EP0335339B1 - Basecourse finisher - Google Patents

Description

• einen Fertigerrahmen mit Fahrwerk;
• wenigstens eine Rüttelplatte oder -bohle;
• einen am Fertigerrahmen gehalterten Halterahmen für die wenigstens eine Rüttelplatte oder -bohle und
• eine Nivelliereinrichtung zur Lagenänderung des Halterahmens gegenüber dem Fertigerrahmen.

The invention relates to a base course paver comprising

• a paver frame with undercarriage;
• at least one vibrating plate or screed;
• a holding frame held on the paver frame for the at least one vibrating plate or plank and
• a leveling device for changing the position of the holding frame relative to the paver frame.

Base course pavers of this type are used, for example, to produce a fine planie. The leveling material tipped by truck in front of the paver is installed at a height of 5 to 10 cm, ie distributed, pulled off and compressed to approx. 95%, for example. Another field of application is the installation of an HGT layer (h ydraulich g ebundene ragschicht T) or ballast base layer thicknesses with fitted between about 15 to 20 cm, in turn, with distribution, stripping and compaction. After all, the base course paver can too can be used to level a fresh mortar layer (mixed in place), since mortar base layers often do not have sufficient evenness without the use of such a paver, especially at the edges.

Road pavers are known (DE-C-35 35 362), in which a vibrating plank is pulled by the paver. A trailing arm attached to the support frame for the vibrating screed is articulated to a height-adjustable hinge point of the paver frame during normal work. In this way, one obtains self-stabilizing, easy-to-control height leveling within certain limits, since a momentary rise in the screed, for example due to increased material accumulation, results in a reduction in the angle of attack (angle between the underside of the screed and the horizontal plane), with the result that that the "floating screed" cuts deeper into the material and automatically assumes a lower height level. Accordingly, if an increased layer thickness is desired, it is sufficient to raise the articulation point of the drag arm on the paver frame side. During a certain travel time, the screed is connected to the rigid frame via a lockable lifting cylinder.

However, such a paver structure is less suitable for a base course paver, mainly because the material to be installed is generally much coarser (e.g. coarse gravel) and premature wear of the augers or chains in the limited installation space between the trolleys and between the rear end of the two side trolleys and the vibrating or smoothing screed. The base course paver often also runs roughly if it accordingly sinks more or less strongly due to its weight on a more or less strongly solidified surface.

In contrast, the object of the invention is to provide a base course paver with a simple structure and improved function.

This object is achieved by a base course paver with the features of claim 1.

The vibrating plate or screed is now arranged in front of the undercarriage (or in front of the two lateral undercarriages), so that the leveling material can be spread out comfortably in front of the vibrating plate or screed without spatial restrictions, for example from a material-shedding vehicle or by means of it a simple distributor blade (claim 9). The wear on such a distributor blade is low; if necessary, the distributor blade can be replaced quickly and inexpensively. The vibrating plate or screed is still "floating", ie it assumes a height position which is essentially determined by the dynamic buoyancy forces generated by the paving material and defined by the angle of attack of the screed. However, since the screed is now pushed and not pulled as in known systems and thus represents a fundamentally unstable equilibrium system (if the screed is raised due to increased material, the angle of attack increases), one could have expected that this system could not be controlled. However, it has been found that in the arrangement according to the invention with essentially rigid, that is to say non-oscillating, attachment of the paver frame to the chassis (while maintaining the floating principle), that is to say to a certain extent by combining indirect and direct Screed control with the help of the corresponding quickly reacting leveling device a uniform paving thickness can be achieved. This also contributes to the fact that the base course paver runs on a self-leveling, leveled surface.

The essentially rigid, but optionally adjustable in height and inclination lever arrangement preferably comprises a main arm rigidly connectable to the holding frame, which is connected to the chassis frame via two spaced-apart, mutually inclined articulated levers. Due to the inclination between the two articulated levers, in contrast to a parallelogram linkage with articulated levers parallel to each other, there is a combined swivel-displacement movement when the position of the main arm relative to the paver frame.

It is particularly preferably provided that one of the two articulated levers forms a first angle between 20 ° and 70 °, preferably 30-60 °, in the region of the fastening point of the holding frame on the main arm with the essentially horizontally extending main arm, and that the other articulated lever with the Main arm forms a second angle between 160 ° and 180 °. Because of these angles, on the one hand there is a toggle lever effect in the area of the other articulated lever, so that the actuating forces for changing the position of the main arm can be relatively low, especially when a first piston-cylinder arrangement acts on the main arm in the area of the other articulated lever in the sense of a change of the second angle. On the other hand, the specified orientation of the one articulated lever with a corresponding main arm length readily results in the desired increase in the angle of attack when the holding frame is raised and reduction in the angle of attack when the holding frame is lowered. The desired height of the holding frame is thus directly through without delay Swiveling the hinge arrangement adjusted, while at the same time the "floating" support of the vibrating plate or screed on the base layer is maintained by adjusting the angle of attack, so that uniform strengthening quality with manageable forces between paver frame and holding frame is guaranteed.

In order to obtain a compact transport unit with the possibility of driving laterally onto a low loader, since the usual transport width is not exceeded, it is proposed that the holding frame be pivotable between a working position and a transport position.

In order to facilitate the conversion, a second piston-cylinder arrangement is preferably provided for pivoting the holding frame between the working position and the transport position, which engages at one end on the holding frame and at the other end on the main arm.

Of particular advantage is the further development of the invention, characterized by a pivoting part hinged to the main arm, the second piston-cylinder arrangement acting directly on the pivoting part for pivoting the pivoting part relative to the main arm, and which can optionally be coupled to the holding frame and to the one articulated lever. This pivoting part, which can be coupled in between the main arm and the articulated lever and can be actuated by the second piston-cylinder arrangement, enables the position of the articulated arm-side joint of the one articulated lever to be changed relative to the main arm. In this way, for example, the main arm placed on the paver frame in the transport position can be raised. The angle of inclination between the two articulated levers can also be optionally changed to change the relationship between the height and the angle of attack of the vibrating plate or screed.

In order to keep the transport width small even when a guide and drive device for the distributor blade is provided, it is proposed to design the guide and drive device to be displaceable between a working position and a transport position. For this purpose, the guide and drive device are preferably provided with support spars extending in the direction of displacement, which are slidably attached to the paver frame and are preferably divided into at least two removable length segments. The length segments protruding from the base layer when the guide and drive device are pushed in at the rear end can thus be removed.

In a particularly preferred embodiment of the invention, at least one vibrating screed is provided in the area of the two side carriages and at least one vibrating plate in the area in between. The vibrating or smoothing screed in the undercarriage area, which is driven particularly by pulse hydraulics, ensures a high compaction of the base course, so that the trailing undercarriage does not destroy the base course. In the area in between, however, the use of vibrating plates is sufficient. Compared to vibrating planks, their simple design means that they are much cheaper to buy and, moreover, less prone to wear.

Since vibrating plates are generally less sensitive to changes in the angle of attack than vibrating screeds, the use of at least one metering slide movable in a substantially vertical direction is proposed, at least in front of the vibrating plate. A further development of the invention which is characterized by an extremely simple construction and reliable function is characterized by a probe arm, the front end of which is articulated on the metering slide and at the rear end of which a tracing head lying behind the vibrating screed or plate and resting on the base layer is attached, as well as a probe arm inclination determining device which is connected to a control device for a metering slide adjusting drive. Due to the articulation of the probe arm on the metering slide, its inclination depends both on the respective actual leveling height of the base layer behind the vibrating plate and on the current metering slide height. As a result, the circuitry complexity for controlling the metering slide adjustment drive is reduced, in particular if an essentially vertically extending switching rod is provided for actuating at least one switch, this switching rod being connected to the latter in the region between the ends of the sensing arm. If, for example, this switch is actuated behind the vibrating plate when a predetermined level is exceeded, it is sufficient to let the metering slide adjustment drive run until the switch has been released again after the metering slide has been lowered accordingly.

A third piston-cylinder arrangement is preferably provided as part of the metering slide adjustment drive, which acts on one end on the holding frame and on the other end on the metering slide.

• Fig. 1 eine vereinfachte Seitenansicht eines erfindungsgemäßen Tragschichtfertigers in Transportstellung;
• Fig. 2 eine vereinfachte Seitenansicht des Tragschichtfertigers gemäß Fig. 1 während des Umbaus in die Arbeitsstellung;
• Fig. 3 eine vereinfachte Seitenansicht des Tragschichtfertigers gemäß Figuren 1 und 2 in der Arbeitsstellung;
• Fig. 4 eine Draufsicht auf den Tragschichtfertiger gemäß Fig. 3 und
• Fig. 5 eine seitliche Detailansicht des Tragschichtfertigers im Bereich einer Rüttelplatte.

The invention is explained below using preferred exemplary embodiments with reference to the drawing. It shows:

• Figure 1 is a simplified side view of a base course paver according to the invention in the transport position.
• FIG. 2 shows a simplified side view of the base layer paver according to FIG. 1 during the conversion into the working position;
• 3 shows a simplified side view of the base layer paver according to FIGS. 1 and 2 in the working position;
• Fig. 4 is a plan view of the base course paver according to Fig. 3 and
• 5 shows a detailed side view of the base course paver in the area of a vibrating plate.

The base layer paver 10, shown in simplified form in the figures, comprises a paver frame, generally designated 12, which carries the required paver aggregates and on which lateral crawler tracks 14 for moving the base layer paver are arranged on the respective subsurface. A driver's seat 16 is arranged on the paver frame 12, for example, and a diesel engine 18 for driving both the lateral crawler tracks 14 and an oil pump for the hydraulics of the base layer paver 10. The direction of travel of the base layer paver 10 during the compaction and leveling work is shown in FIGS. 2, 3 and 5 from left to right (arrow A) and in Fig. 4 from top to bottom.

To carry out the leveling and compaction work, two side vibrating planks 22 are provided on the base course paver 10 within a holding frame 20 running in the horizontal direction transverse to the direction of travel A, and a vibrating plate 24 in a central section. The vibrating planks 22 are shown in FIG. 4 with a dash dot Line indicated. You can see that these extend from the two outer ends of the holding frame 20 into a central area occupied by the vibrating plate 24 between the two crawler tracks 14. Since these vibrating screeds 22, which can also be referred to as high compaction screeds with pulse hydraulic operation, ensure a strong compaction of the base course material to approx. 95%, the base course paver with its two crawler tracks 14 can drive safely on the base course thus produced. The vibrating plate 24, shown in more detail in FIG. 5 in connection with a metering slide height control, generally delivers less compressed base layer material. However, the degree of compaction is generally completely sufficient, especially since in many cases the base layer is then rolled. Since the wear of the coarse-grained and sharp-edged base layer materials to be processed is an essential aspect, the use of the vibration plates, which are far less susceptible to wear, is advantageous.

The holding frame consists of two horizontal T-beams 26 which are parallel to one another and run transversely to the direction A and have connecting plates 28 connecting both at least on both longitudinal ends. The connecting plates 28 recognizable in FIG. 4 at both ends of the paver frame are pulled forward (in direction A) in order to form lateral boundaries for the base layer bulk material to be unloaded from the leading truck.

Between these plates 28 in front of the vibrating planks 22 and the vibrating plate 24, a distributor blade 30 can be moved back and forth in the transverse direction. This distributor blade can comprise, for example, three vertical blade plates 32 which are parallel to one another and run in direction A. The distributor vane 30 is guided over a head 36 which is displaceably displaceable in the transverse direction along a tube 34. The distributor vane 32 can be adjusted in height a piston-cylinder arrangement 38 can be provided on the head 36, the piston 40 of which acts on the distributor blade 30. The head 36 can be moved back and forth in the transverse direction (double arrow B) by means of a traction cable 44 which is guided in a closed loop via lateral deflection rollers 42 at the two ends of the tube 34 and is indicated in FIG. 4 by a dash-dot-dot line . A driven pulley 46 serving for the cable drive can be seen, for example, in FIGS. 3 and 4.

The tube 34 together with the head 36 and rope pulley 46 can be moved from the working position, which can be seen in FIGS. 3 and 4, for example, into the retracted transport position indicated in FIG. 1. For this purpose, two support bars 48, which extend in the direction of travel A and are displaceable in their longitudinal direction and are connected to the pipe 34 at their respective front ends, are attached to the paver frame. In order to prevent in the transport position according to FIG. 1 that the support bars 48 protrude rearward beyond the vehicle outline, a rear segment 50 of the two support spaces 48 is designed to be removable from the rest of the load compartment part. In Fig. 1, the segment 50 is indicated before dismantling or after attachment for preparation of the base course paver after transport for work.

The holding frame 20 is held on the paver frame 12 via a lever arrangement 51. This lever arrangement consists in each case of a main arm 52 and a first articulated lever 54 and a second articulated lever 56 and also a pivoting part 58 to the side next to the two crawler tracks 14. The two articulated levers are articulated on a longitudinal member 60 fixed to the frame, namely the front articulated lever 54 on an articulated projection 62 and the rear articulated lever 56 on an articulated projection 64 approximately in the region of the center of length of the longitudinal member 60. The effective length of the rear articulated lever 56 is about 3 to 5 times, preferably about 4 times, the effective length of the front articulated lever 54. The rear articulated lever 56 is directly articulated to the main arm 52, specifically via an articulated projection 66 projecting downward at the rear end of the main arm 52 The front articulated lever 54 is articulated to the triangular-shaped swivel part 58 (articulated bolt 68). The pivot part 58 is in turn articulated on the main arm 52 via a hinge pin 70. A hinge pin 72 forming the third triangle point connects a piston rod 74 of a piston-cylinder arrangement 76 to the swivel part 58. The cylinder 78 of the piston-cylinder arrangement 76 is articulated to the main arm 52 via a hinge pin 80. At the rear end of the substantially horizontally extending main arm 52, a piston rod 84 of a piston-cylinder arrangement 86 engages via a hinge pin 82, which runs essentially vertically upwards and whose cylinder 88 is connected via a hinge pin 90 to a projection 92 fixed to the frame.

If, in this arrangement, the piston-cylinder arrangement 88 is pressurized with pressure fluid, for example pressure oil, in the sense of extending the piston rod 84, the main arm 52 is increasingly tilted backwards, since its front end has a circular movement around a pivot pin 94 of the joint projection 62 is carried out (ascending branch when moving clockwise in FIG. 3) and its rear end executes a circular movement around a hinge pin 96 of the joint projection 64 (falling branch when moving likewise clockwise in FIG. 3). The prerequisite here is that the piston-cylinder arrangement 76 is blocked, so that the pivoting part 58 is rigidly coupled to the main arm 52. The front end of the main arm 52 is consequently raised while simultaneously lowering the rear end and thus increasing the angle of inclination between the longitudinal direction of the main arm 52 and the horizontal plane.

A corresponding lifting and pivoting movement in the clockwise direction of FIG. 3 also experiences the holding frame 20 together with the vibrating plate 24 and vibrating planks 22, since this is rigidly connected to the main arm 52 in the working position according to FIG. 3. As the comparison of FIGS. 1 to 3 shows, a head part 98 is articulated on the main arm 52 via the hinge pin 70. The head part 98 is rigidly connected to two tabs 100 and 102. The tab 100 which runs downward to the left in FIG. 3 is connected in an articulated manner to the right T-beam 26 of the holding frame 20 via a hinge pin 104. A spindle arrangement 106 engages the free end of the tab 102 which runs to the top left in FIG. 3, the other end of which engages the T-beam which is on the left in FIG.

In addition to the tab 102, a connecting plate 110 is rigidly attached to the head part 98 with two bolt holes 112 and 114. In the bolt hole 114 on the right in FIG. 3, a connecting bolt (not shown) is inserted for the rigid coupling of the head part 98 and thus the holding frame 20 with a fastening bracket 116 which is fixed to the main arm and projects upwards to the left in FIGS. 1 to 3.

The other bolt hole 112 is used for the optional connection with the swivel part 58 in the transport position according to FIG. 1. For this purpose, a removable connecting bracket 117 that can be seen in FIGS. 1 and 2 is connected at one end to the head part 98 via a corresponding connecting bolt to be inserted into the bolt hole 112 and at the other end connected to the swivel part 58 via a connecting bolt to be inserted into a bolt hole 118 of a fastening projection 120 fixed to the swivel part. To pivot the holding frame 20 relative to the main arm 52 by actuating the To allow piston-cylinder assembly 76, the hinge pin 114 between the mounting bracket 116 and the head part 98 must of course be released beforehand.

Starting from the transport position in FIG. 1 with the holding frame 20 pivoted upward about the hinge pin 70 and a transport width a of the base course paver 10, which is consequently determined only by the total length of the lateral crawler tracks 14, the piston is first converted to the working position according to FIG. Cylinder arrangement 76 actuated in the sense of extending the piston rod 74. As a result, the holding frame pivots counterclockwise in FIG. 1 (arrow C) around the hinge pin 70. Here, the main arm 52 rests on side support projections of the side member 60 in a manner not shown in detail. The articulated connection between the articulated projection 62 and the front articulated lever 54 is also currently loosened.

As soon as the bolt hole 114 of the head part 98 coincides with the corresponding bolt hole of the fastening bracket 116 in the course of the pivoting movement, the head part 98 is locked with the fastening bracket 116 by inserting a corresponding connecting bolt. The pivoting part 58 is now decoupled from the head part 98 by dismantling the connecting strap 117. As a result, the pivot part 58 is pivoted until the front articulated lever 54 can be coupled to the projection 62 by inserting the connecting bolt 94. Then, by actuating the piston-cylinder arrangement 76, the pivot part 58 is pivoted in the desired manner until the main arm 52 assumes its desired position above the articulated lever 54, 56.

In order to also be able to bring the distributor shovel together with the tube 34 and the cable drum 46 into the working position, the two additional length segments 50 at the rear end of the Support bars 48 attached and pushed forward with the support bars until the tube 34 is in the desired position.

In order to be able to regulate the supply of base layer material to the vibrating plate 24, a vertically movable metering slide 130 is provided in front of the vibrating plate 24 according to FIG. 5. This is held on a parallelogram linkage composed of two rods 132, 134 approximately parallel to one another on the right-hand T-beam 26 of the holding frame 20 in FIG. 5. The free end of a piston rod 135 engages the inside of the metering slide 130 via an articulated connection 137. The piston rod 135 is part of a piston-cylinder arrangement 136, the cylinder 138 of which is fastened to the T-beam 26 on the left in FIG. 5 via an angle iron 140. The double-acting piston-cylinder arrangement 136 is operated in a manner not shown by a pressure oil pump 142 of a hydraulic system. The pump 142 in turn is controlled by a controller 144. This receives position signals from at least one limit switch 146. This limit switch is actuated by a switching projection 148 at the end of a vertically upward shift rod 150. The switch rod 150 is in turn articulated at its lower end to a probe arm 152, in the region of its center length. The left end of the probe arm 152 in FIG. 5 is connected in an articulated manner to the lower rod 134 in the region of the metering slide end (pivot pin 154). The right end of the probe arm 152 in FIG. 5 carries a probe 160 which rests on the top of the support layer 162 after it has been processed by the vibrating plate 24.

The vibrating plate is connected to the two T-beams 26 via unbalance drives, not shown.

If too much base layer material is supplied to the vibrating plate 24, the base layer material subsequently swells upward on the vibrating plate 24. The probe 160 is raised and with it the switch rod 150. The switch contact 146 is then actuated, whereupon the controller 144 causes the metering slide 130 to lower. Simultaneously with this lowering movement, the switching rod also moves down again (by about half the distance in each case) until finally the switching projection 148 releases the switch 146 again and the pump 142 is immediately stopped again. Since the metering slide 130 is now lower, the vibrating plate 24 is supplied with correspondingly less base layer material.

A corresponding second limit switch can be provided below the limit switch 146 in order to cause the metering slide 130 to be raised when the base layer level is too low.

Claims (15)

1. A base course finisher (10) comprising

- a finisher frame (12) with a chassis (14);

- at least one riddling plate (24) or beam (22);

- supported on the finisher frame (12) and adapted to be rigidly connected to the finisher frame (12) a supporting frame (20) for the at least one riddling plate (24) or beam (22) and

- a levelling arrangement for varying the location of the supporting frame (20) in respect of the finisher frame (12),
characterised in that
the at least one riddling plate (24) or beam (22) is disposed in front of the chassis (14) in the region of the - in the direction of travel (A) - leading end of the finisher frame (12), and in that during compaction and levelling operation, an adjustable lever arrangement rigidly connects the supporting frame (20) to the finisher frame (12) and is optionally so adjustable by means of the levelling arrangement that at the same time it raises the supporting frame (20) and increases the angle of attack of the at least one riddling plate (24) or beam (22) or at the same time lowers the supporting frame (20) and reduces the angle of attack.

2. A base course finisher according to Claim 1, characterised in that the lever arrangement comprises, adapted to be rigidly connected to the supporting frame, a main arm (52) which is connected to the finisher frame (12) via two spaced apart articulating levers (54, 56) which extend at an angle to each other.

3. A base course finisher according to Claim 2, characterised in that one (54) of the two articulating levers (54, 56) is in the region of the point of attachment of the supporting frame (20) on the main arm (52) adapted to form with the substantially horizontally extending main arm (52) a first angle of between 20° and 70° and preferably 30 - 60°, and in that the other articulating lever (56) forms with the main arm (52) a second angle of between 160° and 180°.

4. A base course finisher according to Claim 3, characterised in that a first piston-cylinder arrangement (86) engages the main arm in the region of the other articulating lever (56) with a view to varying the second angle.

5. A base course finisher according to at least one of the preceding Claims, characterised in that the supporting frame (20) is pivotable on the finisher frame (12) between a working position and a transit position.

6. A base course finisher according to Claim 5, characterised by a second piston-cylinder arrangement (76) for pivoting the supporting frame (20) between the working position and the transit position which has one end engaging the supporting frame (20) and the other engaging the main arm (52).

7. A base course finisher according to Claim 6, characterised by, articulated on the main arm (52), a pivoting part (58) on which the second piston-cylinder arrangement (76) for pivoting the pivotable part (58) in respect of the main arm (52) directly engages and which can be optionally coupled to the supporting frame (20) and to the one articulating lever (54) which is articulated on the finisher frame (12).

8. A base course finisher according to at least one of the preceding Claims, characterised by in each case at least one riddling beam (22) in the region of the two lateral chassis (14) and at least one riddling plate (24) in the area in between.

9. A base course finisher according to at least one of the preceding Claims, characterised by a distributor blade (30) displaceable cross-wise to the direction of travel (A) and in front of the at least one riddling plate (24) or beam (22).

10. A base course finisher according to Claim 9, characterised in that a guide and drive means for the distributor blade (30) is constructed for displacement between a working position and a transit position.

11. A base course finisher according to Claim 10, characterised by, supporting the guide and drive means and extending in the direction (A) of displacement, supporting members (48) which are mounted for displacement on the finisher frame (12) and which are preferably subdivided into at least two demountable length segments (50).

12. A base course finisher according to at least one of the preceding Claims, characterised by at least one dispensing slide valve (130) adapted for movement in a substantially vertical direction and situated at least in front of the riddling plate (24).

13. A base course finisher according to Claim 12, characterised by a sensing arm (152), the front end of which is articulated on the dispensing slide valve (130) and at the rear end of which there is, trailing behind the riddling beam or plate and resting on the base course (162), a sensing head (160), together with a sensing arm inclination ascertaining device (146, 148) which is connected to a control device (144, 142) for a dispersing slide valve adjusting drive.

14. A base course finisher according to Claim 13, characterised by a substantially vertically extending shift rod (150) for actuating at least one switch (146) which is connected to the sensing arm (152) in the region between the ends thereof.

15. A base course finisher according to Claim 13 or 14, characterised by a third piston-cylinder arrangement (136) as a part of the dispensing slide valve adjustment drive which has one end engaging the supporting frame (20) while the other engages the dispensing slide valve (130).

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