EP3406837A1 - Hydraulic drive assembly for a vehicle door or vehicle gate - Google Patents

Abstract

The invention relates to a hydraulic drive assembly (1) for a vehicle door or vehicle door (39). According to the invention, the loading of piston-cylinder units (4, 5) takes place via a slide valve (8). The slide valve (8) has a neutral operating position, in which the slide valve (8) pressure chambers (25, 26) of the piston-cylinder units (4, 5) directly to each other, so that also a manual movement of the vehicle door or vehicle door (39) is possible. If control connections (27, 28) of the slide valve (8) are acted upon differently by means of a reversible pump (2), the slide valve (8) is switched to a first or second operating position. In the first operating position, a pressure chamber (25) is acted upon via an unthrottled supply connection (43), while a pressure chamber (26) is connected via a throttled discharge connection (44) to a suction side of the pump (2). About the throttle effect of the discharge connection (44), the opening or closing force for the vehicle door or vehicle door (39) can be influenced.

Description

TECHNICAL FIELD OF THE INVENTION

The invention relates to a drive assembly, by means of which a vehicle door, in particular a single door or a double door of a bus, or a vehicle door, in particular a boot lid, a trunk o. Ä., In the opening and / or closing direction is movable. While such drive assemblies may also be operated by pneumatic or electrical power, the present invention relates to a hydraulic drive assembly.

STATE OF THE ART

DE 10 2010 002 625 B4 discloses a hydraulic drive assembly for a vehicle door of an omnibus. The vehicle door is pivotable here via a vertically oriented pivot column. The rotary column has a pinion, which meshes with a rack. The two end faces of the rack form piston surfaces of oppositely acting piston-cylinder units. The pressure chambers of the piston-cylinder units are connected to the switchable connections of a pressure side and a suction side of a reversible pump. Also via the pump, another piston-cylinder unit is pressurized. By means of this further piston-cylinder unit can be carried out upon reaching the closed position of the vehicle door, a lifting of the rotary column, whereby a locking of the vehicle door is brought about. The drive assembly has a housing in which a plurality of hydraulic components of the drive assembly such as the pump, check valves, a part of the rotary column, the pinion and the other piston-cylinder unit are integrated. The drive assembly may form a structural unit with this projecting rotary column and also from the housing projecting drive shaft for a drive motor of the pump. The Pump is preferably designed as a gear pump. If the pinion and the rack are arranged in the interior of the housing, a sump of the housing can serve as a tank for the hydraulic fluid, in which case the hydraulic fluid can be used simultaneously as a lubricant for the pinion and the rack.

Also according to EP 2 503 086 B1 there is a hydraulic actuation of oppositely acting piston-cylinder units whose pistons are formed by end regions of a meshing with a pinion of a rotary rack. EP 2 503 086 B1 discloses a hydraulic control circuit for the simultaneous hydraulic loading of two vehicle doors of a double door of a bus. Again, the oppositely acting pressure chambers of the piston-cylinder units are acted upon via connections of a reversible pump with a hydraulic fluid. The regulation of the reversible electric drive of the pump via an electronic control unit to which the pressure signal of a pressure sensor is supplied, which detects the pressure in the hydraulic, leading to the piston-cylinder units supply lines. Furthermore, the control unit is supplied with the signal of a position sensor for detecting the position of the vehicle door. The control unit determines on the one hand an operating state of the vehicle door (in particular a defect of the hydraulic control circuit, the impact of the vehicle door on a resistance such as a person trapped by the vehicle door, an approach of the vehicle door to an end position, etc.). The two leading to the piston-cylinder units supply lines are short-circuited via a manually operable, designed as a 2/2-way valve check valve. If the check valve is manually transferred to its passage position, an emergency operation can take place such that as a result of the shorted by means of the check valve pressure chambers of the piston-cylinder units, a manual movement of the vehicle door by the user can take place with which the hydraulic fluid from a pressure chamber of a piston Cylinder unit is transferred into a pressure chamber of the other piston-cylinder unit.

According to DE 10 2012 107 522 B4 finds a hydraulic control circuit according to EP 2 503 086 B1 or DE 10 2010 002 625 B4 Commitment. However, here is a rack drive insert, in which the rotary column driving pinion meshes on opposite sides with two rack parts, wherein the rack members each forming a piston face of a piston-cylinder unit with an end face. In the pressure chambers of the piston-cylinder units spring and / or damping elements are arranged, which in an end region of the stroke of the rack member, including an end portion of the opening or closing movement of the Vehicle door, come into effect to bring about a cushioning. To avoid a game of the vehicle door due to a backlash between the pinion and the rack parts, suggests DE 10 2012 107 522 B4 that the rack parts are acted upon by a permanently acting spring with a basic actuating force. It is also proposed that in each case a throttle is arranged in the supply lines to the piston-cylinder units, which should have the consequence that even with a connection of the piston-cylinder units with a pressure sink of the pump via this supply line, the pressure in the Pressure chamber of the piston-cylinder unit does not fall off too quickly, so that no basic actuating force would be guaranteed. Rather, the throttle is at least for a limited period sufficient pressure in the pressure chamber (and thus the basic actuating force, which excludes or reduces the influence of a backlash, ensure).

Another hydraulic control circuit for a hydraulic actuation of drives of gullwing doors of a bus is out DE 10 2013 100 005 B3 known.

OBJECT OF THE INVENTION

• sowohl eine hydraulisch verursachte Bewegung der Fahrzeugtür oder Fahrzeugklappe als auch eine manuelle Bewegung der Fahrzeugtür oder Fahrzeugklappe ermöglicht,
• eine verbesserte Stellcharakteristik oder erhöhte Stellgenauigkeit bei der hydraulisch verursachten Bewegung der Fahrzeugtür oder Fahrzeugklappe aufweist,
• eine kompakte konstruktive Ausgestaltung ermöglicht und/oder
• eine hohe Betriebssicherheit gewährleistet.

The present invention has for its object to provide a hydraulic drive assembly for a vehicle door or vehicle door, which in particular

• allows both a hydraulically caused movement of the vehicle door or vehicle door and a manual movement of the vehicle door or vehicle door,
• has an improved control characteristic or increased positioning accuracy in the hydraulically caused movement of the vehicle door or vehicle door,
• a compact structural design allows and / or
• ensures a high level of operational safety.

SOLUTION

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

DESCRIPTION OF THE INVENTION

The invention proposes a hydraulic drive assembly for a vehicle door or vehicle door having a first hydraulic piston-cylinder unit and a second hydraulic piston-cylinder unit, which are drivingly coupled to the vehicle door or vehicle door. This coupling can be done directly or indirectly with the interposition of any gear. For example, piston-cylinder units and coupling gear can be used, as these are known from the aforementioned prior art.

Furthermore, the drive assembly according to the invention has a valve assembly. This valve assembly can have individual, interconnected via valves. Preferably, however, the valve assembly is designed as a valve unit, in particular with a common valve body permitting the different operating positions, or as part of a larger structural unit.

• einen Anschluss, der mit einer ersten hydraulischen Versorgungsleitung verbunden ist,
• einen Anschluss, der mit einer zweiten hydraulischen Versorgungsleitung verbunden ist,
• einen Anschluss, der mit der ersten Kolben-Zylinder-Einheit verbunden ist, und
• einen Anschluss, der mit der zweiten Kolben-Zylinder-Einheit verbunden ist.

In the context of the invention, the valve assembly connections, namely

• a port connected to a first hydraulic supply line,
• a port connected to a second hydraulic supply line,
• a port which is connected to the first piston-cylinder unit, and
• a port which is connected to the second piston-cylinder unit.

The valve assembly has different operating positions. Depending on the operating position of the valve assembly, the hydraulic actuation of at least one piston-cylinder unit, preferably simultaneously the admission of both piston-cylinder units, can be changed. This is done by making a connection of the first hydraulic supply line to the first piston-cylinder unit and / or a connection of the second hydraulic supply line to the second piston-cylinder unit through the valve assembly, interrupted or changed.

A change in the operating position of the valve assembly can be carried out hydraulically within the scope of the invention. For this purpose, the valve assembly has at least one hydraulic control connection, via the hydraulic actuation of which the operating position of the valve assembly is "automatically" changeable.

• eine neutrale Betriebsstellung,
• eine erste Betriebsstellung und
• eine zweite Betriebsstellung,

wobei auch möglich ist, dass mindestens eine weitere Betriebsstellung vorhanden ist.The operating positions of the valve assembly are:

• a neutral operating position,
• a first operating position and
• a second operating position,

wherein it is also possible that at least one further operating position is present.

In the neutral operating position, the valve assembly hydraulically connects the ports for the first piston-cylinder unit and the second piston-cylinder unit so that the two piston-cylinder units are "shorted" through the valve assembly. This allows manual movement of the vehicle door or vehicle door for which hydraulic fluid is forced from one pressure chamber of a piston-cylinder unit via the valve assembly into the other piston-cylinder unit as a result of the force applied manually by the user to the vehicle door or vehicle door.

In the first operating position, the valve assembly connects the connection for the first piston-cylinder unit with the connection for the first hydraulic supply line via a first supply connection, while the connection for the second piston-cylinder unit with the second connection for the second hydraulic supply line connected via a first discharge connection. If, for example, the first hydraulic supply line for a first drive direction of the pump is connected to a pressure source, in this case the pressure side, of the pump, while the second hydraulic supply line is connected to a pressure sink, in this case the suction side of the pump, an enlargement of the first operating position takes place Pressure chamber of the first piston-cylinder unit with simultaneous reduction of the pressure chamber of the second piston-cylinder unit, resulting in a movement of the vehicle door or vehicle door in a first direction of movement. Here, hydraulic fluid can be supplied via the first supply connection from the pressure side of the pump of the first piston-cylinder unit, while the hydraulic fluid from the second piston-cylinder unit via the first discharge connection can reach the suction side of the pump.

In the second operating position, the valve assembly connects the connection for the first piston-cylinder unit with the first connection for the first hydraulic supply line via a second discharge connection, while the connection for the second piston-cylinder unit with the second connection for the second hydraulic supply line is connected via a second feed connection. If the second operating position is assumed, when the drive direction of the pump is reversed relative to the first operating position and this is thus driven in a second direction of rotation, the fluid then passes from the pump via the second supply line to the second piston cylinder via the second supply connection Unit, while the fluid from the first piston-cylinder unit passes through the second discharge connection to the suction side of the pump, whereby then a movement of the vehicle door or vehicle door in the second direction of movement is brought about, which is opposite to the first direction of movement.

According to the invention, the first discharge connection has a stronger throttling effect than the first supply connection and / or the second discharge connection has a stronger throttling effect than the second supply connection. By the difference of the throttling effects or the design of the throttle effect in the discharge connection can be given at last, against which resistance the hydraulic fluid from the pressure chamber of the piston-cylinder unit whose volume must be reduced with the movement of the vehicle door or vehicle door, from the piston Cylinder unit must be pushed out. Thus, the throttle effect affects the pressure building up in the decreasing pressure chamber with the movement of the vehicle door or vehicle door. On the one hand, a first force is generated in the associated piston-cylinder unit via the pressure chamber supplied by the supply connection from the pressure side of the pump, whose volume increases with the movement of the vehicle door or vehicle flap. An oppositely acting second force is generated in the other piston-cylinder unit due to the pressure which forms due to the stronger throttling effect in the discharge connection. Thus, for generating the movement of the vehicle door or vehicle door, a resultant force resulting from the difference of the amounts of the first force and the second force acts. The dimensioning of the difference of the throttling effects in the feed connection and the discharge connection can thus ultimately influence the opening and / or closing force of the vehicle door or vehicle flap and / or the closing speed or acceleration. On the other hand, can be influenced by the increased throttle effect in the discharge connection and the control characteristic, the positioning speed and the positioning accuracy of the drive assembly. Thus, for example, as a result of the increased throttling in the discharge connection, a resistance to a movement of the vehicle door or vehicle flap is provided, which leads to a kind of "tension" of the hydraulic drive unit and / or a possible play in the Drive avoids. Advantage is u. U. also the stronger throttle effect in the discharge connection, if in addition to the hydraulic inducing the movement of the vehicle door or vehicle door at the same time a user applies forces in the same direction of movement on the vehicle door or vehicle door, which without stronger throttle effect in the discharge connection to a strong increase in the speed of Movement of the vehicle door or vehicle door could lead, which could then result in that over the supply connection not enough fluid to fill the increasing pressure chamber can be tracked.

In principle, the hydraulic supply of the supply lines can be arbitrary. By way of non-limiting example, the supply lines may be connected via a switching valve to a suction side and a pressure side of a non-reversible pump, in which case a change in movement of the vehicle door or vehicle door is effected by alternately supplying the supply lines via the switching valve either connected to the suction side or the pressure side of the pump. For a particular proposal of the invention, the first supply line and the second supply line are connected to the connections of a reversible pump providing a pressure source and a pressure sink. Such reversible pumps can be provided as standard components. A switching valve of the type described above is u. U. dispensable for such an embodiment, which may result in a simplified structure of the hydraulic drive assembly.

There are many possibilities for the structural design of the hydraulic components of the drive assembly. Thus, these components may be formed individually and connected to each other via hydraulic lines. It is also possible that parts of the components are combined into units, in which case these units can be connected to each other or to components via lines. Thus, for example, the valve assembly may not only be formed with a plurality of individual valves, but the valve assembly may also be formed as a valve unit, in which in particular a common valve body is moved into the different operating positions.

For a particular proposal of the invention, the piston-cylinder units and the valve assembly form a structural unit. The assembly may, for example, have a common housing into which the piston-cylinder units and the valve assembly are integrated could be. It is also possible that the assembly is formed with individual modules or sub-assemblies that can be flanged to each other, for example. It is possible that with the flanging of the modules or sub-assemblies together (in addition to the preparation of the mechanical connection of the modules or sub-assemblies) directly under sealing outward pneumatic connections between channels of the individual modules or sub-assemblies are created.

In principle, it is possible that a gear stage, by means of which a transformation of the movement type and / or a translation or reduction of the movement of the piston-cylinder units to a movement of a drive element for the vehicle door or vehicle door, is formed separately or outside of the aforementioned unit. For a further proposal of the invention, such a gear stage is integrated into the unit. For example, the gear stage may be a rack and pinion gear stage, via which the conversion of a translatory movement of the piston-cylinder units, which are coupled to the rack or are formed with the rack itself, can take place in a rotational movement, the then indirectly or directly, for example, can be used for the rotation of a rotary column of a vehicle door.

In the context of the invention is quite possible that separate piston-cylinder units are used, which then have separate actuating piston, as long as the two adjusting pistons are coupled via suitable mechanical connections and gear stages with the vehicle door or vehicle door. For a hydraulic drive assembly according to the invention, the piston-cylinder units on a common actuator piston, which may be for a particular proposal of the invention also directly a rack of a rack and pinion gear stage.

The equipment of the discharge connection with a stronger throttling effect than that of the feed connection can be done in any way. For one embodiment, the invention proposes that at least one of the discharge connections has a throttle. It is also possible that both the feed connection and the discharge connection has a throttle, in which case, however, the throttling effect of the throttle arranged in the discharge connection is greater. In the context of the invention, the at least one throttle can also be integrated into the valve assembly or valve unit.

As explained above, it is advantageous if the different operating positions of the valve assembly are brought about automatically when the pressure conditions in the supply lines and in particular the driving conditions of the pump connected to the supply lines change. So u. U. be desired that for a magnitude of the pressure difference in the two supply lines below a threshold (in particular for deactivated pump), the neutral operating position is taken, while for an amount of pressure difference in the supply lines above the threshold with a higher pressure in the first supply line the first operating position is taken, while for an amount of the pressure difference above the threshold value with a larger pressure in the second supply line, the second operating position is taken. This can be ensured for an embodiment according to the invention by the valve assembly, in particular the valve unit, having two oppositely acting control connections. A first control port is then connected to the first supply line while a second control port is connected to the second supply line.

For an advantageous development of the drive assembly according to the invention this has a compensation chamber. Such compensation chambers are required to compensate for changes in the volume of hydraulic fluid in the hydraulic control circuit and / or volume changes in the spaces of the hydraulic components and connecting lines for the hydraulic fluid. Such a compensation chamber can provide a corresponding compensation volume. Such a compensation chamber may have a compensation body such as a compensation membrane, which allow changes in the volume of the compensation chamber.

While it is quite possible that the aforementioned compensation chamber is formed separately from other components of the drive assembly and connected thereto via corresponding lines, the invention proposes in a further embodiment, that the compensation chamber is integrated into the assembly, resulting in a particularly compact design the drive assembly according to the invention results.

Unwanted changes in the fluidic loading or deviations from the desired fluidic loading may occur, for example, as a result of leakages or temperature-related Changes in the volume of hydraulic fluid come. These undesirable changes can be accommodated by fluid communication with a compensation chamber or tank as previously explained. For a proposal of the invention, in the neutral operating position, the connections for the first piston-cylinder unit and the second piston-cylinder unit (in particular via the short-circuit connection) are connected to the compensation chamber or to a connection leading to a compensation chamber or a tank. Without this measure, it could happen that undesirable high pressures act in the pressure chambers of the piston-cylinder units, which may in particular result in that seals of the pistons, which serve to seal the pressure chambers, are pressed or "set up". In this case, an undesirable increased friction would act between the pistons and the cylinders of the piston-cylinder units, which would then increase the manually applied actuating forces for movement of the vehicle door or vehicle door. This is inventively avoided in that a connection with the compensation chamber or the tank takes place. Accordingly, it is possible that in the first operating position [or the second operating position], the connection for the second piston-cylinder unit [resp. the connection for the first piston-cylinder unit] via the first discharge connection [resp. via the second discharge connection] with the compensation chamber or one connected to a compensation chamber or to a tank-carrying connection.

The structural design and design of the valve assembly and the valves used here can be basically arbitrary. For example, valves in training can be used as a seat valve. For a particular proposal of the invention, the valve assembly is designed as a slide valve, wherein preferably the different operating positions of the valve assembly are ensured with a single spool of the spool valve.

In a further embodiment of this proposal of the invention, the slide valve on a spool. End faces of the spool are each arranged displaceably in a control chamber. The two limited by the faces of the spool control chambers are then each connected to a hydraulic control port, so that automatically takes place depending on the existing pressure difference in the two supply lines, an adjustment of the position of the spool and thus an adjustment of the operating position of the spool valve.

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 features mentioned in the patent claims and the description are to be understood in terms of their number that exactly this number or a greater number than the said number is present, without requiring an explicit use of the adverb "at least". For example, when talking about an element, it should be understood that there is exactly one element, two elements or more elements. These features may be supplemented by other features or be the only characteristics that make up the product in question.

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

BRIEF DESCRIPTION OF THE FIGURES

Fig. 1

zeigt schematisch eine hydraulische Antriebsbaugruppe mit einem eine Ventilbaugruppe oder -einheit aufweisenden hydraulischen Steuerkreis, der zwischen eine Pumpe und Kolben-Zylinder-Einheiten zwischengeschaltet ist.

Fig. 2

zeigt in einem schematischen Schnitt eine als Baueinheit ausgebildete hydraulische Antriebsbaugruppe, in die eine Zahnstangen-Ritzel-Getriebestufe, Kolben-Zylinder-Einheiten, eine als Schieberventil ausgebildeter Ventilbaugruppe und eine Ausgleichskammer integriert sind.

Fig. 3

zeigt in einem Detail III die Antriebsbaugruppe gemäß Fig. 2 im Bereich des Schieberventils, welches sich hier in einer neutralen Betriebsstellung befindet.

Fig. 4

zeigt die Antriebsbaugruppe in einem Fig. 3 entsprechenden Schnitt, wobei sich hier das Schieberventil in der ersten Betriebsstellung befindet.

Fig. 5

zeigt die Antriebsbaugruppe in einem Fig. 3 und 4 entsprechenden Schnitt, wobei sich hier das Schieberventil in der zweiten Betriebsstellung befindet.

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

Fig. 1

schematically shows a hydraulic drive assembly with a valve assembly or unit having hydraulic control circuit which is interposed between a pump and piston-cylinder units.

Fig. 2

shows in a schematic section a designed as a unit hydraulic drive assembly, in which a rack and pinion gear stage, piston-cylinder units, designed as a slide valve valve assembly and a compensation chamber are integrated.

Fig. 3

shows in detail III the drive assembly according to Fig. 2 in the area of the slide valve, which is here in a neutral operating position.

Fig. 4

shows the drive assembly in one Fig. 3 corresponding section, with the slide valve is in the first operating position here.

Fig. 5

shows the drive assembly in one Fig. 3 and 4 corresponding section, with the slide valve is in the second operating position here.

DESCRIPTION OF THE FIGURES

Fig. 1 shows a hydraulic drive assembly 1. In the drive assembly 1 is a reversible pump 2 via a hydraulic control circuit 3 (the at Fig. 1 deviating embodiment may also include a control) with oppositely acting piston-cylinder units 4, 5 hydraulically connected.

Without this being absolutely necessary, according to Fig. 1 the hydraulic control circuit 3 exclusively via a valve assembly 6, which is designed here as a valve unit 7, the pump 2, the piston-cylinder units 4, 5 and an optional compensation chamber 19 and connecting lines between said hydraulic components. Preferably, the valve unit 7 is a slide valve 8.

The valve assembly 6 is designed as exclusively hydraulically controlled 5/3-way valve 9. The 5/3-way valve 9 has a connection 10 which is connected via a first supply line 11 to a first connection 12 of the pump 2. A connection 13 of the 5/3-way valve is connected via a second supply line 14 to a second port 15 of the pump 2. A further connection 16 is connected via a compensation line 17 via a branch 18 both to a tank or a compensation chamber 19 and to a supply connection 20 of the pump 2. In addition, the 5/3-way valve 9 has ports 21, 22, which are connected via Beaufschlagungsleitungen 23, 24 each with a pressure chamber 25, 26 of the piston-cylinder units 4, 5. Finally, the 5/3-way valve 9 also opposite to each other acting hydraulic control terminals 27, 28. The control terminals 27,28 are over in Fig. 1 dashed hydraulic control lines 29, 30 each connected to an associated supply line 11, 14.

The pump 2 is driven via a mechanical drive shaft 31 via an example, electrically driven drive unit 32, wherein depending on the desired operating position of the valve assembly 6 and the desired direction of movement of the vehicle door or vehicle door 39, the drive direction is reversible. U. U. also control or regulation of the rotational speed of the drive unit 32 is possible.

The pressure chambers 25, 26 of the piston-cylinder units 5 are limited by pistons 33, 34, which are formed for the illustrated embodiment of the opposite end portions of a common actuating piston 91, here a rack 35. To form a rack and pinion gear stage or rack gear 36 meshes with a translational movement of the rack 35, which is caused by pressurization of the pressure chambers 25, 26, the rack 35 with a rotatably connected to a rotary column 37 pinion 38. The rotary column 37 is (Direct or indirect) with a vehicle door or a vehicle door 39 shown here symbolically connected such that the rotation of the rotary column 37 leads to an opening movement or closing movement of the vehicle door or vehicle door 39.

• Ohne Antrieb der Pumpe 2 ist der Druck in den Versorgungsleitungen 11, 14 und damit der Druck an den Steueranschlüssen 27, 28 gleich groß. Dies hat zur Folge, dass, insbesondere durch eine neutrale Gleichgewichtslage vorgebende Federn 40, 41 des 5/3-Wegeventils 9, das 5/3-Wegeventil die in Fig. 1 wirksame mittige neutrale Betriebsstellung einnimmt. Diese wird u. U. auch erst dann verlassen, wenn der Betrag der Druckdifferenz der Drücke in den Versorgungsleitungen 11, 14 einen Schwellwert überschreitet. In der neutralen Betriebsstellung verbindet eine Kurzschlussverbindung 42 unmittelbar die Anschlüsse 21, 22 miteinander, wobei die Kurzschlussverbindung 42 ungedrosselt oder gedrosselt ausgebildet sein kann. Über die Kurzschlussverbindung ist eine manuelle Bewegung der Fahrzeugtür oder Fahrzeugklappe 39 durch den Benutzer möglich, welche dazu führt, dass auf die Zahnstange 35 und damit auf die Kolben 33, 34 eine Kraft ausgeübt wird. Diese Kraft hat wiederum zur Folge, dass das Hydraulikfluid aus einer Druckkammer 25 (bzw. 26) über die Beaufschlagungsleitung 23 (bzw. 24), den Anschluss 21 (bzw. 22), die Kurzschlussverbindung 42, den Anschluss 22 (bzw. den Anschluss 21), die Beaufschlagungsleitung 24 (bzw. die Beaufschlagungsleitung 23) in die Druckkammer 26 (bzw. die Druckkammer 25) verdrängt wird, wobei die Bezugszeichen ohne Klammern die Bewegung des Hydraulikfluids für die manuelle Bewegung der Fahrzeugtür oder Fahrzeugklappe 39 in eine erste Bewegungsrichtung und die Bezugszeichen in Klammern die Bewegung des Hydraulikfluids für die manuelle Bewegung der Fahrzeugtür oder Fahrzeugklappe 39 in eine zweite Bewegungsrichtung kennzeichnen. Zusätzlich erfolgt in der neutralen Betriebsstellung die Verbindung der Anschlüsse 21, 22 wie dargestellt mit dem Anschluss 16, während die Anschlüsse 10, 13 abgesperrt sind.

The function of the hydraulic drive assembly according to Fig. 1 is as follows:

• Without driving the pump 2, the pressure in the supply lines 11, 14 and thus the pressure at the control terminals 27, 28 are equal. This has the consequence that, in particular by a neutral equilibrium position predetermining springs 40, 41 of the 5/3-way valve 9, the 5/3-way valve in the Fig. 1 effective central neutral operating position occupies. This will u. U. leave only when the amount of pressure difference of the pressures in the supply lines 11, 14 exceeds a threshold. In the neutral operating position, a short-circuit connection 42 directly connects the terminals 21, 22 to each other, wherein the short-circuit connection 42 may be formed unthrottled or throttled. About the short-circuit connection, a manual movement of the vehicle door or vehicle door 39 by the user is possible, which leads to that on the rack 35 and thus on the piston 33, 34, a force is exerted. This force in turn has the consequence that the hydraulic fluid from a pressure chamber 25 (or 26) via the supply line 23 (or 24), the terminal 21 (or 22), the short-circuit connection 42, the terminal 22 (or the port 21), the supply line 24 (or the charge line 23) in the pressure chamber 26 (or the pressure chamber 25) is displaced, wherein the reference numerals without brackets, the movement of the hydraulic fluid for the manual movement of the vehicle door or vehicle door 39 in a first direction of movement and the reference numbers in parentheses indicate the movement of the hydraulic fluid for manual movement of the vehicle door or vehicle door 39 in a second direction of movement. In addition, in the neutral operating position, the connection of the terminals 21, 22 as shown with the terminal 16, while the terminals 10, 13 are shut off.

If a drive of the pump 2 in a first drive or rotational direction, the port 12 of the pump 2 forms a pressure side of the pump 2, while the port 15 corresponds to the suction side of the pump 2. Thus results in the supply line 11, a pressure which is greater than the pressure in the supply line 14, wherein the amount of the differential pressure exceeds the aforementioned threshold value for the switching of the valve assembly 6. Thus, the pressure acting on the control port 27 on a piston surface of the valve assembly 6 can generate a force which is greater than the force caused by the pressure at the control port 28 on an oppositely acting piston surface of the valve assembly. There is thus an automatic switching of the valve assembly 6 in a first operating position. In the first operating position, the connection of the terminals 10, 21 via a first feed connection 43, while the terminal 22 is connected via a first discharge connection 44 to the terminal 13. For the illustrated embodiment via the discharge connection 44 is also a connection of the terminal 22 to the terminal 16. In the first discharge connection 44, a throttle 45 is arranged so that the throttling action of the first feed connection 43 is smaller than that of the first discharge connection 44. In this first Operating position of the valve assembly 6 reaches the pumped from the pump 2 through the supply line 11 hydraulic fluid unthrottled via the first feed connection 43 to the pressure chamber 25, whereby a force is generated on the piston 33 of the piston-cylinder unit 4, which the rack 35 in a acted upon the first direction of movement. For a movement of the rack 35 in accordance with this force acting on the piston 33 in the first direction of movement hydraulic fluid must be displaced from the pressure chamber 26, which takes place via the first discharge connection 44 to the suction side of the pump 2. As a result of acting in the first discharge connection 44 throttle 45 but a resistance to the displacement of the hydraulic fluid from the pressure chamber 26 is generated so that the piston 34 of the piston-cylinder unit 5 acts a force which on the piston 33 of the piston Cylinder unit 4 opposite force is opposite, but which is smaller than the latter force.

If a movement of the vehicle door or vehicle door 39 in a second direction of movement is desired, the drive direction of the pump 2 is reversed, so that the connection 15 is the pressure side of the pump 2, while the connection 12 is the suction side of the pump 2. It then takes place as a result of the application of the control port 28 with a greater pressure than the pressure at the control port 27, a changeover of the valve assembly 6 in the second operating position. In this, the supplied with the larger pressure supply line 14 is connected via a second feed connection 46 to the pressure chamber 26 of the piston-cylinder unit 5, while the pressure chamber 25 of the piston-cylinder unit 4 via a second discharge connection 47 with arranged therein throttle 48th with the supply line 11, which is acted upon by the smaller pressure is connected. Thus prevails in the second operating position of the valve assembly 6 and for the second drive direction of the pump 2, the pressure exerted in the pressure chamber 26 on the piston 34 force against the force exerted in the pressure chamber 25 on the piston 33 force, so that movement of the vehicle door or vehicle door 39 takes place in a second direction of movement. Again, a resistance or a counter force is caused by the arranged in the second discharge connection 47 throttle.

It is possible that the rack gear stage 36, the piston-cylinder units 4, 5, the admission lines 23, 24, the valve assembly 6, the control lines 29, 30 and a part of the supply lines 11, 14 are arranged in a structural unit 49. In this case, the pivot post 37 protrudes out of the assembly 49 beyond a suitable sealed interface 50. Furthermore, the assembly 49 has connections 51, 52, over which in the assembly 49 extending sub-line strands 11a, 14a of the supply lines 11, 14 with the outside of the unit 49 extending sub-line strands 11 b, 14b of the supply lines 11, 14 are connected. Via a further connection 53 of the structural unit 49, a partial line 17a of the compensating line 17 running in the structural unit 49 can be connected to the pump 2.

Fig. 2 schematically shows a structural design of such a structural unit 49. In a recess 54 of a housing 55, the rack 35 is slidably guided by at least one sealing element 56 by sealing. The rack 35 meshes with a toothing 57 with a corresponding external toothing 58 of the pinion 38, which is rotatably connected to the rotary column 37. The rack 35 integrally forms the two pistons 33, 34 of the piston-cylinder units 4, 5. Here, the piston 34 is formed with a flat, formed by the end face of the rack 35 piston surface 59. In contrast, a piston surface 60 of the piston 33 of the piston-cylinder unit 4 is formed stepped with a partial piston surface 61 a, which is formed by an end face of the rack 35, and another, offset partial piston surface 61 b, wherein between the partial piston surfaces 61 a, 61 b, the toothing 57 extends. In the in Fig. 2 shown operating position, the volume of the pressure chamber 25 of the piston-cylinder unit 4 is maximum, while the volume of the pressure chamber 26 of the piston-cylinder unit 5 is minimal. For the illustrated embodiment, the volume of the pressure chamber 26 is vanishingly small, so that the piston surface 59 bears against the housing 55 on the end face. Fig. 2 Thus shows the assembly 49 in an open or closed position of the vehicle door or vehicle door 39th

The toothing 57 and the external toothing 58 are arranged in the pressure chamber 25 filled with the hydraulic fluid, so that the hydraulic fluid also serves for a lubrication of the engagement and the rolling contact of the toothing 57 and the external toothing 58. The recess 54 of the housing 55 is sealed to the outside via a closure body 62 screwed in here.

In Fig. 2 It can be seen that in each case an admission line 23, 24 opens into the pressure chambers 25, 26.

The control of the pressurization of the admission lines 23, 24 via the valve assembly 6 is in the detail III according to Fig. 3 shown in more detail: The admission lines 23, 24 open into a recess 63 of the housing 55. For the illustrated embodiment, the recess 63 is formed as a through hole 64 with a constant cross-section, which is sealed at the end by screw plugs 65, 66. In the recess 63, a spool 67 is slidably guided. In the recess 63 open also connected to the supply line 11 and port 10 connected to the supply port 14 terminal 13. In the housing 55 and a compensation chamber 19 is arranged. The compensation chamber 19 is bounded by a flexible membrane 68, whereby the volume of the compensation chamber 19 is variable, and closed by a closure body 69. The compensation chamber 19 is hydraulically connected via the compensation line 17, which also opens into the recess 63, with the recess 63 in connection.

For the illustrated embodiment, the Beaufschlagungsleitungen 23, 24 are formed in the form of also opening into the compensation chamber 19 channels, but which are shut off by sealing elements 70, 71 (such as Königsexpander) against the compensation chamber 19. The spool 67 has control edges and is relative to the Beaufschlagungsleitungen 23, 24 and the compensation line 17 and their mouth areas in the recess 63 slidably that according to the explanation Fig. 1 the neutral operating position and the first and the second operating position of the valve assembly 6 with the different created and blocked connections described there, in particular with the feed connections 43, 46 and discharge connections 44, 47, can be created.

For that in the Fig. 3 to 5 illustrated embodiment, the spool 67 has outgoing from the end faces blind holes 72, 73, which are closed in the region of the end faces of the spool 67 by closure elements 74, 75. In the inner end regions, the blind holes 72, 73 are each connected via transverse channels 76, 77 with a common annular space 78. The annular space 78 is radially inwardly limited by the control slide 67, while this is bounded radially outwardly by the recess 63. The spool 67 has further, here stepped transverse channels 79, 80, which are arranged on the side facing away from the annular space 78 of the transverse channels 76, 77 and also open into the blind holes 72, 73.

In the in Fig. 3 effective neutral operating position are the transverse channels 79, 80 and the control edges formed by them in the mouth region of the admission lines 23, 24th arranged. Thus, in the neutral operating position, the admission line 23 via the short-circuit connection 42, which here with the transverse channel 79, the blind hole 72, the transverse channel 76, the annular space 78, the transverse channel 77, the blind hole 73 and the transverse channel 80 is formed with the supply line 24 connected.

Between the end faces of the spool 67 and the screw plugs 65, 66 are oppositely acting on the spool 67 control chambers 81, 82 are formed. In the control chambers 81, 82 is in each case a compression spring 83, 84 between the associated end face of the spool 67 and an end face of the locking screws 65, 66 biased. On the other hand, in the in Fig. 3 The operation of the pump 2, the same pressures are applied to the terminals 10, 13, whereby the hydraulic forces acting on the end faces of the spool 67 are equal. Due to the action of the compression springs 83, 84 of the spool 67 is held in the neutral operating position.

If, however, the pump 2 is driven in the first direction of rotation, the pressure at the port 10 is greater than the pressure at the port 13, so that the force exerted in the control chamber 81 on the spool 67 force is greater than that corresponding to the other side in the control chamber 82 on the spool 67 force exerted. The spool 67 is thus from the neutral operating position according to Fig. 3 in the first operating position according to Fig. 4 postponed. In the first operating position according to Fig. 4 the connection 10 is connected to the supply line 23 via the first supply connection 43, which is here formed by an end-side annular space 85. On the other hand, due to the movement of the spool 67 in the first operating position, the connection between the transverse channel 79 and the admission line 23 is shut off and the transverse channel 80 enters the mouth region of the terminal 13. In the first operating position, hydraulic fluid from the admission line 24 through the discharge connection 44, the here with a stepped transverse channel 86 with this formed throttle 45, the blind hole 73 and the transverse channel 80 is formed, reach the terminal 13. At the same time, the blind hole 73 is connected via the transverse channel 77 and the annular space 78 with the compensation line 17.

The same applies to the second operating position, which in Fig. 5 is shown.

The measures according to the invention can also be used in conjunction with embodiments according to the aforementioned prior art. Thus, for example, in addition, a lifting of the rotary column 37 via a suitable piston-cylinder unit, as in the document DE 10 2010 002 625 B4 is described. For the inventive design, the throttle 45 acts over the entire stroke in the discharge connection 44 in the first direction of adjustment, while the throttle 48 acts in the second discharge connection 47 over the entire adjusting stroke in the other direction of adjustment.

To avoid that in the first and second operating position due to the control chamber 81, 82 with minimized volume due to the trapped in the control chamber 81, 82 hydraulic movement of the spool 67 is not possible, the control chambers 81, 82 via further transverse channels 87, 88 with therein arranged throttles 89, 90 connected to the blind holes 72, 73. Preferably, the transverse channels 87, 88 with the throttles 89, 90 disposed therein result in an influence on the damping of the movement of the control spool 67, since a change in the volume of the control chambers 81, 82 requires an exchange of the hydraulic fluid between the blind bore 72 and the control chamber 81 and the blind hole 73 and the control bore 82 through the choke 89 and 90, respectively.

While the control edges to ensure the different operating positions may well be formed with sealing elements of the spool, is also possible that only a small gap (in particular less than 30, 20 or even 10 microns) between the housing 55 and the spool 67 remains, which from the hydraulic fluid then can not (or possibly with a small leakage) can be passed.

Fig. 2 shows a structural configuration, the assembly 49 according to Fig. 1 , In particular, parts of the supply lines 11, 14 which do not run through the housing 55 in the region of the sections selected here are not shown. The assembly 49 according to Fig. 2 communicates, as for Fig. 1 explained, hydraulically via the terminals 51, 52, 53 with an external pump 2 and via a mechanical interface 50 with the vehicle door 39, without being in Fig. 2 the connections 51, 52, 53 and the mechanical interface 50 are shown.

LIST OF REFERENCE NUMBERS

1

hydraulic drive assembly

2

reversible pump

3

hydraulic control circuit

4

Piston-cylinder unit

5

Piston-cylinder unit

6

valve assembly

7

valve unit

8th

spool valve

9

5/3-way valve

10

Connection for the first supply line

11

first supply line

12

first connection pump

13

Connection for the second supply line

14

second supply line

15

second connection pump

16

connection

17

compensation line

18

branch

19

Tank, compensation chamber

20

supply terminal

21

connection

22

connection

23

impingement line

24

impingement line

25

pressure chamber

26

pressure chamber

27

control connection

28

control connection

29

control line

30

control line

31

mechanical drive shaft

32

power unit

33

piston

34

piston

35

rack

36

Rack and pinion gear stage, rack and pinion

37

rotating column

38

pinion

39

Vehicle door, vehicle flap

40

feather

41

feather

42

Fistula

43

first feed connection

44

first discharge connection

45

throttle

46

second feed connection

47

second discharge connection

48

throttle

49

unit

50

interface

51

connection

52

connection

53

connection

54

recess

55

casing

56

sealing element

57

gearing

58

external teeth

59

piston area

60

piston area

61

Part piston area

62

closure body

63

recess

64

Through Hole

65

Screw

66

Screw

67

spool

68

membrane

69

closure body

70

closure element

71

closure element

72

Blind hole

73

Blind hole

74

closure element

75

closure element

76

Querkanal

77

Querkanal

78

annulus

79

Querkanal

80

Querkanal

81

control chamber

82

control chamber

83

compression spring

84

compression spring

85

annulus

86

Querkanal

87

Querkanal

88

Querkanal

89

throttle

90

throttle

91

actuating piston

Claims (14)

Hydraulic drive assembly (1) for a vehicle door or vehicle flap (39) with a) a first and a second hydraulic piston-cylinder unit (4, 5), which are drivingly coupled to the vehicle door or vehicle door (39), b) a valve assembly (6), ba) which connections (10, 13, 21, 22) for a first hydraulic supply line (11), a second hydraulic supply line (14), the first piston-cylinder unit (4) and the second piston-cylinder unit (5 ) having, bb) via which, depending on the operating position of the valve assembly (6), the hydraulic actuation of the piston-cylinder units (4, 5) is variable by a connection of the terminal (10) for the first hydraulic supply line (11) with the terminal (21 ) for the first piston-cylinder unit (4) and / or a connection of the connection (13) for the second hydraulic supply line (14) to the connection (22) for the second piston-cylinder unit (5) made interrupted or changed, and bc) which has at least one hydraulic control connection (27, 28), via the hydraulic actuation of which the operating position of the valve assembly (6) can be changed, in which c) the valve assembly (6) ca) has a neutral operating position in which the valve assembly (6) hydraulically connects the ports (21, 22) for the first piston-cylinder unit (4) and the second piston-cylinder unit (5), cb) has a first operating position in which the valve assembly (6) the connection (21) for the first piston-cylinder unit (4) with the connection (10) for the first hydraulic supply line (11) via a first feed connection (43 ) and connects the connection (22) for the second piston-cylinder unit (5) with the second connection (13) for the second hydraulic supply line (14) via a first discharge connection (44) and cc) has a second operating position, in which the valve assembly (6) the connection (21) for the first piston-cylinder unit (4) with the first port (10) for the first hydraulic supply line (11) via a second discharge connection (47) connects and the connection (22) for the second piston-cylinder unit (5) with the second connection (13) for the second hydraulic supply line (14 ) connects via a second feed connection (46), and d) the first discharge connection (44) has a stronger throttling effect than the first supply connection (43) and / or the second discharge connection (47) has a stronger throttling effect than the second supply connection (46). Hydraulic drive assembly (1) according to claim 1, characterized in that the first supply line (11) and the second supply line (14) with a pressure source and a pressure sink providing connections (12, 15) of a reversible pump (2) are connected. Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that the piston-cylinder units (4, 5) and the valve assembly (6) form a structural unit (49). Hydraulic drive assembly (1) according to claim 3, characterized in that in the structural unit (49) a gear stage is integrated. Hydraulic drive assembly (1) according to claim 4, characterized in that the gear stage comprises a toothed rack (35) and with the rack (35) meshing pinion (38). Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that the piston-cylinder units (4, 5) have a common actuating piston (91). Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that at least one discharge connection (44; 47) has a throttle (45; 48). Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that the valve assembly (6) has two oppositely acting Control terminals (27, 28), wherein a first control terminal (27) to the first supply line (11) is connected and a second control terminal (28) to the second supply line (14) is connected. Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that a compensation chamber (19) is provided. Hydraulic drive assembly (1) according to claim 9 in direct or indirect reference to claim 3, characterized in that the compensation chamber (19) in the assembly (49) is integrated. Hydraulic drive assembly (1) according to claim 9 or 10, characterized in that the compensation chamber (19) is connected to a tank. Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that a) in the neutral operating position, the connections (21, 22) for the first piston-cylinder unit (4) and the second piston-cylinder unit (5) with the compensation chamber (19) or one leading to a compensation chamber or a tank Connection (16) are connected, b) in the first operating position of the connection (22) for the second piston-cylinder unit (5) via the first discharge connection (44) with the compensation chamber (19) or to a compensation chamber or a tank (19) leading terminal (16 ) and / or c) in the second operating position of the connection (21) for the first piston-cylinder unit (5) via the second discharge connection (48) with the compensation chamber (19) or to a compensation chamber or a tank (19) leading terminal (16 ) connected is. Hydraulic drive assembly (1) according to one of the preceding claims, characterized in that the valve assembly (6) is designed as a slide valve (8). Hydraulic drive assembly (1) according to claim 13, characterized in that the slide valve (8) has a control slide (67) whose end faces in each case slidably disposed in a control chamber (81, 82), wherein the control chambers (81, 82) are each connected to a hydraulic control port (27, 28).

Images