ES2733626T3 - Vehicle door drive for a bus - Google Patents

Abstract

Vehicle door drive (1) for a bus, with an actuator (2) that can be coupled through a drive coupling mechanism (1) to a vehicle door, where the coupling mechanism is made with a drive of drive mechanism (19), and where a) the actuator (2) is coupled in such a way to the axis of rotation (6) of a roller (7) of the drive (1), that a drive path (16 ) of the actuator (2) induces a displacement of the axis of rotation (6) of the roller (7), b) a traction means (8) of the traction mechanism drive (19) surrounds the roller (7), c) the traction means (8) forms a traction branch (13), which extends on one side of the roller (7) from the roller (7) towards an articulation member (11) connected to the vehicle door, and d) the roller (7) on the other side has an instantaneous center of rotation (15), e) the articulation member (11) moved by the drive d The traction mechanism (19) for the vehicle door carries out a translation movement and with the translation movement of the articulation member (11) an additional articulation point of the vehicle door is moved along a curved guide of the drive (1), whereby the vehicle door with the translation movement of the articulation member makes a pivoting-sliding movement, and / or the movement of the traction mechanism drive (19) is coupled at least through a partial stroke, through a coupling bar (58) and a drive lever (61) to a rotating column (63).

Description

DESCRIPTION

Vehicle door drive for a bus

Technical Field of the Invention

The present invention relates to a vehicle door drive for a bus, in which an actuator is coupled to a vehicle door through a coupling mechanism. Additionally, the present invention relates to a new use of a known drive. A vehicle door drive of this type is known from EP 2752546 A2.

State of the art

The prior art regarding vehicle door drives can be found, for example, in patent applications DE 102012107527 A1, DE 102012103638 A1, EP 12180508 A2, DE 102011 001003 A1, DE 102011 001 478 A1, DE 102010 002625 A1, DE 102008 034 994 A1, DE 102008 011 315 A1, DE 10 2006031477 A1, DE 3630229 A1; EP 2698547 A2 and EP 2184431 A1.

When designing vehicle door drives for a bus, a conflict of objectives may occur:

- On the one hand, a vehicle door must be as wide as possible, to allow getting on and off the bus comfortably, in some cases even for several people at the same time and / or carrying bulky objects or a pram for children. While in principle, for the closing of the entrance opening through two vehicle doors that move in the opposite direction a relatively large width is required, for closing the entrance opening with just one vehicle door, it is required an even wider width of the vehicle door.

- On the other hand, the conditions of the available constructive space require that the vehicle door drive used for the opening and closing of the at least one vehicle door occupies the smallest possible space, which governs in particular as regards the axial constructive length. For example, if a fluidic piston-cylinder unit is used for the vehicle door drive, the adjustment stroke of the piston-cylinder unit corresponds to the opening and closing stroke of the vehicle door, which in turn corresponds approximately to the width of the vehicle door. Therefore, in order to achieve the desired small mounting volume for driving the vehicle door, it is advantageous to provide the smallest possible width for the vehicle door.

In order to be able to use a small constructive size for a vehicle door drive, usually instead of piston-cylinder units as actuators in the vehicle door drives, for example, electric drives are used, which by means of a pocket drive they cause the movement of opening and closing the door of the vehicle with a compact constructive form.

The document not in accordance with US 3,863,390 refers to a drive for a door for an oven for hot metal. Due to the high active temperatures, deformations occur in this type of doors. The drive must be able to move the door reliably, regardless of possible deformations or warps. In addition, for this type of furnaces there is a requirement that in case of a drive failure, the door can be operated in another way. In US 3,863,390 it is described as something known that doors of this type are moved by means of a driven chain wheel and a chain, which must be arranged in a position away from the oven opening, so that they are not exposed to the heat and the flame of the oven. Due to this, the design possibilities are strongly limited by the drive and the place where the chain and chain wheel are arranged. US 3,863,390 proposes to use a double-acting cylinder in a drive for a door of an oven, which must be arranged laterally in the vehicle door. In a cylinder rod that emerges on both sides in a displaceable manner from a cylinder housing, in each end zone a roller is rotatably supported. A flexible chain or a cable is attached with end zones in the cylinder housing, then wrapped around the two rollers and with the other end zone fixed on the other side of the cylinder housing. By means of a clamp, the chain or the cable is also attached to an oven door. Alternatively to the movement of the piston rod through a double acting cylinder, a joint movement of the rollers can also be carried out through a cylinder driven by electric, hydraulic or pneumatic means. It is also possible to perform the drive as a rack gear.

Documents FR 2950922 A1 and WO 98/15486 A1 employ a corresponding principle drive for a telescopically extensible garden gate or an elevator door.

Object of the invention

The objective of the present invention is to propose a compactly constructed vehicle door drive for a bus. Furthermore, the objective of the present invention is to propose a new use of a known drive.

Solution

The object of the present invention is achieved in accordance with the invention with the characteristics of the independent patent claims. Other preferred embodiments according to the present invention are derived from the dependent claims.

Description of the invention

The present invention proposes that the actuator of a vehicle door drive be coupled through a coupling mechanism formed with a drive mechanism drive with a vehicle door. In this regard, the tractor mechanism drive may be performed correspondingly to the drive mechanism drives that are themselves known, also referred to as link gears. Within the framework of the present invention any desired tractor means can be used, in particular a cable, which can be made of natural fibers, synthetic fibers or individual or braided wires, a chain, a belt with any longitudinal geometry and of desired cross-sectional , etc., just to mention some non-limiting examples. In the tractor mechanism gear, at least one roller is also used, which is surrounded by the tractor means, where in the context of the present invention under the term "rollers" a pulley is also understood, for example, for a tractor half made as a belt.

In accordance with the present invention, the actuator is coupled in such a way with the axis of rotation of a roller, that a drive stroke or a drive stroke of the actuator (directly or by interleaving other construction elements or gear connections) produces a displacement of the axis of rotation of the roller. The tractor means surrounds the roller, which may be the case for any given bonding angle, for example, 180 ° or also 180 ° n x 360 ° (n = 1, 2, 3, ...). The tractor means a traction branch. The traction branch extends on one side of the roller from a separation site of the roller to an articulation member connected to the vehicle door. By means of the traction force exerted by the traction branch on the articulation member, therefore, an opening or closing force of the vehicle door can be produced. On the other side (that is, in particular on the side oriented in the opposite direction to the traction branch with respect to the axis of rotation of the roller), the roller has an instantaneous center of rotation.

In principle, for actuator actuation and therefore for vehicle door actuation, the roller makes a movement that is a superposition of a translation and a rotation. In this respect, the instantaneous center of rotation corresponds to a site in relation to which the movement of the roller can be represented as pure rotation. In this regard, within the framework of the present invention, the instantaneous center of rotation can be located in the area of the roller, or also outside it, while it is arranged on the side oriented in the opposite direction to the traction branch (or the separation site of the traction branch of the roller). Without this necessarily having to be the case, for a particular embodiment of the present invention, the instantaneous center of rotation has the same distance from the axis of rotation of the roller as the separation site of the traction branch in the roller, in which case the instantaneous center of rotation and the aforementioned separation site can be arranged diametrically opposite on the roller.

The use of the roller with the axis of rotation which is not stationary within the framework of the present invention, but moved by the actuator, leads to the fact that the actuator's travel path may differ from the traction path of the traction branch and therefore of the drive stroke of the articulation member and the movement of the vehicle door. Therefore, with the traction mechanism drive according to the present invention, a transmission can be produced in such a way that with a small drive path a relatively large traction path of the traction branch can be produced and, therefore, , a relatively large movement of the vehicle door. Therefore, with a predetermined opening and closing stroke of the vehicle door, according to the present invention, the axial constructive size of the vehicle door drive can be reduced and hence the construction space required for the door drive of the vehicle on the bus. The multiplication described above leads to a reduction of the actuator driving force, such that the tensile force acting on the traction branch and the force that opens or closes the vehicle door is less than the actuator driving force. actuator However, in the context of the present invention it has been recognized that this, if necessary, can be easily compensated through a stronger embodiment of the vehicle door drive, despite the reduced axial construction size, for example, in the case that a piston-cylinder unit is used, through a larger dimensioning of effective fluid loading surfaces.

The specification of the multiplication of the drive path and the demultiplication of the drive force can be made by constructively predetermining the position of the instantaneous center of rotation. For the special case of the position of the instantaneous center of rotation with the same distance from the axis of rotation of the roller as the distance from the point of attack of the traction branch in the roller, but with the arrangement of the instantaneous center of rotation diametrically opposite the point of attack of the traction branch, the actuator drive travel is doubled with respect to the traction path of the traction branch, in in which case the driving force of the traction branch with respect to the actuating force of the actuator is divided in half.

In accordance with the present invention, the articulation organ made a translation movement. With this movement of the articulation member (and ultimately also of the actuator drive), an additional articulation site of the vehicle door moves along a curved guide, where this curved guide also presents by at least one component of movement in the direction transverse to the vehicle. Through the movement of the additional articulation point of the vehicle door along the curved guide the vehicle door with the translational movement of the articulation member is allowed to effect a movement not only purely of thrust, but rather a twist-push movement. This can be advantageously used to move the vehicle door first from a closed position with the movement with a transverse component outside the access opening to the outside and / or adjust it obliquely and then move the vehicle door next to a wall outside the vehicle, until it has reached its open position.

In an alternative or cumulative embodiment of the present invention, the movement of the traction mechanism drive is coupled with a rotating column at least along a partial stroke by means of a coupling bar and a drive lever. In this respect, the movement of the traction mechanism drive leads to torsion of the rotating column. With this, existing suspensions can be integrated in the invention for a vehicle door, in which a rotating column is used.

To provide the instantaneous center of rotation of the roller, within the framework of the present invention there are multiple possibilities. For an embodiment according to the present invention, the roller is guided by means of a rolling movement of the roller along a guide track, such that in this case the instantaneous center of rotation is located in the contact area of the roller with the guide track. To mention only one possible example, the roller may have a gear (whose distance from the axis of rotation may correspond to the distance from the separation site of the traction branch, or it may also be different) that rolls along a rack that It represents the driving guide.

For another proposal of the present invention, for the formation of the instantaneous center of rotation there is a traction means, in which it can be a traction means made separately from the traction branch, or it can also be the same means of traction. For this embodiment, this traction means forms a support branch, which extends on the other side of the roller towards a support. Therefore, the support branch does not move with the actuator drive. Rather, with the movement of the roller increases the length of the support branch between the support and the roller. In principle it is possible for the support to move. However, the support is preferably made immobile or stationary in the vehicle frame during the opening and closing movement.

In principle it is possible that there is only one roller and that the traction branch acts exclusively either in the opening direction of the vehicle door or in the closing direction of the vehicle door. In this case, an inversion of the direction of movement of the actuator would lead to the traction means being loaded with a pressure force, which is not possible with a traction means. Therefore, for this embodiment by means of the actuator no movement of the vehicle door in the reverse direction could occur. Rather, for this embodiment the recoil movement has to occur in another way, for example, by means of an additional actuator or by a spring device that is loaded through the actuator with the movement. In a particular embodiment of the present invention there is an additional roller. The actuator is also coupled with the axis of rotation of the additional roller, such that a drive stroke of the actuator causes a displacement of the axis of rotation of this additional roller. In this regard, preferably the axes of rotation of the two rollers carry out the same driving path in the same direction. The additional roller is surrounded by an additional traction means. The additional traction means forms an additional traction branch, which extends on one side of the additional roller towards the articulation member for the vehicle door. The additional roller also has an instantaneous center of rotation on the side facing away from the traction branch. In this regard, the traction branch and the additional traction branch act in the opposite direction, such that respectively one traction branch is responsible for the opening movement of the vehicle door, while the other traction branch moves towards back during said opening movement. In contrast, the other traction branch is responsible for the closing movement of the vehicle door, while during the closing movement the first traction branch moves back again. By means of this embodiment according to the present invention, despite the transmission of the forces of the drive through the traction means, movement in opposite directions of movement can occur, that is, in the direction of opening and in the closing direction.

In principle, any desired actuator can be used as an actuator for the movement of the roller and / or the additional roller. In accordance with a particular proposal of the present invention, the actuator includes a fluidic piston-cylinder unit. In this regard, the (at least one) piston remains at rest, while the housing that forms the cylinder moves under fluidic load. For this purpose, for example, a drive unit made by the piston-cylinder unit and a fluidic control circuit are used to load it, as described in principle also in EP 2752546 A2. The present invention proposes that in this respect the housing is made in a multifunctional manner, where the roller and the additional roller are supported (directly or indirectly) in a rotating manner with respect to the housing of the piston-cylinder unit.

As a development of the present invention, it is proposed that the movement of the rotating column caused by the movement of the traction mechanism drive in turn produces the movement of the additional articulation point of the vehicle door along the curved guide.

In principle it is possible that the rotating column is used primarily for a vehicle door guide, for example, also producing a component of movement transverse to the longitudinal axis of the vehicle. For another proposal of the present invention, the rotary column is designed in a multifunctional manner, because it through its torsion in front of the movement of the traction mechanism drive also drives and / or releases interlocking elements for blocking the vehicle door Such a locking of the vehicle door is required, for example, to keep the vehicle door closed reliably during the ride, in order to prevent accidental opening, whereby a passenger could even fall out of the vehicle. . On the other hand, due to the aerodynamics of the vehicle, pressure variations that act on the door of the vehicle occur during walking. Without unlocking the vehicle door, an undesirable "flutter" of the vehicle door could occur, which can be prevented by interlocking in accordance with the present invention.

It may be of interest to detect the movement of the vehicle door and therefore also of the drive mechanism drive. This may have the purpose of detecting the state of opening or closing of the vehicle door, if a person or an object is stuck in the vehicle door, perform the actuator adjustment, slow down a movement of the vehicle door with approach to a final position, etc. The present invention proposes that the movement of the traction mechanism drive be associated with a movement detected by a sensor. This sensor can be based on any desired measuring principle and detect, for example, an adjustment path, an adjustment speed, an adjustment angle or an angular adjustment speed. In a preferred embodiment of the present invention, a sensor sensor element is coupled through a spindle nut with a stationary spindle bar. The spindle nut also moves with the movement of the drive mechanism drive. Similar to a spindle drive, the movement of the spindle nut is transformed into a twist of the spindle nut and a sensor element connected thereto. This torsion of the sensor element can then be detected by the sensor. Therefore, by means of a simple rotation angle sensor or an angular rotation speed sensor, the movement of the vehicle door can be detected. Depending on the design of the spindle drive, a predetermined dependence on the movement of the traction mechanism drive or the movement of the spindle nut with respect to the torsion of the sensor element can be produced, thereby also ensuring an influence on the measurement accuracy and / or optimal use of the sensor measurement zone.

A further solution of the objective of the present invention is the use of a drive of the type described above for a vehicle door drive for a bus to drive a sliding sliding door.

Additional advantageous developments of the present invention are derived from the patent claims, description and drawings. The advantages mentioned in the description of features and combinations of features are given by way of example only and can be applied alternatively or cumulatively, without the advantages necessarily having to be achieved by embodiments according to the present invention. Without modifying the purpose of the attached patent claims, in relation to the disclosed content of the original application documents and the patent, the following applies: additional features can be seen in the drawings, in particular as regards the geometries represented and the relative dimensions of several constructive elements with each other, as well as their relative arrangement and their effective relationship.

The characteristics mentioned in the claims and in the description, in relation to their number are to be understood in such a way that there is exactly that number or a number greater than the mentioned number, without the explicit use of the adverb being required "so less". For example, if you talk about an element, this must be understood in such a way that there is exactly one element, two elements or more elements. These features can be complemented with other features or be the only features that make up the respective product.

The reference characters included in the claims do not represent any limitation on the scope of the objects protected by the patent claims. They are only intended to facilitate the understanding of the claims.

Brief description of the figures

The present invention is described in more detail below with reference to preferred embodiments shown in the figures.

Fig | 1 to 5 show different principle schemes of a vehicle door drive.

Fig. 6 shows a vehicle door drive for a pivot-sliding door of a bus in a closed position in an oblique spatial view from above.

Fig. 7 shows the vehicle door drive according to Fig. 6 in the closed position in a frontal view with the observation direction in the transverse direction of the vehicle outwards.

Fig. 8 shows the vehicle door drive according to Fig. 6 and 7 in the closed position in a view from above.

Fig. 9 shows the vehicle door drive according to Fig. 6 to 8 in an open position in a view from above.

Fig. 10 shows a horizontal section through the vehicle door drive according to Figs. 6 to 9 in the closed position.

Fig. 11 shows in an horizontal section an enlarged detail of a vehicle door drive according to Figs. 6 to 10 in the closed position.

Description of the figures

Fig. 1 schematically shows a vehicle door drive 1. The vehicle door drive 1 has an actuator 2. The actuator 2 directly forms an actuator 3 or is coupled (directly, indirectly or in drive relation) with a drive member 3. The drive member 3 in this example is guided by guides 4a, 4b, such that the drive member 3 in Fig. 1 performs a horizontal translation movement. Depending on the actuation of the actuator 2, therefore, actuation forces 3 can act on the actuator 3 along the mentioned degree of freedom and a movement of the actuator 3 can be induced by means of the actuator along the degree of freedom of translation. In front of the actuator 3, in a joint 5, which defines a rotation axis 6, which is oriented vertically to the plane of the drawing according to Fig. 1, a roller or pulley 7 is rotatably supported (by simplicity reasons hereinafter referred to only as "roller 7"). A pulling means 8, which can be a cable 9 or a belt, is surrounding the rolling surface of the roller 7. One end of the pulling means 8 is articulated in a support 10. Preferably, the joint 10 is fixed in A frame of the bus. The other end zone of the traction means 8 is articulated in an articulation member 11. The articulation member 11 is guided on a guide 12. The partial area of the traction means 8 that extends between the separation site 17 of the branch of traction of the roller 7 and the articulation member 11 forms a traction branch 13, while the partial area of the traction means 8 that extends between the roller 7 and the support 10 forms a support branch 14.

For the exemplary embodiment shown, the angle of attachment is nx 360 ° 180 ° with n = 0, 1, 2, ... The traction branch 13 leaves the roller 7 at the detachment site 17 in a position of 12 : 00 hours, while the support branch 14 is directed diametrically opposite in the area of a position of 6:00 hours to the roller 7. The traction branch 13 and the support branch 14 are oriented parallel to each other and in relation to the degree of freedom predetermined by the guide 4 of the actuator 3 or the actuation direction of the actuator 2. Any other orientations other than the traction branch 13, the support branch 14, the degree of freedom and of the drive direction of the drive member 3 or of the actuator 2. (To mention just one example, the movement of the articulation member 11 along the guide can also be carried out not as shown in Fig. 1 in a manner parallel to the driving direction of the driving member 3 and parallel to the traction branch 13 and the supporting branch 14. Rather, the guide 12 can also guide the articulation member 11 along a straight inclined guide path or curved.)

The articulation member 11 is directly or indirectly articulated to a bus door of a bus, such that at least in a partial area the movement of the articulation member 11 correlates with the movement of the vehicle door or corresponds to the same. Preferably, the articulation member 11 is articulated directly to the vehicle door, such that the movement of the articulation member 11, which is caused by the actuation of the vehicle door 1 according to Fig. 1, coincides with the movement of a reference point of the vehicle door. It is possible that the opening and closing forces generated for the vehicle door are produced exclusively or mainly by the components of the vehicle door drive 1 shown in Fig. 1. However, it is also possible that a complementary influence is exerted on through actuators, spring devices, etc. For example, the articulation member 11 may be loaded with a spring along the entire adjustment path, such that the traction branch 13 and the support branch 14 are held tight and the traction means is pressed against the roller sleeve surface 7.

Due to the articulation of the support branch 14 in the support 10, the support branch 14 does not move with a movement of the actuating member 3. Rather, the roller 7 "rolls" along the support branch 14, with successive elongation or shortening of the support branch 14. During this rolling movement, the 6:00 o'clock position of the roller 7, in the area where the support branch 14 contacts the roller 7, forms an instantaneous center of concomitant rotation 15. This movement of the roller 7 is caused by a drive path 16 of the drive member 3 or of the actuator 2, which also corresponds to the displacement of the rotation axis 6 of the roller 7. The rolling movement of the roller 7 around The instantaneous center of rotation 15 with the drive path 16 in the area of the rotation axis 6 results in the separation site 17 of the traction means 8 of the roller 7 moving along a traction path 18. In this regard, the traction path 18 has the same directional direction as the actuation path 16. Through the traction branch 13, the traction path 18 is also transmitted to the articulation member 11 and hence to the vehicle door . With the traction means 8 and the roller 7, as well as its support in the area of the joint 5 in the actuator 3, a traction mechanism drive 19 is formed. This allows a multiplication or reduction of the drive path 16 from actuator 2 to traction travel on 18 and with it to the vehicle door. For the exemplary embodiment shown, by duplicating the drive mechanism 19, a doubling of the drive path 16 to the drive path 18 can occur.

For the exemplary embodiment shown in Fig. 2 , the instantaneous center of rotation 15 of the traction mechanism drive 19 does not exist by means of a stationary support branch 14 and its articulation in the support 10. Rather, in this case the guide of the roller 7 to form the instantaneous center of rotation 15 is carried out by means of a conduction guide 20, which in this example is made as a kind of rack 21, which meshes with the outer teeth 22 of the roller 7. In this In this case, the end oriented in the opposite direction to the articulation member 11 of the traction means 8 is fixed on the roller, where the traction means 8 preferably surrounds the roller 7 several times. For the exemplary embodiment shown, the outer teeth 20 of the roller 7 and the circumferential surface, on which the traction means 8 rests on the roller 7, have the same diameter, although it is also possible that the diameter of the den tado exterior 22 is greater than or less than the effective surface of the roller 7 in relation to the traction branch 13 (see also the following descriptions with reference to Fig.

3 ).

Other design possibilities for the transmission of the drive path 16 and the pull path 18 are achieved if the instantaneous center of rotation 15, on the one hand, and the separation site 17, on the other hand, have different distances from the axis of rotation 6: For the embodiment shown, the roller 7 is formed with two effective surfaces 23, 24. the effective surface 23 has a radius r (see reference numeral 25), while the effective surface 24 has a radius R (see reference numeral 26). A first traction means 8a, fixed at an end zone in the roller 7, is surrounding the effective surface 23 and extends from the separation site 17 under the formation of the traction branch 13 towards the articulation member 11. Another means of additional traction, also fixed on the roller 7, surrounds around the effective surface 24 of the roller 7 and extends from the instantaneous center of rotation 15 under the formation of the support branch 14 towards the support 10. In this case, the traction path 18 results from the product of the drive path 16 with the quotient of (R r) and R. For the exemplary embodiment shown, it governs that R> r, whereby the multiplication of the drive path 16 to the traction path 18 is less than 2. If R <r is selected instead, multiplications> 2 can also occur.

For the exemplary embodiments of Figs. 1 to 3, it has been assumed that the support 10 for the support branch 14 or the driving guide 20 or the rack 21 is stationary in the vehicle frame. It is also perfectly possible that the support 10 at least during a partial movement of the actuator 3 also moves with a support path 27 (see Fig. 4 ). In this case, the instantaneous center of rotation 15 does not meet the point of the roller 7 where the support branch 14 comes into contact with the roller. Rather, if the support path 27 has the same directional direction as the drive path 16, the instantaneous center of rotation 15 is then located under the roller, that is, with a greater distance from the axis of rotation 6 of the roller 7, while for the opposite directional direction of the support path 27 and of the drive path 16, the instantaneous center of rotation 15 is disposed between the contact site of the support branch 14 in the roller 7, that is, with a smaller distance to the axis of rotation 6.

Therefore, by selecting the radii R, r and a possible movement of the support 10, in the case also of a coupled movement of the support 10 by means of an appropriate coupling kinematics with the drive path 16 of the actuator 2 or of the drive organ 3, multiplication can be constructively predetermined. Under certain circumstances, complex driving guides of the articulation member 11 and / or of the support 10 and / or of the actuator 3 can also be used. Another additional possibility of influencing multiplication and force relations is given by the design of the effective surface (s) of the roller 7 with a non-round sleeve surface, for example, elliptical.

For the exemplary embodiments according to Figs. 1 to 4, only one movement of the vehicle door in one direction can be caused with the construction elements shown in the drive mechanism 19, as the traction means 8 it can only transmit tensile forces on the articulation organ 11 and with it on the vehicle door. This direction of traction of the traction means 8 can be correlated with an opening or closing movement of the vehicle door. For these embodiments, the movement of the vehicle door in the opposite direction has to be caused by an actuator not represented in the example, by a spring device, against which the traction means 8, or something similar, works, whereby the recoil movement of the roller 7 and of the actuator 6 and, if necessary, of the actuator 2 is also induced. For a further embodiment of the present invention according to Fig. 5 , they are used two traction mechanism drives 19a, 19b that act opposite to each other, of which a traction mechanism drive 19a handles the closing movement of the vehicle door (in Fig. 5, movement of the articulation member 11 to the right), while the other traction mechanism drive 19b is responsible for the opening movement (movement of the articulation member 11 in Fig. 5 to the left). In Fig. 5, the corresponding construction elements of both traction mechanism drives 19a, 19b are designated with equal reference characters, but with complementary individualization letters a, b for the two traction mechanism drives 19a, 19b. According to Fig. 5, the respective end zones of the traction means 8a, 8b are articulated on opposite sides of both the articulation member 11 and also of the support 10. The actuator member 3 supports in this example respectively of the end zones the rollers 7a, 7b rotatably supported around the rotation axes 6a, 6b. To allow a free play assembly of the traction means 8a, 8b, an adjustment device for the distance of the rotation axes 6a, 6b and / or an adjustment device for the length of the traction means 8a can be provided , 8b. It is also possible for a spring element to be integrated into at least one of the traction means 8a, 8b in the area of their articulation to the articulation member 11 or the support 10.

Figs. 6 to 11 show a constructive embodiment of a vehicle door drive 1, which is designed substantially corresponding to the principle scheme according to Fig. 5. In the figures, in the reference character " x ”designates the longitudinal direction of the vehicle, while“ y ”designates the transverse direction of the vehicle outwards and“ z ”designates the vertical axis of the vehicle (directional direction upwards).

The vehicle door drive 1 has a frame 28, with which it is fixed to the vehicle frame or to the bus door frame above the entry or exit opening. The frame 28 is formed with a support plate 29 oriented in the transverse direction "y", a mounting and adjustment housing 30 and a retaining strap 31 extending in the longitudinal direction of the vehicle "x" and connecting the support plate 29 with the mounting and adjustment housing 30. The guide 12 in this example is made with a guide bar 32, which extends horizontally under a particular acute angle in the range of 3 ° to 10 ° with with respect to the longitudinal direction of the vehicle "x". An end zone of the guide bar 32 is fixed, for example, by means of a screwed connection, on the support plate 29. The other end zone of the guide bar 32 is held through an adjustment device 33 in the mounting and adjustment housing 30. By means of the adjustment device 33 the position of the assigned end zone of the guide bar 32 can be adjusted, both in the vertical direction "z" and also in the transverse direction of the vehicle "y", which is associated with a small elastic and / or plastic deformation of the support plate 29, in particular a flexion of the support plate 29 around the vertical direction of the vehicle "z" and / or a twist around the transverse direction of the vehicle "y" of the support plate 29.

As can be seen in particular in Figs. 6 and 10, the end zone of the guide bar 32 assigned to the adjustment direction 33 is held in a guide body 34. Through a hole in the guide body 34 oriented in the transverse direction of the vehicle "y", a guide bar 35 extends in the transverse direction of the vehicle "y", thereby forming a guide of the guide body 34. If the guide body 34 is arranged in the correct axial position along the guide bar 35, it can be fixed, which in accordance with the exemplified embodiment shows the guide body 34 between two stop nuts 36, 37 screwed with the guide bar 35. In this way, the position of the end zone of the guide bar 32 in the transverse direction of the vehicle "y" (and thus also the angle of guide bar 32 in the x-y plane).

While the outward-facing end zone of the guide bar 35 is held in the retaining strap 31, the guide bar 35 disposes in the inner end area of a vertical passage hole 38. From the mounting box and adjustment 30, which extends above the guide body 34 and the guide bar 35 over these elements, extends an adjustment screw 39, whose head rests on the upper side of the mounting and adjustment box 30, in the vertical direction of the vehicle "z" down through the passage hole 34. With the protruding end area downwards of the adjusting screw 39, a nut 40 is screwed. The guide bar is supported from above the nut 40 35. By changing the screw nut nut 40 with the adjusting screw 39, the assigned end zone of the guide bar 32 can be raised or lowered in the vertical direction of the vehicle "z". This also allows an adjustment of the angle of inclination of the guide bar 32 in the x-z plane.

After mounting the frame 28 on the bus, therefore, by adjusting the stop nuts 36, 37, on the one hand, and by adjusting the nut 40 on the adjusting screw 39, on the other hand, You can adjust the relative position and location of the guide bar 32 relative to the door frame and therefore also to the vehicle door guided on the guide bar.

During the opening and closing movement of the vehicle door drive 1, a guide carriage 42 moves along the guide bar 32. In the guide carriage 42 a retaining arm 43 is held downwardly extending and outwards, in which the vehicle door can be fixed by means of a flange or hinge 44. With the guide carriage 42, the retaining arm 43 and the flange 44, the articulation member 11 is formed, in which the drive mechanism drives 19a, 19b are grasped.

The movement of the articulation member 11 with the vehicle door along the guide bar 32 is caused by the actuator 2 with the assigned drive mechanisms 19a, 19b (see Fig. 11 ). Actuator 2 is made in this case as a fluidic piston-cylinder unit 45, in which a piston 46 remains at rest, while a housing 47 that forms the cylinder moves depending on the fluidic load in the piston-cylinder unit 45. With reference to the basic construction of a piston-cylinder unit 45 of this type, reference is made to EP 2752 546 A2. A piston rod 48 with a piston 46 held thereon is rigidly held in the frame 28 and is oriented parallel to the guide bar 32. The piston rod 48 is held in an end area in the body of guide 34 and in another end zone on a support plate 49, such that through the adjustment direction 33 the position and orientation of the piston rod 48 can also be adjusted. The piston rod 48 extends from tightly through holes 50, 51 at the ends from the front walls of the housing 47, wherein the piston 46 supported by the piston rod 48 inside the housing 47 separates the control chambers 52 on opposite sides, 53 defined by piston 46. Control chambers 52, 53 are delimited

- axially by a piston surface of the piston 46,

- radially outwards by the cylindrical inner surface of the housing 47, along which the piston 46 can be moved in a sealed manner,

- axially through the front walls of the housing 47, and

- radially inwards by the piston rod 48,

respectively.

In Fig. 11 the left control chamber 52 is shown in its maximum extension state, while the right control chamber 53 has the minimum extent. The fluidic connections 54, 55 are connected by means of longitudinal channels of the piston rod 48 and radial outlet channels respectively with an assigned control chamber 52, 53. A fluidic pressure load of the connection 54, as well as a discharge of the The fluid pressure of the connection 55 results in the housing 47 moving out of the position shown in Fig. 11 to the right, whereby the right control chamber 53 increases its axial extension under reception of fluid from the connection 54 , while fluid is discharged from the control chamber 52 through the connection 55. Therefore, by means of an appropriate fluidic control circuit, depending on the fluidic load of the connections 54, 55, an actuation can be performed and the actuator 2 formed with the piston-cylinder unit 45, which is associated with the movement of the housing 47 in relation to the piston rod 48.

In the housing 47 the rollers 7a, 7b are held in both end zones. For the present embodiment, this is done below the housing 47 with orientation of the rotation axes 6a, 6b in the vertical direction of the vehicle "z". The support 10 in this case is formed with a support 56, in which the two assigned end zones of the traction means 8a, 8b are articulated and which is attached to the retaining strap 31 (Fig. 10, 11). In contrast, the other end areas of the pulling means 8a, 8b (after surrounding the rollers 7a, 7b with a 180 ° bonding angle) are held by means of a clamping device 57 in the guide carriage 42 .

Parallel to the guide bar 32 extends a coupling bar 58. The coupling bar 58 extends through a hole in the guide carriage 42. In the end area facing the mounting and adjustment housing 30, the coupling bar 58 has a drive element 59, in this case a nut 60. In the other end zone, the coupling bar 58 is articulated to a drive lever 61, which pivotally rests around the vertical axis. of the vehicle "z" with respect to the frame 28. The drive lever 61 is loaded by a spring 62 in an open position. With the movement of the guide carriage out of the opening position according to Fig. 9 , during a partial stroke the guide carriage 42 slides along the coupling bar 58 first, without dragging the same. When the guide carriage 42 reaches the drive element 59, the guide carriage 42 drags the coupling bar 58 and thereby also the actuating lever 61, until the closing position according to Fig. 8 has been reached . . A rotational movement of a rotating column 63 is coupled with the rotation movement of the actuating lever 61, which for the exemplary embodiment shown is achieved by means of an external toothing of the actuating lever 61, which engages with a corresponding pinion 66 of the rotating column 63 ( Fig. 7 ). The mode of operation of the vehicle door drive 1 according to Figs. 6 to 11 is as follows: In an opening position of the vehicle door, shown in Fig. 9, the retaining arm 43 and The flange 44 is displaced outward on the right edge of the access opening, such that the vehicle door is guided next to the outer skin of the vehicle. Also the rotating column 63 is in the opening position induced by the spring 62. The housing 47 of the piston-cylinder unit 45 is located in this opening position in its right end position with minimum axial extension of the control chamber 52 and maximum axial extension of the control chamber 53.

If the door of the vehicle is then to be closed, fluidic loading of connection 55 occurs with simultaneous pressure discharge of connection 54. Due to the increase in pressure in the control chamber 52 and the reduction in pressure in the chamber control 53, the housing 47 moves in the figures to the left along the piston rod 48. This is associated with a drive of the drive mechanism drives 19a, 19b, which in turn leads to the guide carriage 42 performs a traction path 18, which is twice the size of the drive path 16 of the guide carriage 42.

In a first partial stroke of the closing stroke, the coupling bar 58 slides along the guide carriage 42, without a drag thereof. Therefore, also the operating lever 61 and the rotating column 63 remain in their open position. The vehicle door guide is produced during this partial stroke, both by means of the retaining arm 43 and the flange 44, as well as at another point of additional suspension of the vehicle door, which in that case can be carried out, by example, using a slide guide. Towards the end of the closing movement, the drag element 59 acts in such a way that the guide carriage 42 drags the coupling bar 58 by means of the drag element 59, whereby the rotation of the actuating lever 61 and of the rotary column 63 against the load exerted by the spring 62. This rotary column drive can be used for multiple purposes, for example, to induce a closing movement of the vehicle door in the transverse direction of the vehicle "y" for the approach or for the hermetic closing of the door in the entrance frame and / or for a blocking of the vehicle door, by means of the action of blocking elements coupled with the rotating column 63.

Figures 6, 7, 8, 10 and 11 respectively represent the closing position induced in this way.

Preferably, a guide of circulating balls is used to guide the guide carriage 42 in front of the guide bar 32. Optionally, the vehicle door drive 1 may be equipped with a sensor device 64 to detect the drive path 16 or the pull path 18. For the exemplary embodiment shown, the sensor device 64 is equipped with a spindle bar 65 , which extends parallel to the piston rod 48 and is held correspondingly in the support plate 49 and the guide body 74. With the movement of the guide carriage 42, the torsion of a spindle nut that moves together occurs with the guide carriage 42 around the spindle bar 65. A sensor detects the angle of rotation of the spindle nut, such that by converting the angle of rotation of the spindle nut in the movement of the guide carriage 42 corresponding to the inclination of the spindle bar 65, the drive travel 16 or the pull path 18 can be determined.

If in the present application reference is made to an instantaneous center of rotation 15, it is in this case an instantaneous center of rotation in a relative system that moves together with the vehicle door.

List of reference characters

1 Vehicle door drive

2 Actuator

3 Drive body

4 Guide

5 Joint

6 Rotation axis

7 Roller, pulley

8 Traction medium

9 Cable

10 support

11 Organ of articulation

12 Guide

13 Traction branch

14 Support branch

15 Instant center of rotation

16 Drive travel

17 Separation Site

18 Traction travel

19 Drive mechanism drive

20 Driving Guide

21 Zipper

22 External Teeth

23 Effective surface

24 Effective surface

Radius r

R radius

Support travel Frame

Support plate Mounting and adjustment housing Retaining strap Guide bar

Adjustment device Guide body

Guide bar

Stop nut

Stop nut

Hole

Set screw

Nut

Guide car

Support arm

Flange

Piston-cylinder unit Plunger

Case

Piston rod Support plate Hole

Hole

Control camera Control camera Connection

Connection

Support

Clamping device Coupling bar Drag element Nut

Spring operating lever

Rotary column Sensor device

Spindle bar

Pinion

Claims (11)

1. Vehicle door drive (1) for a bus, with an actuator (2) that can be coupled through a drive coupling mechanism (1) to a vehicle door, where the coupling mechanism is made with a traction mechanism drive (19), and where a) the actuator (2) is coupled in such a way to the axis of rotation (6) of a roller (7) of the drive (1), that a drive path (16) of the actuator (2) induces a displacement of the axis of rotation (6) of the roller (7), b) a traction means (8) of the traction mechanism drive (19) surrounds the roller (7), c) the traction means (8) forms a traction branch (13), which extends on one side of the roller (7) from the roller (7) towards an articulation member (11) connected to the vehicle door, Y d) the roller (7) on the other side has an instantaneous center of rotation (15), e) the articulation member (11) moved by the drive mechanism drive (19) for the vehicle door makes a translation movement and with the translation movement of the articulation member (11) an additional articulation point is moved of the vehicle door along a curved guide of the drive (1), whereby the vehicle door with the translation movement of the articulation member performs a pivoting-sliding movement, and / or the movement of the mechanism drive Traction (19) is coupled at least through a partial stroke, through a coupling bar (58) and a drive lever (61) to a rotating column (63). 2. Vehicle door drive (1) according to claim 1, characterized in that the roller (7) has on the other side an instantaneous center of rotation (15), because the roller (7) moves with a rolling movement along a driving guide (20). 3. Vehicle door drive (1) according to claim 1, characterized in that the roller (7) on the other side has an instantaneous center of rotation (15), because the traction means (8) ) forms a support branch (14), which extends on the other side from the roller (7) towards a support (10). 4. Vehicle door drive (1) according to one of the preceding claims, characterized in that there are two drive mechanism drives (19a, 19b) that act opposite to each other, wherein a drive mechanism drive (19a) is responsible for the opening movement of the vehicle door and the other drive mechanism drive (19b) is responsible for the closing movement of the vehicle door 5. Vehicle door drive (1) according to one of the preceding claims, characterized in that there is an additional roller (7b), wherein a) the actuator (2) is coupled in such a way to the axis of rotation (6b) of the additional roller (7b) that a drive path (16) of the actuator (2) causes a rotation of the axis of rotation (6b) of the roller additional (7b), b) an additional traction means (8b) surrounds the additional roller (7b), c) the additional traction means (8b) forms an additional traction branch (13b), which extends on one side of the additional roller (7b) from the additional roller (7b) to the articulation member (11) for the door of the vehicle, and d) the additional roller (7b) on the other side has an instantaneous center of rotation (15b), where e) the traction section (13a) assigned to the roller (7a) for an opening movement of the vehicle door is loaded with a tensile force, while the additional traction branch (13b) assigned to the additional roller (7b) for the closing movement of the vehicle door it is loaded with a pulling force. 6. Vehicle door drive (1) according to claim 5, characterized in that the actuator (2) is formed with a fluidic piston-cylinder unit (45), in which the piston (46) is at rest and by means of a fluidic load, the housing (47) that forms the cylinder is moved, where the roller (7a) and the additional roller (7b) are each rotatably supported in relation to the housing (47) of the unit piston-cylinder (45). 7. Vehicle door drive (1) according to one of the preceding claims, characterized in that a) the articulation member (11) moved by the drive mechanism drive (19) for the vehicle door performs a translation movement and with the translation movement of the articulation member (11) an additional point of articulation is moved of the vehicle door along a curved guide, whereby the vehicle door with the translation movement of the articulation member makes a sliding sliding movement, and b) the movement of the traction mechanism drive (19) at least along a partial stroke it is coupled by a coupling bar (58) and a drive lever (61) to a rotating column (63), and c) the movement of the rotating column (63) caused by the movement of the traction mechanism drive (19) results in the movement of another additional articulation point of the vehicle door along the curved guide. 8. Vehicle door drive (1) according to one of the preceding claims, characterized in that a) the movement of the traction mechanism drive (19) at least along a partial stroke is coupled through a coupling bar (58) and a drive lever (61) to a rotating column (63) , Y b) the movement of the rotating column (63) caused by the movement of the traction mechanism drive (19) drives and / or releases locking elements for the interlocking of the vehicle door. 9. Vehicle door drive (1) according to one of the preceding claims, characterized in that the movement of the traction mechanism drive (19) is associated with a movement detected by a sensor device (64). 10. Vehicle door drive (1) according to claim 9, characterized in that a sensor element of the sensor device (64) is coupled through a spindle nut to a spindle bar (65), wherein the Spindle nut moves with the movement of the traction mechanism drive (19) and the movement of the spindle nut, similar to a spindle drive, is transformed into a torsion of the sensing element that is detected through the device sensor (64). 11. Use a) of an actuation with an actuator (2), which is coupled to a door through a coupling mechanism, wherein the coupling mechanism is made with a traction mechanism drive (19), wherein the actuator ( 2) is coupled in such a way to the axis of rotation (6) of a roller (7) that a drive path (16) of the actuator (2) causes a displacement of the axis of rotation (6) of the roller (7), a traction means (8) surrounds the roller (7), the traction means (8) forms a traction branch (13) that on one side of the roller (7) extends from the roller (7) towards an articulation member (11) connected to the door, the roller (7) on the other side has an instantaneous center of rotation (15), and the articulation member (11) moved by the drive mechanism drive (19) for the door performs a translation movement and with the translation movement of the articulation member (11) an additional point of a The articulation of the door moves along a curved guide, whereby the door with the translation movement of the articulation member makes a pivoting-sliding movement, and / or the movement of the traction mechanism drive (19) by at least during a partial stroke it is coupled through a coupling bar (58) and a drive lever (61) to a rotating column (63), b) for a vehicle door drive (1) for a bus, to drive a pivot-sliding vehicle door that forms said door.