EP2636794B1 - Large-scale self-propelled milling machine for machining road surfaces and method for machining road surfaces - Google Patents

Description

The invention relates to a self-propelled large milling machine for machining road surfaces according to the preamble of claim 1 and a method for machining road surfaces according to the preamble of claim 14.

As large milling machines, for example, road milling machines with a milling width of about 1500 mm and above are referred to. Such road milling machines have a high weight and are therefore usually carried by a chassis with crawler tracks. The milling drum is mounted on the machine frame between the crawlers of the front axle and the rear axle, at a distance from them. Large milling machines have a height-adjustable chassis with front and rear drives in the direction of travel, which form the front axle and the rear axle. The machine frame is carried by the landing gear, wherein between the axes of the front and rear drives a Fräswalzengehäuse is arranged on the machine frame having a single, rotatably mounted in the Fräswalzengehäuse milling drum. At the milling drum housing, a conveyor belt device for transporting the milling material processed and ejected from the milling drum is coupled in the direction of travel forward with the aid of a belt shoe.

Such a large milling machine is for example from the EP 2 011 921 A known.

The Fräswalzengehäuse is almost flush with an end face with an outside of the machine frame, the so-called zero side to allow the closest possible milling along edges or obstacles. The Fräswalzengehäuse is not height adjustable relative to the machine frame, so that the full machine weight can be transferred to the milling drum to allow high cutting forces and thus a high milling depth.

Large milling machines are u. a. because of their limited maneuverability so far mainly been used only for processing large areas, which also road curves with a large radius of curvature could be edited according to the road.

Particularly in the case of milling operations which lead inwards relative to the neutral side, there is the problem with large milling machines that the driver could not exactly follow a predetermined curve line with a tight curve radius. This is in the EP 2 011 921 a solution was removed, through which a visual inspection has been made possible for the steering of a large milling machine, whereby the maneuverability of a large milling machine could be improved.

For right-hand traffic, the neutral side of a road milling machine is preferably arranged on the right-hand side of the machine in the direction of travel. On roads with left-hand traffic, the null side is preferably on the left (in the direction of travel). It is understood that a large milling machine, if there is enough space for a turning maneuver can also be turned and thus a large milling machine with the zero side on the right in the direction of travel can be used for roads with left-hand traffic. This has the disadvantage that the road milling machine, which has its zero side on the right in the direction of travel, must drive against the flowing traffic, if a road during operation can not be completely disabled. Such a situation occurs, for example, when the left lane is to be milled flush with the left side of the road on a highway. The disadvantage here is that even the trucks that receive the milled material in front of the road milling machine, contrary have to drive the traffic flow in front of the road milling machine and have to drive away from there again. But even in the case of narrow streets is often the desire to edit the road either on the left or the right side flush, without having to turn the large milling machine.

For this it is for example from the DE 83 15 139 U provided in a road milling machine carried by a wheel gear, to move a single hydraulically driven milling drum transversely to the direction of travel, along sliding guides to a small stroke. It is not a large milling machine, with the high cutting forces can be realized because the milling drum is mounted pivotably about a horizontal axis and rests only by its own weight on the ground. The milling drum can therefore be raised or lowered relative to the machine frame and can additionally be pivoted about an axis extending in the vehicle direction in order to adapt to the road incline. The Querverschieblichkeit should allow precise control of the milling track. It is understood that due to this oscillating mounting of the milling drum no high cutting forces can be applied and such a router is only suitable for surface milling without high cutting depths.

From the US 3767262 is a road milling machine with a substantially over the entire working width of the machine extending milling drum is known, which is to reduce the curve radius of a cutting path to the inside of the curve in an outward position beyond the outer contour of the machine out.

This road milling machine is not a large milling machine, with the high cutting forces can be realized because the milling drum relative to the machine frame is height adjustable and can not support vertically rigidly directly to the machine frame.

Furthermore, from the EP 0 752 501 a road milling machine with a rotating milling drum for milling grooves or slots in road surfaces known. The milling drum is suspended at the rear end of the road milling machine transversely displaceable under a rail system. The milling drum can be transversely displaced along the rail system outside of the milling operation and is locked in one of several positions via a locking system during milling operation.

The invention has for its object to provide a self-propelled large milling machine of the type mentioned, and a method for editing road surfaces, which is universally applicable and their maneuverability is improved.

To solve this problem serve the features of claim 1 and 14th

The invention advantageously provides that the milling drum drive is a hydraulic or electric drive integrated in the milling drum, and that the milling drum is displaceable transversely to the direction of travel on the machine frame together with the milling drum housing fixed rigidly to the machine frame in the vertical direction and in the direction of travel is mounted, whereby optionally the zero side on the one outer side or on the opposite outer side of the machine frame can be fixed and wherein at the front edges of the milling drum additional chisel tools for transversely displacing the milling drum are provided during the milling operation.

The solution according to the invention has the advantage that substantially the entire weight of the machine due to the arrangement of the milling drum between the axes of the landing gear acts on the milling drum, whereby large cutting depths are possible at high speeds propulsion. Due to the displaceability of the milling drum, the zero side can be set either on the one outer side or on the opposite outer side, so that while maintaining the direction of travel either left or right-aligned along obstacles can be worked. In this case, according to the invention, the milling drum can also be moved during the milling operation, for which purpose the milling drum has the additional chisel tools at its end edges. The milling drum is moved linearly with the milling drum housing and the milling drum drive integrated into the milling drum and transversely to the direction of travel on the machine frame. The linear guide below the machine frame has the advantage that neither the milling depth nor the bank of the milling drum is influenced by the linear displacement. This is important when leveling the large milling machine with the aid of a height-adjustable chassis. A significant advantage is that only the position of the machine frame must be monitored in order to be able to carry out corrections if necessary. Another advantage is that the milling drum can be moved during operation without interrupting the operation.

The milling depth can be adjusted via the height-adjustable chassis. The high pressure load of the milling drum on the machine frame in conjunction with the milling drum housing allows milling depths of at least 30 cm, so that in a single crossing the entire road surface can be removed.

The departure from the usual mechanical drive concept with a belt drive and the integration of preferably two motors in the milling drum make it possible to vary the position of the milling drum transversely to the direction of travel.

The milling roller drive is preferably carried out on both sides, ie with two integrated in the end faces of the milling drum drive means.

It is preferably provided that the linear displacement of the Fräswalzengehäuses along two linear, spaced in the direction of travel of the machine frame guides takes place.

The two linear guides cause a stiff mounting of the milling drum housing on the machine frame and thus also a rigid mounting of the milling drum in the vertical direction, so that a precise routing depth adjustment is maintained. Furthermore, the storage of the Fräswalzengehäuses in the direction of travel is stiff, so that a mobility of the milling drum is only in the transverse direction to the direction of travel.

A first of the linear guides is a pipe guide and forms a fixed bearing and a second of the linear guides is a guide between flat surfaces and forms a floating bearing.

The storage of the Fräswalzengehäuses therefore has a fixed bearing and a movable bearing, wherein the game between the flat surfaces of the movable bearing can be adjustable.

It is preferably provided that the linear guides are fastened below the machine frame to the machine frame.

The arrangements of the linear guides below the machine frame have the advantage that the weight of the machine can be transferred directly to the milling drum via the milling drum housing, and that the guides can be arranged to save space.

The Fräswalzengehäuse is fixed in the vertical direction and in the direction of travel rigidly to the machine frame.

The milling drum housing has at the end faces in each case a height-adjustable side plate. The cutting circle at the end faces of the milling drum when milling along an obstacle, for example a lantern or a bridge pier, preferably has a distance from the obstacle of less than 120 mm, preferably 105 mm, or less than 105 mm.

The maximum lateral travel of the milling drum is between 500 and 1000 mm. This travel makes it possible to optionally set the zero side on the left or right side of the road milling machine.

The milling drum is preferably hydraulically driven on both sides. The two-sided drive has the advantage that the torsional load of the milling drum can be reduced, and that ultimately a higher power can be transferred to the milling drum. Alternatively, an electric drive is possible.

At the Fräswalzengehäuse a band shoe for receiving the lower end of the conveyor belt device can be fixed in height adjustable. The belt shoe can follow the movement of the milling drum housing transversely to the direction of travel, so that the lower end of the conveyor belt device is always arranged at the discharge opening for the milled material on the milling drum housing.

For this purpose, it is provided that the conveyor belt device is pivotally connected to the belt shoe.

The belt shoe has for the articulated receiving of the lower end of the conveyor belt device on a substantially concave, preferably spherical receiving socket, which cooperates with a shape adapted to the receiving pan bottom of the lower end of the conveyor belt device.

The front end of the conveyor belt device on the machine frame is longitudinally displaceable and gimbaled along the longitudinal axis of the conveyor belt device.

The conveyor belt device is pivotable at the front end about a horizontal axis of the machine frame vertical vertical axis and a parallel to the Fräswalzenachse transverse axis.

The conveyor belt device has for movable mounting at least at the front end on the underside a substantially in the longitudinal direction of the conveyor belt device extending conveyor belt side support member with preferably convex bearing surface laterally guided on a transverse fixed to the direction of travel on the machine frame frame-side support member rests with preferably convex support surface. The support surface and the support surfaces form a gimbal joint, with the additional advantage that even a slight rolling around the longitudinal axis of the conveyor belt device is possible.

The conveyor belt-side support member and / or the frame-side support member may be formed from a rounded profile or hollow profile. These can advantageously rest on one another and thus enable point-like storage, which permits a displacement of the conveyor belt device in its longitudinal axis.

The belt shoe is preferably height adjustable via a synchronous guide. The leadership of the belt shoe for raising and lowering in a kind of linear guide, in which the height adjustment takes place synchronously on the right and left side of the belt shoe by the same amount.

A hydraulic angle distributor for supplying the hydraulic drives provided on the milling drum housing, at least the milling drum drives, can be stationarily arranged on the milling drum housing.

The fixedly arranged on the Fräswalzengehäuse hydraulic angle distributor makes it possible that the hydraulic lines can be performed rigidly on the Fräswalzengehäuse to the drives and prevent tight bending radii of the leads from the hydraulic pumps.

To improve the maneuverability and universal applicability of a large milling machine can also be provided that the rear end in the direction of travel of the Fräswalzengehäuses concludes with a height-adjustable wiper blade, which rests laterally in the milling track of the milling roller resiliently against the road surface orthogonal Fräskanten the milling track.

Due to the fact that the scraper blade can deflect laterally, the large milling machine can drive tight curve radii without the scraper blade tilting. Another advantage is that the wiper blade by the elastic concern of the scraper blade against the milling edge of the milling track can pull off the milling track without milled material residues.

The rear end of the milling drum housing in the direction of travel can conclude with a height-adjustable scraper blade, which has at both lateral ends in each case a movable shield element which is substantially flush with the scraper blade at the lower edge and height-adjustable together with the latter, wherein the shield elements are parallel to the Scraper blade and the Fräswalzenachse are adjustable against a spring preload for dynamic adjustment of the Abstreiferschildbreite during milling.

Such a scraper blade with side movable shield elements has the advantage that the blade width adapts dynamically to the milling track. This is particularly advantageous for tight turns with large milling machines, but also when the milling track moves in the transverse direction to the direction of travel due to a controlled transverse movement of the Fräswalzengehäuses.

The spring preload is preferably generated hydraulically and may also be provided adjustable in terms of the amount of bias. Alternatively, the spring preload can be generated mechanically or with a gas spring. In a method for processing road surfaces, with a self-propelled large milling machine with a machine frame with lateral outsides, with a single rotatably mounted milling drum, and with a milling drum drive for the milling drum, wherein the milling drum with an end face almost flush with a lateral outside of the machine frame, the so-called zero side closes, in order to allow the closest possible milling along edges or obstacles is provided that optionally the zero side is fixed on the one outer side or on the opposite outer side of the machine frame by the Fräswalzenantrieb in the milling drum as a hydraulic or electric drive is integrated and the milling drum is mounted displaceably transversely to the direction of travel together with the milling drum drive, wherein for moving the milling drum during the milling operation additional chisel tools provided on the front edges of the milling drum are.

An embodiment of the invention will be explained in more detail below with reference to the drawings.

Fig. 1

eine schematische Teilansicht der selbstfahrenden Großfräse,

Fig. 2

das Fräswalzengehäuse als verschiebbares Modul,

Fig. 3

das Fräswalzengehäuse mit gelenkig gekoppelter Transportbandeinrichtung,

Fig. 4

das Fräswalzengehäuse in Rückansicht mit Abstreifschild, und

Fig. 5

eine perspektivische Ansicht der Kombination des Fräswalzengehäuses mit der angekoppelten Transportbandeinrichtung von unten.

Show it:

Fig. 1

a schematic partial view of the self-propelled large milling machine,

Fig. 2

the milling drum housing as a displaceable module,

Fig. 3

the milling drum housing with articulated conveyor belt device,

Fig. 4

the milling drum housing in rear view with scraper blade, and

Fig. 5

a perspective view of the combination of the Fräswalzengehäuses with the coupled conveyor belt device from below.

Fig. 1 shows a large milling machine 1 with a machine frame 8 and a chassis 4 with in the direction of travel 31 front and rear drives 5.6. The drives 5.6 form a steerable front axle and steerable rear axle. The chassis 4 is connected via lifting columns 7 with the machine frame 8, by means of which the distance of the machine frame 8 from a road surface 2 is adjustable. Each chassis axle has at least one track drive 5, 6 or a wheel drive.

At the front end of the large milling machine 1 in the direction of travel, a conveyor belt device 18, which is pivotable in the vertical and lateral direction, is arranged for the removal of the milled material to be milled.

The front and rear drives 5,6 of the chassis 4 may consist of crawler tracks or wheels.

The machine frame 8 has substantially vertically and parallel to the longitudinal center axis of the road construction machine 1 extending lateral outer sides 26,28. It is understood that the outer sides 26,28 do not have to be strictly vertical and absolutely parallel to the longitudinal center axis of the large milling machine 1, but that slight deviations are possible. The outer side 26,28 is preferably made in one piece, wherein the outer sides 26 and 28 are preferably in a plane.

Between the drives 5.6 a milling drum 12 is arranged, which is mounted with its Fräswalzenachse in a Fräswalzengehäuse 10.

The milling drum 12 extends with its one end face 22 to the in Fig. 1 shown as zero side outside 26,28 of the machine frame 8 zoom. On the null side, the corresponding end face 22 of the milling drum is very close to the outside of the large milling machine 1, so that it can be milled very closely past road edges or obstacles.

In the end face 22 of the milling drum 12 hydraulic or electric Fräswalzenantriebe 14 are preferably integrated on both sides, which are supplied by arranged on the machine frame 8 hydraulic pumps or generators, which in turn are driven by an internal combustion engine 3, the drive energy for the traction drive, the Milling drive and ancillary equipment provides.

At the end faces 22 of the milling drum 12 and adjacent to the Fräswalzengehäuse 10 each a height-adjustable side plate 15 is arranged, which serves as edge protection.

The milling drum 12 is preferably arranged centrally between the front drive 5 and the rear drive 6 in the direction of travel 31.

The milling drum 12 is provided with tools 13. The milling drum 12 rotates in the view from the right side of Fig. 2 seen in clockwise direction.

The single milling drum 12 can also be composed of several parts, or for example consist of at least one pushed onto a base roller tube. Likewise, the milling drum can also be composed of several segments.

Above the milling drum 12 is a control station 16, which may have two seats 20 with two steering devices 24, which are provided for left- or right-aligned milling along a road. It is understood that also a transverse to the direction of travel control station can be used with a seat with associated steering device 24, which is displaced as needed on the left or right side of the large milling machine 1.

The seat 20 is preferably oriented in such a way to the lateral outer wall 26,28 that the seat 20 at least partially laterally opposite the outer wall 26,28 protrudes.

When the large milling machine 1 is moved with a null side along an obstacle, e.g. On a lamppost, the control console 16 with the seat 20, the armrest and the control panel 25 can be moved inwards to allow the most flush as possible past the obstacle.

The outside 26,28 has a recess 32 in front of the driver's cab 16. This recess 32 allows the observation of the front drive 5 and thus the observation of the current steering angle.

In Fig. 1 the milling drum housing 10 is shown with a raised scraper blade 64, wherein the side plate 15 is raised to show the position of the milling drum 12. The milling drum housing 10 is mounted linearly and transversely to the direction of travel 31 on the machine frame 8, as a result of which the zero side can be fixed selectively on one outer side 26, 28 or on the opposite outer side of the machine frame 8.

The displacement of the Fräswalzengehäuses 10 takes place by means of two spaced in the direction of travel of the machine frame 8 guides 34,36, which are designed as linear guides.

The first of the linear guides 34 is a pipe guide which fits into the FIGS. 2 to 4 are arranged at the top of the Fräswalzengehäuses 10.

The second linear guide 36 is also arranged at a distance at the top of the Fräswalzengehäuses 10. The linear guide takes place between the flat surfaces 37,38, as best from the FIGS. 2 and 3 can be seen. The flat surface 37 is provided both on the top and on the underside of a beam 39 which is fixedly secured with flange portions 41 on the underside of the machine frame 8. The flat surfaces 37 are comprised of guide members 43 fixedly connected to the milling drum housing 10 and having the flat surfaces 38 in contact with the flat surfaces 37 of the beam 39. The distance of the flat surfaces 38 in contact with the respective flat surfaces 37 is adjustable, so that the play between the flat surfaces 37 and 38 can be adjusted by means of the guide members 43.

The second linear guide 36 forms a floating bearing, while the pipe guide of the first linear guide 34 forms the fixed bearing.

The pipe guide consists of a stationary over flange 42 on the underside of the machine frame 8 fixed inner tube 33 on which a stationary with the Fräswalzengehäuse 10 connected hollow cylinder 35 can slide.

A piston-cylinder unit 45, which is fixed at one end to the machine frame 8 and at the other end to the Fräswalzengehäuse 10, the entire unit of the Fräswalzengehäuses 10 with the milling drum 12 and the in the FIGS. 2 and 3 apparent further elements of the Fräswalzengehäuses 10, including the lower end 44 of the conveyor belt device 18, between a left-aligned to the outside of the large milling machine 1 or right-aligned position of the milling drum 12 move.

The stroke of the piston-cylinder unit 45 is preferably between about 500 and about 1000 mm. This means that the Fräswalzengehäuse 10 with all in the FIGS. 2 and 3 apparent components, this travel can be moved transversely to the direction of travel 31. For example, if the end face of the milling drum 12 in a position on the left side of the machine in the direction of travel 31 on the other side or in the vicinity of the outside 26,28, so is the zero side of the machine on the left side.

The stroke of the piston-cylinder unit 45 can be seen in relation to the width of the milling drum 12, which in large milling machines is about 1500 mm and more, typically 2000 mm. The piston-cylinder unit 45 can apply sufficiently high forces in order to displace the milling drum housing 10 with the milling drum 12 during the milling operation. For this purpose, additional tools 13 may be provided on the milling drum at the respective end faces.

The two linear, spaced in the direction of travel of the machine frame 8 guides 34,36 preferably have a maximum distance from each other. You can transfer the weight of the machine on the Fräswalzengehäuse 10 and mounted on the milling drum 12 to allow high cutting forces at large milling depths.

The combination of the linear guides 34,36 allows optimal capture of the forces and torques occurring.

The side plate 15 is fastened on both sides to the milling drum housing 10 via a double arrangement of piston-cylinder units 17, the double arrangement allowing a particularly large stroke of the piston-cylinder units 17.

How only out Fig. 2 As can be seen, the exemplary embodiment of a milling drum drive 14 shown can have at least one hydraulic drive 80 which is integrated into the end face 22 of the milling drum 12. The illustrated embodiment shows a double-sided hydraulic drive 80 in both end faces 22 of the milling drum 12, wherein hydraulic supply lines 82 are connected to the drives 80 via a manifold 84 and via further hydraulic lines 86 with a driven by the engine 3 hydraulic pump.

The further hydraulic lines 86 are shown schematically as a single line. It is understood that at least one inlet and -return line is required for the at least one hydraulic drive 80. The manifold 84 is fixedly secured to the Fräswalzengehäuse 10, so that the hydraulic lines 82 need not be flexible and only the other hydraulic lines 86 must be deformable so that the travel of the sliding unit, as shown Fig. 2 can be seen, executed.

In FIGS. 2 and 3 is on the front side of the Fräswalzengehäuses 10, a belt shoe 40 is arranged, which serves to receive the lower end 44 of the conveyor belt device 18.

The belt shoe 40 receives the lower end 44 of the conveyor belt device 18. The belt shoe 40 is centered to an ejection opening 11 of the Fräswalzengehäuses 10 arranged and can be adjusted by means of a tracking guide 60 in height. The synchronous guide 60 consists of two laterally arranged next to the conveyor belt device 18 joint gears 62, each having a piston-cylinder unit 63, wherein the synchronism of the two linkage 62 is ensured via a coupling shaft 66, so that the synchronization can not tilt.

Fig. 3 shows a representation accordingly Fig. 2 with integrated conveyor belt device 18.

The front bearing of the conveyor belt device 18 is best in Fig. 5 seen. On the machine frame, a frame-side support member 56 is stationary. The frame-side support member 56 preferably has a convexly rounded support surface, in the embodiment, a tube, on which the front upper end 46 of the transport device 18 can support with a conveyor belt-side support member 52. Since both support members 52,56 have convexly rounded support surfaces, the front end 46 of the conveyor belt device 18 is mounted point-shaped, wherein the storage forms a gimbal joint. In addition, the conveyor belt-side support member 52 can be displaced in the longitudinal direction when the Fräswalzengehäuse 10 is moved from one side to the other side of the large milling machine 1. The articulated mounting also allows a slight rolling of the conveyor belt device 18.

Lateral guides 54 hold the conveyor belt side support member 52 in position.

Due to the sliding movement of the milling drum housing 10 transversely to the direction of travel 31, it is also necessary to accommodate the lower end 44 of the conveyor belt device 18 articulated on the belt shoe 40.

The belt shoe 40 can for pivotally receiving the lower end 44 has a substantially concave, preferably spherical receiving socket 48, which cooperates with one of the shape of the receiving pan 48 adapted underside of the lower end 44 of the conveyor belt device 18. This articulated Receiving the lower end 44 of the conveyor belt device 18 allows lifting of the belt shoe 40 with the lower end 44 of the conveyor belt device 18, and a displacement of the Fräswalzengehäuses 10 by a travel of 500 to 1000 mm, the lower end 44 of the conveyor belt device 18 always before the discharge opening 11 of the milling drum housing 10 is arranged.

The receiving pan 48 is formed by inclined surfaces 50 which receive the lower end 44 of the conveyor belt device 18. In addition, lateral guide elements 51 are provided which allow a pivoting of the lower end 44 about a vertical axis on the one hand and on the other hand hold the lower end 44 laterally in position. The lower end 44 of the conveyor belt device 18 has centrally in the bottom of an in Fig. 2 only shown in phantom, preferably spherical, support means 49 which rests on the belt shoe 40 in the area in front of the middle slope 50 on the belt shoe 40. The support member 49 and its support position is also in Fig. 5 shown in dashed lines.

The ejection opening 11 of the milling drum housing 10 need not be arranged centrally to the Fräswalzengehäuse 10, but may also be provided eccentrically. The tools 13 of the milling drum 12 are arranged spirally in the circumferential direction, wherein the milling drum 12 has opposite spirals of tools 13, which transport the milled material to the ejection opening 11 and convey from the ejection opening 11 to the conveyor belt device 18.

Fig. 4 shows a rear perspective view of the Fräswalzengehäuses 10, on which a height adjustable by means of piston-cylinder units 65 Abstreiferschild 64 is arranged. The scraper blade 64 can also be pivoted upward when the tools 13 on the milling drum 12 must be accessible.

The scraper blade 64 has on its side facing the milling drum 12 at its lateral outer edges in each case a movable shield element 74, which by means of a resilient biasing means 76 (FIGS. Fig. 4 ) against the milling edge 70 orthogonal to the road surface 2 (FIG. Fig. 1 ) are pressed.

The lower edge 78 of the laterally movable shield element 74 terminates flush with the lower edge of the scraper blade 64. The shield elements 74 are height adjustable together with the Abstreiferschild 64. The resilient biasing means 76 may produce the bias in a different manner. In the embodiment of Fig. 4 the biasing means 76 are shown as piston-cylinder elements which can be hydraulically biased.

Claims (14)

1. A self-propelled road milling machine (1) for milling road surfaces (2), comprising

   - a height adjustable traveling gear unit (4),

   - front and rear traveling gear unit axles, as seen in the direction of travel, of said traveling gear unit,

   - a machine frame (8) supported by said traveling gear unit (4),

   - a milling roller housing (10) arranged at said machine frame (8) between said front and rear traveling gear unit axles,

   - a single milling roller (12) rotatably supported in said milling roller housing (10),

   - a milling roller drive unit (14) for said milling roller (12), and

   - a conveyor belt means (18) cooperating with said milling roller housing (10) for removing milling product milled off by said milling roller (12) in forward direction as seen in the direction of travel,

   - wherein a lateral front end (22) of said milling roller housing (10) is nearly flush with a lateral outer side (26,28) of said machine frame (8), the so-called zero side, to allow milling to be performed as near to edges or obstacles as possible,

   wherein said milling roller drive unit (14) is a hydraulic or electric drive unit (80) integrated in said milling roller (12),
   wherein said milling roller (12), together with said milling roller housing (10) rigidly fastened to the machine frame in the height direction and in the direction of travel, and with said milling roller drive unit (14), is supported in a displaceable manner transversely to the direction of travel at said machine frame (8), whereby said zero side can optionally be defined on one outer side (26,28) or on the opposite outer side (26,28) of said machine frame (8),
   and the milling roller (12) comprises, at the front edges, additional chiseling tools (13) for lateral displacement of the milling roller (12) during milling operation.
2. The self-propelled road milling machine according to claim 1, characterized in that the milling roller housing (10) is linearly displaced along two linear guides (34,36) spaced from each other in the direction of travel of the machine frame (8).
3. The self-propelled road milling machine according to claim 2, characterized in that a first one of the linear guides (34) is a tubular guide defining a locating bearing, and a second one of the linear guides (36) is a guide arranged between plane surfaces in the manner of a non-locating bearing.
4. The self-propelled road milling machine according to any one of claims 1 to 3, characterized in that the maximum lateral traveling distance of the milling roller (12) ranges between 500 and 1000 mm.
5. The self-propelled road milling machine according to any one of claims 1 to 4, characterized in that at the milling roller housing (10) a belt shoe (40) for receiving a lower end (44) of the conveyor belt means (18) is fixed in a height-adjustable manner.
6. The self-propelled road milling machine according to claim 5, characterized in that the conveyor belt means (18) is articulated to the belt shoe (40).
7. The self-propelled road milling machine according to claim 5 or 6, characterized in that the belt shoe (40) comprises an essentially concave, preferably spherical receiving socket (48) for articulatedly receiving the lower end (44) of the conveyor belt means (18), said receiving socket (48) cooperating with a lower side of said lower end (44) of said conveyor belt means (18) the shape of which is adapted to the shape of said receiving socket (48).
8. The self-propelled road milling machine according to any one of claims 1 to 7, characterized in that a front upper end (46) of the conveyor belt means (18) is supported by a cardan joint at the machine frame (8) such that it is longitudinally displaceable along a longitudinal axis of said conveyor belt means (18).
9. The self-propelled road milling machine according to claim 7 or 8, characterized in that, for ensuring flexible support, at least on the front side (46) the conveyor belt means (18) comprises on the lower side a conveyor-belt-side supporting element (52) extending essentially in the direction of the conveyor belt and preferably having a convex bearing surface, said support element (52) being laterally guided and resting on a frame-side support element (56) preferably having a convex supporting surface and being fixed transversely to the direction of travel to the machine frame (8).
10. The self-propelled road milling machine according to claim 9, characterized in that the conveyor belt-side support element (52) and/or the frame-side support element (56) are defined by a profile with a rounded cross section or a hollow profile.
11. The self-propelled road milling machine according to any one of claims 5 to 10, characterized in that the belt shoe (40) is adjustable in height via a synchronous guide (60).
12. The self-propelled road milling machine according to any one of claims 1 to 11, characterized in that a rear end, as seen in the direction of travel, of the milling roller housing (10) is flush with a height adjustable stripper shield (64) which rests laterally in a milling track (68) of the milling roller (12) and resiliently against the milling edges (70) of said milling track (68) extending orthogonally to the road surface (2).
13. The self-propelled road milling machine according to any one of claims 1 to 12, characterized in that the rear end, as seen in the direction of travel, of the milling roller housing (10) is flush with a height adjustable stripper shield (64) which comprises at both lateral ends a respective movable shield element (74) whose lower edge (78) is essentially flush with said stripper shield (64) and is adjustable in height together with the latter, and that said shield elements (74), parallel to said stripper shield (64), are adjustable against a spring bias for dynamically adjusting a stripper shield width to the milling track (68) during milling operation.
14. A method for milling road surfaces (2) using a self-propelled road milling machine (1) comprising

    - a machine frame (8) including lateral outer sides (26,28),

    - a single rotatably supported milling roller (12), and

    - a milling roller drive unit (14) for said milling roller (12),

    - wherein a front end (22) of said milling roller (12) is nearly flush with a lateral outer side (26,28) of said machine frame (8), the so-called zero side, to allow milling to be performed as near to edges or obstacles as possible,

    wherein said zero side is adapted to be optionally defined on one outer side (26) or on the opposite outer side (28) of said machine frame (8) by integrating said milling roller drive unit (14) in said milling roller (12) as a hydraulic or electric drive unit (80) and supporting said milling roller (12), together with the milling roller housing (10) rigidly fastened to the machine frame in the height direction and the direction of travel and with said milling roller drive unit (14, in a displaceable manner transversely to the direction of travel, wherein, for displacement of the milling roller (12) during milling operation, additional chiseling tools are used on the front edges of the milling roller (12).

Images