HK1009706B - Combination of a digger with a vibrating device - Google Patents

Description

The present invention relates to a layer fabricator for applying a compressed uniform layer or similar material to a substrate comprising a finished ball and a dosing slide pre-loaded to the finished ball, and also relates to a process for producing a compressed uniform layer or similar material on a substrate by means of a layer fabricator.

In modern road or railway construction, it is known to be used for the manufacture of load-bearing layers, such as hydraulically bound load-bearing layers (HGT), anti-freeze layers or planum layers, a load-bearing layer manufacturer, as known from the general term of claim 1, EP 0 335 339 A1. This load-bearing layer manufacturer comprises a crawler chain drive and a shaker shaft mounted at the front of the load-bearing layer manufacturer, which can be set by a number of cylinder units in their height and angle to the load-bearing layer. A suitable compressed-time manufacturing layer is possible in the case of known shaker shafts, provided that the dynamic distribution of the material produced is determined by a dynamic rotation of the material in the direction of its rotation and is designed to be moved in a steady position, which is significantly higher than the pressure of the material being compressed.

However, the problem often arises in the construction of railway installations in particular, where the railway line has to be run through rough terrain and therefore there is little space available for the equipment required for the construction of the track. However, the construction of a load layer with the load layer manufacturer known from EP-A-0 335 339 requires that, in addition to the equipment already present on the site, such as excavators, lorries, etc., an additional piece of equipment must be placed in the space without restrictions. Furthermore, in some cases, in order to manufacture a load layer, an additional piece of equipment (e.g. a sea-conveyor belt) must be used to produce the material required, which is less than the load force required.

The well-known fabricator of the layer entails considerable costs of purchase or maintenance of equipment which is not otherwise usable and which, whenever a layer is to be manufactured, must be transported to the site and then removed from that site.

DE-OS 20 64 180 is known to have a combination of an excavator and a crane, in which the crane is loaded by a section of the crane arm remaining on the top of the excavator to create a sufficient pressure against a substrate, but this results in the loss of the function of the excavator as such.

DE-OS 28 00 31 shows a planar screen which uses a planar plate placed on one side of the same front as a suspension for auxiliary units, such as a hydraulic unit or the like.

The present invention is intended to provide a layer fabricator or a layer manufacturing process that can produce a uniform layer without the use of additional equipment, and is solved by the layer fabricator or the process specified in claim 1 or claim 32.

Since excavators are generally available at every railway or road construction site to work the subsoil and perform a variety of other tasks, the provision of a holding device on the excavator, on which a furtiger ball can be either mounted or removed, can easily provide a work equipment for shaking or preparing load layers at the respective construction site.

The use of a load layer manufacturer, which would take up additional space on the site, is therefore no longer necessary.

The excavator arm already fitted to the excavator can be used to lift the final excavator shaft from a landing site, e.g. on a truck or at the edge of a construction site, and to attach it to the stopping device. The excavator arm can also be used with the excavator shovel fitted to the excavator arm to lift the material produced, e.g. on a truck, from the truck and distribute it on the substrate in front of the excavator and the excavator shaft. An additional excavator, which had to carry out this unloading and distribution and had to drive on the uncompressed substrate in front of the rotary device, is therefore not necessary. This is therefore particularly advantageous, since the tyres produced by the extra excavator shaft in the substrate, which are not yet evenly distributed, produce a very high amount of excess material, but not equally as much as the excavator shaft.

The excavator itself has a very high specific weight (up to 25 t), so it is ensured that the finishing ball is placed on the material to be shaken with a very high pressure, so that a good coupling is ensured to transfer the vibrations produced by the finishing ball from the finishing ball to the material to be compressed.

The excavator bore may be part of a crane which has a mounting base which can be attached to the support by hook sections, so that the excavator can lift the crane with the excavator arm from the ground on its own without any additional assistance and attach it to the excavator by hooking the crane sections to the support, thus reducing the time required for a crane to be provided to produce a load.

This is particularly advantageous if the first restraint includes a support plate placed on one side of the front of the vehicle and if the backrest is provided with a counter-plate which, if fitted, is attached to the backrest, with at least a hook-like section on the upper edge of the backrest which overlaps one edge of the backrest. The excavator thus needs to move the backrest with the support arm only as far as the backrest is attached to the backrest, until the backrest is attached to the backrest. Following the backrest arrangement by means of the backrest device leads to a cut-off in the direction of the backrest, which is set at least to the backrest.

The counter plate can be attached to the support plate by a number of bolt connections to prevent the upward movement of the support device relative to the excavator by external forces.

To ensure that at each height of the cradle relative to the body, the cradle has the same inclination relative to the body and thus to the ground, it is proposed that the cradle be connected to the counter-plate by at least two pairs of overlapping, side-by-side spaced swing arms, which are adjustable to the counter-plate at one end and adjustable to the cradle at the other end, providing a parallelogram for the cradle.

In an alternative design, the supporting device consists of at least two supporting plates, spaced sideways and extending from one side of the chassis to the other, and one supporting plate, each connected to the chassis by swivel connections, extending in a direction opposite the chassis and the chassis, to the chassis, on which the supporting device, the manufacturer's ball, can be mounted. All the elements necessary for attaching the supporting device to the excavator are thus firmly connected to the excavator in such a way as to provide a particularly stable attachment of the supporting device to the excavator.

It is advantageous for the support of the supporting structure to have supporting plates, each of which is attached to the supporting plates on the undercarriage, to be laid out vertically and in the direction of the undercarriage, and the swing connections to include a lower swing arm, which is rotatable on a lower section of the supporting plates and on a lower section of the supporting plates, and a swing arm, which is rotatable on an upper section of the supporting plates and on a higher section of the supporting plates, which is essentially parallel to the lower swing arm and forms with it a parallelogram for the supporting plate.

For lifting and lowering the finished bolt, it is proposed that each pivot connection also comprise a first cylinder unit, and that the first cylinder unit be mounted at one end in the area of attachment of the lower swing arm to the support plate at this pivot and at the other end in the upper swing arm at its area of attachment to the support plate at this pivot. The whole cylinder unit thus extends entirely within the steering parallelogram formed by the upper and lower swing arms, so that there are no carriages carrying the upper swing arms or the upper section of the carrying plate.

If the length of the support of the crampon in the transverse direction of the vehicle is less than or equal to the maximum width of the vehicle, it shall be ensured that there are no components protruding from the side of the vehicle so that transport or movement of the vehicle on public roads can be carried out without difficulty.

For the coupling of the finishing bolts to the support of the cradle, it is proposed that coupling elements be provided in the area of the outer ends of the support of the cradle in the transverse direction of the chassis for the fixed coupling of the support of the cradle to the finishing bolt.

In another alternative design of the suspension, it may consist of swivel devices mounted on the side surfaces of the chassis frames, which can be securely coupled to the excavator shaft. The coupling of the excavator shaft to the excavator shaft on each side of the chassis, i.e. outside the crawler chassis, allows a significant reduction in the torque transferred from the excavator shaft to the chassis, in particular around a rotation axis parallel to the direction of travel, which provides for a particularly stable coupling of the excavator shaft to the excavator.

It is advantageous if the rotary devices each have a vertical upper and lower rotary frame, one at each end of which is directed to the frame of the chassis, which are firmly coupled to the finished shaft at the other end, so as to provide the respective parallelogram guides for the finished shaft.

It is proposed that each of the swivel devices for lifting the finishing shaft should also contain a first cylinder unit, which is coupled to the upper or lower swing arm on the one hand and the drive frame on the other to raise and lower the finishing shaft in any way.

If the upper swing arm is further from the chassis frame in a transverse direction of the chassis than the lower swing arm and the first cylinder unit is coupled to the lower swing arm, it is possible to use a cylinder unit whose length ensures sufficient lift for the cradle.

To ensure that the lifting force exerted by the first cylinder unit is not exceeded by the weight of the end ball transferred by the swing arm to the first cylinder unit and that the lift provided by the swinging device and the first cylinder unit is sufficient for a variety of operations, it is proposed that the cylinder unit attaches to the upper or lower swing arm in a middle section of the latter.

In order to enable the swivel devices with the upper and lower swivel arms and the cylinder unit to be easily and quickly attached to the chassis frame of the excavator, it is proposed that the upper and lower swivel arms of each swivel device and the first Zy-slung unit be mounted on a swivel mounted plate to be mounted on the chassis frame.

In order to adjust the angle of the crane relative to the underbody and thus to the ground, and thus to perform various types of shaking operations, it is proposed that the upper and/or lower swing arms be adjustable in length to adjust the angle of the finishing shaft relative to the underbody.

The excavator shaft preferably consists of a shaker shaft with a shaker plate and at least one shaker; a first cylinder unit is also provided to adjust the vertical position of the shaker shaft relative to the excavator, thereby avoiding the need to provide a cylinder unit on the excavator which, if fitted, must be coupled to it to adjust the vertical position of the excavator shaft.

If the shaker plate is held on a frame of the shaker bore with rubber elastic elements interposed, it is ensured that the vibrations produced by at least one shaker are primarily transferred to the shaker plate and not to the frame of the finishing shaft and excavator, thus significantly improving the efficiency of the finishing shaft.

In order to produce a particularly uniform load layer, it is proposed that the dosing slide be adjusted in its vertical position relative to the finished ball by a second cylinder unit so that the material unloaded before the excavator or the finished ball passes under the finished ball in a dosed position depending on the vertical position of the dosing slide and a load layer with uniform layer thickness and density is produced.

The first and second cylinder units and at least one shaker can be operated in a particularly simple way because the first and second cylinder units and at least one shaker can be operated hydraulically.

It is proposed that an auxiliary drive shaft be provided on an excavator motor mounted on the top of the excavator and that the auxiliary drive shaft be capable of operating a hydraulic pump mounted on the top of the excavator for the hydraulic operation of the first and second cylinder units and at least one shaker, thus eliminating the need for additional drive units on the excavator, so as to reduce the total cost of the combination of the invention.

Conventional excavators are generally not able to operate at the same speed in the lower speed range, i.e. in the 1-3 m/min range, as is desirable for the production of load layers. This is because conventional excavators are designed for higher speeds of, for example, more than 3 km/h (50 m/min). Although the oil pumps intended for the operation of the drive engines are also adjustable in terms of their conveying power, they cannot discharge the same amount of oil in the low conveying power range, since they are already operating at least in the leakage flow range. To eliminate this disadvantage, it is proposed that the hydraulic pumps operate with a triple-damp pump, with one pump operating at a low speed and no additional pumps being necessary for the first engine and one pump running at the same speed, and that the second pumps can be operated by the same engine and with the same fuel pumps, provided that no additional pumps are required for the second engine and no additional pumps are fitted to the first engine.

Since the finished bolt is preferably mounted on one side of the front of the chassis, it is proposed that hydraulic line connections be provided on one side of the top of the chassis to connect the hydraulic pump to the first and second cylinder units and to at least one shaker and that the top of the chassis be provided with angle limiting devices to limit the angle of swing of the chassis to a predetermined value.

Alternatively, a hydraulic pressure line can be provided in a rotary crane of the excavator to carry hydraulic pressure lines from the hydraulic pump to the first and second cylinder units.

In order to be independent of the excavator's drive engine, it is also possible to provide a diesel unit and a hydraulic pump driven by the diesel unit on the undercarriage to operate the first and second cylinder units and at least one shaker.

In this case, it is advantageous to provide a second support plate at the rear of the chassis, to which a back plate is attached to support the diesel engine and hydraulic pump and which, with a hook-like section, crosses the top edge of the second suspension plate, thus making it possible to attach and remove the diesel engine and hydraulic pump to be mounted on the chassis to the excavator by means of the excavator arm without the need for additional support staff, which in turn saves time and costs.

If the support is attached by at least a screw connection to the second support plate, it shall be ensured that the support does not detach from the excavator even in the event of strong shocks or external forces.

It is proposed that the hydraulic lines from the hydraulic pump to the first and second cylinder units and to the shaker be run along the underside of the chassis in order to avoid damage to the hydraulic lines by the crankshaft or the top chassis.

The attachment of the rod to the excavator by means of the excavator arm is considerably facilitated if the rod is fitted with coupling elements for selective coupling to the excavator arm.

In order to minimise the impact on the load-bearing layer produced by the combination according to the invention by subsequent driving, it is proposed that the chassis comprise a caterpillar chain suspension with two caterpillar chains provided on each side of the chassis.

The invention is described below by means of a preferred embodiment with reference to the accompanying drawings.It shows:Fig. 1a side view of the load layer manufacturer according to the invention as a combination of an excavator and a rod device;Fig. 2a schematic view of the combination along a line II-II in Fig. 4;Fig. 3a cross-sectional view of the rod line along a line III-III in Fig. 4;Fig. 4a cross-sectional view of the combination of a third excavator and a rod device.Fig. 5a corresponding schematic cross-sectional view of Fig. 2, showing an embodiment of the hold device for the second rod device;Fig. 6a cross-sectional view of the hold device;Fig. 7a cross-sectional view of the first and fifth rods;Fig. 8a cross-sectional view of the first and third rods.

Figure 1 shows a general excavator with 10 excavators, comprising a top wagon 12 and a bottom wagon 14. The top wagon 12 is mounted on the bottom wagon 14 in a way that is familiar to the user, e.g. by means of a rotary crane, which can be rotated.

At a free end 22 of the second arm section 20 is a drill bit 24. The second arm section 20 has a rotary device 26 by which the part 28 of the second arm section 20 connected to the shovel 24 can be rotated 360° about a longitudinal axis of the second arm section 20 relative to the part 30 held rotatable on the first arm section 18. Since the shovel 24 is known to be held rotatable at the end 22 of the second arm section 20 on a substantially horizontal axis, the shovel 24 can be moved by the top driver to virtually any working position. On both sides of the excavator 14 there are 32 sub-chains 32 which form the drill bit 31 which are mounted by an engine (not fitted) and are arranged in the excavator 12 in the excavator.

As shown in detail in Figure 2, a crane 34 is fitted to the excavator 10 and a support plate 40 is attached to a front 36 of the chassis 14 by means of a plurality of hooks, either longitudinally to the excavator or diagonally to this extending support plate 38. The support plate 40 extends essentially parallel to the front 36 of the chassis along essentially the entire width of the chassis between the crawler chains 32. A counter plate 42 of the support device 34 has a hooked section 44 in an upper end 46 (see Figure 3) which is essentially carried over the entire width of the chassis plate.

The support plate 40 and the counter plate 42 can be connected by means of additional screw joints 50, e.g. bolts, which create openings in both the support plate 40 and the counter plate 42 and thus prevent unintended release of the support device 34 from the excavator 10, e.g. by lifting the support device 34.

The rod assembly 34 shown in Figure 3 contains a known shaker or a finishing rod 52 At a frame section 54 of the shaker 52 pairs of supporting arms 56 and 58 are fixed sideways, at a distance of 64,65 degrees, on each other by essentially horizontal axes with their first ends adjustable.

As can be seen in particular from Figure 4, one of the upper and/or lower arms 56,58 spaced side by side, is essentially A-shaped and is articulated by the end section 64 of the support arm 56, which is used to attach the support arm 56 to the shaker shaft, and which is adjustable transversely to the side support arm 66 to be extended in the direction of the support structure. The side support arm 66 is also adjustable by its free end 68 to a support 68 on the counter-plate 42 on a substantially horizontal axis. Between the two end sections 68 and 72 of the support arm 66 and the support arm 56 fixed on the counter-plate 42, the support arm 56 is essentially designed to extend the direction of the stabilizer excavator, which is fixed both on the 56 and on the support arm 66.

The upper and lower support arms 56 and 58 provide for a parallel passage of the shaker bore 52 in a height direction relative to the excavator, which is secured by the side support arm 66 and the stabilizer 74 against displacements of the shaker bore caused by lateral forces relative to the excavator, so that the shaker bore 52 can only be moved in a vertical direction.

At each side of the counter plate 42 there is a structure 76 which carries a first cylinder unit 80 at its upper end 78 and a first cylinder unit 80 at its lower end 82 which is fixed in a rotating position at the frame section 54 of the vibrating shaft 52 so that the vibrating shaft 52 can be raised and lowered essentially vertically by actuating the cylinder unit 80 i.e. by pulling in or pulling out the piston rod 84.

The structure 76 comprises two arms 86 and 88, each consisting of essentially rectangular supporting parts 89, which are fixed by a terminal section 90 of the arm 88 at the upper edge section 46 of the counter plate 42. An opposite terminal section 92 of the arm 88 is firmly connected by a supporting arm 94 extending essentially slanted downwards to a lower edge section 96 of the counter plate 42 and thus supports the structure 76 at the counter plate 42. In addition, a further supporting arm 98 extends between the terminal section 90 of the arm 88 and the upper end of the arm 78 86 and thus, in addition to stabilizing the arm 76, serves to support the entire weight of the shaker 52 in the main body of the shaker, by means of this weighted backrest.

The mounting 76 at each side of the counter plate 42 is securely connected by a connecting element 77 at the upper end of each arm 86.

The well-known shaker shaft comprises a main frame extending transversely along the length of the excavator, which is essentially composed of two supporting parts 102 connected by a number of transverse plates 105 extending transversely to the supporting parts and welded to them, for example (see Fig. 4). On the opposite plate 42 adjacent to the supporting 102 is the frame section 54 fixed, by which the two upper and lower supporting arms 56 and 58 are connected in a way that the latter can be moved.

The 50 is fitted with a 50-degree-high cylinder, which is fitted with a 50-degree-high cylinder, which is fitted with a 50-degree-high cylinder, which is fitted with a 50-degree-high cylinder, which is fitted with a 50-degree-high cylinder, which is fitted with a 50-degree-high cylinder.

To operate the first and second cylinder units 80 and 114 and the shaker 108 located on the shaker plate 106, a diesel unit 116 is also located on the chassis (see Figures 2 and 4). The diesel unit 116 may be equipped with a hydraulic pump 117 which supplies the working fluid under pressure required to operate the first and second hydraulic units 80 and 114 and the shaker 108. This unit 116 with the hydraulic pump 117 may be mounted on the chassis 14 in a manner corresponding to the mounting of the shaker device 34 on the chassis.A support 125 for the diesel unit 116 and the hydraulic pump 117 comprises a floor section 124 arranged essentially horizontally, on which the diesel unit 116 and the hydraulic pump 117 are fixed, for example, by bolts, and a counter-plate 126 arranged essentially vertically. On the counter-plate 126 two side-by-side sections 128 are provided, which are essentially in the direction of height of the counter-plate 126 and have hooked sections 130 at their upper ends. The sections 130 cover one upper edge of the counter-plate 122,The parts of the plate 130 are fixed to both the counter plate 126 and the floor part 124 by welding, for example, thus increasing the stability or stiffness of the plate 125 for the diesel unit 116 and the hydraulic pump 117.

The connecting lines (not shown) to supply the pressurised hydraulic oil to the first and second cylinder units 80,114 and to the shakers 108 are located along the underside of the chassis 114 to avoid mutual interference with the top chassis 12 when the top chassis 12 is turning.

As an alternative to the addition of a diesel unit, it is also possible to provide an auxiliary drive shaft to the excavator motor fitted to the upper carriage of the excavator, by which a hydraulic pump is connected to the first and second cylinder units and to the shaker.However, since in this case, for example on the front of the overhead vehicle, a hydraulic connection to the overhead vehicle must be provided, it is necessary to install a swing angle limiting device for the overhead vehicle, since the attached wires limit the maximum rotation range of the overhead vehicle on the undercarriage.

As mentioned above, the excavator 34 has 79 rods attached to the structure 76 to connect the 34 rod to the excavator arm. It is therefore possible for the excavator driver to remove the 34 rod without further assistance, for example from a lorry and attach it to the excavator 10. To this end, 24 steel rods can be attached to the 16 rod and to the excavator shovel respectively, which are then hung into each of the 79 rods so that the 34 rod can be lifted by the excavator. Since two laterally spaced loads are designed to attach each of the 79 rods, it is not possible to attach a lateral detachable plate to the 34 rod. To attach the 34 rod to the 10 rod, the excavator needs only a steel plate with 42 pins in the opposite direction of the 40 rod and 42 pins in the rear position of the 34 rod.

In order to place the bumper in a correct lateral position on the excavator, the counter plate and/or the support plate may be provided with self-contained guides (not shown) which, when the bumper is lowered, bring the bumper and thus the whole bumper into a correct lateral position with respect to the support plate.

It is also possible to provide for the use of a latch (not shown) on the support for the diesel unit and the hydraulic pump, so that this additional unit can be attached and removed by the driller without additional assistance.

Figures 5 and 6 show a second preferred embodiment of the suspension 152 for the crane system. The suspension 152 comprises 156.158 support plates, each paired in a front section 154 of the 150 chassis, with two pairs of such support plates 156.158.156',158' spaced sideways on the 150 chassis, as shown in Figure 6. The pairs of support plates 156.158.156',158' are each mounted on the 150 chassis so that they are as close as possible to the respective chassis 160.162 to ensure the most stable support of the 150 chassis at the direction of travel.

The support plates 156.158.156',158' are, as shown in Figure 5, mounted on the chassis 150, e.g. by welding or the like, so that they enclose the chassis 150 with extended sections 164.166 and thus form the largest possible coupling area between support plates 156.156' and 158.158' and chassis 150.

In a top section 168 of the respective pairs of support plates 156,158,156',158', each one of the upper swing arms 170 is located on a support plate 178,178', by means of a bolt 182 around an axis which is essentially transverse to the chassis 150.

At a lower section 184 of the respective pairs of support plates 156,158,156',158', each bolt 186 contains a lower swing arm 188 which can be rotated around an axis extending transversely to the undercarriage 150.

A cylinder unit 196 which is provided for each pair of 156.158.156',158' load plates is also mounted with one end on the bolt 186 on which the lower arms 188 of the 156.158.156',158' load plates are mounted in a rotating position, and is mounted with its other end in the area of the front end 176 of the respective upper rotating arm 170 by a bolt 198 which is rotatable.

The support plates 178.178' are fixed, for example, by welding or the like, to a support 180 of the support 180; the support 180 extends in front of the 160.162 tracks to the undercarriage 150. In the area of the outer ends 200,202 there are attached to the support 180 pairs of 204.206 and 208.210 suspension clasps, to which the support can be attached by means of the respective counter clasps 212 (see Fig. 5) and 214.

Figure 5 shows only one supporting part 216 of the crane, to which a load supporting part 218 is attached, e.g. by bolts or the like, in a section corresponding to pairs of 204.206 and 208.210 cranks, respectively.

The advantage of attaching the load carrier 218 by means of screws or similar means to the load carrier 216 is that, when the length of the supporting device is changed transversely to the underbody 150, e.g. by inserting intermediate elements, the load carrier 218 can be reattached to the supporting device in a position corresponding to the pairs of locks 204.206 and 208.210 respectively.

The embodiment of the housing device 152 described in Figures 5 and 6 has the advantage that there are no components extending beyond the upper edge of the chassis 150; thus the freedom of movement or rotation of a chassis mounted on the chassis is not restricted and the chassis can be deflected backwards by 180°, for example, so that work can also be carried out behind the excavator.In addition, when the crane is dismantled, there are no components which extend laterally beyond the excavator's 160.162 crawler heads, so that no further arrangements need to be made or components removed by the excavator for transporting the excavator equipped with the crane 152. This significantly reduces the time of installation of the crane at the crane 152.

With reference to Figures 7 and 8, a third preferred embodiment of the restraint of the present invention is described below. Figure 7 shows a view of a front section of a straight caterpillar chain suspension 240 with a partial break in the upper part of the caterpillar chain 242. The caterpillar chain suspension 240 runs on a suspension frame 244 which is firmly connected to the excavator's undercarriage. On an outer side area 246 of the suspension frame 244 an upper reinforcement plate 248 is securely attached, e.g. by welding. On the upper reinforcement plate 248 a number of fixed anchorages 250 are fixed by twisting a 252 mm mounting base 252 apart. A 252 mm mounting base 252 is attached to the bottom of the 252 mm mounting base 254 and a rotating mounting base 256 is attached to the first section of the 254 mm mounting base. A rotating mounting base 252 is attached to the bottom of the 254 mm mounting base 252 and a rotating mounting base 254 is attached to the first section of the 254 mm mounting base 252 and a rotating mounting base 254 is attached to the bottom of the 254 mm mounting base 252 and a rotating mounting base 254 is attached to the first section of the 254 mm.

In the area of the second ends 266.268 of the upper swing arm 254 and the lower swing arm 256, these are connected by a swiveling connecting plate 272 fixed to a support 270 of a non-shown swinging device. At the connecting plate 272 there are 254.256 pairs of fasteners 274 for the upper and lower swing arm respectively. Between the fasteners 274 and 276 respectively, a terminal section of the lower swing arm 256 and the upper swing arm 254 respectively is placed. Bolts 278 for the lower swing arm and a bolt 280 for the upper swing arm each provide openings in the whole fastening plate 274 and 276 respectively and 256 and 256 respectively, and the rotor arm 254 and 254 respectively are placed in a single direction (connector) and form a single connection between the swing arm and the swing arm.

The connection of the connecting plate 272 to the supporting part 270 is made, as in the figure 5, by 282 angular elements fixed to the supporting part 270 each, in which bolts cut through 284 openings in the angular elements 282 and the connecting plate 272 and thus fix the supporting part 270 to the connecting plate 272.

The mounting plate 252 also contains a cylinder unit 286 which is mounted on a cylinder support 288 and one of its parts, e.g. the cylinder part, is capable of being moved. With another part, e.g. a piston rod part 290, the cylinder unit 286 is connected to the lower swing arm 256 in a way that is capable of being moved. As can be seen in particular in Figure 7, for this purpose the upper swing arm 254 is further from the mounting plate 252 and hence the chassis frame 244 in a lateral direction than the lower swing arm 256.

For example, the cylinder unit 286 is a hydraulic cylinder unit for raising and lowering the parallelogram line for the crankcase provided by the 254.256 swing arm and the 272 connecting plate. It is advantageous, as shown in Figures 7 and 8, if the cylinder unit 286 attaches to the crankcase in the area of a middle section 257 of the lower crankcase 256. This ensures, on the one hand, that the leverage for raising the crankcase by the lower crankcase 256 with the load from the upper crankcase does not exceed the force applied by the 286 cylinder unit, and, on the other hand, that the smaller cylinder unit 286 is not subjected to a short-range effect by the crankcase, which is not allowed to extend beyond the maximum height of the crankcase, according to the total length of the crankcase provided by the smaller crankcase.

For the transport of the excavator fitted with the third-preferred design's support, bolts 278 and 280 are released from the upper and lower swing arms on each side of the undercarriage, so that the connection of the upper and lower swing arms 254.256 is released from the connecting plate 272 and thus the direction of the excavator, thus ensuring that no components, such as the swing arm, extending laterally beyond the upper swing arm are connected to the excavator, so that the overall width of the excavator allows transport on public roads.

As can be seen from Figures 7 and 8, the upper swing arm 254 is adjustable in one of its end segments by means of known screw elements in its length, so that in the case of a crane mounted on the excavator the angle of the crane relative to the excavator can be adjusted.

The structure of the crane not shown in Figures 7 and 8 corresponds essentially to that of the crane described in Figures 1 to 4 and the hydraulic fluid supply to the cylinder unit 286 not shown or described in these figures corresponds essentially to that of the crane lifting and lowering units shown in Figures 1 to 4.

The combination of an excavator and a pulley in accordance with the invention creates a cost-effective way of producing load layers. Since excavators are always available on road or railway construction sites for working the subsoil and for a variety of other tasks, these excavators can also be used by attaching a pulley unit to produce the load layers. This eliminates the need to provide additional equipment which then has to be transported to the construction site to produce the load layers and then transported back from the construction site after the work has been completed. The total cost of producing one of the entire load layers or the construction costs and the maintenance costs of the construction park are reduced considerably.

No additional equipment is required, such as an additional excavator, which unloads the material to be processed from a truck before the load layer is finished and distributes this material already on the subsoil, which means an additional cost reduction.

The excavator used in the combination of the invention is capable of exerting a very high pressure on the substrate to be worked by means of the crusher, so that the combination of the invention produces uniform and highly compacted layers of load.

Claims (32)

1. Road bed finisher for applying a compressed uniform road bed or similar onto a foundation base comprising a finisher beam (52) and a metering slide valve disposed in front of the finisher beam (52), characterised in that the road bed finisher comprises a combination of a digger (10) with an auxiliary device (34), whereby the digger (10) comprises a substructure (14; 150) with a travelling gear (31) and a superstructure (12) rotatably arranged on the substructure (14; 150), and whereby on the substructure a first holding means (38, 40; 152; 239) is provided, to which the auxiliary device (35) may be selectively attached and removed from this, whereby for application of the compressed uniform road bed or similar onto the foundation base a digger shovel (24) is arranged on the digger arm (16) and whereby the auxiliary device (34) comprises the finisher beam (52) and the metering slide valve (110) in such an arrangement that a material discharge region disposed in front of the metering slide valve (110) lies in the working range of the digger shovel (24).
2. Road bed finisher according to Claim 1, characterised by a vibrating means (34) comprising the finisher beam (52) with an assembly base (42) which may be coupled onto the holding means (38, 40) with hook sections (44).
3. Road bed finisher according to Claim 2, characterised in that the first holding means (38, 40) comprises a holding plate (40) arranged on the front side (36) of the substructure, and that a counter-plate (42), which abuts against the holding plate (40) when the vibrating means (34) is assembled, is provided on the vibrating means (34), and that at least one hook-like section (44) engaging over an upper edge (48) of the holding plate is provided in the region of an upper edge (46) of the counter-plate (42).
4. Road bed finisher according to Claim 2 or 3, characterised in that the counter-plate (42) may be fixed by a plurality of screw connections (50) to the holding plate (40).
5. Road bed finisher according to Claim 3 or 4, characterised in that the vibrating means (34) is connected to the counter-plate (42) by at least two pairs of swivel arms (56, 58), which are arranged one above the other and spaced laterally from one another and which are attached to swivel on the counter-plate in the region of one of their ends (72, 73) and in the region of their other ends (64, 65) to swivel on the vibrating means (34) and provide a parallelogram-type guide means for the vibrating means (34).
6. Road bed finisher according to Claim 1, characterised in that the first holding means comprises:

   - at least two laterally spaced support plates (156, 156', 158, 158') extending forwards from a front side of the substructure (150),

   - a vibrating means support (180), which is respectively articulated to the support plates (156, 156', 158, 158') via swivel joints, extends in front of the substructure (150) and the travelling gear (150, 162) in a direction transverse to the substructure (150), and to which the finisher beam may be selectively attached.
7. Road bed finisher according to Claim 6, characterised in that carrier plates (178, 178'), which are respectively allocated to the support plates (156, 156', 158, 158') on the substructure (150) and extend vertically and towards the substructure (150), provided on the vibrating means support (180), and that the swivel joints respectively comprise a lower swivel arm (188) attached to swivel on the lower section (184) of the support plates (156, 156', 158, 158') and on the lower section (194) of the carrier plates (178), and also an upper swivel arm (170) attached to swivel on the upper section (168) of the support plates (156) and on the upper section of the carrier plates (178), said upper swivel arm being arranged essentially parallel to the lower swivel arm (188) and with this forming a parallelogram-type guide means for the vibrating means (180).
8. Road bed finisher according to Claim 7, characterised in that each swivel joint additionally comprises a first cylinder unit (196), and that the first cylinder unit (196) is attached at one of its ends to the support plate (156) to swivel on this in the region of the articulation of the lower swivel arm (188), and at its other end is attached to the upper swivel arm (170) in the region of its articulation to swivel on the carrier plate (178).
9. Road bed finisher according to one of Claims 6 to 8, characterised in that the length of the vibrating means support (180) in the transverse direction of the substructure (150) is smaller than or equal to the maximum width of the substructure (150).
10. Road bed finisher according to one of Claims 6 to 9, characterised in that coupling elements (204, 206, 208, 210) are provided in the region of outer ends (200, 202) of the vibrating means support (180) in the transverse direction of the substructure (150) for fixed coupling of the vibrating means support (180) to the finisher beam.
11. Road bed finisher according to Claim 1, characterised in that the first holding means comprises swivel means, which are attached respectively on the side faces (246) of the travelling gear frame (244) of the travelling gear facing away from the substructure (150), and which may be selectively coupled firmly to the finisher beam.
12. Road bed finisher according to Claim 11, characterised in that the swivel means comprise upper (254) and lower (256) swivel arms (254, 256), which are respectively articulated to the travelling gear frame (244) at one of their ends and are spaced vertically from one another, and which may be selectively coupled firmly to the finisher beam in the region of their other ends to provide respective parallelogram-type guide means for the finisher beam.
13. Road bed finisher according to Claim 12, characterised in that additionally each of the swivel means respectively comprises a first cylinder unit (286), which is coupled to the upper or the lower swivel arm (254, 256), on the one hand, and to the travelling gear frame (244), on the other hand, for selective raising and lowering of the finisher beam.
14. Road bed finisher according to Claim 13, characterised in that the upper swivel arm (254) is spaced further from the travelling gear frame (244) in a transverse direction of the substructure than the lower swivel arm (256), and that the first cylinder unit (286) is coupled to the lower swivel arm (256).
15. Road bed finisher according to Claim 13 or 14, characterised in that the cylinder unit (286) acts on the upper or lower swivel arm (254, 256) in a central section (257) thereof.
16. Road bed finisher according to Claim 13, 14 or 15, characterised in that the upper or lower swivel arm (254, 256) of each swivel means as well as the associated first cylinder unit (286) are respectively disposed to swivel on an assembly plate (252) which may be attached to the travelling gear frame (244).
17. Road bed finisher according to one of Claims 15 to 16, characterised in that the upper and/or the lower swivel arm (254, 256) is/are adjustable for adjustment of the angle position of the finisher beam relative to the substructure.
18. Road bed finisher according to one of the preceding claims, characterised in that the finisher beam (52) comprises a vibrating beam (52) with a vibrator plate (106) and at least one vibrator (108), and that a first cylinder unit (80) is provided, by means of which the vertical position of the vibrating beam (52) relative to the digger (10) is adjustable.
19. Road bed finisher according to Claim 18, characterised in that the vibrator plate (106) is held on a frame (102) of the vibrating beam (52) with rubber-elastic elements (104) interposed.
20. Road bed finisher according to Claim 18 or 19, characterised in that the metering slide valve (110) may be adjusted in its vertical position relative to the finisher beam (52) by a second cylinder unit (114).
21. Road bed finisher according to Claim 20, characterised in that the first and second cylinder units (80, 114) as well as the at least one vibrator (108) may be operated hydraulically.
22. Road bed finisher according to Claim 21, characterised in that a secondary drive shaft is provided on a digger motor arranged on the superstructure of the digger, and that a hydraulic pump may be driven by the secondary drive shaft for hydraulic operation of the first and second cylinder units and the at least one vibrator (108).
23. Road bed finisher according to Claim 22, characterised in that the hydraulic pump is a triple pump, whereby one pump part serves to operate the first and second cylinder units, one pump part serves to drive the at least one vibrator, and one pump part serves to drive the travelling gear.
24. Road bed finisher according to Claim 22 or 23, characterised in that hydraulic line connections are provided on a front side of the superstructure to connect the hydraulic pump to the first and second cylinder unit and the at least one vibrator, and that swivel angle restriction means are provided on the superstructure in order to restrict the swivel angle of the superstructure to a predetermined value.
25. Road bed finisher according to Claim 22 or 23, characterised in that a hydraulic pressure line passage is provided in a slewing crown of the digger for guidance of hydraulic pressure lines from the hydraulic pump to the first and second cylinder units.
26. Road bed finisher according to Claim 21, characterised in that a diesel aggregate (116) and a hydraulic pump (117) driven by the diesel aggregate (116) are provided on the substructure (14) for operation of the first and second cylinder units (80, 114) and the at least one vibrator (108).
27. Road bed finisher according to Claim 22, characterised in that on a rear side (118) of the substructure (14) a second holding plate (122) is provided, against which a support (125) for the diesel aggregate (116) and the hydraulic pump (117) with a counter-plate (126) abuts, and an upper edge of the second coupling plate (122) has a hook-type section (130) engaging over it.
28. Road bed finisher according to Claim 27, characterised in that the support (125) may be fixed to the second holding plate (122) by at least one screw connection (132).
29. Road bed finisher according to Claim 27 or 28, characterised in that the hydraulic lines are directed from the hydraulic pump to the first and second cylinder unit (80, 114) and to the vibrator (108) respectively along the underside of the substructure (14).
30. Road bed finisher according to one of Claims 2 to 29, characterised in that the vibrating means (34) is provided with coupling elements (79) for selective coupling to the digger arm (16).
31. Road bed finisher according to one of the preceding claims, characterised in that the travelling gear (31) comprises a caterpillar track travelling gear (32; 160, 162; 242) with two caterpillar tracks respectively provided on the sides of the substructure (14; 150).
32. Process for the production of a compressed uniform road bed or similar on a foundation base by means of a road bed finisher, comprising a digger (10), which is constructed with a substructure (14; 150) with travelling gear (31) and a superstructure (12) rotatably disposed on the substructure (14; 140) with digger arm (16) and digger shovel (24), and which is additionally provided with a finisher beam (52) attached to the substructure (14; 150) and a metering slide valve (110) disposed in front of the finisher beam (52), comprising the steps:

    a) unloading the road bed material in a material discharge region in front of the metering slide valve,

    b) distributing the road bed material in front of the metering slide valve (110) by means of the digger shovel (24),

    c) metering the material by means of the metering slide valve (110) and compressing the material by means of the finisher beam (52) during a forward movement of the digger (10) towards the unloaded and distributed road bed material.