DK142178B - Asphalt Paver. - Google Patents

Description

(11) PUBLICATION MANAGEMENT 142178 DENMARK d> None · E 01 C 19/40 '(21} Note 5562/77 (22) Filed on 14 Dec 1977 (24) Lebedeg 14 Dec 1977 (44) The application submitted and presented in 15 * S βρ · 1 9θ0

DIRECTORATE OF

THE PATENT AND TRADEMARK BASIS (30> Pr, omet h® «8 * ®1 Fri (71) AS PH / NIX, 6600 Vejen, DK.

72) Inventor: Svend Højbjerg, Mercurvej 4, 6600 Vejen, DK.

(74) Plenipotentiary in the proceedings:

Hofman-Bang & Boutard Engineering Company.

(54) Asf alt paver.

The invention relates to an asphalt paving machine with a vibrating smoothing and compressing unit, usually referred to as the rear body of the machine. This is arranged to compress and smooth the asphalt web to be laid by means of the machine, there being in front of the rear body means for distributing asphalt material which is straightened to a flat web by means of a scraper plate before the asphalt material is compressed and smoothed by means of of the hindquarters.

Rear bodies are known which have a relatively slow-moving stomping rail, which is arranged at the front of the rear body, and which are caused to move in a plane perpendicular to the longitudinal direction of the tarmac.

2 142178

There are also rear bodies where a plate, the iron, is caused to vibrate rapidly in the vertical direction, and finally there are rear bodies where a combination of the said compression and smoothing units is used.

It has become commonplace that the rear body of the asphalt paving machines of the kind in question can be extended to the side, so that the width of the laid asphalt track can reach up to 12 meters. Thereby, a problem arises, since in the known machines there are only vibration generating members on the main rear body and not on the coupled extensions, the known machines being built up as a rigid unit, which means that standing oscillations can occur in the wide rear body. which thereby vibrates a maximum of some places and does not vibrate anywhere else at all. This results in undesirable inhomogeneity in the asphalt web.

The object of the invention is to provide an asphalt paving machine which results in a uniformly compacted and smoothed asphalt track.

This object is achieved by the fact that the machine is designed as claimed in the characterizing part of the claim, the said standing oscillations in the rear body being prevented by dividing it into a number of vibration independent sections.

By the measures set out in claim 2, it is obtained that the amplitude of vertical vibration is greatest at the front edge of a section where the asphalt material is loose, while the amplitude is smaller at the rear edge of the section where the asphalt material is compressed.

Since each section can vibrate parallel to the longitudinal direction of the tarmac, the oscillators at the leading edge and at the trailing edge must allow equal amplitudes in the longitudinal direction of the tarmac, which is conveniently obtained by the construction of claim 3.

By means of the measures specified in claim 4, the amplitude at the leading edge of the section is further increased compared to the amplitude at the rear edge of the section.

3 142178

The uniformity of the asphalt web can be further improved by the measures set out in claim 5, this form of a scraper plate in connection with said vibration acts both as a leveling rail for the asphalt material and also acts as a plow which sets the asphalt material in a rotating motion. so that it is not the same material that constantly accumulates in front of the scraper plate. Thus, a uniform temperature will be achieved for the laid asphalt material, thereby making the asphalt web more uniform.

The baffles mentioned in claim 6 further improve the even distribution of the asphalt material before compressing and smoothing.

The invention will be explained in more detail by the following description of an embodiment of an asphalt paving machine according to the invention, with reference to the drawing. 1 is a side view of the asphalt paver; FIG. 2 is a schematic rear view of the asphalt paver machine; FIG. 3 shows a section along line III-III of FIG. 2, through an embodiment of the machine according to the invention, while fig. 4 shows an embodiment of the vibration generating means.

FIG. 1 schematically shows a known asphalt laying machine, comprising a vehicle 1 with a driving machine, which is preferably arranged partly to drive the asphalt laying machine forward in the direction of arrow K, and partly adapted to produce hydraulic pressure for controlling the moving parts which will later be mentioned. The machine is controlled from a control desk 2 and has at the front a loading platform for picking up asphalt material 3 which, by means of a conveyor belt in the machine, is brought down to a auger 4 for distribution of asphalt material in front of a rear body 5 over its entire width, which compresses and smooths the asphalt material. for a finished asphalt track. The rear body 5 is fixed on both sides of the machine to an arm 6, the free end of which is pivotally mounted to the bottom frame of the machine so that the height of the rear body 5 can be adjusted by means of a hydraulic cylinder 7 for each arm. shown embodiment symmetrically about the machine's median plane M (Fig. 2) in the direction of travel and "each side of this center line consists of a so-called main iron 8 and a side iron 9, which can be moved to the side outside the main iron, for example by hydraulics. 8's side boundary to increase the width of the laid asphalt track.

FIG. 2, to the left of the central plane M of the machine, shows a main and side iron 8 and 9, respectively, with the side iron 9 being moved out to the left. The main iron 8 is supported by a rigid frame 10 which is attached to the arm 6 which extends rearwardly relative to the frame 10 for the purpose of guiding and carrying a rigid frame 11 of the lateral iron 9 so that it is movable parallel to the main iron 8 immediately behind this. This is achieved by attaching one or more smooth shafts 18 to the ends of the frame 11 which are adapted to slide into associated bushings at the end of the arm 6. By means of hydraulic movement means not shown, the frame 11 can be moved to a desired ratio. to the frame 10 displaced position between an outer position where the laid asphalt web has maximum width relative to the middle plane M and an inner position where the width of the asphalt web is determined by the main iron. The frames 10 and 11 and the corresponding frames on the right-hand side of the median plane M are closely interconnected under all conditions, and according to the invention the smoothing and compression unit of the machine is divided into a number of sections, in the embodiment shown, so that for each frame a separate smoothing and compression section 12, 13, which is connected to the associated frame 10 and 11 respectively via a plurality of vibration dampers, of which in FIG. 2 can be seen two vibration dampers 14 and 16 for the section of the main iron and two vibration dampers 15 and 17 for the section of the side iron. Each section has separate vibration generating means and by means of the vibration dampers the vibrations of each section are prevented from interacting and propagating to the other part of the machine via the arms 6. The sections have such size,. that no standing oscillations with nodes occur in them, so that the asphalt material is uniformly affected by the entire underside of the section, and that the vibrations do not propagate to the rest of the machine, the wear on the machine is reduced.

5 142178

FIG. 3 shows a section along line III-III of FIG. 2 through a vibration damper consisting of a front vibration damper 17A and a rear vibration damper 17B. FIG. 3 could indicate for the smoothing and compression section 13 a corresponding section through any of the sections, while the upper frame 11 belongs to one of the side extension sections, two smooth shafts 18, 19 bearing the section 13 being shown and arranged for sliding into bushings which are fixedly positioned relative to that of FIG. 2. The bushings will preferably not extend outside the main iron 8, so that the length of the smooth shafts 18, 19 is a bit longer than the frame 11, which corresponds to the length of the bushings.

A smoothing and compression section such as that of FIG. 3 has a front concave scraper plate 20, as well as a smooth smoothing and compression plate 21 at the bottom. The scraper plate 20 and the bottom plate 21 are stiffened by plates, of which the plate 22 is shown, and a longitudinal profile 23, which carries a vibration generating means 24, which comprises rotating, eccentric weights rotating in the direction indicated by the arrow P, whereby the section 13, a vibrating motion in both the horizontal and vertical seals of FIG. Third

According to the invention, the section 13 is suspended in a vibration-damping manner relative to the frame 11, which is obtained by vibration dampers, where all vibration dampers located in the leading edge are designed as the one shown in FIG. 3, while all the rear vibration dampers are designed as the vibration damper 17B shown. The vibration damper 17A consists of a sleeve 25 secured to the stiffening plate 22, in which there is an elastic cuff 26 with a bore for a shaft 27 which is fixed at the ends to a pair of flanges, of which the flange 28 is shown, on the frame 11. The vibration damper 17B also consists of a bushing 29 which is secured to a flange 30 of the frame 11.

Inside the sleeve 29 is an elastic cuff 31 with a bore for a shaft 32, the ends of which are housed in the branches of a fork 34, of which the branch 33 can be seen. The fork 34 has a rotatable threaded pin 35 for cooperating with an internal thread at one end of a clamping piece 36, the other end of which is formed.

D

as a fork, the branches of which the branch 37 can be seen extend on either side of the support plate 22 and are pivotally attached thereto by a shaft 38. Thus, the section 13 is pivotally suspended for horizontal movements in FIG. Third

According to the invention, the sleeve 26 is made of a more elastic material than the material of which the sleeve 31 is made, which means that the vibration amplitude may be greater at the leading edge of section 13 than the vibration amplitude may be at the rear edge of section 13. Since the vibration damper 17B is pivotally suspended with respect to horizontal movements in FIG.

3, this will cause the rigid section 13 to be damped only for horizontal vibrations by the vibration damper 17A, while the vibration damping for vertical movements allows a greater vertical amplitude at the leading edge of the section 13 than at its trailing edge. This is an advantage as the asphalt material is looser at the leading edge of section 13 than it is at the trailing edge, and by properly adjusting the total length of the fork 35 and clamp 36, an optimal, even compression of the asphalt material is achieved. The horizontal plate vibration movement of the base plate 21 causes a smoothing of the tarmac, making it very even.

In connection with FIG. 4, the vibration generating means 24 will be further described. These means comprise a shaft 40 which extends over most of the length of an associated smoothing and compression section and is rotatably mounted relative thereto by bearing brackets 4, 42 attached to the profile plate 23, also shown in FIG. 3. The shaft 40 is driven around via a V-belt pulley 45 and a motor not shown, and has in the vicinity of the bearing blocks 41, 42 similar eccentric devices 43, 44. Each of these devices comprises a flange 46 and a corresponding flange 47 attached to the shaft 40. , between which flanges are arranged two identical washers 48, 49 and associated bores eccentrically located bores for the shaft 40 of each disk 40. Each disk 48, 49 has a number of through holes for receiving bolts 50, 51 »which extend through the flanges 47, 48 so that the eccentric washers 48, 49 can be clamped between the flanges 46 and 47 with a desired, angular rotation predetermined by the placement of the through holes in the washers 48, 49. The effective 43 eccentricity can thus be varied, e.g. depending on the properties of the asphalt material used, by pulling out the bolts 50, 51 and rotating the discs 48, 49 between them until a new set of holes in the discs aligns with the holes in the flanges 46, 47. bolts 50, 51.

As the shaft 40 rotates in it by the arrow P in FIG. 3, the entire section 13 will perform a vibrating, rotary motion, the amplitude of which is determined by the devices 43, 44fs eccentricity and the effect of the vibration dampers. As previously mentioned, the vibration movement at the front of the section 13 is not the same as the vibration movement at the rear edge of the section, since the front of the section 13 performs vertical movements whose amplitudes are greater than the vertical movements at the rear edge. This advantageous distribution of the vertical movement pattern is further enhanced by the shaft 40 being positioned so that its distance to the oscillation damper 17A is less than the distance to the oscillation damper 17B.

The described vibrational movement achieved by the machine according to the invention can be utilized to further improve the uniformity of the asphalt web, the movement pattern of the front of the section 13 in conjunction with the scraper plate 20 concluding that the asphalt material is not only transported to the outside of the section, but also is turned around so that it is not the same asphalt material that accumulates in front of the scraper plate 20 where it can lie and become cold. As the asphalt material is constantly turned around, the material compressed below the base plate 21 will have a uniform temperature, thereby making the finished asphalt web itself more uniform. The transport of the asphalt material in front of the scraper plate 20 can be further improved by providing the scraper plate with a number of inclined baffles, two baffles 52 and 53 of FIG. 3 · It will be seen from FIG. 3 shows that the guide plates extend from a location at the bottom of the scraper plate 20 and thence upwardly and away from the center line M (Fig. 2). The asphalt material is hereby transported so efficiently to the outside of the extension sections that it is not necessary to extend it in FIG. 1, conveyor auger 4 in addition to the width of the machine.

Claims (4)

In addition to the many advantages mentioned by the machine according to the invention, it also results in an improved working environment for the operators, the vibration damping resulting in a lower noise level. For the operator who is on a step board on the rear body 5 itself to check the quality of the tarmac, it will be a clear advantage that the step board does not vibrate vigorously, as is the case with known machines. 1. Asphalt laying machine having a vibrating smoothing and compressing unit, characterized in that the smoothing and compressing unit is divided into a number of sections, each of which is connected to the machine via vibration damping means and each having associated vibration generating means. Asphalt paving machine according to claim 1, characterized in that each smoothing and compression action in the front, calculated in relation to the laying direction of the machine, is connected to the machine by means of vibration dampers which allow vibration of the associated section in a plane perpendicular to the leading edge and that each section at the rear is connected to the machine by vibration dampers which are less resilient than the former vibration dampers perpendicular to the section smoothing and compression plane. Asphalt paving machine according to claim 2, characterized in that the front and rear pivot dampers are of the same kind, in which a shaft attached to the associated section parallel to its front edge extends through an elastic sleeve in a bushing attached to the machine. the respective shafts for rear oscillation dampers are connected to the section via an arm which is pivotal about the associated shaft. The asphalt paving machine according to any one of the preceding claims, wherein the vibration generating means comprises a rotary shaft with eccentric weights, which shaft is arranged in the main shaft.