Trageinrichtung 67 von dem Anlenkpunkt des Kniehebelmechanismus 81 an dem Führungsschlitten 69 vergrößert. Entgegen der Beaufschlagung des Federelements 73 kommt es somit zu einer Bewegung der mit dem Führungsschlitten 69 gebildeten Abstützeinrichtung 39, 40, der Längsführungseinrichtungen 11, der Aktuatoren 3a, 3b, der Halteeinrichtungen 5a, 5b und letztendlich der Flügeltüren 6a, 6b in y-Richtung (entgegengesetzt zu dem Richtungssinn von y in den Figuren). Eine Charakteristik des Ausmaßes der Bewegung der Führungsschlitten 69 in Abhängigkeit der Bewegung der Zylindergehäuse 8 ergibt sich über die Kinematik des Kniehebelmechanismus 81, nämlich die Lage der Anlenkpunkte und die Längen der Kniehebel 82, 83.
• – Werden hingegen die Aktuatoren 3a, 3b in Öffnungsrichtung beaufschlagt, führt die Beaufschlagung des Federelements 73 dazu, dass mit der Öffnungsbewegung der Kniewinkel des Kniehebelmechanismus 81 wieder größer wird, wobei das Federelement 73 so lange dafür sorgt, dass die Koppelstange 77 mit dem Mitnehmer 78 an den Fortsatz 75 gepresst wird, bis der Führungsschlitten 69 maximal nach außen in y-Richtung bewegt ist, womit die Kopplung der Bewegung der Zylindergehäuse 8 mit der Bewegung des Führungsschlittens bewegungsgesteuert beseitigt wird.

The coupling between the cylinder housing 8th and the guide carriage 69 is done as follows:

• - In the open position of the drive device 1 and the double doors 6 according to 3 is the cylinder housing 8a maximally shifted to the left. In this open position, the extension has 75a opposite the position in 8th also moved far to the left, leaving the driver 78a the extension 75a not contacted.
• - With actuation of the actuators 3a . 3b the double doors are moving 6a . 6b towards each other up to the position according to 4 , In this own the double doors 6a . 6b still a small remaining gap. In the position according to 4 begins the partial lift, for which a coupling of the movement of the gullwing doors 6a . 6b and the movement of the cylinder housing 8th with the movement of the guide carriages 69 starts. In the operating position according to 4 is thus just the extension 75 come to the plant to the driver.
• - Another pressurization of the actuators 3a . 3b As a result, the cylinder housing 8th be moved towards each other, which also has the consequence that the coupling rods 77a . 77b be drawn to each other. With the continuation of the closing movement actuate the coupling rods 77 the toggle mechanism 81 , The toggle mechanism 81 becomes from the angled operating position according to 9 (Knee angle, for example, about 70 ° ± 20 °) according to 9 in the direction of its extended position ( 10 , Knee angle, for example, about 80 ° ± 8 °) moves. The change in the knee angle has the consequence that the distance of the articulation point of the toggle mechanism 81 on the carrying device 67 from the point of articulation of the toggle mechanism 81 on the guide carriage 69 increased. Contrary to the application of the spring element 73 Thus, it comes to a movement of the guide carriage 69 formed support device 39 . 40 . the longitudinal guide devices 11 , the actuators 3a . 3b , the holding devices 5a . 5b and finally the gullwing doors 6a . 6b in the y direction (opposite to the sense of y in the figures). A characteristic of the extent of movement of the guide carriage 69 depending on the movement of the cylinder housing 8th results from the kinematics of the toggle mechanism 81 , namely the position of the articulation points and the lengths of the toggle lever 82 . 83 ,
• - Become, however, the actuators 3a . 3b acted upon in the opening direction, the application of the spring element 73 to that with the opening movement the knee angle of the toggle mechanism 81 becomes larger again, the spring element 73 as long as that ensures that the coupling rod 77 with the driver 78 to the extension 75 is pressed until the guide carriage 69 is moved outward in the y-direction, bringing the coupling of the movement of the cylinder housing 8th is removed motion controlled with the movement of the guide carriage.

It is possible that the drive device 1 has only the explained degrees of freedom in the direction x and y. This embodiment is used in particular when a double door control for the opening and closing movement of the gullwing doors 6a . 6b is desired.

Optionally, an extended embodiment is proposed, according to which the support means 39 . 40 , Longitudinal guide devices 11 , the cylinder housing 8th and the guide rods 66 are jointly pivotable about a vertical axis Z, whereby the directions x, y, along which a movement along said degrees of freedom, change. This pivoting about the vertical axis Z is preferably carried out when only a single door control is desired, for which, for example, the hinged door 6b remains closed, but with an opening movement of the cylinder housing 8a the gullwing door 6a is opened. This has the consequence that with the opening movement of the single hinged door 6a the toggle mechanism 81b maintains its end position near the extended position, so that the guide slide 69b maintains its position in the y-direction as far as possible in the transverse direction inwards. On the other hand, the actuation of the actuator leads 3a cause the knee angle of the toggle mechanism 61a enlarged and the guide carriage 69 moved outward in the transverse direction. Thus, the explained single-door control leads to the fact that with the pivoting about the vertical axis Z, the effective direction of the actuator 3a from a first direction of action 85 changes in a second effective direction 86 (schematically dash-dotted in 5 shown). Here, the maximum angle change between the first direction of action 85 and the second direction of action 86 may be relatively small, for example in the range of 5 ° ± 4 ° or 5 ° ± 2 °. This change in angle on the one hand has the consequence that the gullwing door 6b remains closed (possibly with a small "angle error"), while it is possible that the gullwing door 6a can be opened and this can be passed for example on an outer skin of the vehicle. If such an additional degree of freedom for pivoting about the vertical axis Z is desired, it is necessary that the guide rod 66 not rigid on the carrying device 67 is attached. Rather, it is an end area 87 the guide rod 66 articulated in a bearing eye 88 mounted such that an axial fixation of the guide rod 66 opposite the carrying device 67 done, but the orientation of the guide rod 66 limited in space is variable. Also the opposite end area 89 the guide rod 66 is not rigid on the carrying device 67 held. Rather, it's about a ball joint 90 on the carrying device 67 an approximately vertically downwardly extending coupling element 91 hinged. The coupling element 91 is in its lower end by an end vertical bore of the guide rod 66 passed through and on the opposite side by a nut 92 secured. For the illustrated embodiment, the coupling element 91 designed with adjustable length. As shown, the end area 89 the guide rod 66 via a spring element 93 against the mother 92 are pressed, while increasing the bias of the spring 93 also a movement of the end area 89 the guide rod 66 away from the mother 92 is possible.

As explained above, it is possible that a once assumed position of the folding doors 6a . 6b is secured exclusively fluidically. For a particular embodiment, securing the position of the wing doors 6a . 6b and thus the drive device 1 via an additional locking or locking device 94 , While it is basically possible that by means of the locking or locking device 94 at least one arbitrary part of the drive device is set, which is moved in the course of the opening and closing movement, according to the illustrated embodiment by means of the latching or locking device 94 the guide carriage 69 opposite the guide rod 66 latched or locked. For this purpose, has the guide rod 66 a latching or locking groove 95 , in which a latching or locking element (for example, a Verrieglungsstift) of the locking or locking device 94 intervenes. A control of the locking or locking device 94 , In particular, the movement of the locking element in the latching or locking groove 95 , can be electrical, pneumatic, hydraulic, electropneumatic or electrohydraulic.

Optionally possible is that together with the operation of the toggle mechanism 81 also a pivoting of rotary columns 96 on both sides of the double doors 6a . 6b assigned entry opening of the vehicle takes place. The rotary columns 96 are oriented in the direction of the vertical axis Z here. The rotary columns 96 are here also rotatable about the vertical axis relative to the support device 67 stored. In the upper end of the turn column has 96 via a rocker extending radially therefrom 97 , In a radially outer end region is on the rocker 97 a coupling rod 98 hinged. The coupling rod 98 is in an end area by means of a ball head 99 on the guide carriage 69 or articulated by this downwardly extending bearing pin. In the other end area is the coupling rod 98 over a ball head 106 on the swingarm 97 hinged. A movement of the guide carriage 69 in y-direction is thus about the connection between the rocker 97 and the coupling rod 98 converted into a rotational movement of the rotary column 96 around its longitudinal axis. In the area of the vehicle floor and in the lower end of the rotary column 96 is another holding device 100 for the gullwing door 6a . 6b arranged. The holding device 100 has an arcuate swingarm 101 , which with the rotary column 96a is pivoted in an xy plane. The radially outer end region of the rocker 101 is about a leadership unit 105 with a guide element, in particular a guide pin, in a guide rail on the underside of the hinged door 6a . 6b , in particular a guide, guided. A movement of the gullwing door 6a . 6b in the direction x is thus by the rocker and the guide unit 105 not obstructed while the swingarm 101 and the leadership unit 105 the distance of the hinged door 6a . 6b from the vehicle in the transverse direction y at the holding device 100 pretend. A pivoting of the rotary column 96 leads to a change in the distance of the hinged door 6 at the holding device 100 from a door frame or the vehicle in the direction of y.

In the figures and the description are those of the respective hinged door 6a . 6b or the different actuators 3a . 3b assigned components also partially marked with the amended letter a or b. Also marked with supplementary letters a, b are the components of the left support means 39 and the right support device 40 , If reference numbers are used without the supplementary letter, this may be exclusive to one of the components or may hereby be the two hinged doors 6a . 6b be described associated components.

With the between the holding devices 5 . 100 Intermediate components is a suspension 102 for the double doors 6a . 6b educated. Even if no drive via the actuators 3a . 3b takes place, a correspondingly formed suspension 102 be used for the specification of the kinematics of at least one wing door 6a . 6b , In this case, any actuator may be responsible for movement of one of the components involved in the suspension, which then via the suspension 102 to the holding devices 5 . 100 is transmitted.

As another option, in the drive device 1 be integrated into a sensor system. This is the opening and closing movement 4a and / or the opening and closing movement 4b detected. For an exemplary embodiment, the sensor system is formed with a magnetorestrictive measuring system, which is in a measuring rod 103 is integrated, which is between the two support devices 39 . 40 extends. The cylinder housing 8th each have a magnet or transmitter, which along the measuring rod 103 is moved. The measuring rod 103 magnetorestrictively detects the current position of the transmitter. This can be done a continuous detection of the way. It is also possible that the detection of the path takes place only in a partial stroke. Alternatively, it is also possible to use a sensor in the form of a switch which detects the reaching or passing of at least one operating position, for example reaching the opening and / or closing position.

For the illustrated embodiment, the pump 25 integrated into the drive unit, namely preferably from the support device 40 worn, so the pump 25 is moved in the direction of y. Furthermore, on the support device 39 . 40 a valve block 104 be held in which valves, in particular the 3/2-way solenoid valves 28 . 34 . 35 are integrated and the fluidic loading of the drive device 1 Taxes. Also the valve block 104 becomes with the movement of the support device 39 . 40 moved.

In the event of emergency release of the locking or locking device 94 can the spring 73 cause the gullwing door 6 is moved away from the door frame in the direction y, in which case as to the 1 and 2 explains a manual opening of the double doors 6 can take place in the direction of x.

The in the 3 to 16 illustrated drive device 1 can, for example, by means of a fluidic control circuit 2 according to 1 or 2 controlled (which also a regulation is understood) and fluidly acted upon.

The movement of the hinged door in the longitudinal or transverse direction described here can describe a movement of a pivot point of the hinged door itself. Likewise included, however, is also a movement of only one guide element of the Gullwing in this direction, while the guide member is connected via a further geared connection with the hinged door, wherein the geared connection may also result in that the hinged door moves in a different direction than the guide element.

• – eine Einzeltürsteuerung,
• – eine Doppeltürsteuerung mit verringerter Betätigungsgeschwindigkeit (diese Betriebsstellung der Ventileinrichtung ist auch als ”erste Betriebsstellung” bezeichnet) sowie
• – eine Doppeltürsteuerung mit erhöhter Betätigungsgeschwindigkeit (diese Betriebsstellung der Ventileinrichtung ist auch als ”zweite Betriebsstellung” bezeichnet).

17 shows a fluidic control circuit 2 , which depending on the operating position of a valve device 108 allows different modes of operation, namely

• - a single door control,
• - A double door control with reduced operating speed (this operating position of the valve device is also referred to as "first operating position") and
• - A double door control with increased operating speed (this operating position of the valve device is also referred to as "second operating position").

In the fluidic control circuit 2 according to 17 is the primary side 27 the pump 25 via a controllable non-return valve 109 or controllable shut-off valve with the connection 18a and the pressure room 14a of the actuator 3a connected. The connection 19a of the actuator 3a is with a connection 110 a valve 111 , here a controlled 3/2-way valve 112 , connected. The valve 111 has further connections 113 . 114 , In the in 17 effective position of the valve 111 , which corresponds to the non-actuated position as a result of the application of a spring, are via the valve 111 the connections 110 . 113 connected together while connecting 114 is locked. In the other position of the valve brought about by the control 111 this connects the connections 110 . 114 with each other while connecting 113 is locked.

The secondary side 29 is via a controllable non-return valve 115 or controllable shut-off valve with the connection 19b and thus the pressure room 15b of the actuator 3b connected. The other connection 18b of the actuator 3b is with a connection 116 a valve 117 , here a controlled 3/2-way valve 118 , connected. The valve 117 has further connections 119 . 120 , In the in 17 effective position of the valve 117 , which corresponds to the non-actuated position as a result of the application of a spring, connects the valve 117 the connections 116 . 119 while the connection 120 is locked. In the other position of the valve brought about by activation 117 connects the valve 117 the connections 116 . 120 with each other while connecting 119 is locked.

For the in 17 illustrated embodiment are the valves 111 . 117 controlled fluidically. This can be done by means of the fluid, which in any case in the control circuit 2 is used. The control pressure for the valves 111 . 117 can be specified by at least one not shown in the figures pilot valve, which, for example, is controlled as needed by an electronic control device. Preferably, however, the valves 111 . 117 (Deviating from the embodiment according to FIG 17 ) are designed as solenoid valves, so that they are directly controlled by an electronic control device.

The connection 113 of the valve 111 is over a branch 121 and the check valve 115 with the secondary side 29 the pump 25 connected. On the other hand is the connection 119 of the valve 117 over a branch 122 and the check valve 109 with the primary side 27 the pump 25 connected. The connections 114 . 120 the two valves 111 . 117 are connected. About one in 17 Control device, not shown, can be used as required to pressurize the control terminals of the valves 111 . 117 done according to what 17 fluid (in particular pneumatic) takes place. For example, an electronic control device with a corresponding control logic generate an electrical control signal, by means of which an electromagnetic pilot valve is controlled, which controls a fluid pressure, the control connection of the valves 111 . 117 is supplied.

• a) In der in 17 wirksamen Schaltstellung der Ventile 111, 117, in welcher die Steueranschlüsse der Ventile 111, 117 nicht fluidisch beaufschlagt sind, wird das Fördervolumen der Pumpe 25 im Bereich der Verzweigung 122 aufgeteilt. Ein Teil, insbesondere die Hälfte, des Fördervolumens der Pumpe 25 gelangt über den Anschluss 18a zu dem Druckraum 14a des Aktuators 3a. Der andere Druckraum 15a ist über den Anschluss 19a und das Ventil 111 infolge der Verbindung der Anschlüsse 110, 113 über das Rückschlagventil 115 mit der Sekundärseite 29 verbunden. Infolge der Druckbeaufschlagung der Primärseite 27 liegt in einer Steuerleitung 123 für das Rückschlagventil 115 Steuerdruck an, sodass das Rückschlagventil 115 geöffnet wird und entgegen der eigentlichen Öffnungsrichtung Fluid zu der Sekundärseite 29 gelangen kann. Mit dem Teil des Fördervolumens der Pumpe 25, welcher von der Verzweigung 122 zu dem Anschluss 18a gelangt, kann somit die Betätigung des Aktuators 3a erfolgen. Der andere Teil des Fördervolumens gelangt über die Verzweigung 122, die miteinander verbundenen Anschlüsse 119, 116 des Ventils 117 zu dem Anschluss 18b des Aktuators 3b und somit zu dem Druckraum 14b des Aktuators 3b. Hingegen ist der Druckraum 15b des Aktuators 3b über den Anschluss 19b und das infolge der Druckbeaufschlagung der Steuerleitung 123 geöffnete Rückschlagventil 115 mit der Sekundärseite 29 verbunden. Somit kann mit dem anderen Teil des Fördervolumens der Pumpe 25, welcher von der Verzweigung zu dem Anschluss 18b gelangt, die Betätigung des Aktuators 3b erfolgen. Entsprechendes gilt für die Umkehrung der Förderrichtung der Pumpe 25, wobei in diesem Fall eine Steuerleitung 124 zur Öffnung des Rückschlagventils 109 druckbeaufschlagt ist. Für die in 17 wirksame Betriebsstellung, welche auch als ”erste Betriebsstellung” bezeichnet ist, sind die Druckräume 14a, 14b der Aktuatoren 3a, 3b in fluidischer Parallelschaltung mit der Primärseite 27 der Pumpe 25 verbunden. Da hier die Beaufschlagung der beiden Aktuatoren 3a, 3b nur mit einem Teil des Fördervolumens der Pumpe 25 erfolgt, führt diese erste Betriebsstellung der Ventileinrichtung 108 zu einer Betätigung der Aktuatoren 3a, 3b mit einer verringerten Betätigungsgeschwindigkeit für eine Doppeltürsteuerung.
• b) Werden beide Ventile 111, 117 umgeschaltet in die nicht in 17 wirksame Stellung, so liegt die zweite Betriebsstellung der Ventileinrichtung 108 vor. In der zweiten Betriebsstellung verbindet das Ventil 111 die Anschlüsse 110, 114 miteinander, während der Anschluss 113 abgesperrt ist, und das Ventil 117 verbindet die Anschlüsse 116, 120 miteinander, während der Anschluss 119 abgesperrt ist. In der zweiten Betriebsstellung ist eine Doppeltürsteuerung mit einer erhöhten Betätigungsgeschwindigkeit ermöglicht: Angesichts der Absperrung des Anschlusses 119 durch das Ventil 117 erfolgt primärseitig im Bereich der Verzweigung 112 keine Aufteilung des Fördervolumens der Pumpe 25. Vielmehr wird das gesamte Fördervolumen der Pumpe 25 über den Anschluss 18a dem Aktuator 3a zur Verfügung gestellt. In diesem Fall ist mit dem Druckraum 15a eine Art ”Geberzylinder” gebildet: Der Druckraum 15a ist über den Anschluss 19a und die Anschlüsse 110, 114 des Ventils 111 sowie die Anschlüsse 120, 116 des Ventils 117 mit dem Anschluss 18b des Aktuators 3b verbunden. Mit dem Druckraum 14b ist dann eine Art ”Nehmerzylinder” gebildet. Die Druckräume 15a, 14b sind also fluidisch miteinander verkoppelt, wodurch eine Kopplung der Bewegung der beiden Aktuatoren 3a, 3b miteinander erfolgt. Führt diese Kopplung der Bewegungen zu einer Stellbewegung auch des Aktuators 3b, verändert sich das Volumen des Druckraums 15b des Aktuators 3b, womit Fluid aus dem Druckraum 15b ausgeschoben wird. Dieses gelangt über den Anschluss 19b und das angesichts der Druckbeaufschlagung der Steuerleitung 123 geöffnete Rückschlagventil 115 zur Sekundärseite 29 der Pumpe 25. Da eine Betätigung des Aktuators 3a mit dem vollen Fördervolumen der Pumpe 25 erfolgt, erfolgt eine Betätigung des Aktuators 3a mit erhöhter Betätigungsgeschwindigkeit. Infolge der Kopplung der beiden Aktuatoren 3a, 3b miteinander ergibt sich auch eine erhöhte Betätigungsgeschwindigkeit des Aktuators 3b. Entsprechendes gilt bei Umkehrung der Förderrichtung der Pumpe 25.
• c) Ebenfalls möglich ist eine Einzeltürsteuerung mit einer reinen Betätigung des Aktuators 3a: Hierzu nimmt das Ventil 111 die in 17 wirksame Stellung ein, während das Ventil 117 in die in 17 nicht wirksame Stellung gesteuert wird. Angesichts der Absperrung des Anschlusses 119 durch das Ventil 117 erfolgt keine Aufteilung des Fördervolumens im Bereich der Verzweigung 122. Vielmehr wird das gesamte Fördervolumen der Pumpe 25 über den Anschluss 18a dem Aktuator 3a zur Verfügung gestellt. Der Druckraum 15a ist über den Anschluss 19a und die Anschlüsse 110, 113 des Ventils 111, die Verzweigung 121 und das angesichts der Druckbeaufschlagung der Steuerleitung 123 geöffnete Rückschlagventil 115 mit der Sekundärseite 29 verbunden. Somit ist eine Stellbewegung des Aktuators 3a ermöglicht. Hingegen ist der Druckraum 14b des Aktuators 3b über den Anschluss 18b, die Anschlüsse 116, 120 des Ventils 117 und den Anschluss 114 in der Schaltstellung des Ventils 117 gemäß 17 abgesperrt, sodass sich eine eingenommene Stellung des Aktuators 3b nicht ändern kann. Somit ergibt sich eine Einzeltürsteuerung über den Aktuator 3a, welche mit dem vollen Fördervolumen der Pumpe 25, also einer großen Betätigungsgeschwindigkeit erfolgt. Entsprechend kann auch eine Einzeltürsteuerung für den Aktuator 3b erfolgen, indem das Ventil 111 in die in 17 nicht wirksame Stellung umgeschaltet wird, während das Ventil 117 in die in 17 wirksame Stellung gesteuert wird.

The valve device 108 is with the valves 111 . 117 educated. Depending on the control of the valve device 108 , ie depending on the control of the valves 111 . 117 , can by means of the fluidic control circuit 2 the following different modes of operation are possible:

• a) In the 17 effective switching position of the valves 111 . 117 , in which the control connections of the valves 111 . 117 are not fluidly charged, the delivery volume of the pump 25 in the area of the branch 122 divided up. A part, in particular half, of the delivery volume of the pump 25 gets over the connection 18a to the pressure room 14a of the actuator 3a , The other pressure chamber 15a is about the connection 19a and the valve 111 due to the connection of the connections 110 . 113 over the check valve 115 with the secondary side 29 connected. As a result of the pressurization of the primary side 27 lies in a control line 123 for the check valve 115 Control pressure on, so the check valve 115 is opened and contrary to the actual opening direction fluid to the secondary side 29 can get. With the part of the delivery volume of the pump 25 which is from the junction 122 to the connection 18a can thus, the actuation of the actuator 3a respectively. The other part of the delivery volume passes over the branch 122 , the interconnected connections 119 . 116 of the valve 117 to that connection 18b of the actuator 3b and thus to the pressure chamber 14b of the actuator 3b , By contrast, the pressure chamber 15b of the actuator 3b over the connection 19b and that as a result of the pressurization of the control line 123 opened check valve 115 with the secondary side 29 connected. Thus, with the other part of the delivery volume of the pump 25 which is from the junction to the port 18b passes, the actuation of the actuator 3b respectively. The same applies to the reversal of the conveying direction of the pump 25 , in which case a control line 124 for opening the check valve 109 is pressurized. For the in 17 effective operating position, which is also referred to as "first operating position", are the pressure chambers 14a . 14b the actuators 3a . 3b in fluidic parallel connection with the primary side 27 the pump 25 connected. Since here the admission of the two actuators 3a . 3b only with a part of the delivery volume of the pump 25 takes place, this first operating position of the valve device 108 to an actuation of the actuators 3a . 3b with a reduced operating speed for a double door control.
• b) Be both valves 111 . 117 switched to not in 17 effective position, so is the second operating position of the valve device 108 in front. In the second operating position, the valve connects 111 the connections 110 . 114 with each other while connecting 113 is shut off, and the valve 117 connects the connections 116 . 120 with each other while connecting 119 is locked. In the second operating position, a double door control with an increased operating speed is possible: Given the barrier of the connection 119 through the valve 117 occurs on the primary side in the area of the branching 112 no distribution of the delivery volume of the pump 25 , Rather, the entire delivery volume of the pump 25 over the connection 18a the actuator 3a made available. In this case, with the pressure chamber 15a formed a kind of "master cylinder": the pressure chamber 15a is about the connection 19a and the connections 110 . 114 of the valve 111 as well as the connections 120 . 116 of the valve 117 with the connection 18b of the actuator 3b connected. With the pressure room 14b is then a kind of "slave cylinder" formed. The pressure chambers 15a . 14b are thus coupled fluidly to each other, whereby a coupling of the movement of the two actuators 3a . 3b with each other. Does this coupling of the movements lead to an actuating movement of the actuator as well 3b , the volume of the pressure chamber changes 15b of the actuator 3b , which fluid from the pressure chamber 15b is ejected. This passes over the connection 19b and that in view of the pressurization of the control line 123 opened check valve 115 to the secondary side 29 the pump 25 , As an actuation of the actuator 3a with the full delivery volume of the pump 25 takes place, there is an actuation of the actuator 3a with increased operating speed. Due to the coupling of the two actuators 3a . 3b together also results in an increased actuation speed of the actuator 3b , The same applies when reversing the conveying direction of the pump 25 ,
• c) Also possible is a single door control with a pure actuation of the actuator 3a : For this the valve takes 111 in the 17 effective position while the valve 117 in the in 17 not effective position is controlled. Given the barrier of the connection 119 through the valve 117 there is no distribution of the delivery volume in the area of the branch 122 , Rather, the entire delivery volume of the pump 25 over the connection 18a the actuator 3a made available. The pressure room 15a is about the connection 19a and the connections 110 . 113 of the valve 111 , the branch 121 and that in view of the pressurization of the control line 123 opened check valve 115 with the secondary side 29 connected. Thus, an actuating movement of the actuator 3a allows. By contrast, the pressure chamber 14b of the actuator 3b over the connection 18b , the connections 116 . 120 of the valve 117 and the connection 114 in the switching position of the valve 117 according to 17 shut off, so that a assumed position of the actuator 3b can not change. This results in a single door control via the actuator 3a , which with the full delivery volume of the pump 25 , So a large actuation speed occurs. Accordingly, a single door control for the actuator 3b done by the valve 111 in the in 17 not active position is switched while the valve 117 in the in 17 effective position is controlled.

• – Auf Grundlage des Signals des Drucksensors 125 und/oder des Wegsensors 126 kann eine Steuerung der Beendigung des Betriebs der Pumpe 25 erfolgen, wenn ein Zieldruck oder ein vorbestimmter Stellweg, insbesondere eine Öffnungsstellung oder eine Schließstellung erreicht ist.
• – Auf Grundlage des Signals des Drucksensors 125 und/oder des Wegsensors 126 kann eine Regelung des Förderbetriebs, des Fördervolumens und/oder einer Drehzahl der Pumpe 25 erfolgen.
• – Auf Grundlage des Signals des Drucksensors 125 und/oder des Wegsensors 126 kann eine Umschaltung zwischen den unterschiedlichen Betriebsstellungen der Ventileinrichtung 108 erfolgen. Beispielsweise kann mit der Erfassung der Annäherung der Flügeltüren 6a, 6b an die Schließstellung einer Umschaltung von der zweiten Betriebsstellung in die erste Betriebsstellung erfolgen.
• – Ist jeweils jedem Aktuator 3a, 3b ein Wegsensor 126, 126a zugeordnet, kann auch eine Einzeltürsteuerung auf Grundlage des zugeordneten Wegsensors 126, 126a für beide Aktuatoren 3a, 3b erfolgen.

It is possible that in the control circuit 2 , for example in the line between the primary side 27 and the actuator 3a and / or in a line between the secondary side 29 and the actuator 3b , a pressure sensor 125 is arranged. It is also possible that via a displacement sensor 126 the actuating movement of an actuator 3a . 3b is detected, wherein the displacement sensor 126 also with the measuring rod 103 may be formed according to the embodiments explained above. The signal of the pressure sensor 125 and / or the displacement sensor 126 can be used for different purposes:

• - Based on the signal from the pressure sensor 125 and / or the displacement sensor 126 may be a control of the termination of the operation of the pump 25 take place when a target pressure or a predetermined travel, in particular an open position or a closed position is reached.
• - Based on the signal from the pressure sensor 125 and / or the displacement sensor 126 may be a control of the delivery mode, the delivery volume and / or a speed of the pump 25 respectively.
• - Based on the signal from the pressure sensor 125 and / or the displacement sensor 126 can be a switch between the different operating positions of the valve device 108 respectively. For example, with the detection of the approach of the wing doors 6a . 6b to the closed position of a switch from the second operating position to the first operating position.
• - Is each actuator 3a . 3b a displacement sensor 126 . 126a can also be a single door control based on the associated displacement sensor 126 . 126a for both actuators 3a . 3b respectively.

Preferably, the fluidic control circuit 2 in the embodiments, a hydraulic control circuit, so that the actuators 3a . 3b be operated hydraulically. This is particularly advantageous for the second operating position, since then for the fluidic coupling of the two actuators 3a . 3b in series the same the incompressibility of the hydraulic medium can be used.

The invention finds application for any vehicles, especially passenger transport vehicles such as buses or trains of any kind and design. At the gullwing doors 6a . 6b it is preferably swinging sliding doors.

• – Der Steuerkreis 2 gemäß 17 kann bestimmt sein für zwei Flügeltüren 6a, 6b eines Fahrzeugs, insbesondere eines Busses, wobei diese beiden Flügeltüren 6a, 6b einer gemeinsamen Einstiegsöffnung zugeordnet sind. Durchaus möglich ist, dass zusätzlich zu den im Folgenden genannten zwei Flügeltüren 6a, 6b über den fluidischen Steuerkreis 2 auch weitere Flügeltüren angesteuert werden, welche weiteren Einstiegsöffnungen zugeordnet sind.
• – Die Begriffe ”steuern” oder ”Steuerkreis” umfassen auch eine Regelung bzw. einen Regelkreis, in welchem beispielsweise eine Regelung auf Grundlage einer Rückführung eines fluidischen Drucks oder eines Stellweges einer Flügeltür oder eines Aktuators erfolgt.
• – Die beiden einer Einstiegsöffnung zugeordneten Flügeltüren 6a, 6b können bei Steuerung durch den fluidischen Steuerkreis 2 gegenläufig zueinander bewegt werden, also aufeinander zu bewegt werden zum Schließen der Flügeltüren 6a, 6b sowie voneinander weg bewegt werden zum Öffnen der Flügeltüren 6a, 6b. Der Antrieb der Flügeltüren 6a, 6b erfolgt über zwei doppelt wirkende Aktuatoren 3a, 3b. Hierzu besitzen die Aktuatoren 3a, 3b jeweils zwei entgegengesetzt wirkende und durch den fluidischen Steuerkreis beaufschlagte Druckräume 14a, 15a, 14b, 15b.
• – In dem fluidischen Steuerkreis 2 kann eine Ventileinrichtung 108 Einsatz finden, welche unterschiedliche Betriebsstellungen besitzt und somit unterschiedliche Betriebsweisen ermöglicht. Hierbei umfasst die ”Ventileinrichtung 108” sowohl eine singuläre Ventileinrichtung mit einer Ventileinheit als auch eine mit mehreren verteilt angeordneten, über fluidische Leitungen miteinander verbundenen singulären Ventileinheiten oder Ventilen 111, 117.
• – In dem fluidischen Steuerkreis 2 verbindet u. U. die Ventileinrichtung 108 in einer ersten Betriebsstellung Druckräume 14a, 14b beider Aktuatoren 3a, 3b in fluidischer Parallelschaltung mit einer Primärseite 27 einer Pumpe 25. Somit teilt sich in dieser Betriebsstellung das Fördervolumen der Pumpe 25 auf die Druckräume 14a, 14b beider Aktuatoren 3a, 3b auf. Anders gesagt steht einem Aktuator 3a (3b) für dessen Beaufschlagung lediglich das halbe Fördervolumen der Pumpe 25 zur Verfügung. Dies hat zur Folge, dass für diese erste Betriebsstellung der Ventileinrichtung 108 eine verhältnismäßig langsame Stellbewegung der Aktuatoren 3a, 3b erfolgt, während andererseits unter Umständen in dieser Betriebsstellung verhältnismäßig große Stellkräfte der Aktuatoren 3a, 3b erzeugt werden können.
• – Es kann auch eine zweite Betriebsstellung der Ventileinrichtung 108 herbeigeführt und genutzt werden. In dieser zweiten Betriebsstellung ist lediglich ein Druckraum 14a eines ersten Aktuators 3a mit der Primärseite 27 der Pumpe 25 verbunden. Somit ist an sich durch Betrieb der Pumpe 25 unmittelbar lediglich dieser erste Aktuator 3a betätigbar. Der andere Druckraum 15a des ersten Aktuators 3a ist mit einem Druckraum 14b des zweiten Aktuators 3b verbunden. Der andere Druckraum 15a des ersten Aktuators 3a dient somit als eine Art ”Geberzylinder”, welcher entsprechend der Betätigung dieses Aktuators 3a durch die Pumpe 25 einen Druck erzeugt, welcher dem Druckraum 14b des zweiten Aktuators 3b zugeführt wird, der somit als eine Art ”Nehmerzylinder” wirkt. Anders gesagt sind die beiden Aktuatoren 3a, 3b fluidisch miteinander gekoppelt. Durch diese Kopplung erfolgt eine Kopplung der Bewegung der beiden Aktuatoren 3a, 3b miteinander. In der zweiten Betriebsstellung der Ventileinrichtung 108 wird das gesamte Fördervolumen der Pumpe 25 einem Druckraum 14a des ersten Aktuators 3a zugeführt, womit eine verhältnismäßig schnelle Öffnungs- oder Schließbewegung herbeigeführt werden kann. Diese schnelle Öffnungs- oder Schließbewegung wird dann über die Kopplung zwischen ”Geberzylinder” und ”Nehmerzylinder” auch auf den anderen Aktuator 3b übertragen. Anders gesagt befinden sich für die zweite Betriebsstellung der erste Aktuator 3a und der zweite Aktuator 3b in einer fluidischen Reihenschaltung zwischen der Primärseite 27 und der Sekundärseite 29. Die zweite Betriebsstellung ist insbesondere dann von Vorteil, wenn eine schnelle Bewegung der Flügeltüren 6a, 6b gewünscht ist. Unter Umständen ergeben sich aber für diese Betriebsstellung verringerte Stellkräfte der Aktuatoren 3a, 3b.
• – Die Wahl zwischen den beiden genannten Betriebsstellungen kann je nach Bedarf erfolgen. So kann beispielsweise eine normale Bewegung der Flügeltüren 6a, 6b in der ersten Betriebsstellung erfolgen, während eine Notöffnung oder Notschließung, für welche eine erhöhte Stellgeschwindigkeit der Flügeltüren 6a, 6b gewünscht ist, in der zweiten Betriebsstellung erfolgen kann.
• – In besonderer Ausgestaltung ist der fluidische Steuerkreis 2 mit einer Steuervorrichtung ausgestattet. Diese Steuervorrichtung ist geeignet ausgebildet, um die Ventileinrichtung 108 bedarfsgerecht von der ersten Betriebsstellung in die zweite Betriebsstellung und/oder umgekehrt zu überführen. Diese Überführung erfolgt während einer Öffnungs- und/oder Schließbewegung der Flügeltüren 6a, 6b. Um lediglich ein nicht beschränkendes Beispiel zu nennen, kann während einer Schließbewegung die Ventileinrichtung 108 zunächst die zweite Betriebsstellung einnehmen, womit eine große Schließgeschwindigkeit gewährleistet ist. Nach einem gewissen Schließweg erfolgt dann die Umschaltung der Ventileinrichtung 108 in die erste Betriebsstellung, womit eine Verlangsamung der Bewegung der Flügeltüren 6a, 6b erfolgt mit Annäherung an die Schließstellung. Unter Umständen können für erhöhte Stellkräfte in der ersten Betriebsstellung auch erhöhte Schließkräfte erzeugt werden, womit ein enges und dichtes Anlegen der Flügeltüren 6a, 6b an einen Türrahmen, eine Dichtung u. ä. gewährleistet werden kann.
• – Für die Steuerung der Überführung von der ersten Betriebsstellung in die zweite Betriebsstellung und/oder umgekehrt gibt es vielfältige Möglichkeiten:
• – Für eine besondere Ausgestaltung sind eine Steuervorrichtung (bei der es sich auch um die vorgenannte Steuervorrichtung handeln kann) und ein Drucksensor 125 vorgesehen. Der Drucksensor 125 dient der Erfassung eines Drucks in dem fluidischen Steuerkreis 2, beispielsweise in einer der Druckräume oder einer zu dieser führenden Leitung. Abhängig von dem von dem Drucksensor 125 erfassten Druck wird die Ventileinrichtung 108 dann von der ersten Betriebsstellung in die zweite Betriebsstellung und/oder umgekehrt überführt. Beispielsweise möglich ist, dass der Wechsel der Betriebsstellung durch die Steuervorrichtung herbeigeführt wird, wenn ein Schwellwert des Drucks über- oder unterschritten wird. Um lediglich ein nicht beschränkendes Beispiel zu nennen, kann zunächst die Schließbewegung in der zweiten Betriebsstellung herbeigeführt werden. Liegen dann die Flügeltüren 6a, 6b an einem Türrahmen oder einer Dichtung an, steigt der Druck, welcher von dem Drucksensor 125 erfasst wird. Mit Überschreiten des Schwellwertes kann dann umgeschaltet werden auf die erste Betriebsstellung, um die für das endgültige Schließen der Flügeltüren 6a, 6b erforderlichen Stellkräfte herbeizuführen. Durchaus möglich ist, dass die Kinematik der Antriebseinrichtung für die Flügeltüren 6a, 6b derart ausgebildet ist, dass sich je nach Stellweg der Aktuatoren 3a, 3b und der Flügeltüren 6a, 6b ein unterschiedlicher Druck ergibt, der von dem Drucksensor 125 erfasst wird. Dies ist insbesondere dann der Fall, wenn die Bewegung gegen eine zunehmend beaufschlagte Rückstellfeder erfolgt. Über den Drucksensor 125 kann dann mittelbar auch der Stellweg des Aktuators 3a, 3b erfasst werden, sodass für einen vorbestimmten Öffnungs- oder Schließweg mit dem hiermit korrelierenden erfassten Druck das Umschalten der Betriebsstellung erfolgt.
• – Für eine weitere besondere Ausführungsform sind eine Steuervorrichtung (bei welcher es sich auch um die vorgenannte Steuervorrichtung handeln kann) und ein Wegsensor 126 vorgesehen. Der Wegsensor 126 dient der Erfassung eines Wegs eines Aktuators 3a, 3b oder einer Flügeltür 6a, 6b. Hierbei wird unter einen Wegsensor 126 bzw. einen Weg auch ein Winkelsensor oder ein Geschwindigkeitssensor subsumiert, mittels dessen letztendlich die Stellbewegung des Aktuators 3a, 3b oder der Flügeltür 6a, 6b erfasst werden kann. Abhängig von dem von dem Wegsensor 126 erfassten Stellweg wird die Ventileinrichtung 108 von der ersten Betriebsstellung in die zweite Betriebsstellung und/oder umgekehrt überführt. Um lediglich ein einfaches, nicht beschränkendes Beispiel zu nennen, kann zunächst die Schließbewegung aus der Öffnungsstellung in der zweiten Betriebsstellung der Ventileinrichtung 108 bewirkt werden, womit eine schnelle Schließung der Flügeltüren 6a, 6b herbeigeführt werden kann. Überschreitet der durch den Wegsensor 126 erfasste Stellweg einen Schwellenwert, kann die Umschaltung auf die erste Betriebsstellung erfolgen, sodass der letzte Teil des Stellwegs für die Schließung der Flügeltüren 6a, 6b mit verringerter Geschwindigkeit und/oder erhöhten Stellkräften herbeigeführt werden kann.
• – Für die Ausbildung der Steuervorrichtung gibt es vielfältige Möglichkeiten. Durchaus möglich ist, dass die Steuervorrichtung als fluidische Steuervorrichtung ausgebildet ist, welche beispielsweise druckabhängig oder bewegungsgesteuert umgeschaltet werden kann. In bevorzugter Ausgestaltung findet als Steuervorrichtung eine elektronische Steuereinheit Einsatz, welcher Betriebssignale wie beispielsweise die von dem Drucksensor 125 oder Wegsensor 126 erfassten Signale zugeführt werden. Auf Grundlage dieser Betriebssignale kann dann die Steuervorrichtung unmittelbar direkt angesteuerte Ventile in Ausbildung als Magnetventile oder elektromagnetisch vorgesteuerte Ventile 111, 117 der Ventileinrichtung 108 ansteuern, um die genannten Betriebsstellungen herbeizuführen.
• – Durchaus möglich ist, dass für die Beaufschlagung der Aktuatoren 3a, 3b mittels der Pumpe 25 immer beide Aktuatoren 3a, 3b der Flügeltüren 6a, 6b, die einer Einstiegsöffnung zugeordnet sind, gleichzeitig angesteuert werden. Dieses wird im Folgenden auch als ”Doppeltürsteuerung” bezeichnet.
• – Optional möglich ist, dass mittels einer Handnotbetätigung (ohne Betrieb der Pumpe) auch eine manuelle Öffnung lediglich einer Flügeltür oder beider Flügeltüren möglich ist.
• – In bevorzugter Ausgestaltung besitzt die Ventileinrichtung 108 eine weitere Betriebsstellung, in welcher eine Einzeltürsteuerung erfolgt. Dies bedeutet, dass bei Betrieb der Pumpe 25 eine der beiden Flügeltüren ihre eingenommene Stellung behält, was vorzugsweise bedingt ist dadurch, dass zumindest ein Druckraum des Aktuators, der dieser Flügeltür zugeordnet ist, abgesperrt ist. Hingegen kann in der weiteren Betriebsstellung mittels Betriebs der Pumpe 25 gezielt das Öffnen und/oder Schließen der anderen Flügeltür erfolgen. Für diese Ausgestaltung besitzt somit die Ventileinrichtung 108 drei unterschiedliche Betriebsstellungen mit drei unterschiedlichen Betriebsweisen, nämlich
• – eine Einzeltürsteuerung,
• – eine Doppeltürsteuerung mit verringerter Betätigungsgeschwindigkeit (erste Betriebsstellung der Ventileinrichtung) sowie
• – eine Doppeltürsteuerung mit erhöhter Betätigungsgeschwindigkeit (zweite Betriebsstellung der Ventileinrichtung).
• – Für die konkrete konstruktive Ausgestaltung des fluidischen Steuerkreises 2 gibt es vielfältige Möglichkeiten. Für eine besondere Ausgestaltung ist eine Primärseite 27 einer Pumpe 25 mit einem Druckraum 14a des ersten Aktuators 3a verbunden. Des Weiteren ist ein Ventil 111 vorhanden, über welches optional die Primärseite 27 der Pumpe 25 zusätzlich mit einem Druckraum 14b des zweiten Aktuators 3b verbindbar ist. Entsprechendes gilt für eine Sekundärseite 29 der Pumpe 25, die mit einem Druckraum 15b des zweiten Aktuators 3b verbunden ist: Über ein Ventil 117 ist dann die Sekundärseite 29 der Pumpe 25 optional zusätzlich mit einem Druckraum 15a des ersten Aktuators 3a verbindbar. Je nach Betriebsstellung der beiden genannten Ventile 111, 117 kann somit eine Einzeltürsteuerung, eine Doppeltürsteuerung mit verringerter Betätigungsgeschwindigkeit und/oder eine Doppeltürsteuerung mit erhöhter Betätigungsgeschwindigkeit erfolgen.
• – In weiterer Ausgestaltung ist eine Primärseite 27 der Pumpe 25 mit einem Druckraum 14a des ersten Aktuators 3a verbunden, während der andere Druckraum 15a des ersten Aktuators 3a je nach Betriebsstellung der Ventileinrichtung 108
• – mit der Sekundärseite 29 der Pumpe 25 verbindbar ist, was vorzugsweise in der ersten Betriebsstellung der Fall ist, womit eine Doppeltürsteuerung mit verringerter Betätigungsgeschwindigkeit ermöglicht ist,
• – absperrbar ist, womit dieser Aktuator 3a deaktiviert sein kann, sodass eine Einzeltürsteuerung über den anderen Aktuator 3b ermöglicht ist, oder
• – mit einem Druckraum 14b des zweiten Aktuators 3b verbindbar ist, womit insbesondere die zweite Betriebsstellung gewährleistet ist, in welcher eine Doppeltürsteuerung mit erhöhter Betätigungsgeschwindigkeit möglich ist.
• – Für die in der Ventileinrichtung 108 eingesetzten Ventile 111 gibt es vielfältige Möglichkeiten. In besonderer Ausgestaltung ist mindestens eines der genannten Ventile 111, 117 oder sind beide genannten Ventile 111, 117 als 3/2-Wegeventil(e) 112, 118 ausgebildet. Derartige Ventile erfüllen die oben genannten Funktionen, sind aber einfach ausgebildet und können zu geringen Kosten hergestellt oder bezogen werden. Hierbei kann das 3/2-Wegeventil 112, 118 in beliebiger Bauart ausgebildet sein, insbesondere als Schieberventil oder als Sitzventil. Möglich ist die Ausbildung der Ventile 111, 117 als Magnetventile zur Ermöglichung einer direkten elektrischen Ansteuerung durch eine elektronische Steuereinheit.
• – Durchaus möglich ist, dass die Ventile 111, 117 unmittelbar gesteuert sind. Möglich ist durchaus, dass die Ventile 111, 117 elektromagnetisch durch die Steuervorrichtung, hier eine elektronische Steuereinheit, direkt gesteuert sind. Wie erläutert kann auch eine unmittelbare Steuerung beispielsweise durch den Druck in einem Druckraum oder bewegungsgesteuert erfolgen. In anderer Ausgestaltung sind die Ventile 111, 117 elektropneumatisch vorgesteuert, was insbesondere den Vorteil hat, dass mit kleinen Steuerströmen und klein bauenden elektromagnetischen Aktuatoren eines Vorsteuerventils die Steuerdrücke und mit diesen die erforderlichen Stellkräfte des Ventils 111, 117 erzeugt werden können.
• – Entsprechend den aus obigem Stand der Technik bekannten Ausführungsformen kann auch eine Handnotbetätigung der Flügeltüren 6a, 6b ermöglicht sein. In bevorzugter Ausgestaltung ist in dem fluidischen Steuerkreis 2 zwischen eine Primärseite 27 und eine Sekundärseite 29 einer Pumpe 25 eine Bypassleitung 30 zwischengeschaltet. In der Bypassleitung 30 ist ein Handnotventil 31 angeordnet. Mit manueller Betätigung des Handnotventils 31 kann somit die Pumpe 25 ”überbrückt” werden, sodass unabhängig vom Betrieb der Pumpe 25 eine manuelle Öffnung zumindest einer Flügeltür 6a, 6b erfolgen kann, womit letztendlich Fluid von einem Druckraum in einen anderen Druckraum infolge der manuell aufgebrachten Kräfte umgewälzt wird.
• – In weiterer Ausgestaltung ist zwischen Pumpe 25 und Aktuator 3a, 3b eine in Richtung eines Druckraums des Aktuators öffnendes Rückschlagventil 109, 115 angeordnet. Das Rückschlagventil 109, 115 ermöglicht bei Betrieb der Pumpe 25 einen fluidischen Fluss von der Pumpe 25 in Richtung des zugeordneten Druckraums des Aktuators. Hierdurch ist die Öffnungsrichtung des Rückschlagventils 109, 115 vorgegeben. Ohne Betrieb der Pumpe 25 sperrt das Rückschlagventil 109, 115 den Druckraum ab, sodass eine einmal eingenommene Öffnungs- oder Schließstellung (oder auch eine Mittenstellung) der Flügeltür 6a, 6b beibehalten wird. Das Rückschlagventil 109, 115 ist aber auch derart zusätzlich angesteuert, dass dieses entsperrt werden kann und in entgegengesetzte Richtung geöffnet werden kann. Diese Ansteuerung erfolgt bei Umkehrung der Förderrichtung der Pumpe 25 derart, dass das Rückschlagventil 109, 115 einen fluidischen Fluss von dem Druckraum zu der Pumpe 25 ermöglicht. Entsprechendes gilt für den Einsatz eines Sperrventils anstelle des Rückschlagventils 109, 115, welches ebenfalls die genannten Funktionen und die genannte Ansteuerung ermöglicht.
• – Vorzugsweise finden in den Ventilen 111, 117 der Ventileinrichtung 108 Federelemente Einsatz, welche eine nicht angesteuerte Stellung der Ventile 111, 117 vorgeben. Vorzugsweise befinden sich die Ventile 111 117 bzw. befindet sich die Ventileinrichtung 108 ohne Ansteuerung in der ersten Betriebsstellung.
• – Vorzugsweise findet eine reversierbare Pumpe 25 Einsatz. Somit sind die Zuordnungen ”Primärseite 27” sowie ”Sekundärseite 29” nicht fest – vielmehr hängen diese ab von der jeweils wirksamen Förderrichtung der Pumpe 25.

The drive device according to the invention 1 as defined in the claims may be used in conjunction with the following alternative or cumulative embodiments or refinements of the fluidic control circuit 2 :

• - The control circuit 2 according to 17 can be determined for two double doors 6a . 6b a vehicle, in particular a bus, these two double doors 6a . 6b associated with a common manhole. It is quite possible that in addition to the two hinged doors mentioned below 6a . 6b via the fluidic control circuit 2 Also further gullwing doors are controlled, which are associated with further access openings.
• - The terms "control" or "control circuit" also include a control or a control circuit in which, for example, a control based on a return of a fluid pressure or a travel of a wing door or an actuator takes place.
• - The two hinged doors assigned to a manhole 6a . 6b can be controlled by the fluidic control circuit 2 be moved in opposite directions to each other, so moved towards each other to close the folding doors 6a . 6b as well as moving away from each other to open the double doors 6a . 6b , The drive of the gullwing doors 6a . 6b via two double-acting actuators 3a . 3b , The actuators have this feature 3a . 3b two oppositely acting and acted upon by the fluidic control circuit pressure chambers 14a . 15a . 14b . 15b ,
• - In the fluidic control circuit 2 can be a valve device 108 Use find that has different operating positions and thus allows different modes of operation. In this case, the "valve device 108 "Both a singular valve device with a valve unit as well as with a plurality of distributed, interconnected via fluidic lines singular valve units or valves 111 . 117 ,
• - In the fluidic control circuit 2 connects u. U. the valve device 108 in a first operating position pressure chambers 14a . 14b both actuators 3a . 3b in fluidic parallel connection with a primary side 27 a pump 25 , Thus, in this operating position divides the delivery volume of the pump 25 on the pressure chambers 14a . 14b both actuators 3a . 3b on. In other words, an actuator stands 3a ( 3b ) for its admission only half the delivery volume of the pump 25 to disposal. This has the consequence that for this first operating position of the valve device 108 a relatively slow actuating movement of the actuators 3a . 3b takes place, while on the other hand under certain circumstances in this operating position relatively large actuating forces of the actuators 3a . 3b can be generated.
• - It can also be a second operating position of the valve device 108 be brought and used. In this second operating position is only a pressure chamber 14a a first actuator 3a with the primary side 27 the pump 25 connected. Thus, in itself by operation of the pump 25 immediately only this first actuator 3a actuated. The other pressure chamber 15a of the first actuator 3a is with a pressure room 14b of the second actuator 3b connected. The other pressure chamber 15a of the first actuator 3a thus serves as a kind of "master cylinder", which according to the operation of this actuator 3a through the pump 25 generates a pressure which the pressure chamber 14b of the second actuator 3b is supplied, which thus acts as a kind of "slave cylinder". In other words, the two actuators 3a . 3b fluidly coupled together. Through this coupling, a coupling of the movement of the two actuators takes place 3a . 3b together. In the second operating position of the valve device 108 becomes the total delivery volume of the pump 25 a pressure room 14a of the first actuator 3a supplied, whereby a relatively fast opening or closing movement can be brought about. This fast opening or Closing movement is then via the coupling between "master cylinder" and "slave cylinder" on the other actuator 3b transfer. In other words, the first actuator is located for the second operating position 3a and the second actuator 3b in a fluidic series connection between the primary side 27 and the secondary side 29 , The second operating position is particularly advantageous if a fast movement of the gullwing doors 6a . 6b is desired. Under certain circumstances, however, reduced actuating forces of the actuators result for this operating position 3a . 3b ,
• - The choice between the two mentioned operating positions can be made as required. For example, a normal movement of the gullwing doors 6a . 6b take place in the first operating position, during an emergency opening or emergency closure, for which an increased positioning speed of the folding doors 6a . 6b is desired, can be done in the second operating position.
• - In a special embodiment, the fluidic control circuit 2 equipped with a control device. This control device is designed to be suitable for the valve device 108 to transfer from the first operating position to the second operating position and / or vice versa as needed. This transfer takes place during an opening and / or closing movement of the folding doors 6a . 6b , To mention only a non-limiting example, during a closing movement, the valve device 108 first occupy the second operating position, whereby a large closing speed is guaranteed. After a certain closing path then the switching of the valve device takes place 108 in the first operating position, bringing a slowing down the movement of the gullwing doors 6a . 6b takes place with approach to the closed position. Under certain circumstances, increased closing forces can be generated for increased restoring forces in the first operating position, whereby a tight and dense application of the gullwing doors 6a . 6b to a door frame, a seal u. Ä. Can be guaranteed.
• - There are many possibilities for controlling the transfer from the first operating position to the second operating position and / or vice versa:
• - For a particular embodiment, a control device (which may also be the aforementioned control device) and a pressure sensor 125 intended. The pressure sensor 125 serves to detect a pressure in the fluidic control circuit 2 , For example, in one of the pressure chambers or a leading line to this. Depends on that of the pressure sensor 125 detected pressure is the valve device 108 then transferred from the first operating position to the second operating position and / or vice versa. For example, it is possible that the change of the operating position is brought about by the control device when a threshold value of the pressure is exceeded or fallen below. To mention only a non-limiting example, the closing movement in the second operating position can first be brought about. Then lie the double doors 6a . 6b on a door frame or gasket, the pressure exerted by the pressure sensor increases 125 is detected. When the threshold value is exceeded, it is then possible to switch over to the first operating position, that for the final closing of the folding doors 6a . 6b necessary restoring forces to bring about. It is quite possible that the kinematics of the drive device for the folding doors 6a . 6b is formed such that depending on the travel of the actuators 3a . 3b and the double doors 6a . 6b a different pressure results from that of the pressure sensor 125 is detected. This is the case in particular when the movement takes place against an increasingly acted upon return spring. About the pressure sensor 125 can then indirectly also the travel of the actuator 3a . 3b be detected, so that the switchover of the operating position takes place for a predetermined opening or closing path with the correlated detected pressure.
• - For another particular embodiment, a control device (which may also be the aforementioned control device) and a displacement sensor 126 intended. The displacement sensor 126 serves to detect a path of an actuator 3a . 3b or a double door 6a . 6b , This is under a displacement sensor 126 or a path also subsumes an angle sensor or a speed sensor, by means of which ultimately the adjusting movement of the actuator 3a . 3b or the gullwing door 6a . 6b can be detected. Depending on the distance sensor 126 detected travel is the valve device 108 transferred from the first operating position to the second operating position and / or vice versa. To mention only a simple, non-limiting example, first, the closing movement from the open position in the second operating position of the valve device 108 be effected, bringing a rapid closure of the double doors 6a . 6b can be brought about. Exceeds the through the displacement sensor 126 If the travel detected was a threshold value, the switchover to the first operating position can take place, so that the last part of the travel path for closing the folding doors 6a . 6b with reduced speed and / or increased restoring forces can be brought about.
• - There are many possibilities for the design of the control device. It is entirely possible that the control device is designed as a fluidic control device, which, for example, pressure-dependent or motion-controlled can be switched. In a preferred embodiment, an electronic control unit is used as a control device, which operating signals such as those of the pressure sensor 125 or displacement sensor 126 be supplied detected signals. On the basis of these operating signals, the control device can then directly directly controlled valves in training as solenoid valves or solenoid pilot operated valves 111 . 117 the valve device 108 control to bring about the aforementioned operating positions.
• - It is quite possible that for the actuation of the actuators 3a . 3b by means of the pump 25 always both actuators 3a . 3b the gullwing doors 6a . 6b , which are assigned to a manhole, are controlled simultaneously. This is also referred to below as "double door control".
• - It is optionally possible that by means of a manual override (without operation of the pump) also a manual opening of only a double door or both wing doors is possible.
• - In a preferred embodiment, the valve device has 108 another operating position, in which a single door control takes place. This means that when operating the pump 25 one of the two hinged doors retains its assumed position, which is preferably due to the fact that at least one pressure chamber of the actuator associated with this hinged door is shut off. However, in the further operating position by means of operation of the pump 25 purposefully opening and / or closing the other hinged door done. For this embodiment, thus has the valve device 108 three different operating positions with three different operating modes, namely
• - a single door control,
• - A double door control with reduced operating speed (first operating position of the valve device) and
• - A double door control with increased operating speed (second operating position of the valve device).
• - For the concrete structural design of the fluidic control circuit 2 There are many possibilities. For a particular embodiment is a primary page 27 a pump 25 with a pressure room 14a of the first actuator 3a connected. There is also a valve 111 available, via which optionally the primary side 27 the pump 25 additionally with a pressure room 14b of the second actuator 3b is connectable. The same applies to a secondary page 29 the pump 25 that with a pressure room 15b of the second actuator 3b connected: via a valve 117 is then the secondary side 29 the pump 25 optionally with a pressure chamber 15a of the first actuator 3a connectable. Depending on the operating position of the two valves mentioned 111 . 117 Thus, a single door control, a double door control with reduced operating speed and / or a double door control with increased operating speed can be carried out.
• - In a further embodiment is a primary page 27 the pump 25 with a pressure room 14a of the first actuator 3a connected while the other pressure chamber 15a of the first actuator 3a depending on the operating position of the valve device 108
• - with the secondary side 29 the pump 25 is connectable, which is preferably the case in the first operating position, whereby a double door control with reduced operating speed is made possible,
• - Lockable, what this actuator 3a can be disabled, allowing a single door control over the other actuator 3b is possible, or
• - with a pressure chamber 14b of the second actuator 3b is connectable, which in particular the second operating position is ensured, in which a double door control with increased operating speed is possible.
• - For those in the valve device 108 used valves 111 There are many possibilities. In a particular embodiment, at least one of said valves 111 . 117 or are both valves mentioned 111 . 117 as 3/2-way valve (s) 112 . 118 educated. Such valves fulfill the above-mentioned functions, but are simple in design and can be manufactured or purchased at low cost. Here, the 3/2-way valve 112 . 118 be designed in any type, in particular as a slide valve or seat valve. It is possible to design the valves 111 . 117 as solenoid valves to allow direct electrical control by an electronic control unit.
• - It is quite possible that the valves 111 . 117 are directly controlled. It is quite possible that the valves 111 . 117 Electromagnetically by the control device, here an electronic control unit, are directly controlled. As explained, an immediate control, for example, by the pressure in a pressure chamber or motion-controlled done. In another embodiment, the valves 111 . 117 electro-pneumatically piloted, which in particular has the advantage that with small control currents and small-sized electromagnetic actuators of a pilot valve, the control pressures and with these the required actuating forces of the valve 111 . 117 can be generated.
• - According to the known from the above prior art embodiments, a manual override the gullwing doors 6a . 6b be possible. In a preferred embodiment, in the fluidic control circuit 2 between a primary page 27 and a secondary side 29 a pump 25 a bypass line 30 interposed. In the bypass line 30 is a manual emergency valve 31 arranged. With manual actuation of the manual emergency valve 31 can thus the pump 25 Be "bridged" so that regardless of the operation of the pump 25 a manual opening of at least one hinged door 6a . 6b can be done, which ultimately fluid is circulated from one pressure chamber to another pressure chamber due to the manually applied forces.
• - In another embodiment is between pump 25 and actuator 3a . 3b a non-return valve opening in the direction of a pressure chamber of the actuator 109 . 115 arranged. The check valve 109 . 115 allows operation of the pump 25 a fluidic flow from the pump 25 in the direction of the associated pressure chamber of the actuator. As a result, the opening direction of the check valve 109 . 115 specified. Without operation of the pump 25 locks the check valve 109 . 115 the pressure chamber, so that once taken open or closed position (or a center position) of the hinged door 6a . 6b is maintained. The check valve 109 . 115 but is also controlled in such a way that it can be unlocked and can be opened in the opposite direction. This control takes place in case of reversal of the conveying direction of the pump 25 such that the check valve 109 . 115 a fluidic flow from the pressure chamber to the pump 25 allows. The same applies to the use of a check valve instead of the check valve 109 . 115 , which also allows the said functions and the aforementioned control.
• - Preferably found in the valves 111 . 117 the valve device 108 Spring elements use, which is a non-activated position of the valves 111 . 117 pretend. Preferably, the valves are located 111 117 or is the valve device 108 without activation in the first operating position.
• - Preferably finds a reversible pump 25 Commitment. Thus, the assignments are "primary page 27 "As well as" secondary side 29 "Not fixed - but these depend on the effective direction of the pump 25 ,

LIST OF REFERENCE NUMBERS

1

driving means

2

fluidic control circuit

3

actuator

4

Opening and closing movement

5

holder

6

hinged door

7

cylinder unit

8th

cylinder housing

9

Sealing and guiding unit

10

Sealing and guiding unit

11

Longitudinal guide device

12

guide tube

13

inner space

14

pressure chamber

15

pressure chamber

16

piston area

17

piston area

18

connection

19

connection

20

channel

21

channel

22

check valve

23

check valve

24

separating body

25

pump

26

power unit

27

primary

28

3/2-way solenoid valve

29

secondary side

30

bypass line

31

Handnotventil

32

branch

33

bypass line

34

3/2-way solenoid valve

35

3/2-way solenoid valve

36

bypass line

37

branch

38

connecting line

39

support means

40

support means

41

through recess

42

through recess

43

sealing element

44

coupling sleeve

45

Federation

46

coupling screw

47

paragraph

48

head

49

channel

50

inner space

51

branch bore

52

sealing element

53

sealing element

54

ring body

55

spigot

56

spigot

57

Sealing and guiding surface

58

groove

59

sealing element

60

channel

61

channel

62

branch bore

63

branch bore

64

Cylinder housing tube

65

Lateral guidance device

66

guide rod

67

support means

68

body

69

guide carriage

70

recess

71

guide bush

72

guide bush

73

spring element

74

Driver unit

75

extension

76

recess

77

coupling rod

78

takeaway

79

shell

80

mother

81

Toggle mechanism

82

first toggle

83

second toggle

84

knee

85

first effective direction

86

second direction of action

87

end

88

bearing eye

89

end

90

ball joint

91

coupling element

92

mother

93

spring element

94

Latching or locking device

95

Latching or locking groove

96

Spin column

97

wing

98

coupling rod

99

ball head

100

holder

101

wing

102

suspension

103

measuring rod

104

manifold

105

Guide unit

106

ball head

107

swivel angle

108

valve means

109

controllable non-return valve

110

connection

111

Valve

112

3/2-way valve

113

connection

114

connection

115

controllable non-return valve

116

connection

117

Valve

118

3/2-way valve

119

connection

120

connection

121

branch

122

branch

123

control line

124

control line

125

pressure sensor

126

displacement sensor

Claims (20)

Drive device ( 1 ) for at least one hinged door ( 6a . 6b ) of a vehicle with an actuator ( 3a . 3b ), by means of which a movement of at least one hinged door ( 6a ; 6b ) can be brought in a longitudinal direction (x) over a longitudinal stroke, which only in a partial stroke of the longitudinal stroke with the movement of the at least one hinged door ( 6a . 6b ) is mechanically coupled in a transverse direction (y), wherein the mechanical decoupling outside the sub-stroke via a game, a lot, a telescopic outside the sub-stroke drive connection, an effective outside the sub-stroke slot, a motion-controlled switching element or an electrically or electro-pneumatically controlled and switchable coupling element takes place. Drive device ( 1 ) according to claim 1, characterized in that a cylinder housing ( 8a . 8b ) of the actuator ( 3a . 3b ) with the movement of the hinged door ( 6a . 6b ) is moved. Drive device ( 1 ) according to claim 1 or 2 with a) a holding device ( 5a . 5b ), where the hinged door ( 6a . 6b ), b) a longitudinal guide device ( 11a . 11b ) for the holding device ( 5a . 5b ) or the cylinder housing ( 8a . 8b ), c) support devices ( 39 . 40 ) for the longitudinal guide device ( 11 ) which are movable in the transverse direction (y), d) wherein by means of the actuator ( 3a . 3b ) a movement of the holding device ( 5a . 5b ) or the cylinder housing ( 8a . 8b ) along the longitudinal guide device ( 11a . 11b ) can be brought in the longitudinal direction (x) over the longitudinal stroke, which only in the partial stroke of the longitudinal stroke with the movement of the supporting device ( 39 ; 40 ) is coupled in the transverse direction (y). Drive device ( 1 ) according to claim 3, characterized in that the coupling of the movement of the holding device ( 5a . 5b ) or the cylinder housing ( 8a . 8b ) with the movement of the support device ( 39 ; 40 ) via a driver unit ( 74 ) takes place, which mechanically only for the partial stroke the holding device ( 5a . 5b ) or the cylinder housing ( 8a . 8b ) with the support device ( 39 . 40 ) couples. Drive device ( 1 ) according to claim 4, characterized in that the position of the driver unit ( 74 ) and thus the size of the partial stroke is adjustable. Drive device ( 1 ) according to one of claims 3 to 5, characterized in that the supporting devices ( 39 . 40 ) as a support carriage ( 69 ) are formed, which by a transverse guide device ( 65 ) are guided in the transverse direction (y). Drive device ( 1 ) according to claim 6, characterized in that the Cross guide device ( 65 ) with a guide rail or guide rod ( 66 ) is formed. Drive device ( 1 ) according to one of claims 3 to 7, characterized in that the support means ( 39 . 40 ) via a toggle mechanism ( 81a . 81b ) on a carrying device ( 67 ) are supported, wherein a coupling of the movement of the holding device ( 5a . 5b ) or the cylinder housing ( 8a . 8b ) with the movement of the support devices ( 39 . 40 ) via the toggle mechanism ( 81a . 81b ) he follows. Drive device ( 1 ) according to claim 8 when appended to one of claims 5 to 7, characterized in that on a toggle lever ( 82 ) of the toggle mechanism ( 81 ) or on a knee joint ( 84 ) a coupling rod ( 77 ) is hinged, which in the partial stroke on the driver unit ( 74 ) with the holding device ( 5 ) or the cylinder housing ( 8a . 8b ) is coupled. Drive device ( 1 ) according to one of claims 3 to 9, characterized in that the movement of the supporting device ( 39 . 40 ), the guide carriage ( 69 ) and / or the toggle mechanism ( 81 ) via a rotary column ( 96 ) with the movement of a second holding device ( 100 ), where the hinged door ( 6 ) in addition is coupled. Drive device ( 1 ) according to claim 10, characterized in that the rotary column ( 96 ) via one on the rotary column ( 96 ) attached rocker ( 97 ) and a coupling rod ( 98 ) with the movement of the support device ( 39 . 40 ), the guide carriage ( 69 ) or the toggle mechanism ( 81 ), wherein an end region of the coupling rod ( 98 ) on the rocker ( 97 ) is hinged and another end portion of the coupling rod ( 98 ) on the toggle mechanism ( 81 ), the support device ( 39 . 40 ) or the guide carriage ( 69 ) is articulated. Drive device ( 1 ) according to one of the preceding claims, characterized in that the actuator ( 3a . 3b ) is a fluidically actuated actuator. Drive device ( 1 ) according to one of the preceding claims with a) a movable cylinder housing ( 8th ), b) one between the support devices ( 39 . 40 ) extending longitudinal guide device ( 11 ), opposite which the cylinder housing ( 8th ), c) one of the longitudinal guide device ( 11 ) carried separating body ( 24 ), which two in the cylinder housing ( 8th ) pressure chambers ( 14 . 15 ) separates. d) channels ( 20 . 21 ) over which the pressure chambers ( 14 . 15 ) are acted upon by the fluid and e) of the cylinder housings ( 8th ) formed piston surfaces ( 16 . 17 ). Drive device ( 1 ) according to claim 13, characterized in that the channels ( 20 . 21 ) at least partially in the longitudinal guide device ( 11 ) are formed. Drive device ( 1 ) according to claim 13 or 14, characterized in that the pressure chambers ( 14 . 15 ) via at least one throttle or at least one check valve ( 22 ; 23 ) are coupled together. Drive device ( 1 ) according to one of claims 3 to 15, characterized in that at least one support device ( 39 . 40 ) via a latching or locking device ( 94 ) in the transverse direction (y) can be locked or locked. Drive device ( 1 ) according to one of claims 3 to 16, characterized in that the support devices ( 39 ; 40 ) via a spring element ( 73 ) on a carrying device ( 67 ) supported by a movement of the support device ( 39 ; 40 ) in the transverse direction (y) can be acted upon. Drive device ( 1 ) according to one of claims 6 to 17, characterized in that the transverse guide device ( 65 ) with at least one degree of freedom relative to a carrying device ( 67 ), wherein a movement along this degree of freedom a change in the orientation of the longitudinal guide device ( 11 ). Drive device ( 1 ) according to one of the preceding claims, characterized in that by means of the drive device ( 1 ) two double doors ( 6a . 6b ) can be opened and closed synchronously. Drive device ( 1 ) according to one of the preceding claims, characterized in that by means of the drive device ( 1 ) a) two hinged doors ( 6a . 6b ) can be opened and closed synchronously or b) only a hinged door ( 6a ; 6b ) is opened or closed while the other hinged door ( 6b ; 6a ) remains open or closed.

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