DE102013100005B3 - Fluidic control circuit for two wing doors of a bus - Google Patents

Abstract

The invention relates to a fluidic control circuit (2) for two wing doors of a vehicle. Controlled by the fluidic control circuit (2), the wing doors can be moved in opposite directions. The wing doors are driven by two double-acting actuators (3a, 3b). The actuators (3a, 3b) each have opposing pressure chambers (14a, 15a; 14b, 15b) acted upon by the control circuit (2). The fluidic control circuit (2) has a valve device (108). In a first operating position of the valve device (108), pressure chambers (14a, 14b) of both actuators (3a, 3b) are connected in fluidic parallel connection to a primary side (27) of a pump (25). Thus, in the first operating position, the delivery volume of the pump (25) is divided between the two pressure chambers (14a, 14b) of both actuators (3a, 3b), which means that the operating speed of the wing doors can be reduced. In a second operating position, the valve device (108) connects only one pressure chamber (14a) of an actuator (3a) to the pump (25), while the other pressure chamber (15a) of this actuator (3a) connects to a pressure chamber (14b) of the other actuator ( 3b), whereby the movement of the two actuators (3a, 3b) is coupled to one another. In this way, an increased actuation speed can be brought about in the second operating position.

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 pressure chambers both in a first operating position 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 of 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.

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 folding 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. About the pressure sensor can then indirectly also the travel of the actuator can be detected, so that for a predetermined opening or closing path with the Hereby correlated detected pressure, the switching of the operating position takes place.

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. Furthermore, a valve is provided, via which optionally the primary side of the pump can be additionally connected 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 is enabled with reduced operating speed,
• - Can be shut off, so this actuator can be disabled, so that a single door control on the other actuator is enabled, or
• - Can be connected to a pressure chamber of the second actuator, which 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, however, the valves are 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

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

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

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

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

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

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

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

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

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

9 shows a detail of the suspension with drive device for two wing doors in a spatial representation obliquely from below, 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.

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

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

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

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

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

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

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

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

DESCRIPTION OF THE FIGURES

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

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

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

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

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

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

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

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

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

The operation of the drive device 1 is as follows:

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

be sealed.

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

The movement of the hinged door in the longitudinal or transverse direction described here can describe a movement of a pivot point of the hinged door itself. 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 takes place 102 Use together with a drive device which can be equipped with the following alternative or cumulative features:

• - The drive device 1 can be an actuator 3a . 3b possess, by means of which a movement of at least one gullwing 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 is mechanically coupled in a transverse direction y.
• - It is also possible that a cylinder housing 8a . 8b of the actuator 3a . 3b with the movement of the gullwing door 6a . 6b is moved.
• - It is also possible that in the drive device 1 a holding device 5a . 5b is present at the the gullwing 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 , support devices 39 . 40 are available for the longitudinal guide device 11 which are movable in the transverse direction y. By means of the actuator 3a . 3b is a movement of the holding device 5a . 5b or the cylinder housing 8a . 8b along the longitudinal guide device 11a . 11b in the longitudinal direction x over the longitudinal stroke can be brought, which only in the partial stroke of the longitudinal stroke with the movement of the support device 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 device 39 . 40 via a driver unit 74 takes place, which mechanically only for the partial stroke the holding device 5a . 5b or the cylinder housing 8a . 8b with the support device 39 . 40 coupled.
• - It is possible that the position of the driver unit 74 and so that the size of the partial stroke is adjustable.
• The actuator can be a fluidically actuated actuator, in particular a pneumatic or a hydraulic actuator 3a . 3b be.
• - The drive device 1 can be formed with a movable cylinder housing. The cylinder housing 8th is in this case compared to a longitudinal guide device 11 extending between the support devices 39 . 40 extends, guided. From the longitudinal guide device 11 is a separator 24 carried. The separating body 24 separates two in the cylinder housing 8th formed pressure chambers 14 . 15 , About channels 20 . 21 are the pressure chambers 14 . 15 acted upon by the fluid. The cylinder housing 8th forms piston surfaces in this case 16 . 17 out. It is possible that the channels 20 . 21 at least partially in the longitudinal guide device 11 are formed.
• - Optionally, the pressure chambers 14 . 15 via at least one throttle or at least one check valve 22 . 23 be coupled with each other. In the drive device, the at least one support device 39 . 40 via a latching or locking device 94 be latchable or lockable in the transverse direction y. The locking or locking device 94 For example, it can be operated mechanically controlled by motion, pneumatically, hydraulically, pneumatically, electrically, electrohydraulically or electropneumatically.
• - It is also proposed that the support devices 39 . 40 via a spring element on a support device 67 are supported, which with a movement of the support device 39 . 40 in the transverse direction y can be acted upon.
• - It is also possible that the transverse guide device 65 with at least one degree of freedom relative to a carrying device 67 is supported, wherein a movement along this degree of freedom a change in the orientation of the longitudinal guide device 11 entails.
• - It may be possible via the drive device 1 two double doors 6a . 6b be opened and closed synchronously.
• - It is also possible that by means of the drive device 1 optionally two hinged doors 6a . 6b can be opened and closed synchronously or just a double door 6a . 6b opened or closed, while the other double 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).

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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 the drive of two common doors associated with a common entry door ( 6a . 6b ) of a vehicle, a) the gullwing doors ( 6a . 6b ) controlled by the fluidic control circuit ( 2 ) are movable in opposite directions to each other and the drive of the gullwing doors ( 6a . 6b ) via two double-acting actuators ( 3a . 3b ), each having two opposite and by the control circuit ( 2 ) acted upon pressure chambers ( 14a . 15a ; 14b . 15b ), 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 ) with the primary side ( 27 ) of the pump ( 25 ), 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, the valve device ( 108 ) 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 pressure sensor ( 125 ) for detecting a pressure in the fluidic control circuit ( 2 ), depending on the pressure sensor ( 125 ) detected pressure the 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, depending on the of the displacement sensor ( 126 ) detected travel the 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 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) with a pressure chamber ( 14a ) of a first actuator ( 3a ) and bb) via a valve ( 117 ) optionally with a pressure chamber ( 14b ) of a second actuator ( 3b ), and b) a secondary side ( 29 ) of the pump ( 25 ) ba) with a pressure chamber ( 15b ) of the second actuator ( 3b ) and bb) via a valve ( 111 ) optionally with 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 ), 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 ) 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 controlled 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 the 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 pump ( 25 ) and actuator ( 3a ; 3b ) in the direction of a pressure chamber ( 14a ; 15b ) of the actuator ( 3a ; 3b ) opening check valve ( 109 ; 115 ) or shut-off valve is arranged, which a) during operation of the pump ( 25 ) a fluidic flow in the direction of the pressure chamber ( 14a ; 15b ) of the actuator ( 3a ; 3b ), b) without operating the pump ( 25 ) the pressure space ( 14a ; 15b ) and c) upon reversal of the conveying direction of the pump ( 25 ) is controlled in such a way that it generates 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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