DE4427901A1 - Freight container loading mechanism with load retainer - Google Patents

Abstract

The loading mechanism comprises a load retainer (16), insertable into the container (1), coupled to the main vehicle (14) by a coupling (13) and movable vertically at least. The mechanism has wheels (8,9) for supporting a torque generated by the load retainer. The wheels are fitted on two wheel arms (6,7) on either container side, which are movable on the outside of the container long walls (3,4). Their ends, away from the wheels are coupled to the main vehicle. The load retainer is linked to the coupling by a jib (15) movable at least in the vertical direction.

Description

The invention relates to a device for loading containers with an insertable into the container, with a base vehicle connected by a coupling device and at least in vertical load moving device and with Wheels for supporting one of the load suspension devices generated torque.

The dimensions of containers are due to international Norms given in feet. The lengths of such containers are between 20 and 40 feet, that's about 6 to 12 meters. It deals so-called freight containers for the transport of General cargo. It has proven to be because of the length of these containers proved difficult to perform the loading process without the Container floor through the wheel pressure of transport vehicles to strain excessively. The tendency is towards the Use containers as long as possible, because the Freight rates for this are significantly cheaper than the freight rates for shorter containers. The problem here is in the length of the  Loading devices belonging to loading vehicles, which in loaded condition a tipping moment on the loading vehicle exercise that can be, for example, a forklift. Used a forklift with an empty weight of 2.5 Tons, the result is a permissible payload below Consideration of stability with a factor of 1.3 a front axle load of 5 tons. For driving on vehicles with such an axle load, the container bases are not suitable.

It is already known to use a forklift as a loading vehicle use correspondingly long fork tines on their front End with support rollers or wheels are provided to the To absorb the tilting moment. Retracting the forks with the But training wheels is difficult because the front edge of the Container floor a distance of 15 to 20 cm from the Has footprint of the container, so that in front of the Container opening loading ramps must be set up, the maximum height the distance of the said leading edge from the Footprint corresponds. Nevertheless, here too Container floor exposed to large axle loads for which the container is usually not designed. It will be particularly difficult Loading the container if it is not on the ground, but stands on the back of a truck. On such a distance from the ground can at least be increased by ramps no longer bridging easily.

The invention is therefore based on the object of a device specify the genus described at the beginning, when using it the torque generated by the load handling device is not more must be carried by the container floor, which is a loading of containers where the container floor has different distances from the ground and with the large one  Loads reliably moved into the entire depth of the container can be.

The task is solved at the beginning specified loading device according to the invention in that the Wheels are arranged on two wheel arms, which are on both sides of the Containers on the outside of the longest container walls on Containers can be moved along and with their edges turned away Ends are connected to the base vehicle, and that the Load suspension device via an at least vertical Toward the movable boom with the coupling device connected is.

It is through the constructive measures according to the invention possible by the load suspension device with the associated Boom generated tipping or torque as close as possible to intercept the load suspension device outside the container, to load the container in question even if it is Soil surface at different distances from the ground located, and in particular it is possible to put the container on to load its entire length without the load on the Container floor would have to be moved.

It is particularly advantageous if the virtual common Axis of rotation FA-FA of the wheels between the Load suspension device and the coupling device. Here it is again particularly advantageous if the horizontal Distance D1 of the axis of rotation FA-FA of the wheels from the Load suspension device is smaller than the horizontal distance D2 the same axis of rotation FA-FA from the coupling device. The smaller the, the better the conditions Distance is D1.  

It is part of a further embodiment of the invention again particularly advantageous if the boom by a Arrangement of parallelogram links is formed, in particular by parallelogram handlebars, the articulation points of both vertical as well as horizontal movement of the Allow load suspension device.

It is in the course of yet another configuration of the Invention particularly advantageous when two top, on train stressed parallelogram handlebars and one in the middle below arranged, stressed parallelogram handlebar are present, and if the lower parallelogram handlebar with at least one linear actuator is connected.

This constructive measure allows the top Parallelogram handlebars very slim and therefore lightly trained be, while the lower parallelogram, which is due its compressive load with high buckling stiffness must also be subjected to bending by the linear actuator can be.

To bring about the different degrees of freedom of the boom it is particularly advantageous if the coupling device Rotary column on which the lower parallelogram link in swiveling in the vertical direction, but in the horizontal direction is arranged non-rotatably, and on which a rotary drive engages. Again, it is the lower one with high buckling stiffness Provided parallelogram handlebar, which absorbs the lateral forces the rotary actuator is used.

The individual articulation points of the parallelogram links of the boom are designed according to the characteristics of subclaims, that with any movement in the vertical or horizontal direction  as well as in the direction of superimposed movements Load suspension device is always moved parallel to itself.

It is also advantageous if the distance between the common axis of rotation FA-FA of the wheels of the Coupling device is changeable, especially if the Wheel arms for changing the center distance with Telescopic guides are equipped.

Through these measures, the maneuverability of the device be significantly improved at least in the unloaded state, and due to the telescopic extension of the wheel arms in loaded Condition, tilting or torques can be absorbed generated by an extremely long boom.

To a universal application of the device ensure, it is again particularly advantageous if the Wheel arms at their ends facing away from the wheels through a yoke a U-shaped chassis are interconnected. This The chassis can then be designed in very different ways Basic vehicles are connected:

For example, it is possible to use one as the basic vehicle Forklift to use and the wheel arms in the area of To connect the coupling device to the forklift.

This connection is particularly advantageous and simple Way in that the chassis in the area of the yoke over Swivel bearings with horizontal and swivel bearings with vertical Axles connected with two fork pockets into which the forks of the Forklift truck with fork bags lying on the floor can be inserted.  

On the other hand, it is possible to use the drive part of a base vehicle Reach truck to use and the wheel arms and the Coupling device fixed to the drive part of the To connect reach truck.

This drive part contains those for driving a traction motor required accumulators and a around a vertical axis rotatable drive wheel or a pair of drive wheels. Such reach trucks are usually made with relatively short Radar arms provided to ensure the stability and stability of the To ensure reach trucks. Instead of this short one According to the invention, wheel arms now pedal a great deal longer length, which is also a much larger one with each other Have distance, in such a way that the at the ends of the Wheel arms arranged wheels on both sides and outside the longest side walls of the container are movable.

On the one hand, it is possible to have a drive part of the To use reach trucks with a cab; but it is with particular advantage possible to close the driver's cab from the drive part disconnect and near the load handler in the Integrate parallelogram handlebar arrangement.

When using the drive part of a reach truck, a particularly high maneuverability of the invention Reach device. By arranging the cab in the immediate vicinity of the load suspension device Operator an excellent overview of all Movements and the spatial position of the cargo in each phase of the Loading and unloading process. The work of Operator can be facilitated in that the Driver's cab with lighting equipment and / or with  additional observation facilities such as mirrors and / or Video cameras.

The driver's cab can be opened in a particularly simple manner Attach particularly rigid lower parallelogram handlebars.

Here, however, the driver's cab leads with the operator the same tilting movements as the lower one Parallelogram handlebar itself.

In the event that the driver's cab is always in the same position compared to the load suspension device, it is particularly advantageous if the load suspension device on the Front of a support frame is attached to the back a supporting structure is rigidly attached to the driver's cab, and when the front articulation points of the parallelogram handlebars the rear of the cab.

Furthermore, it is particularly advantageous if in the Parallelogram handlebar arrangement for adjusting Change the inclination of the load handling device arranged is. In this case, a similar change in the Bring space, as by changing the inclination the mast of a forklift is possible.

It is a weight-saver, especially for long booms particularly advantageous if the boom has a single steering arm has on a linear actuator and a rotary actuator is connected and at both ends via a joint, which each have a horizontal axis and a vertical axis, with the coupling device on the one hand and with the Load handler is connected on the other hand, and when the two end sections of the steering arm over in pairs parallel mutually arranged displacement sensors with the coupling device on the one hand and via pairs arranged parallel to each other  Actuators with the load handling device on the other hand are connected, the actuators in accordance with the Determine the position of the load suspension device.

With purely hydraulic drive and control elements is one particularly simple solution characterized in that the Position sensors and the actuators as hydraulic cylinders with pistons and Piston rods are formed, and that the hydraulic cylinder on one side of a middle level on the side of the Piston bottom on the one hand and on the side of the piston rod on the other hand, are connected to one another by hydraulic lines.

Such a device can, however, in terms of mechanical structure and weight, when electrical components are integrated into the control. For example, the actuators can advantageously be used as Hydraulic drives and the travel sensors as electrical travel sensors be executed, the outputs of which via measuring amplifiers control valves for controlling the actuators by a hydraulic unit are activated.

The electrical position sensors can be analog position sensors (e.g. with slide potentiometers) or digital displacement sensors (with Pulse generators and counters).

Various devices can be used as load suspension devices serve, such as a mandrel that is in a cavity of a Roll or roller is insertable, a pair of pliers with the barrel-shaped Objects covered and even around essentially horizontal Axes can be rotated, the can continue Load suspension device consisting of two or more fork tines exist, the lateral distances independently can be changed to include several pallets, for example  being able to pick up, transport and set down at the same time. Of the Distance D1 described above applies in all cases advantageous approximately on the center of mass of the Load suspension device.

Further advantageous refinements of the subject matter of the invention result from the remaining subclaims.

Exemplary embodiments of the subject matter of the invention are explained in more detail below with reference to FIGS. 1 to 9.

Show it:

Fig. 1 is a plan view from above of the loading device according to the invention with two different positions of the boom and load bearing device,

Fig. 2 is a side view of the subject of FIG. 1 with three different mounting positions of the load bearing device and boom,

Fig. 3 shows the use of a device according to FIGS. 1 and 2 in conjunction with a forklift truck,

Fig. 4 shows the use of a comparison with FIGS. 1 and 2 slightly modified device in cooperation with the driving part of a reach truck, having drive part which at the same time a driver's cab,

Fig. 5 shows the use of a comparison with FIGS. 1 and 2 slightly modified apparatus in conjunction with a differently shaped drive part of a reach truck, and with arrangement of a guide object in the vicinity of the load receiving device,

Fig. 6 shows a variant of the subject of Fig. 5, in which the parallelogram formed shortened, and in which program guide rods between the parallelogram and the load receiving device is a driver's cab, whose spatial position remains unchanged for the load receiving device,

Fig. 7 is a side view of a further variant similar to FIG. 3, but with a boom in the form of a single steering arm, the hydraulic with two encoders and two hydraulic actuators cooperating for the load holding device,

Fig. 8 is an enlarged plan view of part of the article of Fig. 7 with additional details regarding the hydraulic control circuits, and

Fig. 9 shows an arrangement analogous to Fig. 8, but in which the hydraulic displacement sensors have been replaced by electronic displacement sensors with measuring amplifiers and control valves.

In Fig. 1, a container 1 with a container bottom 2 and two longest side walls 3 and 4 is shown in dashed lines. The loading opening 5 is also indicated.

An essential part of the loading device are two wheel arms 6 and 7 , at the ends of which two wheels 8 and 9 are arranged and which form the legs of a U-shaped chassis 10 , the yoke 11 of which is composed of three profile parts 11 a, 11 b and 11 c, as shown in Figs. 1 and 2. The two wheel arms 6 and 7 are held at a predetermined distance from one another by a cross member 12 .

The ends of the wheel arms 6 and 7 facing away from the wheels 8 and 9 can be or are connected by a coupling device 13 to a base vehicle 14 , which is shown in FIG. 3 as a forklift, the details of which will be discussed in more detail below.

A boom 15 is fastened to the chassis 10 in a manner described in more detail below in such a way that it can carry out both vertical and horizontal and also superimposed movements. At the end facing away from the coupling device 13 , the boom 15 has a load-carrying device 16 which, in the example according to FIGS. 1 and 2, is designed as a mandrel 17 for insertion into the axial cavity of a roller or roller or a winding.

As can be seen from FIG. 1, the virtual common axis of rotation FA-FA of the wheels 8 and 9 lies between the load suspension device 16 and the coupling device 13 , in which case the assumed center of gravity M is considered, which is defined by the load not shown here , the dimensions of which are naturally matched to the dimensions of the load suspension device 16 .

As can be seen from FIG. 1, the horizontal distance D1 of the axis of rotation FA-FA of the wheels 8 and 9 from the load suspension device 16 is considerably smaller than the horizontal distance D2 of the same axis of rotation FA-FA from the coupling device 13 .

As can be seen in particular from an overview of FIGS. 1 and 2, the boom 15 consists of a total of three parallelogram links 18 , 19 and 20 . The two upper parallelogram links 18 and 19 are only subjected to tension and are therefore very slim. In the middle below is the further parallelogram link 20 , which is subjected to pressure and is formed from a box section. This central parallelogram link 20 is connected to a lifting drive 21 , which in the present case consists of two hydraulic cylinders 22 , as can be seen in particular from FIG. 1.

The load suspension device 16 is attached to the front of a support frame 23 , on the rear of which articulation points 24 , 25 and 26 are arranged for the extreme ends of the parallelogram links 18, 19 and 20 . The other ends of the parallelogram links 18 , 19 and 20 are articulated to the coupling device 13 via further articulation points 27 , 28 and 29 . All articulation points are designed so that the parallelogram links 18 , 19 and 20 can perform pivoting movements in horizontal, vertical and composite movement, the support frame 23 being displaced parallel to itself during all movements. In Fig. 1 two such positions are shown; in Fig. 2 three such positions. The lifting drive 21 already described is used for parallel displacement in the vertical direction. The following constructional devices are used to generate a horizontal movement component: The coupling device 13 has a rotating column 30 on which the lower parallelogram link 20 can be pivoted in the vertical direction by means of the articulation point 29 , but is non-rotatably arranged in the horizontal direction. A pivot drive 31 , to which a horizontally lying hydraulic cylinder 32 belongs, engages on the rotary column 30 . It can be seen from this that the articulation points 24 , 25 and 26 assigned to the support frame 23 and the two upper articulation points 27 and 28 assigned to the coupling device 13 are designed such that they also perform a pivoting movement of the associated parallelogram links 18 , 19 in addition to the lifting movement in the vertical direction and 20 allow in the transverse direction to the stroke movement. When the lower parallelogram link 20 swivels in the transverse direction, the rotary column 30 already described plays the decisive role.

FIG. 2 also shows the technical measures for changing the distance of the axis of rotation FA-FA of the wheels 8 and 9 from the clutch device 13, indicated in dashed lines. For this purpose, the wheel arms 6 and 7 are equipped with telescopic guides 33 . The associated hydraulic drive is indicated by a double arrow 34 .

As can be seen from FIG. 2, right, the chassis 10 is connected in the area of the yoke 11 via two pivot bearings 35 with horizontal axes and via a pivot bearing 36 with a vertical axis of rotation with two fork pockets 37 into which the fork tines 38 of a base vehicle 14 can be inserted are, which is designed as a forklift 39 . The two horizontal pivot bearings 35 are connected to one another via a horizontal cross member 35 a, in the middle of which the pivot bearing 36 with its vertical axis of rotation is located at the top. Sliding of the fork pockets 37 is prevented by locking bolts 37 a.

The use of a conventional forklift 39 with a driver's cab 40 is shown in FIG. 3. In this case, the load suspension device 16 is formed from two forks, only one of which is visible. These forks are - with a variable distance from each other - arranged on the support frame 23 already described. The coupling device 13 with the rotary column 30 and all articulation points as well as the lifting drive 21 and the swivel drive 31 and the boom 15 corresponds in all details to FIGS. 1 and 2, so that repetitions can largely be dispensed with. The forklift 39 has a driver's cab 40 and an adjustable mast 41 in order to adjust the height and the inclination of the fork tines 38 , as is known from the usual forklifts. This makes it considerably easier to insert the fork tines 38 into the fork pockets 37 .

In the embodiment of the invention according to FIG. 4, the basic vehicle 14 from the driving part 42 of a reach truck, the wheel arms 6 and 7 and the coupling device 13 with said drive portion 42 is connected rigidly and firmly. The drive part 42 is equipped with a driver's cab 43 and has at least one drive wheel 44 which can be pivoted about a vertical axis, as a result of which the entire device is designed to be extremely maneuverable.

In the exemplary embodiment according to FIG. 5, a differently designed drive part 45 is used as the base vehicle, from which a special driver's cab 46 is separated and arranged in the vicinity of the load suspension device 16 . In this case, the driver's cab 46 is integrated in the parallelogram link arrangement, and is attached to the lower parallelogram link 20 . As shown in the drawing in FIG. 5, this leads to the driver's cab 46 changing its position accordingly when the angular position of the lower parallelogram link 20 changes.

The expression "driver's cab" is representative of every type of actuation and control device. It can be a pronounced driver's cab as in the example in FIG. 3, but also open driver's cabs, such as the embodiment in FIG. 4. If the operator could run the risk of coming into contact with an upper edge of the container the driver's cab is of course secured by stiff protective bars 47 .

In the exemplary embodiment according to FIG. 6, the same drive part 45 is used as in the object of FIG. 5, and also in this case the load suspension device 16 consists of two fork tines which are arranged on the support frame 23, which is adjustable in a horizontal direction. However, a support structure 48 is fastened on the rear side thereof, on which a driver's cab 49 is arranged, which is also provided with protective brackets 47 . In this case, the boom 15 ends at the rear of the driver's cab 49 , namely the front articulation points 24 , 25 and 26 of the parallelogram links 18, 19 and 20 are on the rear of the driver's cab 49 . It is understood that only the front parallelogram links 19 and 20 and the front articulation points 25 and 26 are visible in the side view of FIG. 6.

The possibility of adjusting the inclination of the load suspension device 16 is also explained with reference to FIG. 6. This is done by an adjusting device 50 , which in the present case is formed by two telescopic guides in the two parallelogram links 18 and 19 . In this case too, only the front adjustment device is visible. The adjustment drive is indicated by the double arrow 51 . Alternatively, of course, it is also possible to arrange the adjusting device 50 in the lower parallelogram link 20 , so that only a single adjusting drive is required at this point.

In the device according to FIGS. 7 and 8, the boom 52 has a single steering arm 53 which is articulated to an otherwise largely identical coupling unit 13 and is connected to a lifting drive 21 and to a swivel drive 31 . The connection to the swivel drive 31 takes place via the rotary column 30 .

The steering arm 53 is at both ends via a hinge point 54 , 55 , each having a horizontal axis AH1-AH1 or AH2-AH2 and a vertical axis AV1-AV1 or, AV2-AV2, with the coupling device 13 on the one hand and with the load suspension device 16 on the other hand. The two end portions 56, 57 of the steering arm 13 are connected by pairs of mutually parallel encoders 58 and 59 with the coupling means 13 on one hand and on pairs of mutually parallel actuators 60, 61 with the load receiving means 16 on the other.

The displacement sensors 58 , 59 and the actuators 60 , 61 are designed as hydraulic cylinders 64 , 65 with pistons 66 , 67 and piston rods 68 , 69 , and the hydraulic cylinders 64 , 65 are on one side of a central plane ME-ME on the side of the piston crown on the one hand and on the side of the piston rod 68 , 69 on the other hand connected to one another by hydraulic lines 70 , 71 .

As a rule, it is understood that the hydraulically coupled pistons and piston rods each have the same cross sections, so that the oil displaced by one piston triggers the same displacement on the other piston. Provided that all articulation points at both ends of the steering arm 53 have the same horizontal and vertical distances from one another, this results in a displacement of the load suspension device 16 parallel to itself.

In order to be able to intervene in these movements in a targeted manner, ie with a positive or negative sign, the hydraulic lines 70 , 71 are connected on each side of the center plane ME-ME by a control unit 72 , 73 , by means of which the path relationship between the position sensors 58 , 59 and the actuators 60 , 61 is changeable. It is understood that here the control units 72 on both sides. 73 are correlated with one another, in two ways: Firstly, it must be ensured that the same movement sequences take place on both sides of the center plane ME-ME when the steering arm 53 is moved vertically and the load suspension device 16 is pivoted vertically. On the other hand, with a horizontal pivoting movement of the steering arm 53, it must be ensured that the movement sequences run opposite on both sides of the center plane ME-ME. Without the control units 72 and 73 , this would automatically be the case with the circuit diagram shown in FIG. 8.

The article of Fig. 9 agrees with the exceptions described below in more detail with the object of Fig. 7 and 8 coincide, so that the same reference numerals are used for identical parts or parts with the same function. This also applies, for example, to the actuators 60 , 61 , which are designed as hydraulic drives.

In Fig. 9, however, the displacement sensors 58 a, 59 a are designed as electrical displacement sensors, and their outputs 58 b, 59 b are via measuring amplifiers 74 , 75 , control valves 76 , 77 for actuating the actuators 60 , 61 by a hydraulic unit 78 the lines 70 , 71 connected.

Measuring systems come into consideration here, which are also under the Designation "displacement transducers" are on the market and on potentiometric, inductive, incremental, coded or absolute Measurement principles are based and also indicate the direction of displacement. As Control valves preferably come in so-called proportional directional valves Question how they are used by BOSCH together with measuring amplifiers and whose circuit diagrams are offered.

In order to be able to intervene in a targeted manner, ie with a positive or negative sign, in the movement sequence of the load suspension device 16 , the inputs of the measuring amplifiers 74 , 75 are, if necessary, a control unit in addition to the outputs 58 b, 59 b of the displacement sensors 58 a, 59 a 79 , 80 connected, through which the path ratio between the position sensors 58 a, 59 a and the actuators 60 , 61 can be changed. For the reasons mentioned above, the control units 79 , 80 on both sides are also correlated with one another accordingly.

In the devices according to FIGS. 7 to 9, the ends of the displacement sensors 58 , 59 ; 58 a, 59 a and the ends of the actuators 60 , 61 via cardanic articulation points 62 , 63 with the steering arm 53 on the one hand and with the coupling device 13 and the load suspension device 16 on the other hand, in order to ensure the required degrees of freedom in the movement sequences. To attach a part of the cardanic articulation points 62 and 63 , the steering arm 53 is equipped with cross members 53 a and 53 b.

The circuits in FIGS . 8 and 9 are designed as such mirror-symmetrical to the center plane ME-ME. It also applies in any case that the actuators 60 , 61 in accordance with the displacement sensors 58 , 59 ; 58 a, 59 a determine the spatial position of the load suspension device 16 .

The hydraulic unit 78 , which is also used, at least in analog form, for the objects in the other figures, is - as shown in FIG. 9 - connected to the actuators 60 and 61 via the control valves 76 and 77 and consists of a hydraulic pump 81 with a on the pressure side downstream check valve 82 and a drive motor 83 . A pressure limiter 85 is connected to the pressure line 84 , and the return line 86 opens into a sump 89 via a filter 87 , to which a by-pass valve 88 is assigned.

Apart from the influence of the control units 72/73 and 79/80 , the mode of operation of the arrangements according to FIGS. 7 to 9 is as follows:

With a vertical movement of the boom 52 , the travel signals of the travel sensors 58/59 or 58 a / 59 a are communicated in opposite directions to the actuators 60/61 , so that the load suspension devices 16 move parallel to themselves. When the arms 52 move horizontally, the opposite travel signals of the travel sensors 58/59 or 58 a / 59 a are communicated to the actuators 60/61 on the other side of the center plane ME-ME with a corresponding opposite sign, so that in this case too move the load handling devices 16 parallel to themselves. Corresponding considerations also apply to superimposed horizontal and vertical movements of the boom 52 .

It is of course possible to use the different ones Adjustment options with all others described To combine embodiments.

The term "coupling device" is understood to mean all connecting elements or assemblies by means of which the load suspension device, including its drive elements, can be connected or connected to one of the possible basic vehicles, be it in the form of a releasable connection according to FIGS. 1 to 3 or be it in the form of a permanent connection according to FIGS. 4 to 6.

Claims (26)

1. Device for loading containers ( 1 ) with an insertable into the container, with a base vehicle ( 14 ) connected by a coupling device ( 13 ) and at least vertically movable load carrying device ( 16 ) and with wheels ( 8 , 9 ) for the Supporting a torque generated by the load suspension device ( 16 ), characterized in that the wheels ( 8 , 9 ) are arranged on two wheel arms ( 6 , 7 ) which are located on both sides of the container ( 1 ) on the outer sides of the longest container walls ( 3 , 4 ) movable along the container ( 1 ) and with their ends facing away from the wheels ( 8 , 9 ) are connected to the base vehicle ( 14 ), and that the load-bearing device ( 16 ) has an arm ( 15 , 52 ) which is movable at least in the vertical direction the coupling device ( 13 ) is connected. 2. Device according to claim 1, characterized in that the virtual common axis of rotation (FA-FA) of the wheels ( 8 , 9 ) between the load suspension device ( 16 ) and the coupling device ( 13 ). 3. Apparatus according to claim 2, characterized in that the horizontal distance (D1) of the axis of rotation (FA-FA) of the wheels ( 8 , 9 ) from the load suspension device ( 16 ) is smaller than the horizontal distance (D2) of the same axis of rotation ( FA-FA) from the coupling device ( 13 ). 4. The device according to claim 1, characterized in that the boom ( 15 ) with parallelogram links ( 18 , 19 , 20 ) is equipped. 5. The device according to claim 4, characterized in that two upper, parallelogram link ( 18 , 19 ) and a centrally located pressure-loaded parallelogram link ( 20 ) are present and that the lower parallelogram link ( 20 ) with at least one lifting drive ( 21 ) is connected. 6. The device according to claim 4, characterized in that the load-bearing device ( 16 ) on the front of a support frame ( 23 ) is fixed, on the back of hinge points ( 24 , 25 , 26 ) for the extreme ends of the parallelogram ( 18 , 19 , 20th ) are arranged. 7. The device according to claim 6, characterized in that the other ends of the parallelogram ( 18 , 19 , 20 ) are articulated via further articulation points ( 27 , 28 , 29 ) on the coupling device ( 13 ). 8. The device according to claim 7, characterized in that the coupling device ( 13 ) has a rotating column ( 30 ) on which the lower parallelogram ( 20 ) is pivotable in the vertical direction, but rotatably arranged in the horizontal direction, and on which a pivot drive ( 31 ) attacks. 9. The device according to claim 8, characterized in that the support frame ( 23 ) associated hinge points ( 24 , 25 , 26 ) and the two upper, the coupling device ( 13 ) associated further hinge points ( 27 , 28 , 29 ) are designed so that they additionally allow a pivoting movement of the associated parallelogram link ( 18 , 29 , 30 ) in the transverse direction to the stroke movement. 10. The device according to claim 2, characterized in that the distance between the axis of rotation (FA-FA) of the wheels ( 8 , 9 ) of the coupling device ( 13 ) is variable. 11. The device according to claim 10, characterized in that the wheel arms ( 6 , 7 ) are equipped with telescopic guides ( 33 ) for changing the center distance. 12. The apparatus according to claim 1, characterized in that the wheel arms ( 6 , 7 ) at their ends facing away from the wheels ( 8 , 9 ) are connected to one another by a yoke ( 11 ) to form a U-shaped chassis ( 10 ). 13. The apparatus according to claim 1, characterized in that the basic vehicle ( 14 ) is a forklift ( 39 ) and that the wheel arms ( 6 , 7 ) in the region of the coupling device ( 13 ) are connected to the forklift ( 39 ). 14. Device according to claims 12 and 13, characterized in that the chassis ( 10 ) in the region of the yoke ( 11 ) via two pivot bearings ( 35 ) with horizontal and a pivot bearing ( 36 ) with a vertical axis with two fork pockets ( 37 ) into which the forks ( 38 ) of the forklift ( 39 ) can be inserted. 15. The apparatus according to claim 1, characterized in that the base vehicle ( 14 ) is the drive part ( 42 , 45 ) of a reach truck and that the wheel arms ( 6 , 7 ) and the coupling device ( 13 ) with the drive part ( 42 , 45 ) of Reach truck are connected. 16. The apparatus according to claim 15, characterized in that the drive part ( 42 ) of the reach truck is equipped with a driver's cab ( 43 ). 17. The apparatus according to claim 15, characterized in that the driver's cab ( 46 ) from the drive part ( 45 ) is separated and integrated in the vicinity of the load suspension device ( 16 ) in the parallelogram link arrangement. 18. The apparatus according to claim 17, characterized in that the driver's cab ( 46 ) is attached to the lower parallelogram ( 20 ). 19. The apparatus according to claim 17, characterized in that the load-bearing device ( 16 ) on the front of a support frame ( 23 ) is fixed, on the back of a support structure ( 48 ) with a driver's cab ( 49 ) is rigidly attached, and that the front Articulation points ( 24 , 25 , 26 ) of the parallelogram link ( 18 , 19 , 20 ) are located on the rear of the driver's cab ( 49 ). 20. The apparatus according to claim 1, characterized in that an adjusting device ( 50 ) for changing the inclination of the load suspension device ( 16 ) is arranged in the parallelogram link arrangement. 21. The apparatus according to claim 1, characterized in that the boom ( 52 ) has a single steering arm ( 53 ) which is connected to a lifting drive ( 21 ) and a swivel drive ( 31 ) and at both ends via a hinge point ( 54 , 55 ), each having a horizontal axis (AH1-AH1, AH2-AH2) and a vertical axis (AV1-AV1, AV2-AV2), is connected on the one hand to the coupling device ( 13 ) and on the other hand to the load suspension device ( 16 ) , and that the two end sections ( 56 , 57 ) of the steering arm ( 53 ) via pairs of parallel sensors ( 58 , 59 ; 58 a, 59 a) with the coupling device ( 13 ) on the one hand and via pairs of actuators ( 60 , 61 ) are connected to the load suspension device ( 16 ) on the other hand, the actuators ( 60 , 61 ) determining the spatial position of the load suspension device ( 16 ) in accordance with the displacement sensors ( 58 , 59 ; 58 a, 59 a). 22. The apparatus according to claim 21, characterized in that the ends of the displacement sensors ( 58 , 59 ; 58 a, 59 a) and the ends of the actuators ( 60 , 61 ) via cardanic articulation points ( 62 , 63 ) with the steering arm ( 53 ) on the one hand and with the coupling device ( 13 ) and the load suspension device ( 16 ) on the other hand. 23. The device according to claim 21, characterized in that the displacement sensors ( 58 , 59 ) and the actuators ( 60 , 61 ) are designed as hydraulic cylinders ( 64 , 65 ) with pistons ( 66 , 67 ) and piston rods ( 68 , 69 ), and that the hydraulic cylinders ( 64 , 65 ) are connected to one another on each side of a center plane (ME-ME) on the side of the piston crown on the one hand and on the side of the piston rod ( 68 , 69 ) by hydraulic lines ( 70 , 71 ). 24. The device according to claim 23, characterized in that the hydraulic lines ( 70 , 71 ) on each side of the center plane (ME-ME) are each connected by a control unit ( 72 , 73 ) through which the path ratio between the displacement sensors ( 58 , 59 ) and the actuators ( 60 , 61 ) can be changed, and that the control units ( 72 , 73 ) on both sides can be correlated with one another. 25. The device according to claim 21, characterized in that the actuators ( 60 , 61 ) as hydraulic drives and the displacement sensors ( 58 a, 59 a) are designed as electrical displacement sensors, the outputs ( 58 b, 59 b) via measuring amplifiers ( 74 , 75 ) control valves ( 76 , 77 ) for controlling the actuators ( 60 , 61 ) are connected by a hydraulic unit ( 78 ). 26. The apparatus according to claim 24, characterized in that the inputs of the measuring amplifier ( 74 , 75 ) in addition to the outputs ( 58 b, 59 b) of the displacement sensor ( 58 a, 59 a) each have a control unit ( 79 , 80 ) , through which the path ratio between the position sensors ( 58 a, 59 a) and the actuators ( 60 , 61 ) can be changed, and that the control units ( 79 , 80 ) on both sides can be correlated with one another.