Vehicle treatment system with actuators

Abstract

The present invention relates to a vehicle treatment system (1) with a carriage (3) which is mounted on a horizontal crossbeam (2) so as to be movable in the transverse direction. The vehicle treatment system further comprises a suspension (4) mounted on the carriage (3) and a wash brush rotatable about an axis of rotation and attached to the suspension (4). The suspension (4) has a first actuator for pivoting the wash brush laterally about a horizontal longitudinal axis and a second actuator for pivoting the wash brush longitudinally about a horizontal transverse axis. In the vehicle treatment system (1) according to the invention, the first actuator is coupled to the carriage (3) on one side and to a connecting element (9) of the suspension (4) on the other side.The second actuator is coupled on one side to the connecting element (9) and on the other side to a brush mounting element to which the treatment brush (5) is attached, wherein the connecting element (9) is arranged at least partially laterally next to the carriage (3) and wherein the coupling of the second actuator with the connecting element (9) of the suspension (4) is arranged above a lower edge of the traverse (2).

Description

[0001] The present invention relates to a vehicle treatment system with a carriage mounted on a horizontal crossbeam for transverse movement. The vehicle treatment system further comprises a suspension mounted on the carriage and a wash brush attached to the suspension, rotatable about an axis of rotation. The suspension includes a first actuator for pivoting the wash brush laterally about a horizontal longitudinal axis and a second actuator for pivoting the wash brush longitudinally about a horizontal transverse axis.

[0002] The vehicle treatment system refers in particular to a vehicle wash system, for example a portal wash or a conveyor wash. Similarly, the treatment brush refers in particular to a washing brush, for example a side washing brush.

[0003] When washing vehicles, it is necessary to clean not only vertical side, front, or rear surfaces, but also inclined or curved surfaces. To satisfactorily clean such surfaces using a wash brush, particularly a side wash brush, it is advantageous if the wash brush is suspended in such a way that it is not only vertically oriented but can also be pivoted to adjust the orientation of its axis of rotation to the inclined side surface. For this purpose, it has been proposed to suspend a freely pivoting, rotating side wash brush. For example, DE 19 36 889 A describes a device for washing the side surface of a vehicle with side wash brushes that are gimbal-mounted at the upper end of the wash brush axis and can pivot freely in all directions.When positioning the wash brush against the vehicle, the side wash brush can adapt to the vehicle's sloping sides by pivoting its axis of rotation away from the vertical. A disadvantage of this is that the weight of the wash brush presses down on the side, placing undesirable stress on more steeply sloping sides of the vehicle.

[0004] To avoid such stress on the inclined side surfaces, WO 2016 / 030 218 A1 proposes a vehicle wash system with a side-washing brush that is rotatably mounted on a crossbeam of the vehicle wash system by means of a suspension system, allowing it to pivot about a first horizontal axis and a second, distinct horizontal axis. The suspension system includes a first actuator for pivoting the side-washing brush about the first axis and a second actuator for pivoting it about the second axis. The suspension system has a first bearing support that is rotatably mounted about one of the pivot axes on a second bearing support, which in turn is rotatably mounted about the other pivot axis on the crossbeam. A disadvantage of this vehicle wash system's suspension system is its large vertical installation space requirement.In particular, the vertical distance between the coupling of the washing brush and the traverse is relatively large.

[0005] CN 1 14 162 091 A describes a portal washing system. The portal includes a left vertical brush cleaning device and a right vertical brush cleaning device, in which the cleaning angle of the brush can be adjusted.

[0006] The invention is based on the objective of providing a vehicle treatment system of the type mentioned above, in which the installation space requirement in the vertical direction is reduced.

[0007] According to the invention, this problem is solved by a vehicle treatment system with the features of claim 1. Advantageous embodiments and further developments are described in the dependent claims.

[0008] In the vehicle treatment system according to the invention, the first actuator is coupled to the carriage on one side and to a connecting element of the suspension on the other side. The second actuator is coupled to the connecting element on one side and to a brush mounting element, to which the treatment brush is attached, on the other side. The connecting element has a vertically oriented connecting plate that is arranged at least partially laterally next to the carriage, and the coupling of the second actuator to the connecting plate of the suspension's connecting element is arranged above a lower edge of the crossbeam.

[0009] In this document, the transverse direction refers to the direction of movement of the carriage on the horizontal crossbeam. Similarly, the longitudinal direction is defined as a horizontal direction perpendicular to the transverse direction. With respect to the vehicle being cleaned by the vehicle treatment system, the longitudinal direction is parallel to the vehicle's length or its direction of travel when driving straight ahead. The transverse direction is parallel to the lateral extent of the vehicle being cleaned. When the treatment brush pivots laterally, its axis of rotation is rotated around a horizontal longitudinal axis, i.e., a horizontal axis oriented lengthwise. This pivoting motion allows the angle of the treatment brush to be adjusted to the angle of a side surface of the vehicle.When the treatment brush is pivoted longitudinally, it is rotated around a horizontal transverse axis, that is, around an axis oriented horizontally in the transverse direction. Such longitudinal pivoting allows the orientation of the treatment brush's axis of rotation to be adjusted, for example, to a sloping rear or front surface of the vehicle.

[0010] The treatment brush of the vehicle treatment system according to the invention can be actively pivoted by means of the first and second actuators, so that it has a defined inclination in both the transverse and longitudinal directions. However, the two actuators are decoupled from each other. This means that each actuator causes a pivoting movement of the treatment brush that is independent of the other actuator. The decoupling of the actuators also results in each actuator pivoting the treatment brush in a plane.

[0011] In this document, a treatment brush in its neutral position means that its axis of rotation is vertically aligned. A treatment brush that is not pivoted means that no forces or torques are exerted on it by the actuators. Depending on the brush's mounting, its axis of rotation will then be vertical or, if applicable, slightly inclined to the vertical. The non-pivoting state of the treatment brush is also referred to as the neutral position.

[0012] The vehicle treatment system according to the invention advantageously has four axes of movement: The carriage with the treatment brush suspended from it (i) is moved translationally on a transverse axis, the treatment brush is pivoted (ii) by means of its suspension about the horizontal longitudinal axis and (iii) the horizontal transverse axis, and the treatment brush is rotated (iv) about its own axis of rotation. These four axes of movement are coupled in series. A so-called kinematic chain is thus established, namely from the horizontal translational movement in the transverse direction to the pivoting movement about the longitudinal axis (transverse pivoting), to the pivoting movement about the transverse axis (longitudinal pivoting), and finally to the rotational movement of the treatment brush about its own axis, i.e., the axis of rotation of the treatment brush.

[0013] Finally, the treatment brush can also be moved translationally in the longitudinal direction by moving the portal on which the vehicle treatment system is mounted longitudinally relative to the vehicle being treated. Alternatively, for example in a vehicle treatment system designed as a car wash, the vehicle is moved longitudinally relative to the treatment brush.

[0014] Advantageously, according to the invention, the sequence of the axes of movement is selected such that, starting from the carriage, the transverse pivoting about the longitudinal axis occurs first, followed by the longitudinal pivoting about the transverse axis. This specific selection of the sequence of pivot axes for the treatment brushes has several advantages: In a car wash, lateral swiveling is a basic function and longitudinal swiveling an additional function. The inventive selection of the sequence of swivel axes of the treatment brush results in a modular design in which the longitudinal swiveling option can also be omitted without requiring complex modifications to the suspension.

[0015] Another advantage of this choice of movement axis sequence is that the washing system's vertical footprint is reduced. The first actuator for lateral pivoting engages the connecting element in such a way that the coupling point lies outside the vertical plane extending laterally, which passes through the axis of rotation or the pivot point of the treatment brush in its neutral position. The coupling point of the first actuator cylinder on the connecting element is therefore not located above the brush's center of gravity with respect to this plane. Rather, it is offset longitudinally. This allows the first actuator to be positioned laterally next to the carriage. If the coupling point were located in the plane of the treatment brush's center of gravity in its neutral position, the actuator could not be positioned laterally next to the carriage, as the treatment brush hangs directly beneath it.

[0016] Advantageously, the washing system according to the invention requires less installation space for the first actuator in the vertical direction. Installation space is particularly limited in this direction, as the vertical distance between the mounting of the treatment brush and the carriage should not be too large.

[0017] Furthermore, this choice of the sequence of movement axes allows the connecting element to be positioned, at least partially, laterally next to the carriage. This design also advantageously reduces the required installation space in the vertical direction. Despite this, a large swivel range can still be provided for the second actuator to swivel the washing brush longitudinally.

[0018] The suspension of the treatment brush in the washing system according to the invention is a so-called gimbal suspension. With such a gimbal suspension, pivoting movements of the treatment brush about mutually perpendicular horizontal axes are possible. However, the two pivot axes of the suspension do not necessarily intersect. In contrast, these axes do intersect in a universal joint. In the suspension of the washing system according to the invention, one pivot axis is specifically arranged above the other pivot axis, so that the straight lines of the pivot axes do not intersect.

[0019] According to a further embodiment of the vehicle treatment system according to the invention, the first actuator is arranged next to the carriage with respect to the longitudinal direction. This arrangement is advantageously possible because, in the washing system according to the invention, the sequence of the axes of movement is selected such that a transverse pivoting is performed first, followed by a longitudinal pivoting. This means that, with a vertical orientation of the connecting element, this connecting element moves in a vertical plane next to the carriage during the transverse pivoting, so that the connecting element does not collide with the carriage during the transverse pivoting. The connecting element can therefore be arranged at the same height as the carriage. When the treatment brush pivots longitudinally about the transverse axis, the connecting element and the first actuator remain stationary. They are not moved during the longitudinal pivoting.During both pivoting movements, the connecting element and the carriage do not reach a stop, even though the first actuator is positioned next to the carriage in the longitudinal direction. The sequence of the pivoting movements ensures that the first actuator is not tilted relative to the carriage in the vertical longitudinal plane (xz-plane). The first actuator and the connecting element can remain in this plane during pivoting. This allows both the connecting element and the first actuator to be positioned close to the carriage. Compared to conventional mountings, they can therefore be offset upwards, saving installation space, as it is not necessary to provide vertical space for the first actuator, since its direction of action does not leave its plane when tilted.

[0020] The first actuator's distance to the carriage remains constant during lateral and longitudinal pivoting. It always moves in a plane parallel to the carriage, allowing it to be mounted very close to it. While the distance between the coupling points of the first actuator may change when the actuator is actuated, these coupling points always remain in the same plane parallel to the side of the carriage.

[0021] Furthermore, the coupling point between the first actuator and the carriage can be located above the lower edge of the carriage. This also results in a saving of installation space in the vertical direction.

[0022] The first actuator is positioned at the same height as the carriage. Furthermore, the direction of action of the second actuator is essentially vertical.

[0023] According to a further embodiment of the vehicle handling system according to the invention, the horizontal longitudinal axis is mounted on the carriage below the crossbeam. In this case, the longitudinal axis can advantageously be mounted longitudinally on both sides of the crossbeam within the carriage. This arrangement advantageously improves the stability of the connection between the suspension and the carriage.

[0024] According to the invention, the connecting element has a vertically oriented connecting plate which is arranged at least partially laterally next to the carriage. This design advantageously allows for the creation of more installation space between the carriage and the treatment brush. This advantageously reduces the required installation space in the vertical direction. Nevertheless, a large swivel range can be provided for the second actuator to pivot the treatment brush longitudinally.

[0025] According to one embodiment of the vehicle treatment system according to the invention, the first actuator is coupled to the connecting plate of the connecting element.

[0026] According to one embodiment of the vehicle treatment system according to the invention, the connecting element has a vertically oriented counter plate arranged laterally next to the carriage. The connecting plate is located, in particular, on one side of the carriage and the counter plate on the other side. The connecting plate and the counter plate are connected, in particular, via at least one transverse element arranged below the carriage.

[0027] According to one embodiment of the vehicle treatment system according to the invention, the horizontal transverse axis is formed by a transverse shaft which is mounted on the transverse element. The horizontal transverse shaft can, for example, be mounted in two vertically oriented projections which extend downwards from the transverse element.

[0028] In the vehicle treatment system according to the invention, the first actuator has, in particular, an actuating cylinder. Alternatively or additionally, the second actuator also has, in particular, an actuating cylinder. The actuating cylinder of the first actuator is also referred to as the first actuating cylinder. Likewise, the actuating cylinder of the second actuator is also referred to as the second actuating cylinder.

[0029] The actuators can be of the same type. However, they can also be different types. For example, the first and / or second actuator cylinder is pneumatically adjustable. It is therefore possible that both actuator cylinders are pneumatically adjustable, or that only one actuator cylinder is pneumatically adjustable and the other actuator cylinder is adjustable in another way, for example hydraulically or by an electric motor.

[0030] The vehicle treatment system according to the invention can be used particularly advantageously when it is designed as a portal car wash in which the front or rear section of the vehicle is cleaned simultaneously with the rims of the vehicle wheels. In this case, it is advantageous if the treatment brush, designed as a side-wash brush, can be pivoted relatively far in the longitudinal direction so that the portal can be located in the area of ​​the vehicle wheels during the cleaning of the front or rear section, thus enabling rim cleaning to be carried out simultaneously with the cleaning of the front or rear section of the vehicle. Advantageously, the vehicle treatment system according to the invention is suitable for this purpose because the suspension of the treatment brush is first pivoted about the longitudinal axis (lateral pivoting) and only then about the transverse axis (longitudinal pivoting).For example, if the suspension's connecting element has a connecting plate to which the actuator for lateral pivoting engages, this connecting plate is pivoted in a parallel orientation to the carriage. If the actuators were arranged in reverse, that is, if the first actuator first pivoted the treatment brush longitudinally around the transverse axis and then the second actuator performed the lateral pivoting around the longitudinal axis, there would be significantly less installation space available for a stroke movement of the second actuator, particularly a second actuating cylinder.

[0031] The inventive design of the vehicle treatment system advantageously allows the connecting element, in particular the connecting plate, to which the actuators are attached, to be moved upwards next to the carriage. This reduces the installation space required in the vertical direction between the crossbeam and the suspension. Advantageously, the actuator cylinders do not attach too low on the suspension, as the treatment brush is located there. The points of application of the actuator cylinders can be moved upwards in the inventive vehicle treatment system because the point of application of the second actuator has been moved laterally next to the carriage. Advantageously, the stroke of the second actuator cylinder for longitudinal pivoting is very large.

[0032] According to one embodiment of the vehicle treatment system according to the invention, the actuator cylinders, in particular the second actuator cylinder, are designed as multi-position cylinders. Multi-position cylinders enable particularly flexible adjustment of the treatment brush. It can be adapted to a wide variety of inclined surfaces of a vehicle. The second actuator cylinder, designed as a multi-position cylinder, can preferably implement very large swivel angles in the longitudinal direction.

[0033] Preferably, the second actuating cylinder is an asymmetrical double cylinder with at least four active positions. Such an asymmetrical double cylinder can, for example, comprise two actuating cylinders arranged in series, each of which can be actively moved into two positions. The distance between these two positions is referred to as the stroke of this double cylinder. The stroke of one actuating cylinder of the double cylinder differs from the stroke of the other actuating cylinder. This results in four active positions and one passive position. In the passive position, the actuating cylinders of the double cylinder do not deflect the treatment brush.In a pneumatic design of the second positioning cylinder, the suspension of the vehicle treatment system according to the invention provides a sufficiently large, and in particular long, installation space to connect two cylinders in series. In this way, the treatment brush can be moved via the second positioning cylinder into various positions that adapt to the individual shape of the vehicle. For example, the treatment brush can adjust to specific angles of inclination of the front and / or rear sections of the vehicle. Similarly, it can advantageously be possible to clean the front or rear sections of the vehicle in different relative positions to the portal of a vehicle treatment system designed as a portal car wash.

[0034] Furthermore, in the vehicle treatment system according to the invention, the actuator cylinders can be modularly constructed, so that, for example, in an embodiment as an asymmetric double cylinder, the individual actuator cylinders of this double cylinder can be replaced in order to be able to move to different active pivot positions by the double cylinder.

[0035] According to one embodiment of the vehicle treatment system according to the invention, the coupling of the first actuator with the connecting element of the suspension is arranged with a lateral offset to a plane that is spanned by the vertical direction and the transverse direction and in which the center of gravity of the treatment brush is in the zero position.

[0036] The connecting element of the gimbal suspension of the treatment brush in the washing system according to the invention offers the possibility of arranging both pivot axes spatially in such a way that they do not intersect and are offset from each other, while at the same time the first actuator can be mounted laterally next to the suspension. This saves further installation space in the vertical direction.

[0037] The longitudinal and transverse axes for pivoting the treatment brush are horizontally aligned and, in particular, perpendicular to each other. However, the rotational axis of the treatment brush is offset from the transverse pivoting axis, so that in the neutral position of the actuators, the rotational axis of the treatment brush is inclined. This inclination is specifically chosen to correspond to the inclination of a typical side surface of a vehicle to be cleaned. In this case, the lower end of the treatment brush pivots outwards in the transverse direction relative to the vehicle being cleaned. In the neutral position of the actuators, that is, when the actuators exert no force or torque, the treatment brush hangs at an oblique angle.

[0038] According to one embodiment of the vehicle treatment system according to the invention, the suspension is designed such that the amount of the lateral offset of the first actuator in the longitudinal direction remains unchanged during transverse and longitudinal pivoting. This advantageously ensures that the coupling of the first actuator does not collide with the carriage when the treatment brush pivots, even if the first actuator is arranged laterally next to the carriage.

[0039] According to one embodiment of the vehicle treatment system according to the invention, the coupling of the second actuator with the connecting element of the suspension is arranged in a plane spanned by the vertical and longitudinal directions, and in which the center of gravity of the treatment brush lies in its neutral position. In contrast to the coupling of the first actuator with the connecting element, the center of gravity of the treatment brush in its neutral position thus lies in the plane in which the coupling point of the second actuator with the connecting element is located.

[0040] The direction of action of the first actuator on a treatment brush in the zero position can be horizontal, vertical, or inclined. The direction of action is defined by the direction passing through the two coupling points where the first actuator is connected to the carriage on one side and the connecting element on the other. If the direction of action of the first actuator is horizontally oriented, for example, if one cylinder of the actuator is horizontally oriented, this advantageously results in a saving of installation space in the vertical direction.

[0041] Functionally, the perpendicular distance of the first actuator's direction of action to the horizontal longitudinal axis is particularly important. This results in a variety of configurations, depending on whether the first actuator's direction of action lies in a plane parallel to the adjacent outer surface of the carriage. The direction of action can be determined by considering the main force direction (the force exerted on the treatment brush by the vehicle), the brush's orientation, the lever arm, and the available space for other components. It can also be taken into account that, at the same pressure, the cylinder force is greater during extension than during contraction.

[0042] According to a further embodiment of the vehicle treatment system according to the invention, the suspension has a first stop which limits the lateral pivoting of the connecting element about the longitudinal axis. Alternatively or additionally, the suspension can also have a second stop which limits the longitudinal pivoting of the connecting element about the transverse axis. The first stop has, in particular, at least a first damping element and a first fastening element for attaching the first damping element to the suspension.

[0043] Similarly, the second stop can have at least one second damping element and one second fastening element for attaching the second damping element to the suspension. The second fastening element also has a predetermined breaking point.

[0044] This design of the suspension allows the swiveling movements of the treatment brush to be limited in a defined way, in order to avoid, for example, damage to the vehicle or the vehicle treatment system caused by excessive swiveling movements of the treatment brush.

[0045] The first and / or second fastening element advantageously features a predetermined breaking point. With this design, if subjected to excessive stress, particularly excessive torque during longitudinal pivoting about the transverse axis or during lateral pivoting about the longitudinal axis, the first and / or second stop breaks at the corresponding predetermined breaking point. Advantageously, in this case, only the first or second fastening element needs to be replaced for repair. This reduces repair costs. Furthermore, it is advantageously possible to easily adjust any desired end angle for the first and / or second stop by replacing the first and / or second fastening element.

[0046] The first and / or the second fastening element can, for example, be designed as a U- or C-profile.

[0047] The first and / or second mounting element allows for easy adjustment of any maximum swivel angle of the treatment brush. To change the maximum swivel angle in a specific direction, simply replace the corresponding mounting element to define a different stop.

[0048] According to a further embodiment of the vehicle treatment system according to the invention, the carriage has a housing comprising at least two sections. It can, for example, be designed in two parts. The first section of the housing is planar, and the second section is curved. In this case, the first actuator is coupled to the second section of the connecting element. Additionally, the second actuator can also be coupled to the second section of the connecting element.

[0049] The contours of the first area can advantageously be produced with high precision using a laser cutting process, whereas the contouring of the curved second area can lead to inaccuracies due to the bending process. Therefore, the first area can advantageously serve as a reference plane for the carriage and the mounting of the components attached to the carriage, allowing for the precise positioning and correct alignment of the attachments.

[0050] The transverse axis can be formed in particular by a transverse wave and the longitudinal axis by a longitudinal wave.

[0051] According to a further embodiment of the vehicle treatment system according to the invention, the connecting element is bent. In this case, the transverse shaft and the longitudinal shaft are fastened in receptacles of the bent connecting element.

[0052] According to a further embodiment of the vehicle treatment system according to the invention, a first flange and a second flange are fixedly mounted on the longitudinal shaft. The first flange has a first axial bearing surface. Furthermore, the second flange also has a second axial bearing surface, wherein the axial bearing surfaces are aligned with each other, in particular parallel. The longitudinal shaft is fastened via the first flange in a first receptacle of the connecting element and via the second flange in a second receptacle of the connecting element, wherein the axial distance of the first axial bearing surface from the axial radial bearing surface is adjustable during fastening.

[0053] In this embodiment, the carriage features a bearing block with a receiving opening in which the longitudinal shaft is arranged. The receiving opening includes, in particular, a first bearing arrangement comprising bearing block bearing surfaces against which the longitudinal shaft rests via bearings, enabling the longitudinal shaft to rotate relative to the bearing block. The longitudinal shaft is axially positioned on the bearing block by means of the first and second flanges. The bearing block rests, in particular, on the first axial bearing surface and the second axial bearing surface via the bearings for axial positioning.

[0054] The shaft of the longitudinal axis is thus connected to the suspension's connecting element, in particular via two flanges that are bolted to the shaft's end faces. The mounting openings in the connecting element are sufficiently large to accommodate the flanges despite any inaccuracies resulting from the connecting element's bending. This allows the flanges to be fixed to the shaft's end faces, and the longitudinal axis can be centered over the shaft's circumferential surface. The flanges have a stop by which they are fixed to the connecting element from the outside. This advantageously ensures that the bearing surfaces are aligned with each other, even if the connecting element is inaccurate due to bending. The flanges have contact surfaces for the bearings. The distance between these contact surfaces is important for the bearing's function.

[0055] According to a further embodiment of the vehicle treatment system according to the invention, this distance can be adjusted, for example, by means of washers between a flange and an end face of the shaft and / or by means of washers between a flange and the connecting element. Furthermore, in this embodiment, a bearing for the longitudinal axis is provided in the carriage. A bearing block for the longitudinal axis is located in the carriage. A bore for the shaft of the longitudinal axis passes through the bearing block. For example, a plain bearing is provided. Thanks to the bearing block, the bearings are precisely axially aligned and spaced relative to each other despite the bending inaccuracies of the carriage housing, which also includes a curved part.The bearing surfaces for the bearings and the bearing surfaces for the longitudinal axis shaft are defined by the shaft and the bearing block, and the distance between the contact surfaces can be adjusted, for example, by the washers between the shaft and a flange and / or between a flange and the connecting element. Thus, the bearing arrangement is advantageously functionally defined by the shaft and the bearing block, which are milled or turned parts, without the need for post-processing of imprecisely bent parts. In this way, the bearing arrangement can be manufactured precisely and cost-effectively.

[0056] The flat parts of the carriage housing can also be manufactured cost-effectively and precisely, for example by laser cutting.

[0057] According to a further embodiment of the vehicle treatment system according to the invention, the transverse shaft is attached to a third and fourth receptacle of the connecting element. In this case, the transverse shaft has, in particular, a first shoulder with a third axial bearing surface and a second shoulder with a fourth axial bearing surface. The transverse shaft is rotatably coupled to a brush mounting element, to which the treatment brush is coupled via a bearing. In this case, the brush mounting element has a second bearing arrangement with bearing receptacles that bear against radial bearing surfaces of the transverse shaft and the third axial bearing surface and the fourth axial bearing surface via bearings, so that a rotational movement relative to the transverse shaft can be executed by the brush mounting element.

[0058] The transverse shaft can be firmly attached to the third mounting point of the connecting element.

[0059] The mounting holes, in which the transverse shaft for longitudinal pivoting is attached, are located in the connecting element. They are aligned relative to each other, for example, by a bending process. Such a bending process introduces inaccuracies, resulting in imprecise alignment. The mounting holes are therefore large enough to allow the transverse shaft to be inserted despite any bending inaccuracies. The transverse shaft can then be welded to the connecting element on the inside of the mounting holes.

[0060] According to a further embodiment of the vehicle handling system according to the invention, the carriage has at least two lower, horizontally spaced bearings and an upper bearing arranged horizontally between the two lower bearings. In this case, the upper bearing rests on the crossbeam, and the lower bearings bear against the crossbeam from below. The first lower bearing is mounted on the carriage such that it has a fixed vertical distance from the upper bearing. The second lower bearing, however, is movably mounted on the carriage such that it is pressed against the crossbeam from below by a spring force, and the vertical distance from the upper bearing is variable.

[0061] Advantageously, the first lower bearing abuts the crossbeam from below in such a way that the stop counteracts an initial torque about a horizontal longitudinal axis. Such a torque occurs in the first operating state of the carriage, in which the cleaning brush experiences a force normal to the vehicle surface during transverse cleaning.

[0062] The second lower bearing also strikes the crossbeam from below with a stop, in such a way that this stop counteracts a second torque about the horizontal longitudinal axis, the second torque being directed opposite to the first torque.

[0063] The spring force acting on the second lower bearing is directed vertically, particularly upwards, and the second lower bearing is mounted on the carriage so as to be vertically movable. The stop of the second lower bearing thus exerts an upward force on the underside of the crossbeam; the magnitude of this force is determined by the spring force. The stop of the second lower bearing is therefore pre-tensioned. The stop of the second lower bearing is mounted in such a way that movement in the direction of the exerted force is possible.

[0064] In the vehicle treatment system according to the invention, the upper bearing can, in particular, comprise the upper bearing and a drive wheel which is coupled to a drive and which is in frictional engagement with the upper surface of the crossbeam. The horizontal frictional force acting between the drive wheel and the upper surface of the crossbeam depends in this case on the magnitude of the spring force. The greater the spring force, the greater the maximum horizontal frictional force. The carriage can be moved on the crossbeam by means of this drive.

[0065] The second lower bearing can include a second roller, rotatably mounted on the carriage such that the axis of rotation of the second roller is movable in the vertical direction, with the spring force acting on the axis of rotation of the second roller. The magnitude of the spring force is selected, in particular, such that in an operating state of the rotating treatment brush, in which the treatment brush absorbs an operating force in the transverse direction during washing, the first bearing does not lose contact with the crossbeam in the vertical direction, and the horizontal frictional force acting between the drive wheel of the upper bearing and the top of the crossbeam is sufficiently large to move the carriage horizontally on the crossbeam by means of the drive. Advantageously, the drive force can be adjusted via the spring force to prevent slippage of the drive wheel on the crossbeam.Even when the rotating cleaning brush is held transversely by the first actuator and experiences a tangential cleaning force when cleaning the front or rear of the vehicle, which in this case acts transversely, the spring force is specifically chosen so that the first bearing does not lose contact with the crossbeam in the vertical direction and the horizontal frictional force acting between the drive wheel of the upper bearing and the top of the crossbeam is sufficiently large to move the carriage horizontally along the crossbeam by means of the drive. Advantageously, the orientation of the carriage remains unchanged in this case. The force exerted on the carriage, and thus on the second lower bearing, by the torque exerted by the pivoting of the cleaning brush is therefore smaller than the opposing spring force.

[0066] The axis of rotation of the second roller is supported in a slot, the slot extending in the direction in which the spring force acts on the axis of rotation of the second roller. The slot extends in the vertical direction.

[0067] The spring force is exerted, in particular, by a spring located above the crossbeam. The second lower bearing can, in particular, have a bracket assembly that transmits the force exerted by the spring to the axis of rotation of the second roller. Preferably, the bracket assembly has at least two legs that extend from above the crossbeam to below it on opposite sides of the crossbeam.

[0068] The spring force is provided in particular by a coil spring or an arrangement of disc springs, each with a vertically oriented axis.

[0069] According to a further development of the vehicle treatment system according to the invention, the horizontal distance of the upper bearing from the second lower bearing, which is movably mounted in the carriage, is less than the horizontal distance of the upper bearing from the first lower bearing, which is fixedly mounted in the carriage. The upper bearing is therefore not arranged centrally between the two lower bearings. This arrangement of the upper bearing advantageously results in a greater lever arm to the rigidly mounted first lower bearing. The counterforces due to the main operating forces, particularly during lateral pivoting during cleaning, are thereby advantageously reduced.

[0070] According to a further embodiment of the vehicle cleaning system according to the invention, the second lower bearing is mounted on an inner side of the carriage that is arranged closer to the vehicle to be cleaned in the horizontal direction than the first lower bearing. The spring-mounted stop of the second lower bearing, and in particular the second lower roller, is thus oriented towards the vehicle. As a result, the main operating forces on the cleaning brush are absorbed by the upper bearing and the rigidly mounted first lower bearing. The opposing forces are therefore rigidly transmitted to the crossbeam, since there is no spring between them.

[0071] The terms "first," "second," etc., used in this document are to be understood as distinguishing between different elements. The number of these elements is not to be limited by this. These terms are used only to differentiate one element from another. For example, a first actuator, which is discussed here, could be referred to as a second actuator without this deviating from the teaching of the present invention. Thus, if a second element is specified in an embodiment, a first element may or may not be present.

[0072] The invention will now be explained using exemplary embodiments with reference to the drawings. Fig. Figure 1 shows an embodiment of the vehicle treatment system according to the invention, which is arranged in a portal car wash. the Fig. Figures 2 to 4 show different views of the exemplary embodiment of the vehicle treatment system according to the invention. Fig. Figure 5 shows a view of the carriage of the exemplary embodiment of the vehicle treatment system according to the invention, on which modular lateral bearings are attached. Fig. Figure 6 shows a view of the carriage of the exemplary embodiment of the vehicle treatment system according to the invention, on which no modular lateral bearings are attached. Fig. Figure 7 shows a top view of the exemplary embodiment of the vehicle treatment system according to the invention. Fig. Figure 8 shows a section through the exemplary embodiment of the vehicle treatment system according to the invention, the Fig. 9, Fig. 10, Fig. 11A and Fig. Figure 11B shows different views of the housing of the carriage of the exemplary embodiment of the vehicle treatment system according to the invention. the Fig. 12 and Fig. Figure 13 illustrates the mounting of the carriage on the traverse in the embodiment of the vehicle treatment system according to the invention. the Fig. Figures 14 to 16 show the bearing of the second lower roller of the embodiment of the vehicle treatment system according to the invention, the Fig. 17 and Fig. Figure 18 shows the bearing of the first lower roller of the embodiment of the vehicle treatment system according to the invention, Fig. Figure 19 shows a first embodiment of the fastening of the side roller of the exemplary embodiment of the vehicle treatment system according to the invention, the Fig. Figures 20 to 21 show a first variant of a second embodiment of the fastening of the side roller of the exemplary embodiment of the vehicle treatment system according to the invention. the Fig. Figures 22 to 30A show a second variant of the second embodiment of the fastening of the side roller of the exemplary embodiment of the vehicle treatment system according to the invention. the Fig. Figures 30B to 31 show a different embodiment of the first design of the fastening of the side roller of the embodiment of the vehicle treatment system according to the invention. the Fig. Figures 32 to 35 show the connecting element of the exemplary embodiment of the vehicle treatment system according to the invention. the Fig. 36 and Fig. Figure 37 shows the bearing of the longitudinal shaft of the embodiment of the vehicle treatment system according to the invention. the Fig. 38 and Fig. Figure 39 shows the bearing of the transverse shaft of the embodiment of the vehicle treatment system according to the invention. the Fig. Figure 40 shows different positions of an actuating cylinder of an actuator of the exemplary embodiment of the vehicle treatment system according to the invention. the Fig. Figures 41 to 43 illustrate the limitations of the swiveling movements of the washing brush in the exemplary embodiment of the vehicle treatment system according to the invention and the Fig. Figures 44 to 53 show different swivel positions of the washing brush of the exemplary embodiment of the vehicle treatment system according to the invention.

[0073] In this document, directional information refers to a Cartesian coordinate system, where the x-axis points in the longitudinal direction of a vehicle being processed by the vehicle handling system. The y-direction is the horizontal transverse direction of the vehicle, and the z-direction is the vertical direction of the vehicle's height.

[0074] The exemplary embodiments described below relate to a vehicle treatment system designed as a vehicle wash system. Accordingly, the treatment brush is a washing brush, in particular a side washing brush.

[0075] The washing brush 5 can be moved on the traverse 2, i.e., in the y-direction. The degree of freedom of this direction of movement is denoted by D1. When describing pivoting movements of a washing brush 5 of the vehicle wash system 1, a lateral pivot is understood to be a pivoting of the washing brush 5 about a horizontal longitudinal axis D2. The longitudinal axis D2 is aligned parallel to the x-axis of the coordinate system. Furthermore, a longitudinal pivot is understood to be a pivoting of the washing brush 5 about a horizontal transverse axis D3. The transverse axis D3 is aligned parallel to the y-axis of the coordinate system. Additionally, a rotation axis R is defined. The rotation axis R is the axis of the washing brush 5 itself, around which it is rotated when cleaning the vehicle.

[0076] The following describes a first embodiment of the vehicle washing system 1 according to the invention: First, the basic structure of the vehicle wash system 1 according to the first embodiment is described with reference to the Fig. Explained in sections 1 to 11: The vehicle wash system 1 is designed as a portal wash system that can move along the vehicle to be cleaned in the longitudinal direction, i.e., in the x-direction. The vehicle wash system 1 has a crossbeam 2 which is attached to two columns (not shown). The columns are in turn mounted on rails so that the vehicle wash system 1 can move in the x-direction. The crossbeam 2 is oriented horizontally in the transverse direction, i.e., in the y-direction, and is located above the vehicle to be cleaned.

[0077] Two carriages 3 are mounted on the traverse 2, each forming a holding device and movable in the transverse direction D1 on the traverse 2. Each carriage 3 has a suspension 4 on which washing brushes 5 are mounted. The washing brushes 5 are side-washing brushes, which can be used to clean the sides, front, and rear of the vehicle. Each washing brush 5 is rotatable about the axis of rotation R by means of a motor and a motor-gear unit 6.

[0078] The vehicle washing system 1 comprises two assemblies, each containing the carriage 3, the suspension 4, the washing brush 5, the motor and motor-gear unit 6, as well as further elements for pivoting the washing brush 5. The two assemblies are mirror images of each other, so that the vehicle to be cleaned can be positioned transversely between the washing brushes 5 of the two assemblies, as shown in Fig. As shown in Figure 1. When cleaning the front and rear of the vehicle, the trolleys 3 can also be positioned so that the washing brushes 5 can completely cover the front and rear of the vehicle.

[0079] The following describes only one arrangement with a holding device designed as a carriage 3, a suspension 4, a washing brush 5, a motor and a motor-gear unit 6, as well as other associated elements of the arrangement. The other arrangement is correspondingly mirrored with respect to an xz-plane in the center of the vehicle wash system 1.

[0080] The suspension 4 is mounted on the carriage 3, which is movably mounted on the horizontally oriented crossbeam 2 in the transverse direction D1. The suspension 4 comprises a first actuator 7 for pivoting the washing brush 5 laterally about the horizontal longitudinal axis D2 and a second actuator 8 for pivoting the washing brush 5 longitudinally about a horizontal transverse axis D3.

[0081] The first actuator 7 is coupled to the carriage 3 on one side and to a connecting element 9 of the suspension 4 on the other side. As, for example, in Fig. As shown in Figure 2, the first actuator 7 is vertically oriented and arranged next to the carriage 3 with respect to the longitudinal direction, i.e., it is located behind the carriage 3 in the x-direction. The coupling of the first actuator 7 to the connecting element 9 is arranged with a lateral offset to the yz-plane. This yz-plane is spanned by the vertical and transverse directions, with the center of gravity of the washing brush 5 in its zero position lying in this yz-plane. This offset V is particularly evident in the Fig. 7 and Fig. 8 shown.

[0082] The second actuator 8 is coupled on one side to the connecting element 9 and on the other side to a brush mounting element 10. The washing brush 5 is in turn attached to this brush mounting element 10.

[0083] The shafts of axes D2 and D3 are driven by the two actuators 7 and 8, thus forming a serial kinematic chain by which the washing brush 5 can first be pivoted about the longitudinal axis D2 and then about the transverse axis D3, starting from the carriage 3. Both movements are independent of each other.

[0084] The following describes details of vehicle wash facility 1: The design of carriage 3 is described with reference to the Fig. 9 to 11B described: The carriage 3 comprises a housing 58, which has at least two sections. For example, the housing 58 of the carriage 3 can be divided into two parts. The first section 59 of the housing 58 is planar, whereas the second section 60 of the housing 58 is curved or connects to the first planar section 59 via a curve. In the described embodiment, the first section 59 is formed from a flat sheet, whereas the second section 60 is formed from a sheet that is bent multiple times to achieve an overall cubic shape for the housing 58 of the carriage 3. The contours of the first section 59 were produced with high precision using a laser cutting process. The contouring of the curved second section 60 leads to inaccuracies due to the bending process.The first section 59 serves as a reference plane for the carriage 3 and the mounting of the attachments arranged on the carriage 3, allowing attachments to be positioned and aligned precisely. The curved section 60 is aligned with the attachments during assembly and has dimensionally tolerant mounting points to enable stress-free fixing of the attachments. In this embodiment, the first actuator 7 is coupled to the second section 60 of the housing 58 at the coupling point 12; see figure. Fig. 2.

[0085] The following describes the mounting of the carriage 3 on the traverse 2 with reference to the Fig. Explained in sections 9 to 31: The carriage 3 has two lower, horizontally spaced bearings 44 and 46, and one upper bearing 41. The upper bearing 41 is arranged horizontally between the two lower bearings 44 and 46. The upper bearing 41 supports a drive wheel 42, which rests on the crossbeam 2, and the lower bearings 44 and 46 support the first and second rollers 45 and 47, which bear against the crossbeam 2 from below. The first lower bearing 44 is mounted on the carriage 3 such that it has a fixed vertical distance from the upper bearing 41. The second lower bearing 46, on the other hand, is mounted on the carriage 3 such that it presses the supported second roller 47 against the crossbeam 2 from below with a spring force, and the vertical distance to the upper bearing 41 is variable.

[0086] In further embodiments, the second roller 47 can also be fixedly mounted so that the distance to the upper bearing 41 cannot change.

[0087] In the Fig. 12 and Fig. Figure 13 shows how the first lower bearing 44 rotatably supports the first roller 45 on the carriage 3 and the second lower bearing 46 rotatably supports the second roller 47 on the carriage 3 such that the axis of rotation of the second roller 47 is movable in the vertical direction, with the spring force acting on the axis of rotation of the second roller 47.

[0088] The drive wheel 42 of the upper bearing is coupled to a drive 43; see Fig. 10. The drive wheel 42 is in frictional engagement with the upper surface of the traverse 2. Thus, when the drive wheel 42 is rotated by means of the drive 43, the carriage 3 is moved laterally D1 along the traverse 2. The horizontal frictional force acting between the drive wheel 42 and the upper surface of the traverse 2 depends, among other things, on the magnitude of the spring force acting on the second roller 47. The greater this spring force, the greater the maximum horizontal frictional force.

[0089] The first roller 45 rests against the crossbeam 2 from below in such a way that the stop of the first roller 45 against the crossbeam 2 counteracts a first torque about a horizontal longitudinal axis. This torque occurs in an operating state of the carriage 3 in which the washing brush 5 has pivoted laterally from a neutral position during vehicle cleaning. In this case, the operating force F acts B on the washing brush 5, as it says in Fig. Figure 12 shows that the second roller 47 strikes the crossbeam 2 from below in such a way that this stop counteracts a second torque about a horizontal longitudinal axis, the second torque being directed opposite to the first torque.

[0090] The carriage 3 is thus supported against rotation about the x-axis by three rollers. The upper roller is formed by the drive wheel 42, and of the two lower rollers, the first roller 45 is rigidly mounted to the carriage 3, while the second roller 47 can move vertically relative to the carriage 3 and is pressed against the underside of the crossbeam 2 by a spring force. The drive wheel 42 therefore forms part of the carriage 3's support system. This integration of functions reduces the number of components and the required installation space.

[0091] The spring force with which the second roller 47 is pressed against the crossbeam 2 increases the normal force between the drive wheel 42 and the crossbeam 2. Since the power transmission occurs by friction, greater drive forces can be transmitted via this friction connection in order to move the carriage 3 on the crossbeam 2.

[0092] The carriage 3 is aligned with the vehicle wash system 1, i.e., with the vehicle to be cleaned, such that the second roller 47, i.e., the lower spring-loaded roller, is aligned with the longitudinal side of the vehicle that is cleaned by the associated wash brush 5 when the wash brush 5 is positioned laterally next to the vehicle. Since two wash brushes 5 are provided in a portal, their mounting positions are mirrored relative to each other with respect to the xz-plane. Because the spring-loaded second roller 47 is aligned with the vehicle, the main operating forces F B During the washing process, the washing brush 5 is absorbed by the drive wheel 42 and the rigidly mounted first roller 45. The opposing forces are rigidly transmitted to the crossbeam 2, as there is no spring between them.

[0093] With regard to the horizontal arrangement in the transverse direction, the horizontal distance H2 of the drive wheel 42 from the second roller 47 is less than the horizontal distance H1 of the drive wheel 42 from the first roller 45, which is rigidly mounted in the carriage 3. The drive wheel 42 is therefore not positioned centrally between the two lower rollers 45, 47. This results in a larger lever arm from the drive wheel 42 to the rigidly mounted first roller 45. Consequently, the counterforces due to the operating force F are B , which occurs when cleaning the side of the vehicle with the wash brush 5, smaller.

[0094] The drive wheel 42 is further offset from the axis of rotation R by a distance L1 in the direction of the second roller 47. The lever for pivoting the washing brush 5 is offset from the axis of rotation R by a distance L2 in the direction of the first roller 45.

[0095] In other embodiments, the distances H1 and H2 can be changed or made variable to adapt them to the forces acting on the carriage 3. In another embodiment, where the roller 47 is not spring-mounted, the drive wheel 42 is arranged horizontally in the middle between the two rollers 45 and 47.

[0096] With reference to the Fig. The variable storage of the second roller 47 is explained in sections 14 to 16: The second lower bearing 46 has a bracket assembly 50 which transmits the force exerted by a spring 49 to the axis of rotation of the second roller 47. The spring 49 is arranged above the crossbeam 2, whereas the second roller 47 is arranged below the crossbeam 2 and is pressed against the crossbeam 2 from below by the spring force exerted by the spring 49. The spring 49 is a coil spring or an arrangement of disc springs.

[0097] The axis of rotation of the second roller 47 is mounted in an elongated hole 48, the elongated hole 48 extending in the direction in which the spring force acts on the axis of rotation of the second roller 47. The elongated hole 48 thus extends in a vertical direction.

[0098] The stirrup arrangement 50 has two legs 51 which are guided from above the traverse 2 to below the traverse 2 on different sides of the traverse 2.

[0099] The spring force exerted by the spring 49 can be adjusted via an adjusting screw 61. The magnitude of the spring force is selected such that, in an operating state of the rotating washing brush 5, the first roller 45 is not moved in the vertical direction and therefore does not lose contact with the crossbeam 2, and the horizontal frictional force acting between the drive wheel 42 and the top of the crossbeam 2 is sufficiently large to move the carriage 3 horizontally on the crossbeam 2 by means of the drive 43. The orientation of the carriage 3 thus remains unchanged during operation, since the torque acting on the carriage 3, which results from the operating force F, B This is balanced by the opposing torque resulting from the spring force.

[0100] The drive wheel 42 is mounted in such a way that it can absorb the force of gravity and simultaneously drive the carriage 3.

[0101] The storage of the first and second rolls 45, 47 is described below with reference to the Fig. 17 and Fig. 18 explained: The first and second rollers 45, 47 are mounted in the same way, so only the mounting of the first roller 45 will be described below. In contrast to the mounting of the first roller 45, the roller shaft 53 of the second roller 47 is mounted in such a way that it can move in a vertical direction.

[0102] The first roller 45 is supported by a combination 79 consisting of a needle bearing 56 and a plain bearing 54, with axial forces being absorbed by the plain bearing 54 and radial forces by the needle bearing 56. The plain bearing 54 includes a reservoir 55, which is sealed by O-rings 78. The reservoir 55 holds lubricant.

[0103] The bearing of the first roller 45 with a needle bearing 56 only allows for radial bearing of the first roller 45. Therefore, an inaccurate alignment of the bearing of the first roller 45 with respect to the crossbeam 2 leads to axial forces that must be absorbed separately. These are absorbed by the plain bearing 54.

[0104] Furthermore, the surface of the roller shaft 53 for the rotatable bearing of the first roller 45 has the same radius throughout. The roller shaft 53 therefore has no steps or projections.

[0105] The carriage 3 further comprises at least two, and in the described embodiment four, lateral bearings 73 and 102 at each region 59, 60 of the housing 58, which are arranged on one and the other side of the crossbeam 2 with respect to the transverse direction. The lateral bearings 73, 102 are spaced apart from each other longitudinally. The crossbeam 2 is located longitudinally between the lateral bearings 73, 102.

[0106] The first embodiment of the lateral bearing 102 fixes the side roller 95 at a fixed longitudinal distance to the crossbeam 2. The second embodiment of the lateral bearings 73 fixes the side roller 95 at a longitudinal distance to the crossbeam 2 such that the longitudinal distance is adjustable by a mechanism.

[0107] The lateral bearings 73, 102 are described below with reference to the Fig. Explained in sections 19 to 31: The lateral bearing 73, 102 has a side roller 95 with a running surface 94, which is mounted on the carriage 3 via a side roller shaft 82. The axial support of the side roller 95 is provided on one side by means of an axial sliding bearing 89 by means of the side roller flange 83 on a curved support plate 84 or on the flat roller retaining plate 96.

[0108] Fig. Figure 19 shows the first embodiment of the lateral bearing 102 for attaching the side roller 95, which is not adjustable in its longitudinal distance from the crossbeam 2. The first section 59 of the housing 58 can be used as the mounting location for this first embodiment, in which the longitudinal distance of the side rollers 95 relative to a part of the housing 58 of the carriage 3 is not adjustable. Due to its precise, straight shape, this section serves as a reference plane for mounting the housing 58. This ensures that the carriage 3, with its first section 59 of the housing 58, moves exactly parallel to the crossbeam 2.

[0109] The Fig. 20 and Fig. Figure 21 shows a first variant of the second embodiment of the lateral bearings 73 for the attachment of the side roller 95, which is adjustable in its longitudinal distance to the crossbeam 2. A flat roller retaining plate 96 is connected to an opposing counter-support plate 91 via a curved retaining plate 97. The curved retaining plate 97 is engaged at point 80 with the first or second section 59, 60 of the housing 58 of the carriage 3. At the opposite point 81, the side roller 95 can be variably adjusted longitudinally relative to the crossbeam 2. The axial support of the side roller 95 is achieved via a sliding bearing of the side roller 95 on the roller retaining plate 96 and the counter-support plate 91.

[0110] The Fig. Figures 22 to 30A show a second variant of the second embodiment of the lateral bearings 73 for the attachment of a side roller 95, which is adjustable in the longitudinal direction with respect to the crossbeam 2 in a different manner. In this second variant, the side roller 95 is supported by an opposing counter-support element, which is designed as a counter-support plate 91. The counter-support plate 91 is attached to the curved support plate 84 by means of hollow bushings 92, such that the length of the hollow bushings 92 determines the distance between the bearings of the side roller 95 on one side and the other. A shank of a screw 87 is inserted through each of the hollow bushings 92, so that the counter-support plate 91 is attached to the support plate 84 by means of the screws 87 in such a way that the distance is determined by the length of the hollow bushings 92. A cover plate 86 is also provided for a side roller housing. A nut 85 is also provided for attaching the side roller housing.

[0111] As in the Fig. As shown in Figures 22 to 30A, the side roller shaft 82 is non-rotatably connected to a side roller flange 83, the side roller shaft 82 being arranged eccentrically with an offset Vs to the axis of rotation of the side roller 95. The side roller shaft 82 is pressed into the side roller flange 83. The longitudinal distance of the side roller 95 to the cross member 2 is adjusted by changing the angular position of the side roller flange 83 relative to the curved support plate 84 through holes 88 using a pin wrench. When the side roller flange 83 is rotated, the longitudinal distance of the side roller 95 to the cross member 2 changes.

[0112] The Fig. 30B and Fig. Figure 31 shows a different embodiment of the first design, in which the side roller 95 is located centrally in the side roller flange 83. These lateral bearings 102 are mounted on the first section 59 of the housing 58 of the carriage 3, which, due to its precise, straight shape, serves as a reference plane for the attachments on the housing 58. The lateral bearings in the second section 60 of the housing 58 can be adjusted in their distance from the crossbeam 2. This ensures that the first section 59 of the housing 58 moves exactly parallel to the crossbeam 2, regardless of any inaccuracies caused by the curvature of the second section 60 of the housing 58.

[0113] The side roller 95 is supported by an axial sliding bearing 89, which acts between the side roller 95 and the side roller flange 83, and an axial sliding bearing 90, which acts between the side roller 95 and the counter support plate 91.

[0114] The following details of suspension 4 are given in relation to the Fig. Explained in sections 32 to 39: The suspension 4 includes a connecting element 9, which has a vertically oriented connecting plate 16 arranged laterally next to the carriage 3. The first actuator 7 and the second actuator 8 are coupled to this connecting plate 16 of the connecting element 9. Furthermore, the connecting element 9 has a vertically oriented counter plate 17, which is also arranged, at least partially, laterally next to the carriage 3, with the connecting plate 16 being located on one side of the carriage 3 and the counter plate 17 on the other side. The connecting plate 16 and the counter plate 17 are connected to each other via at least one transverse element 18. The transverse element 18 is arranged below the carriage 3.

[0115] The connecting element 9 is curved, meaning that the vertically oriented connecting plate 16 is joined, via a bend, by the transverse element 18, which connects the connecting plate 16 to the counter plate 17. Receptacles are formed in the connecting element 9 for fastening a transverse shaft 19, which forms the transverse axis D3, and a longitudinal shaft 20, which forms the longitudinal axis D2.

[0116] As in Fig. Figure 36 shows a first flange 21 and a second flange 22 fixedly mounted on the longitudinal shaft 20. The flanges 21 and 22 are bolted to the end faces of the longitudinal shaft 20 by means of screws 26 and 27. The first flange 21 has a first axial bearing surface 23. Similarly, the second flange 22 has a second axial bearing surface 24. The two axial bearing surfaces 23 and 24 are mounted on the longitudinal shaft 20 such that they are aligned parallel to each other.

[0117] The longitudinal shaft 20 is fastened via the first flange 21 in a first receptacle 62 of the connecting element 9 and via the second flange 22 in a second receptacle 63 of the connecting element 9, wherein the axial distance I of the first axial bearing surface 23 from the second axial bearing surface 24 is adjustable during fastening. In the present embodiment, the distance I of the first axial bearing surface 23 from the second axial bearing surface 24 is adjusted during fastening by one or more washers 25 arranged between the end face of the longitudinal shaft 20 and the first flange 21 or the second flange 22. Furthermore, washers can be included between the flange 21 and the first receptacle 63 of the connecting element 9 and between the flange 22 and the second receptacle 64 of the connecting element 9 to compensate for inaccuracies.

[0118] For coupling the suspension 4 with the carriage 3, the carriage 3 has a bearing block 31 (see Fig. 10 and Fig. 37) in which a receiving opening is formed in which the longitudinal shaft 20 is arranged. For this purpose, the receiving opening includes a first bearing arrangement 70, which has bearing block bearing surfaces 71 in which sliding bearings 72 are included in one section, in which the longitudinal shaft 20 is guided and aligned so that a rotational movement can be performed by the longitudinal shaft 20 relative to the bearing block 31. The bearing block bearing surfaces 71 bear against the longitudinal shaft 20 via the radial sliding bearings 72 and against the first axial bearing surface 23 and the second axial bearing surface 24 via the axial sliding bearings 100. The longitudinal shaft 20, via which the washing brush 5 is pivoted in the transverse direction by means of the first actuator 7, is thus attached to the connecting element 9 and supported in the bearing block 31 of the carriage 3.

[0119] The receptacles 62, 63 contained in the connecting element 9 are sufficiently large to accommodate the flanges 21 and 22 centered over the longitudinal shaft 20, despite the inaccuracies resulting from the bends of the connecting element 9.

[0120] As in Fig. Figure 36 shows that the flanges 21 and 22 are axially centered on the outer surfaces of the end faces of the longitudinal shaft 20 and have a stop by which they are each fixed externally to the connecting element 9. This ensures that the axial bearing surfaces 23 and 24 are aligned with each other, even if the connecting element 9 has inaccuracies due to bends, which result in the mounting openings not being exactly parallel to each other. The axial bearing surfaces 23 and 24 of the flanges 21 and 22 therefore define a specific distance I, which is important for the function of the bearing. This distance I can be adjusted by means of the washers 25 between one of the flanges 21, 22 and the end faces of the longitudinal shaft 20.

[0121] As with the housing 58 of the carriage 3, it is also the case with the connecting element 9 that flat elements, such as the connecting plate 16, can be manufactured very precisely and cost-effectively, for example by laser cutting, while the curved parts cannot be aligned with such precision. If such curved parts require post-processing, this increases manufacturing costs. Although the two receptacles 62 and 63 of the connecting element 9 are not precisely aligned with each other because they are connected via curved parts, it is possible to align the longitudinal shaft 20 precisely with the carriage 3 when connecting it via the flanges 21 and 22, without requiring any post-processing of curved elements of the connecting element 9 or curved elements of the carriage 3.

[0122] In this embodiment, a plain bearing is formed between the longitudinal shaft 20 and the bearing block 31. The bearing arrangement is functionally defined by the longitudinal shaft 20 and the bearing block 31, which are milled and turned parts, without requiring any reworking of the curved elements of the housing 58 of the carriage 3 or the connecting element 9, which may exhibit inaccuracies. This allows for a cost-effective implementation of the bearing arrangement for the longitudinal shaft 20.

[0123] The following explains the coupling of the transverse shaft 19 for longitudinal swiveling: As in Fig. 38 and Fig. Figure 39 shows the transverse shaft 19 attached to a third 64 and fourth receptacle 101 of the connecting element 9. The transverse shaft 19 has a first shoulder 98 with a third axial bearing surface 29 and a second shoulder 99 with a fourth axial bearing surface 30. The transverse shaft 19 is firmly attached to the third 64 and fourth receptacle 101 of the connecting element 9. It is, for example, welded to the connecting element 9 by means of a weld 28.

[0124] To couple the washing brush 5 to the connecting element 9, the transverse shaft 19 is rotatably coupled to the brush mounting element 10, to which the washing brush 5 is attached. The brush mounting element 10 has a second bearing arrangement 75 with bearing receptacles 33, which are supported on the transverse shaft 19, so that the transverse shaft 19 can rotate relative to the brush mounting element 10. The radial bearing surfaces 32 and the axial bearing surfaces 29 and 30 of the transverse shaft bear against the bearing surfaces of the bearing receptacles 33 via the axial-radial sliding bearings 77.

[0125] In this case as well, the mounting openings of the third 64 and fourth receptacles 101, in which the transverse shaft 19 is located, are aligned relative to each other by bending, which results in inaccuracies in the alignment. The mounting openings of the third 64 and fourth receptacles 101 are again large enough to accommodate the transverse shaft 19 despite any bending inaccuracies. However, the transverse shaft 19 is bonded to the mounting openings of the third 64 and fourth receptacles 101 of the connecting element 9 on the inside. The radial 32 and axial bearing surfaces 29 and 30 are formed on the respective outer surfaces and are precisely aligned relative to each other because they are formed on the transverse shaft 19. Since this is a turned part, the distance between the two axial bearing surfaces 29 and 30 can be determined very precisely. The bearing receptacles 33 for the transverse shaft 19 rest against the radial bearing surfaces 32 with a sliding bearing 77 located between them.They are mounted on a mounting plate 34. Since this mounting plate 34 is not curved, it provides a flat mounting surface for the bearing receptacles 33. The axial alignment of the second bearing arrangement 75, as well as the positioning and spacing of the bearing receptacles 33, are determined during the assembly process by the positioning of the sliding bearings 77 by the axial stops of the shoulders 98 and 99 in the transverse shaft 19.

[0126] With reference to the Fig. 2, Fig. 3 and Fig. Section 7 describes how the two actuators 7 and 8 are mounted for pivoting the washing brush 5 laterally and longitudinally.

[0127] In this embodiment, the first actuator 7 comprises an actuating cylinder by means of which the two coupling points, which are arranged on opposite sides of the actuating cylinder, can be moved towards and away from each other in the direction of an axis of the actuating cylinder. The second actuator 8 comprises a corresponding actuating cylinder.

[0128] The first actuator 7 is coupled to the connecting element 9 of the suspension 4 at coupling point 11. On the other side, the first actuator 7 is coupled to the carriage 3 at coupling point 12. When the first actuator 7 moves the coupling points 11 and 12 towards or away from each other, the connecting element 9 pivots about the longitudinal axis D2 to cause the washing brush 5 to pivot laterally. The coupling point 11 of the first actuator 7 with the connecting element 9 is arranged with a lateral offset V to a plane spanned by the yz directions, in which the center of gravity S of the washing brush 5 is located in its neutral position. The coupling point 11 is therefore not located above the center of gravity of the washing brush 5, but is offset in the x direction.This makes it possible to position the first actuator 7 laterally next to the carriage 3, while simultaneously positioning the washing brush 5 vertically below the carriage 3.

[0129] This creates additional installation space in the vertical direction. The rotational axis R of the washing brush 5 is offset from the longitudinal axis D2 for lateral pivoting. This results in the transverse element 18 of the connecting element 9 and the rotational axis R of the washing brush 5 being inclined in the neutral position, corresponding to the inclination of a side surface of the vehicle to be cleaned. In this case, the lower end of the washing brush 5 is pivoted outwards in the transverse direction. This inclination of the rotational axis R of the washing brush in the neutral position of the actuator 7 is caused by the offset of the rotational axis R of the washing brush 5 from the longitudinal axis D2 and occurs when the actuator 7 is not transmitting any drive force.

[0130] The horizontally oriented longitudinal axis D2, which is formed by the longitudinal shaft 20, is supported below the traverse 2.

[0131] The following explains the coupling of the second actuator 8 for longitudinal swiveling of the washing brush 5: The second actuator 8 is coupled to the connecting element 9 of the suspension 4 at a coupling point 13, see Fig. 2 and Fig. 8. On the other side of the actuating cylinder of the second actuator 8, the second actuator 8 is coupled to the brush mounting element 10 at a coupling point 14. The coupling point 13 of the second actuator 8 with the connecting element 9 is arranged in the zero position in the xz-plane, which is spanned by the vertical and longitudinal directions and in which the center of gravity S of the washing brush 5 lies in the zero position. The coupling point 13 of the second actuator 8 is thus arranged without offset to the xz-plane above the center of gravity of the washing brush 5.

[0132] The coupling point 13 of the second actuator 8 with the connecting element 9 is arranged independently of the position of the lower edge 15 of the crossbeam 2. This makes it possible to arrange the vertically oriented connecting plate 16 of the connecting element 9 laterally next to the carriage 3 and enables the integration of an actuator 8 with a comparatively large longitudinal extent between the coupling points 13 and 14.

[0133] When the coupling points 13 and 14 of the second actuator 8 are moved towards or away from each other, the connecting element 9 is pivoted about the transverse axis D3, which is formed by the transverse shaft 19, thereby pivoting the washing brush 5 in the longitudinal direction.

[0134] With reference to Fig. Figure 7, which shows a view from above, explains the positions of the coupling points relative to the center of gravity S of the washing brush 5 in the zero position: The coupling point 11 between the first actuator 7 and the connecting element 9 has an offset V in the x-direction relative to the center of gravity S of the washing brush 5 in its neutral position and relative to the transverse axis D3. For transverse pivoting by means of the first actuator 7, a lever M1 is formed between the coupling point 11 and the longitudinal axis D2 of the longitudinal shaft in the y-direction. The coupling point 13 between the second actuator 8 and the connecting element 9 has no offset in the y-direction relative to the center of gravity S of the washing brush 5 in its neutral position. For longitudinal pivoting by means of the second actuator 8, a lever M2 is formed between the coupling point 13 and the center of gravity S of the washing brush 5 in its neutral position in the x-direction.The alignment of the second actuator 8 to the center of gravity S of the washing brush always lies in a plane spanned by the rotation axis R of the washing brush 5 and the second actuator 8, since the longitudinal pivot axis including the associated actuator 8 is arranged in the kinematic chain after the transverse pivot axis and is therefore moved along with the transverse pivoting.

[0135] Further details of the design of actuators 7 and 8 are described below with reference to Fig. 40 explained: Actuators 7 and 8 comprise pneumatically adjustable cylinders. The cylinder of the second actuator 8 is an asymmetrical double cylinder with at least four active positions and one passive position in which no forces or torques are exerted by the cylinder. As in Fig. As shown in Figure 40, the asymmetric double cylinder comprises two actuator cylinders arranged in series, each of which can be actively moved into two positions. The stroke of one actuator cylinder differs from the stroke of the other, thus defining the four active positions. In this embodiment, the ratio of the two strokes of the two actuator cylinders of the double cylinder is 0.3.

[0136] Such a pneumatic double cylinder requires a relatively large installation space in the axial direction so that the two individual cylinders can be connected in series, see Fig. 44 to 53. The coupling of the actuators 7 and 8 with the connecting element 9 on the one hand and the carriage 3 or the brush mounting element 10 on the other hand is designed to allow for such a long installation space. This makes it possible, in particular, to achieve a large swivel angle, especially for longitudinal swiveling about the transverse axis D3. In this way, the washing brush 5 can be moved into various positions both longitudinally and transversely, according to the individual shape of the vehicle to be cleaned. For example, the angle of the washing brush 5 can be adjusted to the inclination angle of the front, rear, and sides of the vehicle. Furthermore, the washing brush 5 can be adjusted to the position of the crossbeam 2 relative to the vehicle in the longitudinal direction.

[0137] This is advantageous, for example, when the vehicle treatment system is designed as a car wash, since in this case the vehicle moves and the traverse 2 can be moved along with it. If the washing brush 5 can anticipate and release the vehicle by tilting it, a shorter travel length is required for the traverse 2, thus shortening the length of the car wash and resulting in cost savings.

[0138] The pivoting movement of the washing brush 5 by the actuators 7 and 8 is limited by stops, as described below with reference to the Fig. Sections 41 to 43 are described: The suspension 4 has a first stop 36, which limits the lateral pivoting of the connecting element 9 about the longitudinal axis D2 relative to the housing 58 of the carriage 3. For this purpose, the first stop 36 comprises a first damping element 37 and a first fastening element 35, which is part of the connecting element 9. The first damping element 37 is attached to the suspension 4 by means of the first fastening element 35. Likewise, a fourth damping element 74 is connected to the connecting element 9 via the transverse element 18, which is part of the connecting element 9, and limits the range of motion for lateral pivoting in the opposite direction of rotation.

[0139] Similarly, a second stop 39 and a third stop 66 are provided, which limit the longitudinal pivoting of the mounting plate 34 about the transverse axis D3. For this purpose, the second stop 39 comprises a second damping element 40 and a second fastening element 38 for attaching the second damping element 40 to the mounting plate 34. The second fastening element 38 has a predetermined breaking point that breaks when the torque exerted by the washing brush 5 on the transverse shaft 19 exceeds a threshold value. The third stop 66 comprises a third damping element 69 and a third fastening element 93. The second and third fastening elements are designed as U-profiles, with the respective damping element 40, 69 bearing against one leg of the U-profile and the predetermined breaking point being formed on a leg of the U-profile arranged substantially perpendicular to it.The distance between the two opposing legs of the U-profile determines the position of the stop, so that the maximum swivel angle of the washing brush 5 in the longitudinal direction can be defined via these fastening elements 38 and 69. Furthermore, this maximum swivel angle can be easily changed by replacing the fastening elements 38 and 69.

[0140] With reference to the Fig. 44 to 53 explain the different swivel positions of the washing brush 5 and the corresponding deflections of the actuators 7 and 8 or of the first 67 and the second actuating cylinder 68: The Fig. Figures 44 to 47 show different pivot positions of the washing brush 5 during longitudinal pivoting about the transverse axis D3. In the position of the second actuator 8 where the coupling points 13 and 14 of the second actuator 8 with the connecting element 9 and the brush mounting element 10 are moved maximally towards each other, the axis of rotation R of the washing brush 5 is pivoted by 15°. This pivot direction corresponds to the inclination of the rear surface of a vehicle, as shown in Fig. Figure 44 shows that when the coupling points 13 and 14 are moved apart by the second actuator 8, the following results are achieved successively: Fig. The swivel positions of the washing brush 5 shown in Figures 45 to 47 are those of 9°, -3° and -10° relative to the vertical. These four positions can be actively moved using the asymmetric double cylinder of the second actuator 8.

[0141] In the Fig. Figures 48 to 53 show the two actively controllable swivel positions of the wash brush 5 when swiveling laterally about the longitudinal axis D2 by the first actuator 7, as well as the zero position from the front and rear. The wash brush 5 can be tilted 10° away from the vertical, so that the tilt corresponds to one side of the vehicle. Furthermore, the wash brush 5 can be tilted -3.5°, so that the tilt is opposite to the tilt of the side of the vehicle. In the zero position, the wash brush 5 is vertically oriented.

[0142] In the Fig. Figures 51 to 53 show how the coupling points 11 and 12 of the first actuator 7 are connected to the connecting element 9 or the carriage 3 in the respective swivel positions. Reference symbol list 1 vehicle treatment facility 2 trusses 3 trolleys 4 Suspension 5 Washing brush / treatment brush 6 Motor gearbox unit 7 first actuator 8 second actuator 9 Connecting element 10 brush mounting elements 11 Coupling point of the first actuator with the connecting element of the suspension 12 Coupling point of the first actuator with the carriage 13 Coupling point of the second actuator with the connecting element of the suspension 14 Coupling point of the second actuator with the brush mounting element 15 lower edge of the traverse 16 Connecting plate 17 Counter plate 18 transverse elements 19 Transverse wave (second wave) 20 Longitudinal shaft (first shaft) 21 first flange 22 second flange 23 first axial bearing surface 24 second axial bearing surface 25 Washer 26 screw 27 screw 28 welded joints 29 third axial bearing surface 30 fourth axial bearing surface 31 bearing block 32 radial bearing surfaces of the transverse shaft 33 storage recordings 34 Mounting plate 35 first fastening element 36 first attack 37 first damping element 38 second fastening element 39 second attack 40 second damping element 41 upper bearing 42 Drive wheel 43 Drive of the drive wheel 44 first lower camp 45 first role 46 second lower camp 47 second role 48 slotted holes 49 springs 50 iron arrangement 51 thighs 52 tread surface 53 Roller shaft 54 plain bearings 55 Reservoir 56 needle bearings 57 hollow cylinders 58 Housing of the carriage 59 first area of ​​the housing 60 second area of ​​the housing 61 Adjusting screw 62 first recording 63 second recording 64 third recording 65 Gear and bearing unit of the drive wheel 66 third attack 67 first actuating cylinder 68 second actuator cylinder 69 third damping element 70 first storage arrangement 71 storage block storage areas 72 radial plain bearings 73 adjustable lateral storage 74 fourth damping element 75 second storage arrangement 76 storage areas of the second storage arrangement 77 Axial-radial plain bearings of the transverse shaft 78 O-ring 79 Combination needle bearing plain bearing 80 side of the roller housing, which hooks into the carriage housing 81 Adjustable side of the roller housing 82 Side roller shaft 83 Side roller flange 84 curved support plates 85 Mother 86 End plate 87 screws 88 holes for face spanners 89 Axial plain bearings between roller and flange 90 Axial plain bearing against roller and counter support plate 91 Counterhold plate 92 Hollow bushing 93 third fastening element 94 tread surface 95 page roll 96 Roller retaining plate 97 curved retaining plate of the side roller 98 first paragraph 99 second paragraph 100 axial sliding bearings 101 fourth recording 102 non-adjustable lateral bearings

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