Device with lifting and tilting function for a vehicle

Abstract

Device with lifting and tilting function for a vehicle (2), comprising a superstructure (3) detachably mounted on a vehicle frame (1) with a support element (5) pivotably mounted about a tilting bearing (4), at least one first actuator (7) and at least one second actuator (8), which are connected at different coupling points (9.1, 9.2) act on the support element (5), wherein: - the support element (5) can be moved into a first tilting position with the first actuator (7) and / or the second actuator (8), - the support element (5) can be moved from the first tilting position to a second tilting position with the second actuator (8), wherein the first actuator (7) is decoupled from the support element (5), and - the first actuator (7) can be coupled back into the support element (5) when the support element (5) is moved back into the first tilting position, and wherein the tilting bearing (4) is adjustable between a closed position for pivoting the support element (5) and an open position in which the support element (5) can be moved translationally parallel to the vehicle frame (1) with the first actuator (7) and / or the second actuator (8).

Description

The invention relates to a device which is equipped with a lifting function and a tilting function and which can be detachably attached, for example, for the transport of materials and goods on a vehicle, in particular a commercial vehicle. To meet the demands and requirements in the field of material and goods transport, a wide variety of specialized technical superstructures for vehicles, particularly commercial vehicles, have already been developed. These superstructures often serve to receive, transport, and unload materials or goods in a controlled manner and are adapted to specific operating conditions. Superstructures with tipping or lifting functions are used in numerous applications, for example, in construction, waste management logistics, or agriculture. These allow loading platforms or containers to be raised or tilted to ensure controlled emptying. However, established technical solutions for vehicle bodies often exhibit a comparatively complex design, which entails increased manufacturing effort, higher costs, and greater maintenance requirements. Furthermore, the large number of moving components can compromise operational safety and complicate operation. Against this background, the object of the present invention is to provide a device with a lifting function and a tilting function which is structurally simple and at the same time inexpensive to manufacture. The problem is solved by a device with the features according to claim 1. Further developments are specified in the dependent claims. The invention relates to a device with a structure that can be detachably mounted on a vehicle frame. The structure comprises a support element pivotably mounted about a tilting bearing, as well as a first actuator and a second actuator. The first and second actuators are designed such that they engage the support element at different coupling points. The pivotally mounted support element and the actuators are designed such that the pivotably mounted support element can be moved, for example, from a transport position into a first tilting position with the first and / or the second actuator. The support element can then be moved from the first tilting position into a second tilting position with the second actuator, whereby the first actuator is decoupled from the support element. The device is thus designed such that the first actuator is completely disengaged from the support element in the second tilting position.Completely disengaging the actuators allows for a targeted division of functions between them, enabling movement sequences to be clearly separated and efficiently controlled. A further advantage arises with regard to leverage. By positioning the first actuator, which can have a smaller stroke, at a greater distance from the pivot point of the tilting bearing, a comparatively large torque can be transmitted to the support element despite the shorter stroke. This enables efficient force transmission with a compact design. Simultaneously, the second actuator can be positioned closer to the pivot point and takes over the function in other phases of movement, resulting in favorable leverage ratios throughout the entire movement sequence when pivoting the support element. This reduces the power required to drive the actuators and decreases the mechanical stress on the components. Furthermore, the first actuator is designed such that it can be re-engaged with the support element when the support element moves back from the second tilting position to the first tilting position. It may also be provided that the first actuator dampens the return movement of the support element to the transport position. According to the invention, the tilting bearing is adjustable between a closed position for pivoting the support element and an open position. In the open position of the tilting bearing, the support element can be moved translationally parallel to the vehicle frame by means of the first and / or the second actuator. The pivoting movement of the support element and the translational movement thus constitute separate phases of movement. According to one embodiment of the device, the coupling point of the second actuator is located closer to the tilting bearing along the longitudinal direction of the support element than the coupling point of the first actuator. Thus, the coupling point of the second actuator is situated between that of the first actuator and the tilting bearing. Consequently, the support element has two distinct points of application along its length, positioned to ensure a balanced mass distribution, particularly when a translational lifting movement of the support element is performed with the tilting bearing open. The actuators thus stabilize the support element at these coupling points. According to a preferred embodiment, the tilting bearing is attached to the structure by a twist-lock fastener. The tilting bearing can thus be designed as a twist-lock fastener rotatably mounted on a shaft, with the tilting bearing bolts being fixed to the fasteners. To lift the support element, the twist-lock fastener is opened. This corresponds to the open position of the tilting element. To tilt or pivot the support element, the twist-lock fastener of the tilting bearing is connected to and tensioned against the support element. In an alternative embodiment, the open position of the tilting bearing is achieved by removing the tilting bearing bolt positioned in the pivot eyes of the tilting bearing hinge. To provide the closed position, the tilting bearing bolt is reinserted into the axially aligned pivot eyes of opposing hinge elements. Thus, in the closed position of the tilting bearing, the support element can pivot relative to the vehicle frame into the first and second tilting positions, while in an open position of the tilting bearing, the support element can be moved translationally parallel to the vehicle frame. A change between an open position and a closed position of the tilting bearing can therefore be made via a twist-lock fastener or via the tilting bearing bolt. The tilting bearing preferably has two or more separate hinges attached to the support element, each of which can be detachably fastened to the body with a separate twist-lock mechanism. This allows the support element to be connected to the body at multiple points, resulting in improved load distribution as well as increased stability and torsional rigidity. The twist-lock mechanisms of the tilting bearing's hinges can simultaneously serve to fasten the body to the vehicle frame. The invention combines a tilting function and a lifting function in a vehicle structure in a simple constructive manner, advantageously requiring only two actuators for power transmission to perform the functions. Preferably, the first and second actuators are hydraulic actuators assigned to a common hydraulic circuit. The advantage of this design lies particularly in its simplified construction, as both actuators are assigned to a common hydraulic circuit, thus eliminating the need for separate components such as additional pumps, lines, or valves. This reduces the installation space and manufacturing effort. At the same time, it simplifies control, since the actuators can be operated in a coordinated manner via the same hydraulic system, thereby avoiding the complex coordination of different drive systems. Furthermore, improved energy efficiency can be achieved because a common energy source is used and redundant energy conversions are eliminated. Thus, the actuators can be hydraulically connected in parallel when executing the tilting movement of the support element. Nevertheless, it is possible to use valves to influence the operating characteristics of the actuators separately. For example, the first or second actuator can be decoupled from the hydraulic circuit when performing a movement of the support element. Alternatively, the hydraulic coupling between the actuators can be interrupted when performing a translational movement of the support element, so that only one of the two actuators is hydraulically active. A suitable valve can be used for the hydraulic decoupling of an actuator. The hydraulic circuit can be integrated into the device. It includes an oil tank, a pump, and oil lines with valves. The tank stores the oil, the pump generates pressure and delivers it through the lines to the valves, which control the oil flow. The hydraulic cylinders of the actuators convert the pressure into motion and lift or tilt the support element. The oil then flows back into the tank. According to an alternative embodiment, the first actuator and the second actuator can each have an electric linear drive which generates a stroke movement via a spindle mechanism. In this embodiment, the stroke for moving the support element is generated by means of a spindle driven by an electric motor. The mechanical decoupling of the first actuator when the support element is pivoted into the second tilting position can be achieved by a freewheeling device, in particular a ratchet or clamping mechanism. This freewheeling device is integrated into the support element and interacts with the first actuator in such a way that the first actuator automatically decouples from the support element when the support element is moved into the second tilting position by means of the second actuator. The first tilting position thus forms the threshold for decoupling and, during the return movement of the support element, for coupling the first actuator at the coupling point of the support element. The coupling and decoupling of the first actuator can also be achieved by a coupling with direction-dependent force transmission. The devices designed for the automatic mechanical decoupling of the first actuator also serve for the automatic mechanical coupling of the first actuator, held in its end position, to a point of contact or coupling on the support element. It is therefore intended that the first actuator automatically engages with the support element when the support element returns to its initial tilting position. This re-establishment of the functional connection can be either positive locking or frictional locking. The decoupling and / or coupling of the first actuator is thus position-dependent, particularly depending on the tilting position of the support element. The key advantage of this automatic coupling is that no additional control or sensor technology is required. This makes the system simpler in design, more cost-effective, and less prone to failure.Furthermore, the coupling with the pressurized first actuator occurs automatically at the correct time, namely precisely when the components have reached the correct position relative to each other in the first tilting position. This increases functional reliability and prevents misalignments. Another advantage is the potentially reduced wear, since the first actuator can be mechanically decoupled in its end position and is therefore not subjected to continuous stress. According to one embodiment of the device, the first actuator and / or the second actuator can be designed as a scissor lift. The advantage lies in the compact design combined with a large stroke. The scissor mechanism is very flat in the retracted state and yet allows for a comparatively large extension movement. This enables a particularly compact design. Furthermore, the scissor lift ensures stable and uniform force transmission. The symmetrical arrangement of the scissor arms distributes forces effectively, resulting in high rigidity and load-bearing capacity. This is particularly advantageous when loads need to be guided or held securely. Preferably, however, the actuators are designed with simple lifting arms. In a further embodiment, the device can have a third actuator arranged between the second actuator and the tilting bearing. The third actuator is configured, together with the first actuator, to perform a lifting movement of the support element in a translational direction parallel to the vehicle frame when the tilting bearing is open. The third actuator and the first actuator can be arranged on the structure in a mirror image configuration at the same distance from the center of the support element. For this embodiment, it is provided that the second actuator can be decoupled from the support element, so that the second actuator is disengaged from the support element during a translational lifting movement. Therefore, it can be provided that the second actuator is decoupled from the support element during a translational lifting movement of the support element in a direction parallel to the vehicle frame.Accordingly, the second actuator is also designed for hydraulic or electrical decoupling from the hydraulic circuit. According to a further embodiment of the device, the first and second actuators can be arranged side by side along a common axis oriented transversely to a longitudinal direction of the structure or the support element, and have different stroke lengths. As in the preceding embodiments, the first actuator has a shorter stroke than the second actuator. The first actuator, together with the second actuator, thus serves to move the support element into the first tilting position, with the second actuator moving the support element into the second tilting position without assistance from the first actuator. Unlike the preceding embodiments, in which the first and second actuators are arranged one after the other in the longitudinal direction of the vehicle, the actuators are located side by side to save space.In this configuration, the coupling points for both actuators—that is, for the first and second actuators—are located at the same position on the support element. The third actuator and its coupling point on the support element are spaced apart from the first and second actuators in the longitudinal direction of the vehicle, so that the third actuator engages at a different position on the support element to perform the translational lifting movement. Thus, even in this configuration, the support element has two coupling points in the longitudinal direction. Advantageously, the positions of the coupling points are chosen to ensure a balanced mass distribution when the translational lifting movement is performed with the tilting bearing open. To execute the tilting function, the tilting bearing is in a closed position. As with the previously described configurations, coupling / uncoupling mechanisms are provided at the coupling points, so that the first actuator decouples from the support element at tilt angles greater than the first tilt position. These coupling / uncoupling mechanisms are designed such that the first actuator, held in an upright end position, automatically re-couples with the support element at the coupling point when the support element returns to its initial coupling position. This device design is intended for vehicles where the superstructure area is limited or shortened in the longitudinal direction. Furthermore, the support element can be designed with fold-out supports to brace it against the ground. A key advantage is the reduced load on the actuators. In the supported end position, the actuators no longer need to exert holding forces, as the load is transferred directly into the ground via the supports. This allows the actuators to be smaller and reduces wear. The overall system stability is also increased. The additional support secures the support element against unwanted movement, tipping, or vibrations. This is particularly advantageous with heavier loads or eccentric loading. Another benefit is improved safety. Because the load is mechanically supported in the end position, the position is maintained even in the event of an actuator failure or a power supply interruption. This results in fail-safe behavior. Further details, features, and advantages of embodiments of the invention will become apparent from the following description of exemplary embodiments with reference to the accompanying drawings. These show: Fig. 1: a schematic representation of an exemplary embodiment of the device with lifting and tilting functions for a vehicle; Fig. 2: the device shown in Fig. 1 in a second tilting position; Fig. 3: the device shown in Fig. 1 in a first tilting position; Fig. 4: a schematic representation of an exemplary embodiment of the device with lifting and tilting functions in a lifting position; and Fig. 5: a schematic representation of an exemplary embodiment of the device with lifting and tilting functions in a transport position. Recurring and essentially identical features are each provided with identical reference symbols in the figures, so that a repeated explanation of these features is omitted. Fig. 1 shows a schematic representation of an embodiment of the device with lifting and tilting functions. The device comprises a superstructure 3 detachably mounted on a vehicle frame 1 of a vehicle 2, with a support element 5 pivotally mounted about a tilting bearing 4. The tilting bearing 4 includes two hinges, each attached to the superstructure 3 by a twist-lock fastener 6. Each hinge has two hinge halves with interlocking pivot eyes through which a tilting bearing bolt is guided. The twist-lock fasteners 6 secure the support element 5 to the superstructure 3 and allow it to pivot about the axis of rotation of the tilting bearing 4. The attachment of the superstructure 3 to the vehicle frame 1 is also achieved using twist-lock fasteners 6. Furthermore, the device comprises hydraulically actuated actuators 7 and 8, which engage the support element 5 at different coupling points 9.1 and 9.2. A first actuator 7 has a rocker arm 7.1 pivotally mounted on the superstructure 3 and a hydraulic lifting cylinder 7.2 coupled to the rocker arm 7.1. A rocker arm head 7.3 of the rocker arm 7.1 is geometrically designed such that it can interact with the coupling point 9.1 on the support element 5. Fig. 1 shows the device in a tilted position in which the first actuator 7 is decoupled from the support element 5. At coupling point 9.1, the support element 5 is designed such that an effective connection with the swing head 7.3 is provided when the support element 5 is moved into a first tilting position, which corresponds to the illustrated end position of the first actuator 7.The position of the support element 5 in the first tilting position is shown in Fig. 3. The second actuator 8 has a rocker arm 8.1 pivotally mounted on the structure 3 and a hydraulic lifting cylinder 8.2 coupled to the rocker arm 8.1. A rocker arm head 8.3 of the rocker arm 8.1 is geometrically designed such that it engages with the coupling point 9.2 on the support element 5, thus establishing a functional connection between the second actuator 8 and the support element 5. This functional connection is such that extending and retracting the lifting cylinder 8.2 causes the support element to be adjusted about the tilting bearing 4. The coupling point 9.2 is an end-face opening in a U-channel 11, in which the rocker arm head 8.3 is slidably guided when the support element 5 is pivoted into a tilting position. The support element 5 forms a transport platform for various goods. For this purpose, the support element 5 can have different shapes or elements of fastening mechanisms. The first actuator 7 and the second actuator 8 differ in the length of their arms 7.1 and 8.1, respectively, and in their position on the structure 3 relative to the tilting bearing 4. The first actuator 7 has a shorter arm 7.1 than the second actuator 8. However, relative to the tilting bearing 4, the first actuator 7 is located further away than the second actuator 8, so that the second actuator 8 is positioned between the first actuator 7 and the tilting bearing 4. The stroke of the hydraulic lifting cylinder 7.2 is also shorter than the stroke of the hydraulic lifting cylinder 8.2 of the second actuator 8. The second actuator 8 has a larger arm 8.1 than the first actuator 7. By means of the actuators 7 and 8, the support element 5 can be moved into the first tilting position (see Fig. 3) and into a second tilting position (see Fig. 2), wherein the first tilting position corresponds to the end position of the first actuator 7, and wherein the second tilting position corresponds to an end position of the second actuator 8. The hydraulic lifting cylinders 7.2 and 8.2 are assigned to a common hydraulic circuit. To execute a pivoting movement of the support element 5, the hydraulic lifting cylinders 7.2 and 8.2 are hydraulically connected in parallel, so that only one pressure generation device is required to actuate both lifting cylinders 7.2 and 8.2. To execute a pivoting or tilting movement of the support element 5, the actuators 7 and 8 initially work together until the support element 5 reaches a first tilting position, which corresponds to the end position of the first actuator 7. This means that the support element 5 can be moved from a transport position, in which the support element 5 is in a position parallel to the structure 3 (see Fig. 5), to the first tilting position using both actuators 7 and 8. If the angle between the structure 3 and the support element 5 increases due to the stroke of the second actuator 8, the rocker arm 7.1 of the first actuator 7 decouples at the coupling point 9.1 of the support element 5. The lifting work to reach the second tilting position is then performed exclusively by the second actuator 8. Thus, the support element 5 can only be moved into the second tilting position by the second actuator 8. The end position of the hydraulic lifting cylinder 8.2 of the second actuator 8 therefore spans the largest angle between the structure 3 and the support element 5. When the support element 5 returns to its initial tilting position during a return movement (Fig. 3), the first actuator 7 automatically engages with the support element 5 by positively engaging the rocker head 7.3 in the recess formed at the first coupling point 9.1. A coupling or locking mechanism can be provided at the coupling point 9.1 for this purpose. The device shown in the embodiment of Fig. 1 has, in the illustrated variant, a third actuator 10, which is assigned to the hydraulic circuit of the first actuator 7 and the second actuator 8. The function of the third actuator 10 is explained in more detail with reference to Fig. 4. Fig. 2 shows the device shown in Fig. 1 in a second tilting position, in which the first actuator 7 is decoupled from the support element 5. In the second tilting position, the hydraulic lifting cylinder 8.2 is fully extended, so that the support element 5 is at an angle of approximately 45° with respect to the vehicle frame 1. The end of the U-rail 11 opposite the coupling point 9.2 may have a stop for the rocker arm 8.3 guided in the U-rail 11 to limit the pivot angle of the support element 5. In other embodiments of the device, the second actuator 8 and the U-rail 11 for guiding the rocker arm 8.3 of the second actuator 8 may be dimensioned such that larger or smaller end angles are adjustable. Fig. 3 shows the device shown in Fig. 1 in a first tilting position, in which the first actuator 7 is operatively connected to the support element 5. In this first tilting position, the rocker head 7.3 of the rocker arm 7.1 of the first actuator 7 is positively coupled to the coupling point 9.1 of the support element 5. Any further downward movement of the support element 5 into a transport position (see Fig. 5) is dampened by the first actuator 7. The first actuator 7 thus assists the second actuator 8 during pivoting movements of the support element 5 between the transport position and the first tilting position. Figure 4 shows a schematic representation of an embodiment of the device with lifting and tilting functions in a lifting position. The superstructure 3 is located, as in the embodiment shown in Figure 1, on a vehicle frame 1 of a vehicle 2. The superstructure 3 is attached to the vehicle frame 1 by twist-lock fasteners 6. Unlike Figures 1, 2 to 3, the support element 5 is in a lifting position parallel to the vehicle frame 1. The lifting position is achieved by the interaction of the first actuator 7 and the third actuator 10, whereby the second actuator 8 is decoupled from the support element 5 and the tilting bearing 4 is open. The tilting bearing 4 is opened by unlocking the twist-lock fasteners 6 of the hinges of the tilting bearing 4. The tilting bearing 4 is thus no longer connected to the superstructure 3 by its hinges. The design of the third actuator 10 is essentially the same as that of the first actuator 7. It has a rocker arm 10.1 rotatably mounted on the structure 3, with a rocker arm 10.3 and a hydraulic lifting cylinder 10.2. The rocker arm 10.3 engages with the support element 5 at coupling point 9.3. This engagement is achieved by an upward movement of the rocker arm 10.1, whereby the rocker arm 10.3 is positively engaged in the recess formed at coupling point 9.3 of the support element 5. The coupling mechanism corresponds to the coupling mechanism of the first actuator 7 at coupling point 9.1, so that the support element 5 is operatively connected to the first actuator 7 and the third actuator 10 at two positions. The second actuator 8, which is arranged between the first actuator 7 and the third actuator 10, is decoupled from the support element 5. Therefore, only the first actuator 7 and the third actuator 10 are active for this function.The second actuator 8 can be temporarily decoupled from the hydraulic circuit for the lifting task according to this design. The actuators 7 and 10, arranged in a mirror image on the structure, are thus designed to move the support element 5 translationally parallel to the vehicle frame 1. In an embodiment of the device not shown here, the assembly 3 comprises only the first actuator 7 and a second actuator 8, the second actuator 8 being used to execute the lifting movement of the support element 5 when the tilting bearing 4 is open. To compensate for the required support loads / holding loads on the support element 5, the second actuator 8 can be positioned closer to the tilting bearing 4 in this embodiment. In a further embodiment of the device, not shown, the first actuator 7 and the second actuator 8 are arranged side by side along a common axis oriented transversely to a longitudinal direction of the superstructure 3. The longitudinal direction of the superstructure 3 corresponds to the longitudinal direction of the vehicle 2. In this embodiment, the third actuator 10 is arranged closer to the tilting bearing 4 in the longitudinal direction of the superstructure 3 than the first and second actuators 7 and 8, so that the third actuator 10 is located between the tilting bearing 4 and the actuators 7 and 8. Figure 5 shows a schematic representation of an embodiment of the device with lifting and tilting functions in a transport position, with the support element 5 lying parallel to the superstructure 3. The lifting cylinders 7.2, 8.2, and 10.2 are fully retracted, and the swing arms 7.1, 8.1, and 10.1 belonging to the actuators 7, 8, and 10 are folded in to save space. For transport securing, the tilting bearing 4 is closed; that is, the hinges of the tilting bearing 4 are locked with the twist-lock fasteners 6 and thereby firmly connected to the vehicle frame 1. Reference symbol list 1 Vehicle frame 2 Vehicle 3 Body 4 Tilting bearing 5 Support element 6 Twist-lock locking mechanism 7 First actuator 7.1 Swing arm 7.2 Hydraulic lifting cylinder 7.3 Swing arm head 8 Second actuator 8.1 Swing arm 8.2 Hydraulic lifting cylinder 8.3 Swing arm head 9.1 Coupling point 9.2 Coupling point 9.3 Coupling point 10 Third actuator 10.1 Swing arm 10.2 Hydraulic lifting cylinder 10.3 Swing arm head 11 U-rail

Claims

Device with lifting and tilting function for a vehicle (2), comprising a superstructure (3) detachably mounted on a vehicle frame (1) with a support element (5) pivotably mounted about a tilting bearing (4), at least one first actuator (7) and at least one second actuator (8), which are connected at different coupling points (9.1, 9.2) act on the support element (5), wherein: - the support element (5) can be moved into a first tilting position with the first actuator (7) and / or the second actuator (8), - the support element (5) can be moved from the first tilting position to a second tilting position with the second actuator (8), wherein the first actuator (7) is decoupled from the support element (5), and - the first actuator (7) can be coupled back into the support element (5) when the support element (5) is moved back into the first tilting position, and wherein the tilting bearing (4) is adjustable between a closed position for pivoting the support element (5) and an open position in which the support element (5) can be moved translationally parallel to the vehicle frame (1) with the first actuator (7) and / or the second actuator (8). Device according to claim 1, characterized in that the first actuator (7) and the second actuator (8) are hydraulic actuators which are assigned to a common hydraulic circuit. Device according to claim 1, characterized in that the first actuator (7) and the second actuator (8) each have an electric linear drive which generates a lifting movement via a spindle mechanism. Device according to one of the preceding claims, characterized in that the first actuator (7) dampens a return movement of the support element (5) into a transport position. Device according to one of the preceding claims, characterized in that the first actuator (7) is completely disengaged from the supporting element (5) in the second tilting position. Device according to one of the preceding claims, characterized in that the decoupling of the first actuator (7) is effected by a freewheeling device, in particular a ratchet or clamping mechanism. Device according to one of the preceding claims, characterized in that the coupling and decoupling of the first actuator (7) is effected by a coupling with direction-dependent force transmission. Device according to one of the preceding claims, characterized in that the first actuator (7) automatically enters into operative contact with the support element (5) during the return movement of the support element (5) into the first tilting position. Device according to claim 8, characterized in that the restoration of the functional connection is carried out by positive locking and / or force locking. Device according to one of the preceding claims, characterized in that the decoupling and / or coupling of the first actuator (7) is position-dependent, in particular depending on the tilting position of the support element (5). Device according to one of the preceding claims, characterized in that the first actuator (7) and / or the second actuator (8) is / are designed as a scissor lift. Device according to one of the preceding claims, comprising a third actuator (10) which is arranged between the second actuator (8) and the tilting bearing (4), wherein the third actuator (10) is configured to perform a lifting movement of the support element (5) translationally parallel to the vehicle frame (1) together with the first actuator (7). Device according to claim 12, characterized in that the first actuator (7) and the second actuator (8) are arranged side by side along a common axis which is oriented transversely to a longitudinal direction of the structure (3) and have different stroke distances. Device according to the preceding claim, characterized in that the second actuator (8) is decoupled from the support element (5) translationally parallel to the vehicle frame (1) during a lifting movement of the support element (5). Device according to one of the preceding claims, characterized in that the support element (5) has fold-out supports to support the support element (5) in an end position on the substrate.

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