WO2010145645A1 - Drive system for the milling drum of a mobile milling machine - Google Patents

Abstract

The invention relates to a drive system for the milling drum of a mobile milling machine, comprising two side walls, which each carry one rotary body and can be moved to change the distance thereof, whereby the rotary bodies can be engaged and disengaged with the milling drum, characterized in that a mechanical drive train fed by a drive motor is guided on one or on each of the two rotary bodies and each drive train is partially movable to compensate the movement of the side walls. The drive train or each drive train has preferably one section (D) near the rotating body and fixed to the side wall and one moving section (B) far from the rotating body.

Description

 Drive system for the milling drum of a mobile milling machine

The invention relates to a drive system for the milling drum of a mobile milling machine, in particular a road milling machine, with two side walls, each carrying a rotary body and are displaceable to their change in distance, whereby the rotary body with the milling drum in and out can be brought. The invention also relates to a mobile milling machine with this drive system.

Road milling machines with variable-length side walls can be equipped with milling rollers of different lengths, so that they can be used for the different milling widths. By moving apart and moving the side walls of the roll change is relatively easy, and it can be made on the construction site according to the current requirements with already stocked with tools rollers.

From US 4,704,045 and EP 1 197 601 it is known to drive the rotary body by hydraulic motors. The hydraulic milling drum drive is generally associated with a significant loss of power. In addition, the cost of a hydraulic system is considerable. Even tugs on which road milling machines are frequently used are often not equipped with a suitable hydraulic system.

The object of the invention is to provide a drive system for the milling drum of a mobile milling machine of the type mentioned, which is cheaper and more power efficient than a hydraulic roller drive. The drive system should provide the opportunity to combine the milling machine with a tractor without hydraulic device. The drive system to be created should make it possible for self-propelled road milling machines to be able to do without the hydraulic roller drive. Further advantages of the invention will become apparent from the following description.

This task is the road milling machine mentioned above According solved according to the invention, that is guided on one or each of the two rotary body driven by a drive motor mechanical drive train and each drive train to compensate for the displacement of the side walls is partially movable. The drive motor may be the drive motor of the tractor in a coupled to a tractor milling machine. In a self-propelled milling machine, the drive motor is also the engine of the chassis. It is essential that the drive is transmitted purely mechanically to the two or - in one-sided roller drive - only one rotary body. Due to the partial mobility of the or each drive train required to adapt to the roll length displacement of the side walls is possible without making any changes to the drive train. Due to its partial mobility of the drive train can follow the displacement of its side wall. Partial mobility in this sense does not include the movements in the drive train for power transmission (shaft rotation, chain drive).

According to the preferred embodiment of the drive system, the or each driveline has a rotating body side wall portion D and a side wall movable portion B. When the side walls change in pitch, the rotating body portion of the driveline moves together and parallel with its side wall. The rotational close-up portion D has a fixed position relative to the side wall, which is independent of the position of the side wall and the mutual distance of both side walls. The rotating body remote movable portion B of the drive train is movable relative to the side wall and compensates for the displacement of its side wall by its mobility. In this case, this mobility of the rotary body remote section B comprises a displacement and pivoting relative to the side wall and an angle change between the section B and the adjoining parts of the adjacent sections, e.g. of section D, and a change in the length of section B.

According to the preferred embodiment with a milling drum drive on both sides, the drive train issuing from the drive motor is through a transfer case E branches into the two drive trains ABCD guided on the rotary bodies. Due to the two-sided drive of the milling drum with separate drive trains, a high drive power can be transferred to the milling drum. The drive torque sum, for example, can be tapped from the PTO of the tractor.

Preferably, the rotary body distal portion B of each drive train is part of at least one propeller shaft. Due to their joints and sliding parts, the drive shafts can change the angular position to its side wall and its length with changes in the distance of the side walls so that the change in distance is absorbed by the propeller shafts, without the torque transmission is impaired. In a milling drum driven on both sides and movement of the side walls symmetrically to the center plane of the milling machine, the cardan shafts move symmetrically to the median plane. The drive system according to the invention is also suitable for one-sided swinging the milling drum (milling the road surface close to curb or house wall). The two propeller shafts then swivel (asymmetrically to the center plane of the milling machine) to the same side, so that in this case they occupy different positions relative to their side walls and are also stressed differently.

Preferably, the portion close to the rotary body comprises a partial shaft and a chain or belt drive or a gear transmission. Also, the rotary body engaging with the milling drum can be added to this section of the drive train. The split shaft is the one-sided drive shaft, which receives the drive torque from the rotary body distant portion B of the drive train and transmits to the chain or belt drive. Preferably, one will use a chain drive to transfer the necessary drive torques. The partial shaft may be coupled to the inner end of the drive shaft via an angle gear and outside the wheel, in particular a sprocket wear, which drives a drive wheel of the rotary body via a chain or a belt. The angle gear is preferably a crown gear, in particular a Cylkro ^® crown gear. The crown gear is preferred over a bevel gear because of the lower power loss. A chain drive with a toothed chain is preferred over a belt drive, because the required drive torques can be transmitted easily and the toothed chain can work without problems even in the range of 1200 to 1500 rpm. The chain or belt drive is arranged on the outside of the side wall or protected in a double-walled side wall. Instead of the chain drive, a gear transmission can be used.

Preferably, the partial shaft is rotatably mounted in a mounted on the side wall bearing housing. The bearing housing pierces part of the side wall to the outside, or it protrudes in a double-walled side wall in the interior of this side wall. The bearing housing has at the inner end for receiving the angular gear housing enlargement and is flanged to the side wall at the opening, which is pierced by the bearing housing. Perpendicular to the axis of the part shaft is mounted in the housing extension of the output pin of the associated PTO shaft, which pierces the extension and a gear, in particular a crown carries, which meshes with a mounted on the inner end of the partial shaft spur gear. The rotating body close section of the drive train thus includes in addition to the partial shaft and the angular gear and the bearing housing in the extension extension pin of the associated PTO shaft.

In a particularly preferred embodiment of the drive system, the rotating body near section D of each drive train comprises an intermediate shaft which is connected at its one end via a hinge to the part shaft and connected at its other end to the movable portion B of the drive train. The bending of the drive train in section D is not achieved here by an angle gear, but by a joint between the part shaft and intermediate shaft. This construction is more space-saving than the angle gear with its bearing housing, and the drive power is transmitted loss. Conveniently, the intermediate shaft is coupled to the output end of the propeller shaft. The intermediate shaft is supported on the associated side wall. The rotating body close, fixed to the side wall portion D therefore includes in addition to the partial wave and the intermediate shaft and the joint located between these two waves. This compact design allows a small minimum distance of the side walls, so that rollers can be taken from 1.5 m in length. The propeller shafts are preferably constant velocity universal joint, whose diffraction angle can be up to 45 °.

According to the preferred embodiment of the drive system, the transfer case consists of two meshing same spur gears, wherein the drive train coming from the drive motor is guided on the input pin of the shaft of the one spur gear and the drive trains guided to the rotary body depart from the output spigots of the shafts of the two spur gears. Through the transfer case of the drive train coming from the drive motor is divided into two separate strands, which have the same torque, but opposite directions of rotation. By switching the incoming drive train between the inputs of the shafts of both spur gears, the directions of rotation in the two outgoing drive trains can be reversed, whereby the direction of rotation of the milling drum is reversed. This allows the use of the milling machine where the opposite direction of rotation of the milling drum is required, e.g. in the forestry business for clearing stumps, as well as forestry mulcher.

In a further embodiment of the drive system, the spur gear pair can be preceded by a transmission with a continuously variable transmission ratio. This device allows the operator to directly adapt the milling performance to changes in the material to be sawn and / or broken during milling.

Conveniently, the rotary bodies include a reduction gear with torque split. Due to the reduction, the milling drum can be operated at the optimum speed range of, for example, 100 to 200 rpm for milling. Due to the torque branching in the transmission, provided that overall the necessary torquing torques can be transmitted. The reduction gear is described in DE 100 50 496.9 closer.

The drive system of the invention is preferably used in a milling machine, which is formed by a cooperating with the milling roller breaker bar as Fräsbrecher. The load peaks occurring at the cutting crusher (rock crushing) can considerably stress the transmission elements of the drive trains. The mechanical drive system of the invention can safely transmit the required torques.

An embodiment of the invention is directed to a milling machine with a drive system of the type described, which is coupled to the power lift of a tractor and in which the drive train is acted upon by the PTO of the tractor. It can be used with advantage tractor without hydraulic device. The drive torque from the PTO tapping drive train is formed by a propeller shaft, which receives relative movements between the chassis and milling machine.

The invention will be described in more detail with reference to the drawing. Show it

1 and 2 a schematic representation of the drive system with minimum or maximum sidewall distance symmetrical to the median plane,

FIG. 3 shows an illustration as in FIGS. 1 and 2 when the side walls are pivoted to the same side,

Figure 4 is a detailed view of the drive system with minimal spacing of the side walls, wherein chain drives and rotating bodies are shown pivoted about the axis X of the side shafts in the plane of the drawing;

Figure 5 is a side view, partly in section, of a milling machine coupled to a tractor with the front side wall omitted; Figure 6 is a schematic representation of another embodiment of the drive system with minimal lateral clearance;

Figure 7 is a view corresponding to Figure 4 of the drive system of Figure 6;

FIG. 8 shows a first embodiment of the transfer case; and

Figure 9 shows a second embodiment of the transfer case with upstream continuously variable transmission.

Figures 1 to 3 show the drive system from the PTO of a tractor for the minimum and maximum sidewall distance corresponding to the smallest or largest length of a milling drum driven at both ends. Each of the two drive trains has a fixed to the dashed side wall fixed and only together with her movable section D and a displacement of the side wall enabling, movable section B. The drive train section D is connected to the section B via a joint C. The movable portion B is connected to the output pin of the transfer case E by hinge A. From the comparison of Figures 1 and 2 it can be seen that with a change in the distance of the side walls, the drive train sections D maintain their position relative to the side walls and join only the displacement of its side wall. The powertrain sections B respond to the displacement of the side walls by pivoting to the sections D about the joints C and by pivoting to the output pins of the transfer case E about the joints A. The mutual approach and removal of the two side walls is also made possible by the shortening or Extension of sections B. The system is driven by a power take-off via a propeller shaft F connected to one of the two drive pins of the gearbox E.

FIG. 4 shows the drive system for the milling roller of the shortest length of a milling machine, generally designated 1. The drive of the machine is tapped by the PTO shaft 3 of a tractor 2 and by means of a propeller shaft 4 to one of the two drive pin 39th connected to a transfer case E, which is attached to the machine frame 40. By converting the propeller shaft 4 on the other drive pin 39, the direction of rotation of the propeller shafts 5 and 6 and thus the milling drum is changed, as is apparent from Fig. G. In the transmission

E, which is described in more detail below, is the main drive train coming from the PTO shaft 3 divided into two drive trains, which are guided to the rotary body 22 and 23 for the two-sided roller drive. In the transmission E, the torque is divided in the opposite direction of rotation in the two strands. To the two output pins of the transmission E, a respective propeller shaft 5 or 6 is connected with sliding part, the output pin 5 'and 6' in housing extensions 7 'and 8' of bearing housings 7 and 8 are rotatably mounted. The bearing housing 7.8 are flanged to the double-walled side walls 9 and 10 respectively. In each of the two bearing housings 7, 8 a side shaft 11 or 12 is rotatably mounted about the common side shaft axis X. The side shafts 11,12 carry at their inner ends a spur gear 13 and 14 and at their outer ends in the double-walled side walls 9 and 10, a sprocket 15 and 16, the output pins 5 'and 6' of the propeller shafts 5 and 6 contribute Crown wheel 17 and 18, which meshes with the spur gear 13 and 14 respectively. The crown is preferably a Cylkro ^® -Kronenrad. In the

Side walls 9,10 each have a drive sprocket 19 and 20 rotatably supported, of which only the left drive sprocket 19 is shown, while the right drive sprocket 20 is hidden by the chain 21 drawn there. The drive sprockets 19,20 are driven by the sprockets 15 and 16 via the chains 21. The drive sprockets 19, 20 drive rotary bodies 22 and 23, respectively, which are engaged with the hollow ends of the milling drum (not shown). The rotary bodies 22 and 23 include a reduction gear with torque ^¬ branching. They are explained in more detail in DE 10050396.9, to which reference is made here. The chain drives 16,20,21; 15,19,21 can be replaced by Zahnreadgetriebe.

FIG. 5 shows a milling machine 1 in side view. The milling ^¬ machine is attached to the tractor 2 at three points medium lower link 24 and upper link 25. The equipped with round shank chisels 26 Milling roller 27 of the milling machine 1 is driven at both ends to the roller axis eccentrically upwardly offset sprockets, of which the sprocket 20 is shown in Figure 5. The sprocket 20 is driven by the seated at the end of the partial shaft 12 sprocket 16 via the chain 21. The partial shaft 12 is connected via an angular gear (not visible) in the housing extension 8 'to the propeller shaft 6, which is shown in Figure 5 shortened in perspective. The propeller shaft 6 is connected to one of the two output pins of the transfer case E, while from the other (not visible) output pin of the transmission, a same drive train is guided to the rotary body at the other end of the milling drum 27. One of the two drive pins 39 of the transfer case E is connected via the perspective shaft shortened shown propeller shaft 4 with the PTO shaft 3 of the tractor 2.

The milling machine 1 shown here includes a device with adjustable crusher bar 28 and therefore can crush through the milling drum 27 conveyed rock material to an adjustable grain size. For guiding of the two side walls, of which only the hinte- ^re side wall 10 is visible, with its change in distance of two telescopic guides 29 and 30 serve jeweis from two nestable and expandable tubes.

Figure 6 shows schematically the second embodiment of the drive system for the minimum sidewall distance corresponding to the smallest receivable milling drum. Each of the two drive trains has fixed to the dashed lines indicated side wall W and only together with her movable portion D and a displacement of the side wall W enabling movable portion B. The fixed to the wall W section D is shown in more detail in FIG.

In Figure 7, subsequent to the transmission e ^¬ joint waves are 5.6 constant velocity joint shafts, which constitute the movable part of the two drive trains. At the joint 41 of the constant velocity universal joint, a short, inclined intermediate shaft 42 connects, the output side end is coupled via a hinge 43 to the mounted in the side wall 44 part shaft 45. The partial shaft 45 carries a sprocket 46 for the roller drive. The short intermediate shaft 42 is held by a bearing 47 which is fixedly attached to the side wall 44. The function is essentially the same as in the embodiment shown in FIG. 4, the design allowing a smaller minimum distance between the sidewalls 44.

FIG. 8 shows the simplest embodiment of the transfer case E. It has a first shaft 31 with a spur gear 32 fixed thereon and a second shaft 33 with a spur gear 34 fixed thereon. The two meshing spur gears 32, 34 are identical. When connecting the propeller shaft 4 to the drive end of the shaft 31 are at the output ends of the shafts 31 and 33 equal torques of opposite direction of rotation available, with which the two drive trains A-D (Figure 1) are applied for the two-sided Fräswalzenantrieb.

In the embodiment of Figure 9 the transfer case shown in Figure 8 is connected in a steplessly adjustable translation stage 38 in front ^¬. The infinitely adjustable gear ratio allows the operator to continuously adjust the speed of the milling drum when changing the properties of the material to be abrefrenten or to be broken during operation.

The drive system of the invention has been described on an attachment without own chassis, wherein the milling drum drive is tapped by the PTO of the supporting vehicle. However, the drive system is also applicable to self-propelled milling machines and Fräsbrechern, the PTO is part of a suitable tap. The invention extends not only to the illustrated two-strand drive system, but also to milling machines with a drive train for one-sided milling drum drive, wherein driven side of the milling drum is rotatably supported only on the side wall.

The rotary bodies 22,23 include reduction gear when the milling drum 27 is driven on both sides. In one-sided drive of the milling drum, the rotary body on the non-driven side is a rotatable with the milled roller pivot pin.

Claims

claims 1. Drive system for the milling drum of a mobile milling machine with two side walls, each carrying a rotary body and are displaceable to their change in distance, whereby the rotary body with the milling drum in and disengageable, characterized gekennzeinet that to one or each of the two rotary body (22,23) is guided by a drive motor fed, mechanical drive train and each drive train to compensate for the displacement of the side walls is partially movable. 2. Drive system according to claim 1, characterized in that the or each drive train has a rotating body near, fixed to the side wall portion (D) and a rotating body remote, movable portion (B). 3. Drive system according to claim 1 or 2, characterized in that the outgoing drive of the drive motor or the drive train through a transfer case (E) in two to the rotary body (22,23) guided drive lines is branched. 4. Drive system according to claim 2 or 3, characterized in that the rotary body remote section (B) of each drive train is part of at least one propeller shaft (5; 6). 5. Drive system according to one of claims 2 to 4, characterized in that the drehkörpernahe section (D) of each drive train comprises a partial shaft (11; 12) and a chain or belt drive (21) or a gear transmission. 6. Drive system according to claim 5, characterized in that the partial shaft (11; 12) is internally connected via an angle gearbox to the articulated ^shaft (5; 6) and carries on the outside a wheel (15; 21), a belt or one or more gears drives a drive wheel (19; 20) of the rotating body (22; 23). 7. Drive system according to one of claims 5 and 6, characterized in that the partial shaft (11; 12) in a on the side wall (9; 10) mounted bearing housing (7; 8) is rotatably mounted. 8. Drive system according to one of claims 4 to 7, characterized in that the output end (5 ', 6') of the propeller shaft (5; 6) rotatably mounted in an extension (7 ', 8') of the bearing housing (7; is. 9. Drive system according to claim 5, characterized in that the drehkörpernahe section (D) of each drive train comprises an intermediate shaft (42) at its one end via a hinge (43) with the partial shaft (45) and at its other end with the movable portion (B) of the drive train is connected. 10. Drive system according to claim 9, characterized in that the intermediate shaft (42) to the joint (41) of the propeller shaft (5; 6) is coupled. 11. Drive system according to claim 9 or 10, characterized in that the intermediate shaft (42) on the associated side wall (44) is mounted. 12. Drive system according to one of claims 3 to 11, characterized in that the transfer case (E) consists of two identical meshing spur gears (32,34), wherein the coming of the drive motor drive train (F) to the input pin of the shaft (31 or 33) of the one spur gear is guided and the guided to the rotary body drive trains (A-D) depart from the output pin of the shafts (31; 33) of the two spur gears. 13. Drive system according to claim 12, characterized in that the incoming drive train (F) between the input pin of the shafts (31; 33) of both spur gears (32; 34) is switchable. 14. Drive system according to claim 12 or 13, characterized in that the Stirnzahnradpaar (32,34) is preceded by a transmission (38) with continuously adjustable ratio. 15. Drive system according to one of claims 1 to 14, characterized in that the milling machine (1) by a with the milling drum (27) cooperating breaker bar (28) is designed as a Fräsbrecher. 16. Mobile milling machine with a driven by a drive system according to one of claims 1 to 15 milling drum. 17. Mobile milling machine according to claim 16, characterized in that it is coupled to the power lift (24,25) of a tractor (2) and the drive train (F) from the PTO (3) of the tractor (2) is acted upon. 18. Mobile milling machine according to claim 17, characterized in that the of the PTO (3) coming drive train (F) by a propeller shaft (4) is formed.