EP2752547A2 - Fluidic control circuit for two doors of a bus - Google Patents

Abstract

The circuit (2) has wing doors provided with a drive that is made by two doubled-working actuators (3a, 3b). A primary side (27) of a pump (25) is in fluidic parallel connection with pressure chambers (14a, 14b) of the actuators in a first operational position of a valve device. The pressure chamber of the actuator is connected with the primary side of the pump and another pressure chamber (15a) of the actuator is connected with the pressure chamber of another actuator in a second operational position of the valve device such that the movement of the actuators are coupled with one another.

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a fluidic control circuit for two gullwing doors of a vehicle, in particular a bus.

STATE OF THE ART

Buses have entry openings for the driver and passengers, in which a door frame is closed by two counter-opening and closing double doors. From a sealed closed position of the wing doors, in which the wing door are arranged flush with an outer skin of the bus, the wing door are first moved transversely to the longitudinal axis of the bus to the outside to then be moved in opposite directions parallel to the longitudinal axis of the bus, in which case the folding doors can be passed outside of the outer skin of the bus until an open position of the hinged 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 2011 001 003 A1 . DE 10 2010 002 625 A1 . DE 10 2008 011 315 A1 . DE 10 2006 031 477 A1 and the patent DE 10 2008 034 994 B3 Applicants can be found in which in particular measures relating to a cushioning for the actuating movement, structural configurations of fluidic actuators, sensor devices for detecting a travel of the actuators, fluidic control 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.

OBJECT OF THE INVENTION

The invention has for its object to propose a fluidic control circuit for two wing doors of a vehicle, which allows different modes of operation, in particular with different opening and / or closing characteristics as needed.

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 relates to a fluidic, in particular hydraulic control circuit for two folding doors of a vehicle, in particular a bus, wherein these two hinged doors are associated with a common manhole. Quite possible within the scope of the present invention is that, in addition to the two gullwing doors mentioned below, further gullwing doors are also actuated via the fluidic control circuit, which are associated with further access openings. In the context of the invention, the term "control" or the "control circuit" also includes a control or a control circuit in which, for example, a control based on a return of a fluidic pressure or a travel of a wing door or an actuator takes place.

The two gullwing doors associated with a manhole are moved in opposite directions to one another when they are controlled by the fluidic control circuit, that is, moving toward one another for closing the gullwing doors and moving away from each other to open the gullwing doors. The swing doors are driven by two double-acting actuators. For this purpose, the actuators each have two oppositely acting and acted upon by the fluidic control circuit pressure chambers.

According to the invention a valve device is used in the fluidic control circuit, which has different operating positions and thus allows different modes of operation. In this case, the "valve device" comprises both a singular valve device with a valve unit as well as a singular valve units or valves which are arranged distributed over a plurality of fluid channels and are interconnected via fluidic lines.

In the fluidic control circuit according to the invention, the valve device connects in a first operating position pressure chambers of both actuators in fluidic parallel connection with a primary side of a pump. Thus, divided in this operating position, the delivery volume of the pump to the pressure chambers of both actuators. In other words, an actuator for its actuation is only half the delivery volume of the pump available. This has the consequence that for this first operating position of the valve device, a relatively slow adjusting movement of the actuators takes place, while on the other hand under certain circumstances in this operating position relatively large actuating forces of the actuators can be generated.

According to the invention, a second operating position of the valve device can be brought about and used. In this second operating position, only a pressure chamber of a first actuator is connected to the primary side of the pump. Thus, only this first actuator can be actuated by operation of the pump per se. According to the invention, however, the other pressure chamber of the first actuator is connected to a pressure chamber of the other, second actuator. The other pressure chamber of the first actuator thus serves as a kind of "master cylinder", which generates a pressure corresponding to the actuation of this actuator by the pump, which pressure is supplied to the pressure chamber of the second actuator, which thus acts as a kind of "slave cylinder". In other words, the two actuators are fluidly coupled together. Through this coupling, a coupling of the movement of the two actuators takes place with each other. In the second operating position of the valve device, the entire delivery volume the pump is supplied to a pressure chamber of the first actuator, whereby a relatively fast opening or closing movement can be brought about. This fast opening or closing movement is then transmitted via the coupling between "master cylinder" and "slave cylinder" on the other actuator. In other words, for the second operating position, the first actuator and the second actuator are in fluidic series connection between the primary side and the secondary side. The second operating position is particularly advantageous if a fast movement of the wing doors is desired. Under certain circumstances, however, reduced actuating forces of the actuators result for this operating position.

The choice between the two mentioned operating positions can be made as needed. For example, a normal movement of the wing doors in the first operating position, while an emergency opening or emergency closure, for which an increased actuating speed of the wing doors is desired, can be carried out in the second operating position.

In a particular embodiment of the invention, the fluidic control circuit is equipped with a control device. This control device is designed to convert the valve device as needed from the first operating position to the second operating position and / or vice versa. This transfer takes place during an opening and / or closing movement of the folding doors. To mention only a non-limiting example, during a closing movement, the valve device can first occupy the second operating position, whereby a large closing speed is ensured. After a certain setting and closing path then the switching of the valve device takes place in the first operating position, whereby a slowing down of the movement of the wing doors 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 tight application of the wing doors to a door frame, a seal u. Ä. Can be guaranteed.

• Für eine besondere Ausgestaltung der Erfindung sind eine Steuervorrichtung (bei der es sich auch um die vorgenannte Steuervorrichtung handeln kann) und ein Drucksensor vorgesehen.

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 of the invention, a control device (which may also be the aforementioned control device) and a pressure sensor are provided.

The pressure sensor is used to detect a pressure in the fluidic control circuit, for example in one of the pressure chambers or a line leading to this. Depending on the pressure detected by the pressure sensor, the valve device is 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, when the hinged doors on a door frame or a seal, the pressure, which is detected by the pressure sensor increases. When the threshold value is exceeded, it is then possible to switch over to the first operating position in order to bring about the actuating forces required for the final closing of the gullwing doors. It is entirely possible that the kinematics of the drive device for the wing doors is designed such that, depending on the travel of the actuators and the wing doors results in a different pressure, which is detected by the pressure sensor. This is the case in particular when the movement takes place against an increasingly acted upon return spring. The actuating path of the actuator can then indirectly also be detected via the pressure sensor, so that the operating position is switched over for a predetermined opening or closing path with the detected pressure correlated therewith.

For a further particular embodiment of the invention, a control device (which may also be the aforementioned control device) and a displacement sensor are provided. The displacement sensor serves to detect a path of an actuator or a hinged door. Here, a displacement sensor or a path is also an angle sensor or an angle or a speed sensor or a speed subsumed, by means of which or which ultimately the adjusting movement of the actuator or the hinged door can be detected. According to the invention, the valve device is transferred from the first operating position into the second operating position and / or vice versa, depending on the travel detected by the displacement sensor. To mention only a simple, non-limiting example, the closing movement can first be effected from the open position in the second operating position of the valve device, whereby a rapid closure of the hinged doors can be brought about. If the travel detected by the travel sensor exceeds a threshold value, the changeover to the first operating position can take place, so that the last part of the travel for closing the folding doors can be brought about at reduced speed and / or increased actuating forces.

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 can be switched, for example, pressure-dependent or motion-controlled. In a preferred embodiment of the invention, an electronic control unit is used as the control device, which operating signals such as the signals detected by the pressure sensor or displacement sensor are supplied. On the basis of these operating signals, the control device can then control directly actuated valves or electromagnetically pilot operated valves of the valve device in order to bring about the aforementioned operating positions.

It is entirely possible that for actuation of the actuators by means of the pump, both actuators of the gullwing doors, which are assigned to an access opening, are always activated 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 one gullwing door or both gullwing doors is possible.

• eine Einzeltürsteuerung,
• eine Doppeltürsteuerung mit verringerter Betätigungsgeschwindigkeit (erste Betriebsstellung der Ventileinrichtung) sowie
• eine Doppeltürsteuerung mit erhöhter Betätigungsgeschwindigkeit (zweite Betriebsstellung der Ventileinrichtung).

In a preferred embodiment of the invention, the valve device has a further operating position in which a single door control takes place. This means that one of the two hinged doors retains its assumed position during operation of the pump, which is preferably due to the fact that at least one pressure chamber of the actuator which is assigned to this hinged door is shut off. By contrast, in the further operating position by means of operation of the pump, the opening and / or closing of the other hinged door can take place in a targeted manner. For this embodiment of the invention, therefore, the valve device has three different operating positions with three different modes of operation, 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).

There are many possibilities for the concrete structural design of the fluidic control circuit. For a particular embodiment of the invention, a primary side of a pump is connected to a pressure chamber of a first actuator. There is also a valve via which optionally the primary side of the pump is additionally connectable to a pressure chamber of a second actuator. The same applies to a secondary side of the pump which is connected to a pressure chamber of the second actuator: Via a valve, the secondary side of the pump can then optionally additionally be connected to a pressure chamber of the first actuator. Depending on the operating position of the two valves mentioned, a single-door control, a double-door control with a reduced operating speed and / or a double-door control with an increased operating speed can thus take place.

• mit der Sekundärseite der Pumpe verbindbar ist, was vorzugsweise in der ersten Betriebsstellung der Fall ist, womit eine Doppeltürsteuerung mit verringerter Betätigungsgeschwindigkeit ermöglicht ist,
• absperrbar ist, womit dieser Aktuator deaktiviert sein kann, sodass eine Einzeltürsteuerung über den anderen Aktuator ermöglicht ist, oder
• mit einem Druckraum des zweiten Aktuators verbindbar ist, womit insbesondere die zweite Betriebsstellung gewährleistet ist, in welcher eine Doppeltürsteuerung mit erhöhter Betätigungsgeschwindigkeit möglich ist.

In a further embodiment of the invention, a primary side of a pump is connected to a pressure chamber of a first actuator, while the other pressure chamber of the first actuator, depending on the operating position of the valve device

• is connectable to the secondary side of the pump, which is preferably the case in the first operating position, whereby a double door control with reduced operating speed is made possible,
• can be shut off, so this actuator can be disabled so that a single door control over the other actuator is enabled, or
• is connectable to a pressure chamber of the second actuator, whereby in particular the second operating position is ensured, in which a double door control with increased operating speed is possible.

There are many possibilities for the valves used in the valve device. In a particular embodiment of the invention, at least one of said valves or both valves are designed as 3/2-way valve (s). 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 may be designed in any type, in particular as a slide valve or seat valve.

It is possible that the valves are pre-controlled electropneumatically, which has the particular 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 can be generated. In a preferred embodiment, but the valves directly controlled directly. It is possible here that the valves are designed as solenoid valves and are electromagnetically directly controlled by the control device, here an electronic control unit. As explained, an immediate control, for example, by the pressure in a pressure chamber or motion-controlled done.

According to the known from the prior art embodiments, a manual override of the wing doors may be possible. In a preferred embodiment of the invention, a bypass line is interposed in the fluidic control circuit between a primary side and a secondary side of a pump. In the bypass line a manual emergency valve is arranged. With manual actuation of the manual emergency valve, the pump can thus be "bridged", so that regardless of the operation of the pump manual opening of at least one hinged door can be done, which ultimately fluid is circulated from one pressure chamber to another pressure chamber due to the manually applied forces.

In a further embodiment of the invention, a check valve opening in the direction of a pressure chamber of the actuator is arranged between the pump and the actuator. The check valve allows during operation of the pump, a fluid flow from the pump in the direction of the associated pressure chamber of the actuator. As a result, the opening direction of the check valve is predetermined. Without operation of the pump, the check valve blocks the pressure chamber, so that a once taken open or closed position (or a center position) of the wing door is maintained. The non-return valve is also additionally controlled in such a way that it can be unlocked and opened in the opposite direction. This control takes place upon reversal of the conveying direction of the pump such that the non-return valve allows a fluidic flow from the pressure chamber to the pump. The same applies to the use of a check valve instead of the check valve, which also allows the above functions and the aforementioned control.

Preferably find in the valves of the valve device spring elements use that specify a non-actuated position of the valves. Preferably, the valves are or is the valve device without control in the first operating position.

Preferably, a reversible pump is used in the context of the invention. Thus, the assignments "primary side" and "secondary side" are not fixed - but these depend on the respective effective conveying direction of the pump.

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.

The reference numerals contained in the claims do not limit the scope of the objects protected by the claims. They are for the sole purpose of making the claims easier to understand.

BRIEF DESCRIPTION OF THE FIGURES

Fig. 1

zeigt stark schematisiert eine Antriebseinrichtung für zwei Flügeltüren eines Busses mit dem fluidischen Steuerkreis.

Fig. 2

zeigt stark schematisiert die Antriebseinrichtung für Flügeltüren gemäß Fig. 1 mit einer alternativen Ausgestaltung des fluidischen Steuerkreises.

Fig. 3

zeigt in einer räumlichen Darstellung schräg von oben eine Aufhängung mit Antriebseinrichtung für zwei Flügeltüren, wobei die Flügeltüren sich hier in einer Öffnungsstellung befinden.

Fig. 4

zeigt in einer räumlichen Darstellung schräg von oben die Aufhängung mit Antriebseinrichtung für zwei Flügeltüren gemäß Fig. 3, wobei sich hier die Flügeltüren in einer teilweise geschlossenen Stellung befinden.

Fig. 5

zeigt in einer räumlichen Darstellung schräg von oben die Aufhängung mit Antriebseinrichtung für zwei Flügeltüren gemäß Fig. 3 und 4, wobei sich hier die Flügeltüren in einer Schließstellung befinden.

Fig. 6

zeigt einen Horizontalschnitt durch Teile der Aufhängung und Antriebseinrichtung für zwei Flügeltüren gemäß Fig. 3 bis 5.

Fig. 7

zeigt ein Detail VII des Horizontalschnitts gemäß Fig. 6.

Fig. 8

zeigt ein Detail VIII des Horizontalschnitts gemäß Fig. 6.

Fig. 9

zeigt ein Detail der Aufhängung mit Antriebseinrichtung für zwei Flügeltüren in räumlicher Darstellung schräg von unten, wobei hier die Antriebseinrichtung und Aufhängung in einer Betriebsstellung dargestellt sind, in welcher die Flügeltüren einen maximalen Abstand in Querrichtung von einem Türrahmen haben.

Fig. 10

zeigt ein Detail der Aufhängung mit Antriebseinrichtung für zwei Flügeltüren in räumlicher Darstellung schräg von unten, wobei hier die Antriebseinrichtung und Aufhängung in einer Betriebsstellung dargestellt sind, in welcher die Flügeltüren an den Türrahmen angelegt sind, womit eine Schließstellung erreicht ist.

Fig. 11

zeigt in einer räumlichen Detail-Ansicht schräg von oben die Aufhängung und Antriebseinrichtung in teil-demontiertem Zustand.

Fig. 12

zeigt in einer räumlichen Detail-Ansicht schräg von oben die Aufhängung und Antriebseinrichtung in teil-demontiertem Zustand.

Fig. 13

zeigt ein Detail der Antriebseinrichtung und Aufhängung bei Blickrichtung in Querrichtung des Fahrzeugs nach außen.

Fig. 14

zeigt einen Schnitt XIV-XIV gemäß Fig. 13 durch die Antriebseinrichtung und Aufhängung.

Fig. 15

zeigt in räumlicher Detail-Ansicht schräg von unten eine Antriebseinrichtung mit einer Halteeinrichtung für die Flügeltüren.

Fig. 16

zeigt in räumlicher Ansicht schräg von unten eine Antriebseinrichtung mit den Halteeinrichtungen für die Flügeltüren.

Fig. 17

zeigt stark schematisiert eine Antriebseinrichtung für Flügeltüren mit einer alternativen Ausgestaltung des fluidischen Steuerkreises.

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

Fig. 1

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

Fig. 2

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

Fig. 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.

Fig. 4

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

Fig. 5

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

Fig. 6

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

Fig. 7

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

Fig. 8

shows a detail VIII of the horizontal section according to Fig. 6 ,

Fig. 9

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 have a maximum distance in the transverse direction of a door frame.

Fig. 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.

Fig. 11

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

Fig. 12

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

Fig. 13

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

Fig. 14

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

Fig. 15

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

Fig. 16

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

Fig. 17

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

DESCRIPTION OF THE FIGURES

• Fig. 1 shows a highly schematic drive unit 1 with fluidic control circuit 2 for actuating the drive device 1. Here, the control circuit 2 is 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 of the actuators 3a, 3b result, which in about Fig. 1 strongly illustrated holding devices 5a, 5b each to an associated hinged door 6a, 6b (in Fig. 1 not shown). In this case, the opening and closing movements 4a, 4b take place in opposite directions, in order to move the two wing doors 6a, 6b away from one another for an opening movement and for the two leaf doors 6a, 6b to move toward one another for a closing movement. The movement of the cylinder housings 8a, 8b of the actuators 3a, 3b takes place in a longitudinal direction of the vehicle, which is marked "x" in the figures.

In the following, the construction and the mode of operation will be explained with reference to the actuator 3a, the corresponding applies to the actuator 3b. The actuator 3a is as a double-acting Cylinder unit 7a formed. The cylinder unit 7a has the cylinder housing 8a, which has an interior 9a. The cylinder housing 8a is guided in the two end regions via sealing and guide units 9a, 10a with respect to a longitudinal guide device 11a, which is designed here as a guide tube 12a, sealing in the direction x. An inner space 13a of the cylinder housing 8a is divided into two pressure chambers 14a, 15a by a piston-like separator 24a carried by the guide tube 12a. The cylinder housing 8 forms end opposite piston surfaces 16a, 17a, which are each associated with a pressure chamber 14a, 15a. By generating a pressure difference in the pressure chambers 14a, 15a, different pressure forces on the piston surfaces 16a, 17a can be brought about, the resultant of which leads to an opening or closing force. Outside the range of movement of the cylinder housing 8a relative to the guide tube 12a, the guide tube 12a has terminals 18a, 19a. These ports 18a, 19a are each connected via channels 20a, 21a of the longitudinal guide device 11a, in particular in the interior of the guide tube 12a, with an associated pressure chamber 14a, 15a. As an optional feature, moreover, the two pressure chambers 14a, 15a are coupled to one another via throttle valves or two non-return valves 22a, 23a which are connected in parallel and operate in different directions.

• 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

• the during the adjusting movement of the actuators 3a, 3b not moving longitudinal guide means 11a, 11b and also not moving along separation body 24, which forms a stationary separating piston between the two pressure chambers 14, 15, and
• the cylinder housings 8a, 8b moved during the adjusting movement.

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

Fig. 1 shows the 3/2-way solenoid valve 28 in a passage position in which this connects the terminals 19 a, 18 b together. A bypass line 30, in which a manually actuated manual emergency valve 31 is arranged, connects the primary side 27 with the secondary side 29 directly in parallel connection to the pump 25 when the manual emergency valve 31 is open. The bypass line 30 has a branch 32, which is arranged between the manual emergency valve 31 and the primary side 27. The branch 32 is connected to a port of the 3/2-way solenoid valve 28, which in the in Fig. 1 ineffective bypass position of the 3/2-way solenoid valve 28 is connected to the port 18b of the actuator 3b, while in this switching position, the port 19a is shut off via the 3/2-way solenoid valve 28.

1. 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.
2. 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 Fig. 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 Fig. 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 Fig. 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 21 b und den Anschluss 19b herausgepresst und der Sekundärseite 29 zugeführt. Durch die erläuterte fluidische Wirkkette wird eine Schließbewegung für Flügeltüren 6a, 6b erzeugt.
3. c) Für eine Umkehrung der Förderrichtung der Pumpe 25 gilt das unter b) Gesagte entsprechend (mit Umkehrung der Beaufschlagungsrichtungen und der Bewegungsrichtungen).
4. 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.
5. e) Schließlich ist über das Handnotventil 31 (und Überführung des 3/2-Wege-Magnetventil 28 in die in Fig. 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:

1. a) Without operation of the pump 25 and closed emergency valve 31 is a fluidic securing a position taken the actuators 3a, 3b and thus the wing doors 6a, 6b. (In the following, it will be explained that additional securing can also take place by means of a latching or locking device.) Without the check valves 22a, 23a, a fluidic fixation of the winged doors 6a, 6b can take place (ignoring a leakage) in this way. On the other hand, by means of the check valves 22, 23 in the exercise of particular manual forces on the wing doors 6a, 6b, an opening or closing movement in principle allows. The opening or closing movement or the manual forces required for initiating the same are predetermined by the throttle characteristic of the check valves 22, 23. Alternatively or cumulatively, it is possible by means of the check valves 22a, 23a to provide fluidic compensation of leakage flows, for example in the region of End position, can be done.
2. b) If a delivery of the fluid from the secondary side 29 by the pump 25 to the primary side 27, there is an increase in the pressure in the pressure chamber 14 of the actuator 3a. This increase in pressure results in a compressive force on the piston surface 16a. which tends to the cylinder housing 8a in Fig. 1 to move to the left. This loading of the cylinder housing 8a to the left in turn has the consequence that the 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 Fig. 1 to the left and the pressure in the pressure chamber 15a increases. This rising pressure in the pressure chamber 15a is transmitted via the channel 21a, the port 19a, the 3/2-way solenoid valve 28 in its passage position, the port 18b, the channel 20b to the pressure chamber 14b of the actuator 3b, which thus as a Type "slave cylinder" is used. Due to the effective piston surface 16b, this pressurization leads to an action on the cylinder housing 8b of the actuator 3b Fig. 2 to the right. This pressurization of the cylinder housing 8b to the right in turn results in an increase in pressure on the piston surface 17b. In this way, fluid is pressed out of the pressure chamber 18b via the channel 21b and the port 19b and fed to the secondary side 29. The illustrated fluidic action chain generates a closing movement for wing doors 6a, 6b.
3. c) For a reversal of the conveying direction of the pump 25, what has been said under b) applies correspondingly (with reversal of the directions of application and the directions of movement).
4. d) If the 3/2-way solenoid valve 28 is switched to the bypass position, there is a bypass of the actuator 3a via a bypass line 33 which from the 3/2-way solenoid valve 28 via the branch 32, the part of the bypass line 30 without Handnotventil 31 leads to the primary side 27. Since the connection 19a is shut off via the 3/2-way solenoid valve 28 in the bypass position, the position of the cylinder housing 8a of the actuator 3a does not change for this switching state of the 3-2 / way solenoid valve regardless of the operating state of the pump 25. By contrast, 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 take place. Ultimately, depending on the switching state of the 3/2-way solenoid valve 28 via the pump 25 alternatively
   • a double door control with common opposite control of the opening and closing movements 4a, 4b of the cylinder housing 8a, 8b of the actuators 3a, 3b carried 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 take place.
5. e) Finally, via the manual emergency valve 31 (and transfer of the 3/2-way solenoid valve 28 in the in Fig. 1 Bypass position) allows a short circuit of the two pressure chambers 14b, 15b, so that a manual opening or closing of the hinged door 6b, which is associated with the actuator 3b, allows.

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 Fig. 1 not possible.

Fig. 2 shows an alternative embodiment of the drive device 1 with a fluidic control circuit 2, which also allows alternatively a single control of both actuators 3a, 3b (ie, both wing doors 6a, 6b). Here, the actuators 3a, 3b are themselves corresponding Fig. 1 educated. According to Fig. 2 the pump 25 is also bridged by a bypass line 30 with integrated manual emergency valve 31, although here no branch 32 is present. Between the pump 25 facing ports 18a, 19b of the actuators 3a, 3b and the primary and secondary side 27, 29 and the bypass line 30 is a respective 3/2-way solenoid valve 34, 35 interposed, which in Fig. 2 each in their passage position. In the passage position connect the 3/2-way solenoid valves 34, 35 the respective associated port 18 a, 19 b of the actuator 3 a, 3 b with the bypass line 30 and the primary and secondary side 27, 29. In addition, the 3/2 Directional solenoid valves 34, 35 a bypass position, in which the connected to the bypass line 30 and the primary or secondary side 27, 29 connection of the 3/2-way solenoid valve 34, 35 are connected via this with a bypass line 36. The bypass line 36 connects on the one hand the two terminals of the 3/2-way solenoid valves 34, 35 with each other. In addition, the bypass line 36 is connected via a branch 37 to a connecting line 38 which directly (without integration of the 3/2-way solenoid valve 28) connects the terminals 19a, 18b with each other.

• a) bis c) Befinden sich beide 3/2-Wege-Magnetventile 34, 35 in ihrer Durchlassstellung, wie dies in Fig. 2 dargestellt ist, ist eine Betriebsweise gemäß a) bis c), wie diese zu Fig. 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 Fig. 2 is as follows:

• a) to c) Are both 3/2-way solenoid valves 34, 35 in their passage position, as in Fig. 2 is shown, is a mode of operation according to a) to c), as these too Fig. 1 has been described, possible.
• d) If 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 is a single door control with a control only of the actuator 3a allows while no change in the operating situation of the actuator 3b takes place via the blocking of the connection of the 3/2-way solenoid valve 35 connected to the connection 19b of the actuator 3b.
• e) Conversely, the 3/2-way solenoid valve 35 is transferred to its forward position, while the other 3/2-way solenoid valve 34 is in its other switching position, is a single-door control with a control of only the actuator 3b on the operation of the pump 25 possible while the actuator 3a by blocking the terminal 18 a does not change its operating state.
• f) If both 3/2-way solenoid valves 34, 35 in their passage position and the emergency valve 31 is opened, a common manual opening or closing of the wing doors 6a, 6b take place, wherein the fluid between the pressure chambers 14a, 15b on the Handnotventil 31 is circulated in its open position.
• g) If, however, is one of the 3/2-way solenoid valves 34, 35 in its passage position, while the other 3/2-way solenoid valve 34, 35 is in its bypass position, with manual emergency valve 31 is open, a manual opening or closing only a hinged door 6a, 6b take place.

For the control of the 3/2-way solenoid valve 28 according to Fig. 1 and the 3/2-way solenoid valves 34, 35 according to Fig. 2 Preferably, a strategy is chosen such that even with a collapse of the 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 Fig. 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 emergency operation at Burglary of the electrical power supply according to Fig. 2 for both wing doors 6a, 6b desired, the 3/2-way solenoid valves 34, 35 should be de-energized in its passage position. If, on the other hand, only manual override of a wing door 6a, 6b is desired, the associated 3/2-way solenoid valve 34 must be transferred without current to its passage position, while the other 3/2-way solenoid valve 35 then has to assume 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 and the 3/2-way solenoid valves 28, 34, 35 via an electronic control unit or CPU, which is not shown in the figures. This activation takes place in accordance with the respective operating situations, wherein the opening or closing movement can be brought about centrally by the driver and / or via actuators which are accessible to the passengers inside and / or outside the vehicle and which can be arranged adjacent to the wing doors 6a, 6b, for example , In the figures, only the actuators 3a, 3b for a pair of hinged doors 6a, 6b are simplified. It is understood that a plurality of such pairs of gullwing doors can be controlled via a plurality of pairs of actuators. This can be done via one and the same pump 25, which then acts on parallel or serial line branches several actuators, or via several pumps, which can then be assigned to a pair of actuators 3a, 3b (or more pairs of actuators) with in this case several circuits 2.

• Further control 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 design 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 for monitoring 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 Fig. 1 and Fig. 2 merely a movement of the cylinder housings 8a, 8b in a direction x, which for one embodiment correlates with the movement of the wing doors 6a, 6b in the direction of the vehicle longitudinal axis. It is possible that additional actuating devices or coupling devices or degrees of freedom are used, via which additionally a pivotal 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 be articulated 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, 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 said complementary coupling device and / or another actuator, as will be explained in more detail below.

As a special feature is the Fig. 1 and 2 it can be seen that the cylinder housings 8a, 8b of the actuators 3a, 3b are not fixed to the vehicle frame, but are moved by way of their adjusting movement along the longitudinal guide devices 11a, 11b. Here, the movement of the cylinder housing 8a, 8b may be fluidly coupled to each other, in which case a cylinder housing 8a, 8b acts as a kind of "master cylinder", 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 can be canceled. For the embodiment according to Fig. 1 and 2 the longitudinal guide devices 11a, 11b arranged fixed to the vehicle frame, which is not absolutely necessary, as will be explained below.

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

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

• Die Führungsrohre 12a, 12b sind in ihren Endbereichen starr und parallel zueinander an Abstützeinrichtungen 39, 40 gehalten. Wie beispielhaft anhand der Abstützeinrichtung 39 gemäß Fig. 7 dargestellt ist, sind die Abstützeinrichtungen 39, 40 jeweils mit einem Grundkörper 68 gebildet. Der Grundkörper 68 besitzt zwei abgestufte Durchgangsausnehmungen 41, 42, in welche sich unter radialer Abdichtung durch ein Dichtelement 43 eine Kopplungshülse 44 erstreckt, welche stirnseitig in das Führungsrohr 12a, 12b eingeschraubt ist mit einer Verspannung der Stirnseite des Führungsrohrs 12a, 12b gegen einen Bund 45 der Kopplungshülse 44. Durch die Durchgangsausnehmungen 41, 42 hindurch erstreckt sich eine Kopplungsschraube 46, deren Gewindeabschnitt mit einem Innengewinde der Kopplungshülse 44 verschraubt ist. Mit dem Einschrauben der Kopplungsschraube 46 in die Kopplungshülse 44 wird ein zylindrischer verjüngender Absatz 47 der Durchgangsausnehmung 41, 42 verspannt zwischen einem Kopf 48 der Kopplungsschraube 46 und einer Stirnseite oder dem Bund 45 der Kopplungshülse 44. Die Kopplungsschraube 46 besitzt einen inneren Kanal 49, welcher einerseits in einen Innenraum 50 des Führungsrohrs 12a, 12b mündet und andererseits über einen radialen Stichkanal kommuniziert mit einer in den Fig. nicht dargestellten Versorgungsleitung oder - bohrung in dem Grundkörper 68, welche mit einem Anschluss 18, 19 verbunden ist. Ein Übertrittsquerschnitt zwischen der Stichbohrung 51 und der Versorgungsleitung kann über
  • 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 and the cylinder units 7a, 7b are shown in detail in the Fig. 6 to 8 to recognize:

• The guide tubes 12a, 12b are held rigidly and parallel to one another by support devices 39, 40 in their end regions. As exemplified by the support device 39 according to Fig. 7 is shown, the support means 39, 40 are each formed with a base body 68. The main body 68 has two stepped through holes 41, 42, into which a coupling sleeve 44 extends under radial sealing by a sealing element 43, which is screwed into the guide tube 12a, 12b with a clamping of the end face of the guide tube 12a, 12b against a collar 45th the coupling sleeve 44. Through the through holes 41, 42 passes through a coupling screw 46, the threaded portion is screwed to an internal thread of the coupling sleeve 44. With the screwing of the coupling screw 46 in the coupling sleeve 44, a cylindrical tapered shoulder 47 of the through-hole 41, 42 clamped between a head 48 of the coupling screw 46 and an end face or the collar 45 of the coupling sleeve 44. The coupling screw 46 has an inner channel 49, which on the one hand into an inner space 50 of the guide tube 12a, 12b opens and on the other hand via a radial branch channel communicates with a supply line or - not shown in the figure bore in the base body 68, which is connected to a terminal 18, 19. A crossover cross section between the tap hole 51 and the supply line can over
  • the sealing element 43,
  • a sealing element 52, which is braced between the head 48 and body 68, and
  • a sealing element 53, which is clamped between the through-bore of the coupling sleeve 44 and a lateral surface of the coupling screw 46,
  be sealed.

As in particular from the detail VIII according to Fig. 8 can be seen, the guide tubes 12a, 12b are formed in two parts with guide tube parts 12-1 and 12-2. The guide tube parts 12-1 and 12-2 are rigidly connected to one another via the separating body 24. The separating body 24 has an annular body 54, from which pins 55, 56 equipped with an external thread extend in the x direction. 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 are clamped against annular end faces of the annular body 54, so that the separating body 24 and Guide tube parts 12-1 and 12-2 form a rigid unit. The ring body 54 forms radially outwardly a cylindrical sealing and guide surface 57. In the sealing and guide surface 57, a circumferential groove 58 is radially introduced, in which a sealing element 59 is arranged. The inner spaces 50-1 and 50-2 of the guide tube parts 12-1 and 12-2 are connected to each other via channels 60, 61 of the separating body 24 formed with longitudinal bores. In the channels 60, 61, the opening in the opposite direction throttles or check valves 22, 23 are arranged. In the opening direction upstream of the check valves 22, 23 opens into the channels 60, 61 each have a radial tap hole 62, 63rd

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

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

Ultimately, depending on the pressurization of the supply lines in the support means 39, 40, the fluidic admission of the pressure chambers 14, 15 are changed, whereby a movement of the cylinder housing 8a, 8b in the opening and closing direction 4a, 4b can be brought about. The movement of the wing doors 6a, 6b here preferably takes place parallel to the vehicle longitudinal axis and in the direction indicated by x in the figures. The piston surfaces 16, 17 formed by the sealing and guiding units 9, 10 are in this case 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 entirely possible that the support device 1 has only the explained degree of freedom in the direction x. For that in the Fig. 3 to 15 illustrated embodiment, the support means 1 has 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 the longitudinal guide means 11 formed with the guide tubes 12 are movable together with the support means 39, 40 in the direction y relative to a vehicle frame or a door frame. This extra degree of freedom can serve

• after movement of the wing 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 to move the wing doors 6a, 6b in 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 Fig. 12 and 14 It can be seen that such an additional degree of freedom in the y-direction is ensured by means of a transverse guide device 65. This has a guide rod 66 which is oriented in the direction of the Y-axis and which is held on a vehicle frame-fixed or door frame-fixed carrying device 67.

The main body 68 is formed in this case as a kind of guide carriage 69. For this purpose, the guide carriage 69 has a continuous recess 70, in which end two guide bushes 71, 72 are used, which are slidably supported and as possible without play on the guide rod 66. Between the guide carriage 69 and the guide rod 66 acts a spring element 73 which acts on the guide carriage away from the door frame in the y-direction.

The movement of the cylinder housing 8 along the longitudinal guide means 11 in the x direction is only a partial stroke, 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 relative to the guide rods 66 in the direction y. This coupling is done mechanically. For this purpose, the cylinder housing 8, here the sealing and guide units 9, via a driver unit 74, which are effective only for the partial stroke of the cylinder housing 8. For the illustrated embodiment, the driver unit 74 is formed by an extension 75 of 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 8 with the movement of the guide carriage 69 is coupled and thus a coupling of the movement of the cylinder housing 8 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 of the coupling rod 77 on one side to the extension 75, whereby the mechanical coupling between the movement of the Cylinder housing 8 created with the movement of the coupling rods 77 and is effective. For the illustrated embodiment, the driver 78 is formed with a plugged onto the coupling rod sleeve 79, which is secured at the end by a nut 80.

In the support areas 39, 40 facing end portions of the coupling rods 77 are hinged to a toggle mechanism 81 which is movable in a plane x-y. The toggle mechanism 81 has a first toggle lever 82 and a second toggle lever 83, which are connected to one another via a knee joint 84. The knee joint 84 facing away from the end portion of the first knee lever 82 is hinged to the guide carriage 69. The knee joint 84 facing away from the end portion of the second knee lever 83 is hinged to the support means 67. The coupling rod 77 acts on the first toggle lever 82, which preferably takes place approximately centrally between the two articulation points of the first toggle lever 82.

• In der Öffnungsstellung der Antriebseinrichtung 1 und der Flügeltüren 6 gemäß Fig. 3 befindet sich das Zylindergehäuse 8a maximal nach links verschoben. In dieser Öffnungsstellung hat sich der Fortsatz 75a gegenüber der Stellung in Fig. 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 Fig. 4. In dieser besitzen die Flügeltüren 6a, 6b noch einen kleinen verbleibenden Spalt. In der Stellung gemäß Fig. 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 Fig. 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 Fig. 9 (Kniewinkel bspw. ca. 70° ± 20°) gemäß Fig. 9 in Richtung seiner Strecklage (Fig. 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 8 and the guide carriage 69 is carried out as follows:

• In the open position of the drive device 1 and the gullwing doors 6 according to Fig. 3 is the cylinder housing 8 a maximum shifted to the left. In this open position, the extension has 75 a relative to the position in Fig. 8 also moved far to the left, so that the driver 78a does not contact the extension 75a.
• With actuation of the actuators 3a, 3b, the gullwing doors 6a, 6b move toward each other up to the position according to Fig. 4 , In this, the gullwing doors 6a, 6b still have a small remaining gap. In the position according to Fig. 4 begins the partial stroke, for which a coupling of the movement of the wing doors 6a, 6b and the movement of the cylinder housing 8 with the movement of the guide carriage 69 begins. In the operating position according to Fig. 4 is therefore just the extension 75 come to rest on the driver.
• A further pressurization of the actuators 3a, 3b has the consequence that the cylinder housing 8 are moved further toward each other, which also has the consequence that the coupling rods 77a, 77b are pulled towards each other. With the continuation of the closing movement, the coupling rods 77 actuate the toggle mechanism 81. The toggle mechanism 81 is from the angled operating position according to Fig. 9 (Knee angle, for example, about 70 ° ± 20 °) according to Fig. 9 in the direction of its extended position ( Fig. 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 to the support device 67 of the articulation point of the toggle mechanism 81 on the guide carriage 69 increases. Contrary to the loading of the spring element 73, there is thus a movement of the support means 39, 40 formed by the guide carriage 69, 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 the movement of the guide carriage 69 as a function of the movement of the cylinder housing 8 results from the kinematics of the toggle mechanism 81, namely the position of the articulation points and the lengths of the toggle 82, 83rd
• If, on the other hand, the actuators 3a, 3b are acted upon in the opening direction, the action of the spring element 73 causes the knee angle of the toggle mechanism 81 to increase again with the opening movement, with the spring element 73 ensuring that the coupling rod 77 engages with the catch 78 the extension 75 is pressed until the guide carriage 69 is moved maximally outward in the y-direction, whereby the coupling of the movement of the cylinder housing 8 is removed motion controlled with the movement of the guide carriage.

It is possible that the drive device 1 has only the described 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 wing doors 6a, 6b is desired.

Optionally, an extended embodiment is proposed, according to which the support means 39, 40, longitudinal guide means 11, the cylinder housing 8 and the guide rods 66 are pivotable together about a vertical axis Z, which also includes the directions x, y, along which a movement along said degrees of freedom takes place, 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 hinged door 6a is opened. As a result, with the opening movement of the individual hinged door 6a, the toggle mechanism 81b retains its end position near the extended position, so that the guide carriage 69b also retains its position in the y-direction as far as possible in the transverse direction inwards. On the other hand, the actuation of the actuator 3a causes the knee angle of the toggle mechanism 61 a to increase and the guide carriage 69 to move laterally moved outside. Thus, the explained single-door control means that with the pivoting about the vertical axis Z, the effective direction of the actuator 3a changes from a first effective direction 85 into a second effective direction 86 (schematically dash-dotted line in FIG Fig. 5 shown). In this case, the maximum angle change between the first effective direction 85 and the second effective direction 86 may be relatively small, for example in the range of 5 ° ± 4 ° or 5 ° ± 2 °. On the one hand, this change in angle results in the hinged door 6b remaining closed (possibly with a small "angular error"), while it is possible for the hinged door 6a to be opened and, for example, to be guided past an outer skin of the vehicle. If such an additional degree of freedom is desired for pivoting about the vertical axis Z, it is necessary that the guide rod 66 is not rigidly secured to the support means 67. Rather, an end portion 87 of the guide rod 66 is articulated in a bearing eye 88 such that an axial fixation of the guide rod 66 relative to the support means 67 takes place, but the orientation of the guide rod 66 limited in space is variable. Also, the opposite end portion 89 of the guide rod 66 is not rigidly held on the support means 67. On the contrary, a coupling element 91, which extends approximately vertically downwardly, is articulated to the carrying device 67 via a ball joint 90. The coupling element 91 is guided in its lower end region by an end-side vertical bore of the guide rod 66 and secured on the opposite side by a nut 92. For the illustrated embodiment, the coupling element 91 is formed with adjustable length. As shown, the end portion 89 of the guide rod 66 can be pressed against the nut 92 via a spring element 93, wherein as the bias of the spring 93 increases, movement of the end portion 89 of the guide rod 66 away from the nut 92 is also possible.

As explained at the outset, it is possible that a once assumed position of the wing doors 6a, 6b is exclusively secured fluidically. For a particular embodiment, a securing of the position of the wing doors 6a, 6b and thus the drive device 1 via an additional latching or locking device 94. While it is possible in principle that by means of the latching or locking device 94 at least any part of the drive device is set, which is moved in the course of the opening and closing movement is latched or locked according to the illustrated embodiment by means of the locking or locking device 94 of the guide carriage 69 relative to the guide rod 66. For this purpose, the guide rod 66 has a latching or locking groove 95, in which a latching or locking element (for example, a Verrieglungsstift) of Latching or locking device 94 engages. A control of the latching or locking device 94, in particular the movement of the latching element in the latching or locking groove 95, can be carried out electrically, pneumatically, hydraulically, electro-pneumatically or electro-hydraulically.

Optionally, it is possible that, together with the actuation of the toggle mechanism 81, pivoting of rotary columns 96 takes place on both sides of the entry opening of the vehicle assigned to the wing doors 6a, 6b. The rotary columns 96 are in this case oriented in the direction of the vertical axis Z. The rotary columns 96 are in this case also mounted rotatably about the vertical axis relative to the support means 67. In the upper end region of the rotary column 96 has a radially extending therefrom rocker 97. In a radially outer end portion of the rocker 97, a coupling rod 98 is articulated. The coupling rod 98 is articulated in an end region by means of a ball head 99 on the guide carriage 69 and a downwardly extending from this bearing pin. In the other end region, the coupling rod 98 is articulated via a ball head 106 on the rocker 97. A movement of the guide carriage 69 in the y-direction is thus converted via the connection between the rocker 97 and the coupling rod 98 in a rotary movement of the rotary column 96 about its longitudinal axis. In the region of the vehicle floor and in the lower end region of the rotary column 96, a further holding device 100 for the hinged door 6a, 6b is arranged. The holding device 100 has an arcuate rocker 101, which is pivoted with the rotary column 96a in an x-y plane. The radially outer end region of the rocker 101 is guided via a guide 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 groove. A movement of the gullwing door 6a, 6b in the direction x is thus not impeded by the rocker and the guide unit 105, while the rocker 101 and the guide unit 105 predetermine the distance of the gullwing door 6a, 6b from the vehicle in the transverse direction y in the holding device 100. A pivoting of the rotary column 96 leads to a change in the distance of the hinged door 6 in the holding device 100 from a door frame or the vehicle in the direction y.

In the figures and in the description, the components associated with the respective hinged door 6a, 6b or the different actuators 3a, 3b are also partially marked with the added letter a or b. Also marked with supplementary letters a, b are the components of the left support means 39 and the right Supporting device 40. If reference numerals are used without the supplementary letter, hereby only one of the components or can hereby be described the two wing doors 6a, 6b associated components.

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

As a further option, a sensor system can be integrated in the drive device 1. About this, the opening and closing movement 4a and / or the opening and closing movement 4b is detected. For an exemplary embodiment, the sensor system is formed with a magnetorestrictive measuring system which is integrated in a measuring rod 103 which extends between the two support devices 39, 40. The cylinder housings 8 each have a magnet or transmitter which is moved along the measuring rod 103. 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 is integrated into the drive unit, namely preferably carried by the support means 40, so that the pump 25 is moved in the direction y. Furthermore, a valve block 104 can be held on the support device 39, 40, in which valves, in particular the 3/2-way solenoid valves 28, 34, 35 are integrated and which control the fluidic admission of the drive device 1. Also, the valve block 104 is moved with the movement of the support means 39, 40.

In the event of emergency release of the latching or locking device 94, the spring 73 may cause the hinged door 6 is moved away from the door frame in the direction y, in which case how to the Fig. 1 and 2 explained, a manual opening of the wing doors 6 can be made in the direction x.

The in the FIGS. 3 to 16 shown drive means 1 can, for example, by means of a fluidic control circuit 2 according to Fig. 1 or Fig. 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. Also included here, however, is also a movement of only one guide element of the hinged door in this direction, while the guide element is connected via a further geared connection with the hinged door, wherein the geared connection under certain circumstances also means that the hinged door in a different direction moved as the guide element.

• Die Antriebseinrichtung 1 kann einen Aktuator 3a, 3b besitzen, mittels dessen eine Bewegung zumindest einer Flügeltür 6a, 6b in eine Längsrichtung x über einen Längshub herbeiführbar ist, welche nur in einem Teilhub des Längshubs mit der Bewegung der mindestens einen Flügeltür 6a, 6b in eine Querrichtung y mechanisch gekoppelt ist.
• Möglich ist auch, dass ein Zylindergehäuse 8a, 8b des Aktuators 3a, 3b mit der Bewegung der Flügeltür 6a, 6b mitbewegt wird.
• Weiterhin möglich ist, dass in der Antriebseinrichtung 1 eine Halteeinrichtung 5a, 5b vorhanden ist, an der die Flügeltür 6a, 6b gehalten werden kann. Die Antriebseinrichtung 1 verfügt dann über eine Längsführungseinrichtung 11a, 11b für die Halteeinrichtung 5a, 5b oder das Zylindergehäuse 8a, 8b. Abstützeinrichtungen 39, 40 sind vorhanden für die Längsführungseinrichtung 11, welche in die Querrichtung y bewegbar sind. Mittels des Aktuators 3a, 3b ist eine Bewegung der Halteeinrichtung 5a, 5b oder des Zylindergehäuses 8a, 8b entlang der Längsführungseinrichtung 11a, 11b in die Längsrichtung x über den Längshub herbeiführbar, welche nur in dem Teilhub des Längshubs mit der Bewegung der Abstützeinrichtung 39, 40 in Querrichtung y gekoppelt ist.
• Möglich ist auch, dass in der Antriebseinrichtung 1 die Kopplung der Bewegung der Halteeinrichtung 5a, 5b oder des Zylindergehäuses 8a, 8b mit der Bewegung der Abstützeinrichtung 39, 40 über eine Mitnehmereinheit 74 erfolgt, welche nur für den Teilhub mechanisch die Halteeinrichtung 5a, 5b oder das Zylindergehäuse 8a, 8b mit der Abstützeinrichtung 39, 40 koppelt.
• Möglich ist, dass die Position der Mitnehmereinheit 74 und damit die Größe des Teilhubs einstellbar ist.
• Der Aktuator kann ein fluidisch betätigter Aktuator, insbesondere ein pneumatischer oder ein hydraulischer Aktuator 3a, 3b sein.
• Die Antriebseinrichtung 1 kann mit einem bewegbaren Zylindergehäuse gebildet sein. Das Zylindergehäuse 8 ist in diesem Fall gegenüber einer Längsführungseinrichtung 11, die sich zwischen den Abstützeinrichtungen 39, 40 erstreckt, geführt. Von der Längsführungseinrichtung 11 ist ein Trennkörper 24 getragen. Der Trennkörper 24 trennt zwei in dem Zylindergehäuse 8 gebildete Druckräume 14, 15. Über Kanäle 20, 21 sind die Druckräume 14, 15 mit dem Fluid beaufschlagbar. Das Zylindergehäuse 8 bildet in diesem Fall Kolbenflächen 16, 17 aus. Durchaus möglich ist, dass die Kanäle 20, 21 zumindest teilweise in der Längsführungseinrichtung 11 gebildet sind.
• Optional können die Druckräume 14, 15 über mindestens eine Drossel oder mindestens ein Rückschlagventil 22, 23 miteinander gekoppelt sein. In der Antriebseinrichtung kann die mindestens eine Abstützeinrichtung 39, 40 über eine Rast- oder Verriegelungseinrichtung 94 in Querrichtung y rastierbar oder verriegelbar sein. Die Rast- oder Verriegelungseinrichtung 94 kann bspw. mechanisch bewegungsgesteuert, pneumatisch, hydraulisch, pneumatisch, elektrisch, elektrohydraulisch oder elektropneumatisch betätigt werden.
• Vorgeschlagen wird auch, dass die Abstützeinrichtungen 39, 40 über ein Federelement an einer Trageinrichtung 67 abgestützt sind, welches mit einer Bewegung der Abstützeinrichtung 39, 40 in Querrichtung y beaufschlagbar ist.
• Auch möglich ist, dass die Querführungseinrichtung 65 mit mindestens einem Freiheitsgrad gegenüber einer Trageinrichtung 67 abgestützt ist, wobei eine Bewegung entlang dieses Freiheitsgrads eine Veränderung der Ausrichtung der Längsführungseinrichtung 11 zur Folge hat.
• Möglicherweise können über die Antriebseinrichtung 1 zwei Flügeltüren 6a, 6b synchron geöffnet und geschlossen werden.
• Möglich ist auch, dass mittels der Antriebseinrichtung 1 wahlweise zwei Flügeltüren 6a, 6b synchron geöffnet und geschlossen werden können oder lediglich eine Flügeltür 6a, 6b geöffnet oder geschlossen wird, währen die andere Flügeltür 6b, 6a geöffnet oder geschlossen bleibt.

Preferably, the suspension 102 is used together with a drive device which can be equipped with the following alternative or cumulative features:

• The drive device 1 may have an actuator 3a, 3b, by means of which a movement of at least one hinged door 6a, 6b in a longitudinal direction x over a longitudinal stroke can be brought, which only in a partial stroke of the longitudinal stroke with the movement of the at least one hinged door 6a, 6b in a Transverse direction y is mechanically coupled.
• It is also possible that a cylinder housing 8a, 8b of the actuator 3a, 3b is moved with the movement of the hinged door 6a, 6b.
• Furthermore, it is possible that in the drive device 1, a holding device 5a, 5b is present, on which the hinged door 6a, 6b can be held. The drive device 1 then has a longitudinal guide device 11a, 11b for the holding device 5a, 5b or the cylinder housing 8a, 8b. Supporting devices 39, 40 are provided for the longitudinal guide device 11, which are movable in the transverse direction y. 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 means 11a, 11b in the longitudinal direction x over the longitudinal stroke can be brought about, which only in the partial stroke of Longitudinal stroke with the movement of the support means 39, 40 is coupled in the transverse direction y.
• It is also possible that in the drive device 1, the coupling of the movement of the holding device 5a, 5b or the cylinder housing 8a, 8b with the movement of the support means 39, 40 via a driver unit 74, which mechanically only for the partial stroke, the holding device 5a, 5b or the cylinder housing 8a, 8b with the support means 39, 40 couples.
• It is possible that the position of the driver unit 74 and thus the size of the partial stroke is adjustable.
• The actuator may be a fluidically actuated actuator, in particular a pneumatic or a hydraulic actuator 3a, 3b.
• The drive device 1 can be formed with a movable cylinder housing. The cylinder housing 8 is guided in this case with respect to a longitudinal guide device 11 which extends between the support means 39, 40. Of the longitudinal guide device 11, a separating body 24 is supported. The separator 24 separates two pressure chambers 14, 15 formed in the cylinder housing 8. Via channels 20, 21, the pressure chambers 14, 15 can be acted upon by the fluid. The cylinder housing 8 forms piston surfaces 16, 17 in this case. It is entirely possible that the channels 20, 21 are at least partially formed in the longitudinal guide device 11.
• Optionally, the pressure chambers 14, 15 via at least one throttle or at least one check valve 22, 23 may be coupled together. In the drive device, the at least one support device 39, 40 can be locked or locked in the transverse direction y by means of a latching or locking device 94. The latching or locking device 94 may, for example, be operated mechanically controlled by motion, pneumatically, hydraulically, pneumatically, electrically, electrohydraulically or electropneumatically.
• It is also proposed that the support means 39, 40 are supported by a spring element on a support means 67, which is acted upon by a movement of the support means 39, 40 in the transverse direction y.
• It is also possible that the transverse guide device 65 is supported with at least one degree of freedom with respect to a carrying device 67, wherein a movement along this degree of freedom has a change in the orientation of the longitudinal guide device 11 result.
• Possibly, two folding doors 6a, 6b can be opened and closed synchronously via the drive device 1.
• It is also possible that by means of the drive device 1 either two hinged doors 6a, 6b can be opened and closed synchronously or only one hinged door 6a, 6b is opened or closed, while the other hinged door 6b, 6a remains open or closed.

• 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).

Fig. 17 shows a fluidic control circuit 2, which allows depending on the operating position of a valve device 108 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 Fig. 17 the primary side 27 of the pump 25 is connected via a controllable check valve 109 or controllable check valve to the port 18a and the pressure chamber 14a of the actuator 3a. The port 19a of the actuator 3a is connected to a port 110 of a valve 111, here a controlled 3/2-way valve 112. The valve 111 has other ports 113, 114. In the in Fig. 17 effective position of the valve 111, which corresponds to the non-actuated position as a result of the application of a spring, are the connections 110, 113 via the valve 111 connected together while the port 114 is shut off. In the other position of the valve 111 brought about by the drive, the latter connects the connections 110, 114 to each other while the connection 113 is shut off.

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

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

The port 113 of the valve 111 is connected via a branch 121 and the check valve 115 to the secondary side 29 of the pump 25. By contrast, the connection 119 of the valve 117 is connected via a branch 122 and the check valve 109 to the primary side 27 of the pump 25. The connections 114, 120 of the two valves 111, 117 are connected to one another. About one in Fig. 17 Control device, not shown, can be made to act on the control connections of the valves 111, 117, as required, in accordance with what is required Fig. 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 fluidic pressure, which is supplied to the control port of the valves 111, 117.

1. a) In der in Fig. 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 Fig. 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.
2. b) Werden beide Ventile 111, 117 umgeschaltet in die nicht in Fig. 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.
3. c) Ebenfalls möglich ist eine Einzeltürsteuerung mit einer reinen Betätigung des Aktuators 3a: Hierzu nimmt das Ventil 111 die in Fig. 17 wirksame Stellung ein, während das Ventil 117 in die in Fig. 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 Fig. 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 Fig. 17 nicht wirksame Stellung umgeschaltet wird, während das Ventil 117 in die in Fig. 17 wirksame Stellung gesteuert wird.

The valve device 108 is formed with the valves 111, 117. Depending on the control of the valve device 108, that is, depending on the control of the valves 111, 117, the following different operating modes can be made possible by means of the fluidic control circuit 2:

1. a) In the Fig. 17 effective switching position of the valves 111, 117, in which the control terminals of the valves 111, 117 are not fluidly acted upon, the delivery volume of the pump 25 is divided in the region of the branch 122. A part, in particular half, of the delivery volume of the pump 25 passes via the port 18a to the pressure chamber 14a of the actuator 3a. The other pressure chamber 15 a is connected via the port 19 a and the valve 111 due to the connection of the terminals 110, 113 via the check valve 115 to the secondary side 29. As a result of the pressurization of the primary side 27 is in a control line 123 for the check valve 115 control pressure, so that the check valve 115 is opened and against the actual opening direction fluid can reach the secondary side 29. With the part of the delivery volume of the pump 25, which passes from the branch 122 to the port 18a, thus, the actuation of the actuator 3a can take place.
   The other part of the delivery volume passes via the branch 122, the interconnected ports 119, 116 of the valve 117 to the port 18b of the actuator 3b and thus to the pressure chamber 14b of the actuator 3b. On the other hand, the pressure chamber 15b of the actuator 3b is connected to the secondary side 29 via the connection 19b and the non-return valve 115 opened as a result of the pressurization of the control line 123. Thus, with the other part of the delivery volume of the pump 25, which passes from the branch to the port 18b, the actuation of the actuator 3b take place.
   The same applies to the reversal of the conveying direction of the pump 25, in which case a control line 124 to the opening of the check valve 109 is pressurized. For the in Fig. 17 effective operating position, which is also referred to as "first operating position", the pressure chambers 14a, 14b of the actuators 3a, 3b connected in fluidic parallel connection with the primary side 27 of the pump 25. Since the actuation of the two actuators 3a, 3b takes place here only with a part of the delivery volume of the pump 25, this first operating position of the valve device leads 108 to an actuation of the actuators 3a, 3b with a reduced operating speed for a double door control.
2. b) If both valves 111, 117 switched to the not in Fig. 17 effective position, so is the second operating position of the valve device 108 before. In the second operating position, the valve 111 connects the ports 110, 114 to each other while the port 113 is shut off, and the valve 117 connects the ports 116, 120 to each other while the port 119 is shut off. In the second operating position, a double door control with an increased operating speed is made possible: Given the shut-off of the port 119 through the valve 117, there is no division of the delivery volume of the pump 25 on the primary side in the area of the branch 112. Rather, the entire delivery volume of the pump 25 is via the port 18a provided to the actuator 3a. In this case, a kind of "master cylinder" is formed with the pressure chamber 15a: The pressure chamber 15a is connected via the port 19a and the ports 110, 114 of the valve 111 and the ports 120, 116 of the valve 117 to the port 18b of the actuator 3b. With the pressure chamber 14b then a kind of "slave cylinder" is formed. The pressure chambers 15a, 14b are thus fluidly coupled to each other, whereby a coupling of the movement of the two actuators 3a, 3b takes place with each other. If this coupling of the movements leads to an actuating movement of the actuator 3b, the volume of the pressure chamber 15b of the actuator 3b changes, whereby fluid is expelled from the pressure chamber 15b. This passes through the port 19b and the open in the face of the pressurization of the control line 123 check valve 115 to the secondary side 29 of the pump 25. Since actuation of the actuator 3a with the full delivery volume of the pump 25, there is an actuation of the actuator 3a with increased operating speed. As a result of the coupling of the two actuators 3a, 3b with each other also results in an increased actuation speed of the actuator 3b.
   The same applies to reversal of the conveying direction of the pump 25th
3. c) Also possible is a single door control with a pure actuation of the actuator 3a: For this purpose, the valve 111 takes the in Fig. 17 effective position while the valve 117 in the in Fig. 17 not effective position is controlled. In view of the blocking of the port 119 by the valve 117, there is no division of the delivery volume in the region of the branch 122. Rather, the entire delivery volume of the pump 25 is provided to the actuator 3a via the connection 18a. The pressure chamber 15 a is connected to the secondary side 29 via the connection 19 a and the connections 110, 113 of the valve 111, the branch 121 and the check valve 115 opened in view of the pressurization of the control line 123. Thus, an actuating movement of the actuator 3a is possible. By contrast, the pressure chamber 14b of the actuator 3b via the port 18b, the ports 116, 120 of the valve 117 and the port 114 in the switching position of the valve 117 according to Fig. 17 shut off, so that an assumed position of the actuator 3b can not change. This results in a single door control via the actuator 3a, which takes place with the full delivery volume of the pump 25, that is, a large actuation speed.
   Accordingly, a single door control for the actuator 3b can be done by the valve 111 in the in Fig. 17 is switched inactive position while the valve 117 in the in Fig. 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 the adjusting movement of an actuator 3a, 3b is detected via a displacement sensor 126, wherein the displacement sensor 126 can also be formed with the measuring rod 103 according to the previously explained embodiments. The signal of the pressure sensor 125 and / or the displacement sensor 126 can be used for different purposes:

• On the basis of the signal from the pressure sensor 125 and / or the displacement sensor 126, a control of the termination of the operation of the pump 25 can take place when a target pressure or a predetermined travel, in particular an open position or a closed position is reached.
• On the basis of the signal of the pressure sensor 125 and / or the displacement sensor 126, a regulation of the delivery mode, the delivery volume and / or a rotational speed of the pump 25 can take place.
• Based on the signal of the pressure sensor 125 and / or the displacement sensor 126, a switching between the different operating positions of the valve device 108 can take place. For example, can take place with the detection of the approach of the wing doors 6a, 6b to the closed position of a changeover from the second operating position to the first operating position.
• If a displacement sensor 126, 126a is assigned to each actuator 3a, 3b in each case, individual door control on the basis of the associated displacement sensor 126, 126a can also take place for both actuators 3a, 3b.

In the exemplary embodiments, the fluidic control circuit 2 is preferably a hydraulic control circuit, so that the actuators 3a, 3b are also actuated hydraulically. This is particularly advantageous for the second operating position, since then the incompressibility of the hydraulic medium can be utilized for the fluidic coupling of the two actuators 3a, 3b in series connection thereof.

The invention finds application for any vehicles, especially passenger transport vehicles such as buses or trains of any kind and design. The hinged doors 6a, 6b are preferably swing-sliding doors.

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

dog 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 (12)

Fluidic control circuit (2) for driving two gullwing doors (6a, 6b) of a vehicle assigned to a common manhole a) wherein the wing doors (6a, 6b) controlled by the fluidic control circuit (2) are movable in opposite directions and the drive of the wing doors (6a, 6b) via two double-acting actuators (3a, 3b) takes place, each having two oppositely acting and have pressure chambers (14a, 15a, 14b, 15b) acted upon by the control circuit (2), b) with a valve device (108), which ba) in a first operating position pressure chambers (14a, 14b) of both actuators (3a, 3b) in fluidic parallel connection with a primary side (27) of a pump (25) connects and bb) in a second operating position only one pressure chamber (14a) of an actuator (3a) to the primary side (27) of the pump (25) connects, while the other pressure chamber (15a) of this actuator with the pressure chamber (14b) of the other actuator (3b ), whereby the movement of the two actuators (3a, 3b) is coupled together. Fluidic control circuit (2) according to claim 1, characterized in that a control device is provided which, during an opening and / or closing movement, transfers the valve device (108) from the first operating position into the second operating position and / or vice versa. Fluidic control circuit (2) according to one of the preceding claims, characterized in that a control device and a pressure sensor (125) for detecting a pressure in the fluidic control circuit (2) are provided, wherein depending on the pressure detected by the pressure sensor (125) Valve device (108) is transferred from the first operating position to the second operating position and / or vice versa. Fluidic control circuit (2) according to one of the preceding claims, characterized in that a control device and a displacement sensor (126) for detecting a Travel of an actuator (3a, 3b) or a hinged door (6a, 6b) are provided, wherein the valve device (108) is transferred from the first operating position to the second operating position and / or vice versa depending on the travel detected by the displacement sensor (126) , Fluidic control circuit (2) according to one of the preceding claims, characterized in that the valve device (108) has a further operating position in which a single-door control takes place. Fluidic control circuit (2) according to one of the preceding claims, characterized in that a) a primary side (27) of a pump (25) aa) is connected to a pressure chamber (14a) of a first actuator (3a) and bb) via a valve (117) optionally in addition to a pressure chamber (14b) of a second actuator (3b) is connectable, and b) a secondary side (29) of the pump (25) ba) is connected to a pressure chamber (15b) of the second actuator (3b) and bb) via a valve (111) optionally in addition to a pressure chamber (15a) of the first actuator (3a) is connectable. Fluidic control circuit (2) according to one of the preceding claims, characterized in that the primary side (27) of the pump (25) with a pressure chamber (14a) of a first actuator (3a) is connected, while the other pressure chamber (15a) of the first actuator (3a) depending on the operating position of the valve device (108) a) with the secondary side (29) of the pump (25), b) lockable or c) with a pressure chamber (14b) of a second actuator (3b) is connectable. Fluidic control circuit (2) according to claim 6 or 7, characterized in that at least one of the valves (111; 117) is a 3/2-way valve (112; 118). Fluidic control circuit (2) according to one of claims 6 to 8, characterized in that at least one of the valves (111; 117) is designed as a magnetic valve, so that it is directly controllable by an electronic control unit. Fluidic control circuit according to one of the preceding claims, characterized in that between the primary side (27) and the secondary side (29) of a pump (25) a bypass line (30) is interposed, in which a manual emergency valve (31) is arranged. Fluidic control circuit (2) according to one of the preceding claims, characterized in that between the pump (25) and the actuator (3a, 3b) a check valve (109, 115) opening in the direction of a pressure chamber (14a, 15b) of the actuator (3a, 3b) is provided ) or check valve is arranged, which a) during operation of the pump (25) allows a fluidic flow in the direction of the pressure chamber (14a, 15b) of the actuator (3a, 3b), b) without operation of the pump (25) the pressure chamber (14a, 15b) shuts off and c) upon reversal of the conveying direction of the pump (25) is controlled such that it allows a fluidic flow from the pressure chamber (14a, 15b) to the pump (25). Fluidic control circuit (2) according to one of the preceding claims, characterized in that the valve device (108) assumes the first operating position without activation.

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