EP2057348B1 - Method and apparatus for the milling cutting of materials - Google Patents

Description

The invention relates to a device for the milling and / or drilling of materials, in particular for the removal of rocks, minerals or coal, with a rotatably mounted on a drum carrier about a drum axis tool drum, in the plurality of tool shafts which projecting from their projecting from the tool drum Carrying ends machining tools are mounted rotatably driven, wherein at least two of the tool shafts are drivable by a common gear drive having rotatably mounted on the tool shafts driven gears and a common drive element which cooperates with the drive gears, wherein the drive element and the tool drum are rotatable relative to each other , The invention further relates to a method for milling or removal of materials such as rock, coal or the like. and use of such a device as well as the use of the method.

For the removal of hard materials such as rock, ore and other mining products in underground or surface mining, but also for the milling of asphalt or concrete components in road construction or building construction. are known a variety of milling systems, which are provided with rotating driven drums or discs on which milling tools such as round shank chisel are evenly distributed. When used in underground mining drum skid steers rock or coal is mined by means of cutting rollers, which cut the material to be picked in full section, so that about half of all arranged on the circumference of the drum machining tools are simultaneously engaged with the mining front. Because of the relatively long contact times between the processing tools and the material to be degraded is the wear even high with machining tools provided with carbide tips, especially for hard, degradable materials. In addition, because of the large number of simultaneously with the material to be degraded engaged individual processing tools, the remaining pressure force for each tool is relatively low, which is why a relatively high feed force in the feed direction or working direction must be exercised on the device to reduce hard materials.

In order to increase the recovery performance of devices, particularly for the removal of hard rock, the inventors have developed devices which operate with impact superposition in order to obtain a high release impulse for the removal of minerals, hard rock or concrete. In working with impact overlay devices, the storage of the individual elements of the device as well as the noise pollution partly cause considerable problems.

Furthermore, the inventors have from the pre-published WO2006 / 079536 A1 known device which is the basis of the preamble of claim 1 and in which can be achieved with reduced pressure forces even when working hard materials long life of the tools. The working principle of the WO2006 / 079536 A1 known device is based on arranging a plurality of tool spindles in a spindle or tool drum so eccentrically around a drum axis that the spindle axes of the tool spindles are parallel or at most slightly inclined to the axis of rotation of the tool drum. All tool spindles are mounted in the tool drum such that the processing tools are distributed over the circumference in front of the end face of the tool drum. In operation, a rotation of the tool drum is superimposed with a rotation of each tool spindle. By superimposing the rotational movements of the tool drum and the tool spindles can be achieved that only a relatively small number of machining tools are simultaneously in operative engagement with the material to be milled or abzutragenden, resulting in a high dissolving force for each machining tool. In operation, the known processing device is transverse to the axis of rotation of the tool drum and thus also moves transversely to the axis of rotation of each tool shaft. With the known device outstanding service life of the tools are achieved even with hard materials and high removal rate. When removing materials on closed surfaces, but also when drilling boreholes or the like. However, the retraction is partly problematic due to a feed movement of the device in the material to be removed, partly not possible. Further, the degradation of materials over a large area requires a substantial diameter of the tool drum, resulting in a comparatively high overall weight of the device.

The object of the invention is to provide a device which is able to economically remove rocks or other materials with high strengths at high removal rate and large Abtragsfläche. The device is intended to ensure a high level of operational reliability, be used in a wide variety of applications and avoid the disadvantages of the known device.

To solve these objects, a device having the features of claim 1 is proposed. According to the invention it is provided that the shaft axes of the tool shafts are transverse to the drum axis. Unlike the one from the WO2006 / 079536 A1 known device is therefore chosen an arrangement of the tool drum with the co-rotating tool shafts, in which the shaft axes of the individual tool shafts are no longer substantially parallel, but transverse to the drum axis of the tool drum. Due to the significantly changed orientation of the shaft axes of the tool shafts, the machining tools no longer lie on the end face of the tool drum, but the milling or removal takes place radially outside the circumference of the tool drum. Due to the changed orientation of the tool shafts, a fundamentally different superposition of the rotational movement of the tool drum and the rotation of the tool shaft is produced. Nevertheless, even with the device according to the invention, a very short, compact, pulsed engagement of the individual processing tools in the rock to be degraded can be achieved, Therefore, the advantages of the known device, in particular a very high release force, even with reduced, available pressure force of the tool drum can be maintained.

According to an advantageous embodiment, the shaft axes of the tool shafts can be perpendicular to the drum axis. Alternatively, the shaft axes of the tool shafts may also be angled to the drum axis, wherein the angle of the angling is at least 45 ° and preferably greater than about 80 °. In principle, it would also be possible for the shaft axes of one or more tool shafts to be perpendicular and, at the same time, for the shaft shafts of other tool shafts to be the same or different from the axis of the drum. In the device according to the invention is of particular advantage that, in contrast to the prior art, a working movement of the device takes place parallel to the drum axis and / or that a feed movement of the device to the depth of cut for the next Abtragvorgang is perpendicular to the drum axis. In the case of the solution according to the invention, all machining tools are preferably located radially outside the tool drum, in particular radially outside the circumference of the tool drum, and during operation the material, outside the circumference of the tool drum, is crescent-shaped. Due to the rotational movement of the drum and the arrangement of the shaft axes of the tool shafts rotate in the operation insert, the processing tools transverse to the drum axis and the material is removed outside a circumference of the drum. Due to the deviating from the prior art superposition of rotational movements and with the same tool drum size further outward machining tools even shorter tool engagement times can be achieved than in the pre-published system. The contact between each individual machining tool and the material to be removed can advantageously take place, in particular, when the instantaneous direction of movement of the machining tool coincides with the direction of movement of the tool drum.

According to an advantageous embodiment, the tool drum and at least a portion of the tool shafts a common rotary drive exhibit. In this embodiment, by means of a rotation of the tool drum, the tool shafts acted upon by the common rotary drive can also be automatically set in rotation. According to one embodiment, the rotary drive could have a rotatably connected to the tool drum, mounted in the drum carrier, driven by a drive device drive shaft and one or at least one rotatably mounted on the drum carrier drive gear as a drive element, which meshes with the output gears on the respective tool shafts. A corresponding device can be constructed particularly compact, with very high forces and torques are transmitted and at the same time there is a fixed ratio of the rotational speeds between the tool drum and the drive shaft and the driven tool shafts. In order to transmit the drive forces safely, the drive gear and the associated output gears may be formed of bevel gears, built in the manner of a planetary gear bevel gear in which the or the drive gears each form the sun gear and the mitbewegten with the tool drum output gears planetary gears. In an alternative embodiment, the drive gear may consist of a toothed crown wheel, with which cylindrical gears mesh as associated output gears. When using a crown gear with planetary gears the forces exerted on the respective bearings forces are significantly reduced during operation, since no axial forces are transmitted via the crown gear.

In order to achieve a favorable release behavior in a common rotary drive for the tool drum and the tool shafts, the transmission preferably has a transmission ratio between about 3: 1 and 9: 1, in particular about 6: 1 and 8: 1 between the drive shaft and the tool shafts. For particularly hard machining tools such as diamond tools or ceramics, the gear ratio can also be eg 12: 1 and greater. In order to be able to absorb high pressure forces well, according to an advantageous embodiment, the tool drum be supported on both sides of the tool shafts on a drum carrier, preferably on the opposite side of the drive drum of the tool drum Pin or a bearing for two-sided mounting of the tool drum is formed. For smaller tool drums or softer materials to be degraded, however, one-sided mounting of the tool drum could be sufficient.

In an alternative embodiment, the tool drum may have a drum drive which is decoupled from a gear drive for the drive element. In this embodiment, which then operates accordingly with two separate rotary actuators, the speed ratio between the rotational speed of the tool drum, with which rotate the tool shafts transverse to their shaft axes, and the rotational speed of the respective tool shafts can be set almost arbitrarily. For adjustment is particularly advantageous if the drum drive and / or the gear drive consist of adjustable drives. For many applications, the drum drive and the gear drive can be arranged or coupled on the same side of the tool drum. For this purpose, the tool drum may in particular be provided with an axially protruding shaft receptacle in which a rotationally fixed connected to the drive gear, both sides of a receiving bore of the shaft receiving outstanding gear drive shaft is rotatably supported or supported. The gear drive shaft can then be supported in particular by means of a bearing in the receiving bore and by means of a second bearing in a bolted to the tool drum bearing cap. A corresponding embodiment is particularly advantageous when the shaft axes are angled to the drum axis and the drive gear and the output gears are formed as bevel gears of an angular gear with planetary gears. However, the shaft axes could also be perpendicular to each other. Appropriately, then the shaft receiving the drum drive and the transmission input shaft to the transmission drive can be coupled.

In an alternative embodiment with two separate rotary actuators for the drum drive and the gear drive, the drum drive on one side of the tool drum and the gear drive axially offset on the opposite side of the tool drum can be arranged or coupled. According to an advantageous Embodiment, the tool drum can be provided on the opposite side with an axially projecting annular extension with a shaft receiving a rotatably connected to the drive gear, both sides of a receiving bore of the shaft receiving outstanding gear drive shaft is rotatably supported, the tool drum on the other side has a bearing extension to which the drum drive can be arranged or coupled. The gear drive shaft may conveniently be rotatably supported by a first bearing in the shaft receiving the ring extension and by means of a second bearing in the bearing extension, wherein preferably the bearing extension can consist of a bolted to the tool drum bearing flange. The bearing extension can in particular be provided with a toothing or a toothed wheel in order to connect the drum drive and tool drum in a simple manner via gears or toothed belt.

According to a further, advantageous alternative embodiment, the tool drum can be non-rotatably connected to the output side of a first hub gear and the drive gear rotatably connected to the output side of a second hub transmission, both hub gears are arranged in a central receptacle. Such a design is particularly compact and can therefore be good with swivel arms or the like. move along a large excavation front. The hub gears can be designed, in particular, as a slide-in transmission with transmission stages preferably encapsulated in gearbox housings, wherein the mounting flanges of both hub gears can be fastened or fastened to the drum carrier. The drive of the hub gear could be done in particular via timing belt.

In all embodiments with separate rotary actuators, the drive gear and the output gears can be particularly advantageous turn be formed as bevel gears of an angular gear with planetary gears or alternatively a crown gear could form the drive gear, while the driven gears are formed as with this meshing cylindrical gears. To make the device particularly compact, the output gears of all the tool shafts with a single, common drive gear in Meshing. In particular, in this embodiment, the tool shafts can then be arranged uniformly distributed over the circumference in the tool drum. Alternatively, however, the tool shafts could also be arranged unevenly and / or in groups distributed in the tool drum and / or it could be provided for each group a separate drive gear.

It is also advantageous if each machining tool arranged on a tool shaft is arranged offset relative to the arrangement of a machining tool of a tool shaft located in front of or behind the drum circumferential direction by an angular amount and / or at a distance from the drive shaft or drum axis. The machining tools are in this case preferably formed or fastened to tool carriers which are detachably connected to the tool shafts. Alternatively, however, they could also be anchored directly to the ends of the tool shafts. To facilitate the replacement of the tool shafts, they can be rotatably received in bearing bushes by means of bearings and sealed by shaft seals, which is achieved in a relatively simple manner that the tool shafts can be used cartridge-like interchangeable provided by the bearing bushes provided in the drum tool drum and locked.

Depending on the material to be degraded and the purpose of the device according to the invention, different types of tools can be used. When removing materials such as rock, coal or minerals in underground or underground mining is particularly advantageous if the processing tools preferably all tool shafts from chisels or round shank chisels arranged for multi-layer undercutting removal of the material to outwardly tapering tool carriers or ends of the tool shafts are. The tool carriers or ends of the tool shafts may taper conically, arcuately or in steps. It is particularly advantageous if the processing tools are arranged on each tool shaft in cutting rows on pitch circles with different diameters, wherein preferably the distance between two rows of cutting is selected such that all rows of cutting approximately the same size Remove sickle-shaped cutting surfaces. In this embodiment, it can be achieved that the service life of each individual machining tool on the tool head of a tool shaft is approximately the same, so that an exchange of the machining tools can take place with fixed maintenance intervals. Instead of undercutting tools and milling drums can be used. A working with milling rollers as a machining tool device can be used in particular for road construction for removing deposits, in building construction for the renovation of floors and walls or civil engineering for pulling eg trenches and the like or on the boom of an excavator. to be assembled. The milling drums can be cylindrical or taper conically towards the machined material.

At each tool shaft, a plurality of processing tools are preferably formed. It is particularly advantageous if the machining tools are arranged offset in phase from one another in the circumferential direction of the tool drum tool shafts, so that a machining tool of a subsequent tool shaft at another location in the material to be machined or ablated material as the machining tool of the leading tool shaft. In most embodiments, it is sufficient to store the tool shafts within the tool drum. In the case of particularly hard material, however, it may be advantageous if the tool shafts are rotatably supported at their radially outer end by means of a bracket with pins, which in turn is fastened to the tool drum, so that additional support or support of the tool shafts respectively at or near the Processing tools bearing ends of the tool shafts takes place.

For use of the device according to the invention in underground mining for the mining of coal may be particularly advantageous if the tool drum is provided between adjacent tool shafts with radially extending scratches or blades with which the preferably dissolved by means of undercutting processing tools on the mining front material in a conveyor od .dgl. the extraction device is loaded.

The device according to the invention is particularly suitable for use in a method for milling or removing rock, in which the rotational speed of the tool shafts, the rotational speed of the tool drum, the feed rate of the device parallel to the drum axis and / or the angular position of the arranged on the individual tool shafts processing tools relative is set to the angular position of the processing tools in the circumferential direction in front or behind lying tool shafts so that a machining tool of a subsequent tool shaft not at the same point of impact in the rock or the like. strikes like a machining tool of a previous tool shaft. By varying the parameters rotational speed of a planetary carrier forming tool drum, rotational speed of the drive gear bearing drive shaft as Planetenradwelle, feed rate of the device and cutting line spacing of the processing tools, the trajectory of each tool cutting the processing tools can be determined and thus reliably the grain size and surface structure of the machined or abraded material influence. It is particularly advantageous if the rotary drive is carried out by means of controllable drives, so that different rotational speeds can be adjusted continuously without interrupting the cutting work. A corresponding design of the device makes it possible to adapt the respective drive-specific requirements to the geometry of the surface to be machined as well as the properties of the material to be processed or ablated.

Fig. 1

im Schnitt eine erfindungsgemäße Vorrichtung gemäß einer ersten Ausführungsform;

Fig. 2

in Schnittansicht eine zweite Ausführungsform mit Werkzeugwellen, deren Wellenachsen geneigt stehen;

Fig. 3

in Schnittansicht eine erfindungsgemäße Vorrichtung gemäß einer dritten Ausführungsform mit hinterschneidenden Werkzeugen zum Abtragen von Mineraliengestein;

Fig. 4

die Vorrichtung aus Fig. 3 in Draufsicht auf die Stirnseite der Werkzeugtrommel;

Fig. 5

in Schnittansicht ein viertes Ausführungsbeispiel einer erfindungsgemäßen Vorrichtung mit geneigt stehenden und endseitig abgestützten Werkzeugwellen;

Fig. 6A,6B

im Schnitt und in einer Draufsicht eine erfindungsgemäße Vorrichtung gemäß einem fünften Ausführungsbeispiel;

Fig. 7

in Draufsicht ähnlich zu Fig. 6B ein weiteres Anwendungsbeispiel für eine erfindungsgemäße Vorrichtung;

Fig. 8

im Schnitt eine erfindungsgemäße Vorrichtung gemäß einer sechsten Ausführungsform mit entkoppelten Drehantrieben;

Fig. 9

im Schnitt eine erfindungsgemäße Vorrichtung gemäß einem siebten Ausführungsbeispiel mit entkoppelten und auf unterschiedlichen Seiten der Werkzeugtrommel angeordneten Drehantrieben;

Fig. 10

im Schnitt eine erfindungsgemäße Vorrichtung gemäß einem achten Ausführungsbeispiel mit zentral angeordneten Nabengetrieben; und

Fig. 11

eine Verwendung einer erfindungsgemäßen Vorrichtung an einem schwenkbaren Ausleger.

Further advantages and embodiments will become apparent from the following description and the drawings in which preferred embodiments of the invention are illustrated and exemplified in more detail. Show it:

Fig. 1

in section, a device according to the invention according to a first embodiment;

Fig. 2

in sectional view, a second embodiment with tool shafts whose shaft axes are inclined;

Fig. 3

in sectional view of an inventive device according to a third embodiment with undercut tools for the removal of mineral rock;

Fig. 4

the device off Fig. 3 in plan view of the end face of the tool drum;

Fig. 5

in a sectional view of a fourth embodiment of a device according to the invention with inclined standing and end-supported tool shafts;

Fig. 6A, 6B

in section and in a plan view of a device according to the invention according to a fifth embodiment;

Fig. 7

in plan view similar to Fig. 6B another application example of a device according to the invention;

Fig. 8

in section, an inventive device according to a sixth embodiment with decoupled rotary actuators;

Fig. 9

in section, an inventive device according to a seventh embodiment with decoupled and arranged on different sides of the tool drum rotary actuators;

Fig. 10

in section a device according to the invention according to an eighth embodiment with centrally located hub gears; and

Fig. 11

a use of a device according to the invention on a pivotable boom.

In Fig. 1 is a total of reference numeral 10, a device according to the invention for example for the removal of coverings in road construction, for the renovation of floors or walls in building construction or for use in mining according to a first embodiment shown. The device 10 comprises a drum carrier 1, the like at a suitable holding means or moving means for the device 10, for example, the boom of an excavator, the machine boom of a tunneling machine. can be attached. The tubular, here hollow drum carrier 1 has a central, centrally formed to the drum axis or main axis H bearing receptacle 11, in which a rotatably connected to a tool drum 4 drive shaft 3 is mounted freely rotatably by means of two arranged in O arrangement tapered roller bearing 2. The one end of the drive shaft 3 is rotatably connected to the tool drum 4 and the other, protruding from the drum carrier 1 end of the drive shaft 3 is used for rotationally fixed receiving a gear 3b, with which a suitable rotary drive for the device 10 can be coupled. The motorized rotary drive can or the like of a motor with downstream transmission and possibly overload clutch. be formed. The drive shaft 3 and the tool drum 4 are rotatably connected to each other or consist of one piece. The front side 4 'of the tool drum 4 is completely closed and the tool drum 4 has distributed over its circumference a plurality of radial bores or radial passages 12, in which tool shafts 5 are mounted such that the shaft axes W of the tool shafts 5 are transverse to the drum axis H, whereby the free Ends 9 of the tool shafts 5 are located completely radially outside the drum peripheral edge 4 "of the tool drum 4. Depending on the size and diameter of the tool drum 4, approximately three to twelve tool shafts 5 can be distributed over the circumference of the tool drum 4. The bearing of the tool shaft 5 in the radial passage 12 takes place here again by means of two tapered roller bearing 6 in o-employment, the assembly of each bevel gear shaft 5 via the unilaterally open gear receptacle 14 of the tool drum 4 takes place. At the free end 9 of each tool shaft 5 is an in Fig. 1 consisting of a milling drum existing tool carrier 15 with individual processing tools 16 thereon, wherein on each tool carrier 15, a plurality of here only by means of their chisel tips represented processing tools are arranged and the arrangement of the processing tools 16 is such that it spirally distributed over the support periphery of the tool carrier 15 are, so if possible only a chisel tip of a machining tool 16 is on a radial line of each tool carrier 15. In the case of a machining tool 15 embodied as a milling drum, in each case a uniform angular offset and axial offset can exist between all the machining tools 16.

In the machining apparatus 10, only the gear 3B on the drive shaft 3 is engaged with an external drive. During a rotation of the drive shaft 3 rotates the rotatably connected thereto tool drum 4, whereby the arranged in the radial passages 12 tool shafts 5 also rotate around the drum axis H. By means of a generally designated by reference numeral 20 angular gear is now derived from the rotational movement of the tool drum 4, a rotation of the individual tool shafts 5 and this superimposed. The angle gear 20 is arranged protected in the transmission receptacle 14 of the tool drum 4 against contamination. Trained as a planetary gear bevel gear 20 has a non-rotatably mounted on a peripheral flange 47 of the drum support 1, therefore stationary in use drive gear 8, with which in each case a driven gear 7 meshes, which is non-rotatably connected to the protruding into the gear receptacle 14 shaft end of the tool shafts 5. Trained as a bevel gear drive gear 8 is preferably bolted to the peripheral flange 47 by means of the connecting screws 18. Since the drum carrier 1 or the like with a machine boom. is connected, the drive gear 8 is stationary relative to the tool drum 4 and the circulation of the tool drum 4, the output gears 7 run as planet wheels to the drive gear 8 to. The tool drum 4 forms the planet carrier in this regard. The transmission ratio between the drive gear 8 and the output gears 7, depending According to size and design of the device 10, 3: 1 to 12: 1 and more, with a gear ratio of about 6: 1 to 8: 1 offers particularly great advantages.

In the device 10, the shaft axes W and the drum axis H are perpendicular to each other and the angle gear 20 is designed accordingly. By rotating the individual tool holder 15 with the spirally offset machining tools 16 and the additional rotation of the tool drum 4 is when editing material outside the circumference 4 '' of the tool drum 4 each only an extremely short contact time of the individual processing tools 16 and chisel tips with the be removed or removed material such as Reached rock. Because of this short contact time of the wear of the individual processing tools 16 is very low. Depending on the transmission and the drive used, e.g. the tool drum 4 revolve at 60 rpm and the speed of each tool shaft 5 is e.g. 400 rpm. In order to protect the bevel gear 20 and the tapered roller bearings used 2, 6 are at the radial outlet of the radial passages 12 to the circumference 4 '' of the tool drum 4 each shaft seals 17 are arranged and the transmission receiving space 14 by means of an annular disc 19 with shaft seal 13 at the inner opening of the annular disc 19 closed.

Fig. 2 shows a second embodiment of a device 60 according to the invention, wherein in comparison to the embodiment according to Fig. 1 building or functionally identical components are provided with reference numerals increased by 50. As in the previous embodiment, a drive shaft 53 is rotatably mounted within a drum carrier 51, which is rotatably connected to a tool drum 54. The tool drum 54 is, distributed over its circumference, provided with a plurality of radial passages 62 for receiving a corresponding number of tool shafts 55, wherein the bearing of the tool shafts 55 in the radial passages 62 again takes place by means of a pair of tapered roller bearings 56. As in the previous embodiment are on the free shaft ends 59 of each tool shaft 55 tool carrier 65 with a plurality of preferably spirally distributed processing tools 66 arranged. In contrast to the previous embodiment, however, the shaft axes of the tool shafts are not perpendicular to the drum axis H of the tool drum 54, but the shaft axes W of the tool shafts 55 are inclined by the angle 74. The individual processing tools 66 on the circumference of the tool carrier 65 therefore do not rotate perpendicular to the holder axis H, but about an axis of rotation, which is at an angle of about 85 ° to the drum axis H here. The tool carrier 66 is in turn formed as a milling drum as in the previous embodiment. Also in the device 60, the rotation of the tool shafts 55 is derived from the rotation of the drive shaft 53 by means of an angular gear 70, which is arranged as in the previous embodiment in the gear receiving space 64 of the tool drum 54 and a non-rotatably connected to the tool carrier 51 drive gear 58 and each with this includes meshing and planetary gears rotating output gears 57 which are rotatably connected to the individual tool shafts 55. Due to the angling between the shaft axes W, H of the tool shafts or the tool drum 54, the angle gear 70 has a correspondingly inclined toothing on the bevel gears 58, 57. The angling 74 avoids or reduces the grinding of the outer tool rows of the machining tools 66 on the tool carriers 65, and all the tool shafts 55, distributed over the circumference, can be angled with the same angled portion 74. However, individual tool shafts can also be executed in groups with different bends, in which case, in particular if different rotational speeds of the tool shafts are to be achieved, two or more drive gears could also be arranged in the gear receiving space.

In Fig. 3 is a device 110 for a main field of application of a device according to the invention, namely the undercut removal of rocks, coal or other minerals shown in underground or surface mining. Functionally identical components as in the first embodiment are provided with increased by 100 reference numerals. A drive shaft 103 is in a similar with a machine boom or the like. mounted drum carrier 101 and rotatably mounted connected to a tool drum 104, which has distributed over the circumference a plurality of radial passages 112, in each of which tool shafts 105 are arranged such that the shaft axes W of each tool shaft 105 is perpendicular to the axis of rotation or drum axis H of the tool drum 104. The entire apparatus 110 again has only one rotary drive which can be coupled to the gearwheel 103B fastened to the drive shaft 103 and the rotation of the individual tool shafts 105 is effected by means of an angular gear 120, which has a central, concentric with the drum axis H and the drum carrier 101 has locked common drive gear 108 for all planetary gears and attached to the free ends of the tool shafts 105 driven gears 107 has. In contrast to the two previous embodiments, however, the machining tools consist of undercutting working tools 116 with here conically outward or with increasing distance from the drum axis H to be tapered tool carriers 115. The tool carrier 115 has four tool lines 121, 122, 123 in the illustrated embodiment , 124, wherein on each tool line 121-124 one or more, in turn, only indicated by their chisel tips machining tools 116 are arranged here the material to be removed step 130 and split undercutting. The processing tools 116 on the different tool lines 121-124 break through their conical placement on the tool carrier 115, the material to be removed evenly, wherein the individual tool lines 121-124 are preferably arranged such that processing tools 116 on different tool lines 121-124 each have the same size Remove volume. Due to the conical arrangement of the processing tools 116 on the conical tool carrier 115, each tool on the radially outer cutting lines has sufficient clearance for the undercut releasing material. In Fig. 3 the working direction of the device 110 according to the invention is shown with the arrow A and it is easy to see that the working direction A of the device 110 according to the invention is parallel to the drum axis H. The feed movement of the device 110 into the material 130 to be removed takes place correspondingly perpendicular to the working direction A, thus perpendicular to the drum axis House Fig. 3 It can also be clearly seen that the individual processing tools 116 rotate transversely to the drum axis H.

The structure and operation of the device 160 according to the invention Fig. 3 will also be out Fig. 4 can be seen, in which a view of the end face 104 'of the tool drum 104 is shown. Distributed over the circumference of the tool drum 104 here are a total of six tool shafts with associated, conical or rounded tool carriers 115 arranged at their ends, each tool carrier 115 is provided with distributed on three tool lines arranged round shank chisels as a processing tool 116. Due to the superimposed rotation of the tool drum 104 and the tool shafts 115 rotating with the tool shafts, each individual machining tool 116 executes a short cut in the material 130 to be abraded, with the cut surfaces for the different tool rows being sickle-shaped. The machining tools of the same cutting rows on different tool carriers are in this case arranged such that a machining tool 116 of a trailing tool carrier 115 carries out the removal of the material or the knocking out of the material at a location other than the machining tool 116 of the previous tool shaft. With these short tool engagement times, an enormous cutting performance with low contact force for the device 110 and at the same time low wear of the individual machining tools 116 can be achieved. The working direction of the device 110 has parallel to the drum axis in the plane of drawing

Fig. 5 shows a fourth embodiment of a device 160 according to the invention. The tool drum 154 as well as between the individual tool shafts 155 and the common drive wheel 157 intermediate angle gear 170 has in principle the identical structure as in the embodiment according to Fig. 2 and reference is made to the statements there. The device 160 has a special configuration for tool shafts 155 whose shaft axes W are inclined to the drum axis H of the tool drum 154. As in the previous embodiments, the tool shafts 155 between their shaft ends 159, to which the tool carrier 165 are preferably releasably secured, and the radially inner shaft ends 155 ', to which the driven gears 157 are attached, mounted with a bearing formed by two Kegelradlagern 156 in the radial, here oblique radial passages 162. In contrast to the previous embodiments, however, all circumferentially distributed tool shafts 155 are rotatably supported at their free ends 155 '' by means of a bracket 180. The bracket 180 extends approximately U-shaped over the drum side, on which the drive gear 153 B is arranged for coupling with the rotary drive, so that the angled standing processing tools 166 outside the periphery of the tool drum 154 respectively at their most projecting ends freely and unhindered from can pierce the brackets 180 in the material to be removed. The brackets 180 are guided around the outside around the tool carrier 165 and provided with a parallel to the shaft axis W of the tool shafts 155 extending pin 181, which dips with the interposition of other tapered roller bearings 182 in the tool carrier 165 and the shaft end. A corresponding embodiment is particularly advantageous if the processing tools 166 of long milling drums or the like. consist.

In the embodiments described above, the tool drum was supported on one side only on one drum carrier. The FIGS. 6A and 6B show a further embodiment of a device 210 according to the invention with a common rotary drive for the tool drum 204 and here perpendicular, but also angled to the drum axis H tool shafts 205. The rotation, which is introduced via the gear 203 B in the drive shaft 203, as be transferred in the previous embodiments via the angle gear 220 in the tool shafts 205 with appropriate translation. At the gear side 203B and the gear receptacle 214 opposite drum side is in the in the FIGS. 6A and 6B illustrated apparatus 210 on the front side 204 'projecting, strong pin 233 formed which is centered to the drum axis H, the apparatus 210 on both sides of the tool drum 204 on the one hand via the pin 233 and on the other to support over the drum carrier 201. The working movement of the device 210 is in Fig. 6A drawn with the arrow A parallel to the drum axis H and Fig. 6B shows for the device 210 with the total six evenly distributed over the circumference arranged tool shafts 205, the rotational direction R of the tool drum 204th Fig. 6B also clearly shows how with the device 210 material in the working direction, ie in Fig. 6B into the drawing plane, is removed.

Fig. 7 shows a further device 260 according to the invention with a both sides mounted tool drum 254 similar to the embodiment in Fig. 6B , In contrast to the previous embodiment, however, not six, but only four tool shafts 255 are provided here with suitable tool carriers 265, for example, designed as milling drums. Between each offset by 90 ° with respect to each other arranged tool shafts 255 a radially over the circumference 254 '' of the tool drum 254 projecting blade 276 is fixed, with which by means of the rotating processing tools on the tool carriers 265 at the mining front in the rock 280 dissolved material such as in particular Coal can be loaded into a conveyor (not shown). The device 260 is moved along a conveyor, for example, and moves in Fig. 7 into the drawing plane. The machining tools on the tool carriers 265 release material in the direction of rotation R due to the superimposed rotational movement of the tool shafts 255 and the tool drum 254, and the apparatus 260 conveys the dissolved material into a conveyor by means of the scrapers or blades 276 via a suitable ramp. The feed movement of the device 260, as indicated by the arrow Z, perpendicular to the axis of rotation H of the tool drum 254 and the tool drum 254 can be held on both sides as in the previous embodiment by means of the schematically indicated pin 283.

Fig. 8 shows a device 310 in which the drive for the tool drum 304 is decoupled from the rotary drive for the tool shafts 305. The device 310 can in turn be held by a drum carrier 301, for example, on a machine boom or support arm 340 is attached. In contrast to the previous exemplary embodiment, the tool drum 304 is provided with a hollow drum extension 335 projecting axially on one side, which is rotatably supported in the shaft receptacle 311 of the drum support 301 by means of two tapered roller bearings 302 so that the tool drum 304 can rotate about the shaft or drum extension 335 is supported on the drum carrier 301. At the free, protruding from the drum support 301 end of the drum extension 335, a toothing 337 is formed or fixed a gear, via which the shaft extension 335 and thus the tool drum 304 can be connected or coupled to a drum drive, not shown. The drum extension 335 forms, with its hollow shaft bore 336, a shaft receptacle for a gear drive shaft 325 mounted inside the shaft bore 336 by means of a tapered roller bearing 338 arranged in an X arrangement. The gear drive shaft 325 is provided with a toothing 326 at its end protruding from the shaft bore 336. The toothing 326 of the gear drive shaft 325 can be coupled to a separate from the drum drive, not shown gear drive to adjust the speed ratio between the speed of the tool drum 304 and the speed of the tool shafts 305 arbitrarily. The relatively long gear drive shaft 325 is supported with its second, from the receiving bore 336 of the drum extension 335 projecting and the transmission receiving space 314 through end by means of a second tapered roller bearing 326 in a bearing cap 319, screwed from the opposite side of the two drives 304 of the drum 304 here is. The gear receptacle 314 is thus open in the device 310 on the facing in the direction of A end face 304 and closed there by means of the bearing cap 319. The device 310 has tool shafts 305 whose tool shafts W angled at an angle of approximately 80 ° to the drum axis H run. The rotation, which is introduced via the gear 326 in the gear drive shaft 325, is transmitted by means of a sun gear rotationally fixed to the transmission input shaft 325 connected to the drive gear 308 and one rotatably connected to each tool shaft 305 driven gear 307, wherein the device 310 according to Fig. 8 the entire angular gear 320 well protected is arranged in the transmission receptacle 314. At the free shaft ends 309 of the tool shafts 305 conical, undercutting tool carrier 305 are in turn releasably secured via the fastening screws shown. The device 310 in FIG Fig. 8 is provided with individual processing tools 316 for three tool lines 321, 322, 323 to remove undercutting and possibly with the same cutting performance material on the mining front. An exchange of the tool shafts 305 can be carried out in the device 310 in that the bearing shell 319 is released and in each case the output gear 307 is removed after removal of the drive gearwheel 308 lying adjacent to the bearing cap 319. The output gears 307 and the tool shafts 305 are then freely accessible via the transmission receptacle 314 and when the driven gear 307 and dissolved bearing ring 326 for the tapered roller bearings 306, the tool shafts 305 could be pulled outward from the radial passages 312.

In the embodiment of the device 360 in FIG Fig. 9 a drum drive for the tool drum 354 on one side of the tool drum 354 and the gear drive for the bevel gear 370 axially offset on the other side of the tool drum 354 can be arranged. The distributed over the circumference with a plurality of radial passages 362 for receiving the tool shafts 355 provided tool drum 354 has a relatively short annular extension 385, which is mounted on a first bearing 352 in a connectable to a drum carrier or part of a drum support bearing shell 351A. The ring or drum extension 385 forms with its interior in turn a shaft receiving 386 for a gear drive shaft 375, which protrudes with one end of the shaft receiving 386 and is provided at the corresponding exposed end with a toothing 376 for coupling with a gear drive. A second pivot bearing 352 for supporting the device 360 is located on the opposite side of the tool drum 354 and is held with a second bearing shell 351B, which in turn or the like with a tool carrier or the arm of a cantilever. can be connected. At the side opposite the annular extension 385, a here multiply stepped bearing extension 390 is screwed to the tool drum 354, which is provided at its free end with a toothing 387, to which a drum drive can be coupled. The bearing extension 390 is supported on one of its steps and the further bearing 352 on the second bearing shell 351B. The inside of the bearing extension 390 forming here a screwed-on bearing flange is provided with a recess 391, in which the second, free end of the gear drive shaft 375 is supported by means of a second tapered roller bearing 388. The transmission of the rotation of the gear drive shaft 375 to the tool shafts 355, whose shaft axes W are perpendicular to the drum axis H, again takes place via an angle gear 370 with a non-rotatably mounted on the gear drive shaft 375 drive gear 358, with each one as planetary gear with the tool drum 354 rotating and the tool shaft 355 driving output gear 357 meshes. By the end coupling of the drive for the tool drum 354 and the drive for the tool shafts 355, the trajectory of the individual cutting edges can be determined and thus the grain size of the dissolved material can be reliably adjusted to the desired size. If the material properties change, the speed ratio can be infinitely adjusted and adapted to the respective requirements without interrupting the cutting work.

In the Fig. 10 In order to realize the cutting movement according to the invention, the device 410 shown again has a plurality of tool shafts 405 distributed over the circumference of a tool drum 404 whose shaft axes W are angled relative to the drum axis H of the tool drum 404. The individual tool shafts 405, which are equipped with conical, undercutting working tool carriers 415, are respectively arranged in bearing bushes 445, which are screwed on the front side on the circumference of the tool drum 404 by means of a plurality of fastening screws 446. Each bearing bush 445 is exchangeable like a cartridge and inserted via the screw 446 from the peripheral side into a drum chamber 412. The device 410 could be easily converted to a configuration with standing perpendicular to the drum axis H tool shafts by bearing bushes are used, in which the tool shafts are arranged vertically. Within each bearing bush 445 are the tool shafts 405 in turn received with two tapered roller bearings 406, a bearing ring 426 and a shaft seal 417 and on the free, inner shaft end of each tool shaft 405, an output gear 407 is arranged as a bevel gear of an angle gear 420. The drive of the tool drum 404 takes place in the device 410 by means of a toothed belt via a pulley 426 on the right side of the device 410, while the drive of the tool shafts 405 via a pulley 437 on the left side of the device 410. The pulley 426 for drum drive is connected to the drive side of a first, enclosed with a housing and shown only on its housing hub gear 497 and the pulley 437 is connected to the drive side of a second hub transmission 498. The hub gear 497 for driving the tool drum 404 is mounted on a first mounting flange 340A and the hub gear 498 for the drive gear 408 on a second mounting flange 440B, via which the entire device 410 can be attached to a drum carrier, not shown, such as a forked cantilever. The output side 498 'of the second hub gear 498 is bolted to the drive gear 408 via the screws 418 and the output side 497' of the first hub gear 497 is bolted to the tool drum 404 via the screws 499. Between the in Fig. 10 left drum ring 404A of the tool drum 404 and the drive gear 408, a ball bearing 495 is arranged, which is held by means of a bearing ring 494 and a shaft seal 493 protected against contamination in position. The common for all driven gears 407, driven via the hub gear 498 drive gear 408 can thus rotate at any speed relative to the likewise driven tool drum 404, whereby the speed ratio between the tool drum 404 and tool shafts 405 can be set almost arbitrarily. The device 410 is extremely compact, since both hub gears 497, 498 are designed as slide-in gear, are concentric with the drum axis H and substantially fill the interior space inside the tool drum 404.

The devices according to the invention can be moved in a straight line in the working direction and then moved back in the opposite direction after a feed movement in the feed direction has taken place. Fig. 11 shows an embodiment for a pendulum use of a device according to the invention 510 with here four distributed over the circumference of a tool drum 504 tool shafts 505. The tool drum 504 is held on both sides of two boom arms 590A, 590B of a boom 590, which can be pivoted about the pivot point D. During pivoting, the machining tools 516 on the tool carriers 515 carry the material 530 in the pivoting direction S. In this case, both the tool carriers 515 rotate about the shaft axes W and the tool drum 504 about the drum axis H. It is possible to remove only in one direction at a time; Alternatively, it can also be removed in both directions of pivoting, so that after a completed pivoting about a tool width is delivered again, in order subsequently to ablate material in the other pivoting direction on the removal front 530. Further, it would be possible to make the boom 590 movable in height in order to gain even a larger cross section.

Those skilled in the art will recognize from the foregoing description numerous modifications which are intended to be within the scope of the appended claims. It is understood that in almost all embodiments instead of vertical tool shafts and angled tool shafts and vice versa could be used. Instead of an angle gear, a crown gear could be used in each case, which would have the advantage that no forces would be introduced parallel to the axis of the tool shafts in the drive shaft during the mining of rock. In the transmission recording could also be a bevel gear with multiple outgoing shafts are placed or the tool shafts or the like via cardan shafts. are driven. The device can be used in a wide variety of fields and depending on the purpose with almost all known tools. The preferred fields of application are, in particular, mining for the production of ores or coal, road construction for the removal of deposits, open-pit mining, tunneling for the advancement of tunnels, shaft construction, civil engineering when pulling eg trenches or building construction for the renovation of floors and walls.

Claims (27)

1. An apparatus for the milling and/or drilling cutting of materials, in particular for the removal of rock, minerals or coal, with a tool drum (4) which is mounted on a drum carrier (1) rotatably about a drum axis (H), in which a plurality of tool shafts (5), which carry cutting tools (16) at their ends (9) projecting from the tool drum (4), are rotatable drivable mounted, at least two of the tool shafts (5) being drivable by a common gear drive which has power take-off gearwheels (7), arranged fixedly in terms of rotation on the tool shafts (5), and a common drive element (8) which cooperates with the power take-off gearwheels (7), the drive element (8) and the tool drum (4) being rotatable in relation to one another, characterized in that the shaft axes (W) of the tool shafts (5) stand transversely to the drum axis (H).
2. The apparatus as claimed in claim 1, characterized in that the shaft axes (W) of the tool shafts (5; 105; 205; 355) stand perpendicularly to the drum axis (H).
3. The apparatus as claimed in claim 1, characterized in that the shaft axes (W) of the tool shafts (55; 155; 305; 405) stand angled to the drum axis (H), the angle (74) of the angling preferably being greater than about 80°.
4. The apparatus as claimed in one of claims 1 to 3, characterized in that, in operational use, a working movement (A) takes place parallel to the drum axis (H) and/or a feed movement (Z) takes place perpendicularly to the drum axis (H).
5. The apparatus as claimed in one of claims 1 to 4, characterized in that all the cutting tools (16; 66; 116; 166; 216; 316) are located radially outside the tool drum (4) and, in operational use, remove material in a sickle-shaped manner.
6. The apparatus as claimed in one of claims 1 to 5, characterized in that, in operational use, by virtue of the rotational movement of the tool drum (4) the cutting tools rotate transversely to the drum axis (H) and remove the material outside a circumference (4'') of the tool drum (4).
7. The apparatus as claimed in one of claims 1 to 6, characterized in that the tool drum (4; 54; 104; 154; 204) and at least some of the tool shafts have a common rotary drive, wherein preferably the rotary drive has a drive shaft (3; 53; 103; 153; 203), which is connected fixedly in terms of rotation to the tool drum (4; 54; 104; 154; 204), is mounted in the drum carrier (1) and can be driven by means of a drive device, and one or at least one driving gearwheel (8; 58; 108; 158; 208), as a drive element, which is fastened fixedly in terms of rotation to the drum carrier and which meshes with the power take-off gearwheels (7; 57; 107; 157; 207).
8. The apparatus as claimed in claim 7, characterized in that the driving gearwheel (8; 58; 108; 158) and the associated power take-off gearwheels (7; 57; 107; 157) form an angular gear (20; 70; 120; 170) consisting of toothed bevel wheels and having planet wheels, or that the driving gearwheel and the associated power take-off gearwheels form a contrate gear consisting of a toothed contrate wheel and of cylindrical gearwheels as power take-off gearwheels.
9. The apparatus as claimed in one of claims 7 or 8, characterized in that the tool drum (204; 504) is supported on both sides of the tool shafts (205) on a tool carrier, a journal (233) or bearing for holding the tool drum (204) on two sides being formed preferably on that side of the tool drum (204) which lies opposite the drive device.
10. The apparatus as claimed in one of claims 1 to 6, characterized in that the tool drum (304; 354; 404) has a drum drive which is decoupled from a gear drive for the drive element (308; 358; 408).
11. The apparatus as claimed in claim 10, characterized in that the drum drive and/or the gear drive consist/consists of variable drives.
12. The apparatus according to claim 10 or 11, characterized in that the tool drum (304) is provided with an axially projecting shaft receptacle (335) in which a gear drive shaft (325) connected fixedly in terms of rotation to the driving gearwheel (308) and projecting on both sides out of a reception bore (336) of the shaft receptacle is rotatably supported.
13. The apparatus as claimed in claim 10 or 11, characterized in that the drum drive is arranged or can be coupled on one side of the tool drum (354; 404) and the gear drive is arranged or can be coupled, offset axially, on the opposite side of the tool drum (354; 404).
14. The apparatus as claimed in claim 13, characterized in that the tool drum (354) is provided on the opposite side with an axially projecting annular extension (385) with a shaft receptacle (386), in which a gear drive shaft (375) connected fixedly in terms of rotation to the driving gearwheel (358) and projecting on both sides out of a reception bore of the shaft receptacle (386) is supported rotatably, and has on the other side a bearing extension (390) on which the drum drive is arrangable or can be coupled.
15. The apparatus as claimed in claim 14, characterized in that the gear drive shaft (375) is mounted rotatably by means of a first bearing (388) in the shaft receptacle of the annular extension and by means of a second bearing (388) in the bearing extension (390), wherein preferably the bearing extension (390) consists of a bearing flange screwed to the tool drum.
16. The apparatus as claimed in claim 13, characterized in that the tool drum (404) is connected fixedly in terms of rotation to the power take-off side of a first hub gear (497) and the driving gearwheel (408) is connected fixedly in terms of rotation to the power take-off side of a second hub gear (498), the two hub gears being arranged in a central receptacle, wherein preferably, the hub gears (497, 498) are designed as push-in gears with preferably encapsulated gear stages, the fastening flanges of the two hub gears being fastenable or fastened to the drum carrier.
17. The apparatus as claimed in one of claims 12 to 16, characterized in that the driving gearwheel (308, 358, 408) and the power take-off gearwheels (307; 357; 407) are designed as bevel wheels of an angular gear with planet wheels, or in that the driving gearwheel is designed as a contrate wheel and the power take-off gearwheels are designed as cylindrical gearwheels, meshing with this, of a contrate gear with planet wheels.
18. The apparatus as claimed in one of claims 1 to 17, characterized in that the power take-off gearwheels of all the tool shafts (5) are in toothed engagement with a single common driving gearwheel (8).
19. The apparatus as claimed in one of claims 1 to 18, characterized in that the tool shafts (5) are arranged, distributed uniformly over the circumference, in the tool drum (4), and/ot that each cutting tool (16) arranged on a tool shaft (5) is arranged, offset by an angular amount or at a distance from the drive shaft, in relation to the arrangement of a cutting tool (16) of a tool shaft (5) lying in front of or behind it in the drum circumferential direction.
20. The apparatus as claimed in one of claims 1 to 19, characterized in that the cutting tools (116; 316) of preferably all the tool shafts consist of roller chisels or straight shank chisels which, for the undercutting removal of rock, coal or minerals in a plurality of layers, are arranged on outwardly tapering tool carriers (115; 315; 415) or ends of the tool shafts, wherein preferably the tool carriers (315; 415) or ends of the tool shafts taper conically, arcuately or in a stepped manner.
21. The apparatus as claimed in claim 20, characterized in that the cutting tools on each tool shaft are arranged in cutting rows (121-124) on pitch circles with different diameters, the distance between two cutting rows preferably being selected in such a way that all the cutting rows remove sickle-shaped cutting surfaces of approximately identical size.
22. The apparatus as claimed in one of claims 1 to 19, characterized in that the cutting tools of one or more of the tool shafts consist essentially of milling rollers (15; 65; 165), wherein preferably the milling rollers are cylindrical or taper conically toward the cut rock or the like.
23. The apparatus as claimed in one of claims 1 to 22, characterized in that the cutting tools of tool shafts succeeding one another in the circumferential direction of the tool drum are arranged so as to be phase-offset with respect to one another.
24. The apparatus as claimed in one of claims 1 to 23, characterized in that the tool shafts (155) are supported rotatably at their radially outer end by means of a yoke (180) with a journal (181) which is fastened to the tool drum, or that the tool drum (254) is provided between adjacent tool shafts with radially extending scrapers or shovels (276).
25. A method for the milling or removal of rock or the like, using an apparatus as claimed in one of claims 1 to 24, in which the rotational speed of the tool shafts (5; 105; 155;205; 305; 355; 405), the rotational speed of the tool drum (4; 54; 104; 154; 204; 304; 404; 504), the advancing speed of the apparatus parallel to the drum axis and/or the angular position of the cutting tools (16; 116; 316), arranged on the individual tool shafts, in relation to the angular position of the cutting tools of the tool shafts lying in front of or behind them in the circumferential direction are set such that a cutting tool of a following tool shaft does not strike at the rock or the like at the same striking point as a cutting tool of a preceding tool shaft.
26. The method as claimed in claim 25, characterized in that, in operational use, only a few cutting tools are simultaneously in engagement with the material to be milled or to be removed.
27. The use of an apparatus as claimed in one of claims 1 to 24 and/or of the method as claimed in one of claims 25 or 26 for breaking down mineral extraction products, such as coal, ore-bearing rock or the like, or for the cutting of concreted or asphalted surfaces or buildings.

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