EP1734224B1 - Antriebsvorrichtung für rotierende, mit Oszillationsüberlagerung arbeitende Werkzeuge und Werkzeug hiermit - Google Patents

Antriebsvorrichtung für rotierende, mit Oszillationsüberlagerung arbeitende Werkzeuge und Werkzeug hiermit Download PDF

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Publication number
EP1734224B1
EP1734224B1 EP06010277A EP06010277A EP1734224B1 EP 1734224 B1 EP1734224 B1 EP 1734224B1 EP 06010277 A EP06010277 A EP 06010277A EP 06010277 A EP06010277 A EP 06010277A EP 1734224 B1 EP1734224 B1 EP 1734224B1
Authority
EP
European Patent Office
Prior art keywords
tool
driving device
drive
shaft
carrier
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06010277A
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German (de)
English (en)
French (fr)
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EP1734224A1 (de
Inventor
Joachim Raschka
Jens Steinberg
Ulrich Bechem
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Global Mining HMS GmbH
Original Assignee
Bucyrus DBT Europe GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bucyrus DBT Europe GmbH filed Critical Bucyrus DBT Europe GmbH
Priority to PL06010277T priority Critical patent/PL1734224T3/pl
Publication of EP1734224A1 publication Critical patent/EP1734224A1/de
Application granted granted Critical
Publication of EP1734224B1 publication Critical patent/EP1734224B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21C—MINING OR QUARRYING
    • E21C25/00—Cutting machines, i.e. for making slits approximately parallel or perpendicular to the seam
    • E21C25/16—Machines slitting solely by one or more rotating saws, cutting discs, or wheels
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
    • E21D9/00—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries
    • E21D9/10—Making by using boring or cutting machines
    • E21D9/1006—Making by using boring or cutting machines with rotary cutting tools
    • E21D9/104—Cutting tool fixtures
    • E21D9/1046—Vibrating

Definitions

  • the invention relates to a drive device for rotating, working with OszillationsGermanlagerung tools, comprising a drive housing, a rotatably mounted in the drive housing support sleeve, a rotatably mounted in the support sleeve drive shaft, a tool carrier for receiving processing tools and an oscillation exciter for generating the Oszillationsüberlagerung for the tool carrier.
  • the activation of the impact pulse takes place by means of suitable striking mechanisms, imbalance generators and, in particular, eccentric shafts which carry free-rotating or driven processing tools.
  • Overlapping tools are used in particular in mining, tunneling and road construction, e.g. Hard rock or other mineral rock must be loosened, milled or otherwise processed. Due to the impact overlay, the required pressure forces on the material to be removed or removed can be reduced to 1/10 of the required without impact overlapping pressure forces, which allows the use of lighter and smaller tools and machinery and at the same time increases the extraction capacity or propulsive power of the tools.
  • Generic drive devices for impact superimposed tools are from the EP 329 915 A1 and EP 455 994 B1 known.
  • the generic drive devices each comprise a rotatably mounted and driven with a support sleeve drive carrier sleeve with eccentrically arranged inner bore in which a rotatably coupled to the tool carrier shaft is mounted, which is usually referred to in the art as an eccentric shaft.
  • the carrier sleeve are Associated counterweights for a dynamic balancing of the drive device and the eccentric shaft is driven by a second drive, which may consist of a separate drive or a reduction gear.
  • the speed ratio between the speed of the eccentric shaft and the speed of the carrier sleeve is fixed; in drive devices with a separate drive for the eccentric shaft, the speed ratio is variable within limits.
  • the offset of the eccentric shaft in the carrier sleeve can be eg 5 mm and the speed ratio of the faster rotating eccentric shaft to the slower rotating carrier sleeve can be about 30: 1, so that mounted on the tool carrier machining tools with a high number of radial impacts on the degraded or ., impact material or stone to be processed.
  • the achieved in the generic tools with impact overlapping dissolution or degradation is already many times higher than in conventional drive devices without impact overlay.
  • the object of the invention is to provide a drive device for rotating and working with impact overlapping tools, in which the storage and sealing of the drive shaft and carrier sleeve is improved in order to increase the service life of the drive devices and in particular equipped with these tools.
  • the excitation device for the impact superposition is an oscillation excitation device which has at least two intermediate shafts for each tool carrier, which are respectively coupled via an eccentric part to the tool carrier and can be driven synchronously.
  • the drive devices according to the invention have a constructive one fundamentally different structure than the generic impact superimposed drive devices.
  • the impact induction which is referred to in the invention to distinguish from the prior art as oscillation, is no longer by means of a single, eccentrically mounted or arranged eccentric shaft, but by means of at least two intermediate waves, which are coupled in a suitable manner via an eccentric eccentric with the tool carrier are and are drivable synchronously.
  • one or each tool carrier at least two intermediate shafts are assigned, they can be dimensioned considerably smaller than in the prior art, which greatly simplifies the sealing of the shafts and the storage of intermediate shafts.
  • a comparatively large-sized support sleeve which had to be assigned in the prior art, a correspondingly large-sized counterweight.
  • this is no longer necessary.
  • oscillating superimposed working tools can be driven, which can build much larger and more versatile than in the prior art, without the storage or shaft seal of the intermediate shafts, the support sleeve and / or the drive shaft are problematic.
  • Another advantage is that the entire drive-side part according to the invention is not burdened with the oscillations of the tool carrier generated by the Oszillationserreger Anlagenen.
  • all intermediate shafts are mounted concentrically to the axis of rotation of the drive shaft in the carrier sleeve.
  • the drive shaft is mounted concentrically to the support sleeve, but also all the intermediate shafts are mounted concentrically to the common axis of rotation.
  • the plurality of intermediate shafts can then in particular be distributed symmetrically and arranged on a circumferential circle arranged around the axis of rotation of the drive shaft and stored.
  • the intermediate shafts with the drive shaft via a transmission particularly advantageous via a gear transmission, be coupled.
  • a gear transmission is made possible in that the axes of rotation of the intermediate shafts have a constant distance from the common axis of rotation of the drive shaft and support sleeve, regardless of their current position.
  • the gear transmission having a rotatably connected to the drive shaft central gear and each rotatably connected to the intermediate shafts and standing in mesh with the central gear planetary gears.
  • the gear transmission having a non-rotatably connected to the drive shaft central gear and rotatably connected to the intermediate shafts planetary gears, in addition between the central gear and the planetary gears intermediate gears are arranged, which are rotatably mounted in the carrier sleeve.
  • the rotational speed of the intermediate shafts may substantially or exactly correspond to the rotational speed of the drive shaft. The latter is particularly advantageous if a single tool carrier is associated with a rotatably connected to the drive shaft balance weight. It will be apparent to those skilled in the art that the ratio of reduction and reduction depends on the design of the individual gears.
  • the eccentricity is formed directly between the tool carrier and the intermediate shafts and is achieved by means of the eccentric parts.
  • the eccentric parts can be components of the intermediate shafts and be formed by means of an eccentric eccentric to the central axis of the intermediate shaft arranged eccentric pin.
  • one-piece intermediate shafts are provided, on which the eccentric pin is integrally formed.
  • the eccentric portions may be eccentric shaft extensions arranged eccentrically to the central axis of the intermediate shaft, which are detachably connected to the intermediate shaft.
  • intermediate shafts with eccentric shaft extensions and intermediate shafts can be used with concentric shaft journals, in which case the eccentric parts are formed by means of sleeves with eccentric shaft receiving.
  • the shaft journals then engage in the shaft seats, whereby the eccentric arrangement between the intermediate shafts and the tool carriers is formed.
  • the shaft receiving and the shaft journal are conical and non-rotatably intermesh, wherein preferably the rotationally fixed connection is secured by means of a securing means.
  • a connection with conical parts facilitates the disassembly of the tool carrier or carriers from the drive-side part, which comprises the carrier sleeve, the drive shaft and the bearing of the intermediate shafts.
  • the non-rotatable connection between the conical parts may also consist of an oil-press fit or a press-fit releasable by pressurization with hydraulic medium.
  • the assembly is then by a Aufpreßhabilit, with oil or other hydraulic fluid is pressed into the joint gap between the conical parts to expand the outer part for mounting.
  • the necessary pressing pressure can be achieved for example with a multiplier or a hydraulic press. It is understood that in turn then for disassembly an expansion of the outer conical part must be done by means of the hydraulic medium.
  • the drive device or a tool with the drive device can be designed in many different ways.
  • the drive device or the tool has a plurality of tool carriers, wherein at least two intermediate shafts are coupled to each tool carrier.
  • the oscillation generated by the oscillation exciter device for the first tool carrier is out of phase with respect to or to the oscillation (s) generated by the further oscillation exciter device (s).
  • a dynamic balancing of a tool carrier can be carried out exclusively by a phase-shifted oscillation of at least one further tool carrier.
  • an even number of tool carriers can be provided, wherein in each case the mutually opposite tool carriers are superimposed by the arrangement of the eccentric parts of the intermediate shafts of the associated Oszillationserreger wornen with a phase-shifted by 180 ° oscillation pulse.
  • these tool carriers are superimposed by 180 ° out of phase with an oscillation pulse and the oscillation pulse is directed either outwards or inwards, for example, in the case of both tool carriers at a specific point in time.
  • two pairs are then formed, for example, wherein two tool carriers are superimposed within a pair with an oscillation pulse phase-shifted by 180 °, and a phase shift of 90 ° is particularly advantageous between the pairs.
  • All four tool carriers can be arranged in one plane.
  • three tool carriers are provided, wherein the individual tool carriers are superimposed by the arrangement of the eccentric parts of the intermediate shafts of the associated Oszillationserreger foundeden with a phase-shifted by 120 ° oscillation pulse. Again, the dynamic balancing is done exclusively by the phase-shifted oscillation pulse superposition of the other three tool carrier, without additional balancing weights are necessary.
  • two tool carriers arranged in different planes can be provided, which are superimposed by the arrangement of the eccentric parts of the intermediate shafts of the associated oscillation excitation devices with an oscillation pulse phase-shifted by 180 °.
  • the embodiment with tool carriers arranged in different planes if the machining tools attached to them lie in different planes, has the advantage that the pressing forces, which are e.g. are applied by a feed drive, are further reduced, since the individual tool holder are at the same time at no time in engagement with the stone to be removed.
  • each tool carrier three intermediate shafts are assigned, which are arranged alternately distributed over the circumference.
  • the associated tool carrier can be formed in particular spade-shaped, propeller-shaped or star-shaped.
  • an arrangement with three intermediate shafts can also take place with drive devices or tools with only two tool carriers or even only one tool carrier and / or even with spade-shaped or propeller-shaped tool carriers, the receiving areas for the processing tools can be formed on the tool carriers by interleaving or cranking, that the editing tools lie in one plane and act.
  • the tools can be mounted directly on the tool carrier. However, it is particularly advantageous if one-piece or multi-part ring-segment-shaped tool holders with fastening devices for a plurality of processing tools are fastened to each tool carrier.
  • the drive device according to the invention can be used for drilling, milling or removal of rocks and minerals.
  • the processing tools used may consist in particular of self-sharpening round chisels, flat chisels, discs or roller drilling tools.
  • the carrier sleeve is driven at a significantly lower rotational speed than the intermediate shafts, wherein preferably the speed ratio between the rotational speed N 2 of the intermediate shafts and N T of the carrier sleeves> 22 and in particular between 25: 1 and about 31: 1 in dependence from the degraded rock, the number of processing tools, etc. is.
  • the carrier sleeve can be driven with a carrier sleeve drive and the intermediate shafts with an intermediate drive assigned to the drive shaft and a feed rate of the drive device is adjustable via a feed drive, wherein a control device the carrier sleeve drive and the feed drive in response to the intermediate shaft drive, and thus from the drive for the drive shaft, controls.
  • the coupling between the intermediate shaft drive and the carrier sleeve drive can also be achieved by means of a transmission with a fixed transmission ratio.
  • Fig. 1 and 2 is a designated overall by reference numeral 1, impact overlapping working tool only one impact whip generating or effecting drive device 10 shown, the drive housing 11, a driven gear 12 via a drive shaft 13, a driven by a gear 14 and inside the drive housing 11th rotatably mounted carrier sleeve (15, Fig. 3 ) and here two half-disc-shaped tool carrier 16A, 16B has.
  • the coupled with the gears 12, 14 drives and other parts of the tools are not shown.
  • On each tool holder a semi-annular tool holder 17A, 17B is releasably attached, which are equipped here with six arranged in tool holders 2 round shank chisels 3 as processing tools.
  • the two tool holders 17A, 17B are formed ring-segment-shaped, lie with positive engagement at the edges of the tool carrier 16A, 16B and are there releasably secured by means of screw 4.
  • the chisel tips of the processing tools 3 are in the labor input of the tool 1 at a mining face 5 with degraded rock, especially hard rock, in engagement and solve the feed of the tool 1 in the direction of arrow V in Fig. 1 Chunks of material on the mining front 5 from.
  • the carrier sleeve drive not shown, the rotatably coupled to the support sleeve gear 14 is driven during operation, whereby the tool carrier 16 A, 16 B together in rotation in the direction of arrow R in Fig. 2 be offset.
  • each tool carrier 16A, 16B move eccentrically about axes of rotation of intermediate shafts, which, as will be explained, are driven by the drive shaft 13 and an intermediate shaft drive connected to the gear 12, whereby the processing tools 3 in addition to the rotation is impelled by a shock pulse, the release of the rock on the mining front 5 significantly improved, as is known for working with impact overlapping tools in itself.
  • the intermediate shafts, with which the tool carriers 16A, 16B are subjected to the impact superposition referred to below as oscillation superimposition, are each accessible from the front side of the tool 1 or tool carrier 16A, 16B via shut-off flaps 6.
  • each tool carrier 16A, 16B are each assigned three intermediate shafts.
  • FIGS 3 and 4 illustrate a first embodiment of the drive device 10 according to the invention explained.
  • Fig. 3 shows in a sectional view the rotatably mounted on the bearing 18 on the inside of the housing 11 mounted support sleeve 15 and in turn via bearings 19 in a central sleeve bore of the support sleeve 15 mounted drive shaft 13.
  • the drive housing 11 is provided with screw receptacles 7, so that the entire drive device compact unit can be removed from the frame or housing of a tool.
  • both the drive shaft 13 and the support sleeve 15 the identical, denoted by D axis of rotation, and the support sleeve 15 and the drive shaft 13th thus rotate relative to each other without eccentricity.
  • the support sleeve 15 extends at one end into a carrier sleeve head 15A, on whose front side a closure disk 20 is fastened, which also carries the front bearing 19 for the drive shaft 13.
  • Both the head 15A and the closure disk 20 are provided here with a total of six receptacles 21 for intermediate shafts 30, on each of which an eccentric 32, the tool carrier 16A and 16B are attached.
  • the eccentric part consists of an integrally formed on the intermediate shaft 30 shaft extension 32, the central axis 33 is arranged eccentrically to the shaft axis 31 of the intermediate shafts 30.
  • All intermediate shafts 30 are by means of the shaft bearing 22 in the receptacles 21 in the Carrier sleeve 15 and the shutter disc 20 are mounted such that their shaft axes 31 are arranged concentrically around the rotary shaft D around.
  • Each intermediate shaft 30 is rotatably connected to a gear 34 which is in meshing engagement with a central gear 23 which is rotatably connected to the drive shaft 13.
  • the intermediate wheels 30 associated with the gears 34 thus form planetary gears that are driven simultaneously and synchronously by means of the central gear 23, so that all intermediate shafts 30 rotate synchronously.
  • the eccentric parts 32 on the intermediate shafts 30 are arranged in such a way that all intermediate shafts associated with a tool carrier 16A or 16B rotate with the same eccentricity. This is especially clear Fig.
  • the eccentric parts 32 are arranged in such a way to the associated intermediate shafts 30 that the tool carrier 16B results in a 180 ° phase-shifted oscillation to that of the tool carrier 16A.
  • Fig. 5 shows a second embodiment of a drive device according to the invention 110.
  • Construction and functionally identical components as in the first embodiment are provided with identical reference numerals and also in the drive device 110, a support sleeve 15 and a drive shaft 13 are mounted concentrically about the axis of rotation D in a drive housing 11.
  • two tool carriers 116A and 116B are coupled via an eccentric part with intermediate shafts 130 such that an oscillating exciter device for each tool carrier 116A, 116B is formed with the intermediate shafts 130.
  • Both in-plane semi-disc-shaped tool carriers 116A, 116B are coupled to the eccentric portions 132 of three intermediate shafts 130, respectively, and the intermediate shafts 130 of each tool carrier 116A, 116B are synchronously driven.
  • the rotary drive for the intermediate shafts 130 in turn consists of a non-rotatably coupled to the drive shaft 13 central gear 23 and rotationally fixed to the intermediate shafts 130 coupled planetary gears 34.
  • the intermediate shafts 130 concentric with the shaft axis 131 formed and in a bearing receptacle 137 in the tool carriers 116A, 116B projecting shaft journals 132 which is formed as a cone and on which a sleeve 140 is fixed with eccentrically arranged shaft receivers 141.
  • the central axis 143 of the sleeves 140 which corresponds to the central axis of the bearings 135, is in FIG Fig. 5 indicated schematically. Due to the bearings 135 disposed between the sleeves 140 and the tool carriers 116A and 116B, respectively, as in the first embodiment, the tool carriers 116A and 116B may move in an oscillatory motion about the axes 131 of the intermediate shafts 130 in addition to the rotation of the carrier sleeve 15 , which in turn provides a tool equipped with the drive device 110 a beat overlay or oscillation overlay receives for the editing tools.
  • the shaft receptacle 141 in the sleeve 140, adapted to the shaft journal 143, also conical to sleeve 140 and intermediate shaft 130 can easily be separated from each other.
  • the eccentric parts, ie here the sleeves 140 arranged such that all the tool carrier 116A associated sleeves 140 and all the tool carrier 116B associated sleeves 140 with each other have an eccentric offset in the same direction and by the same extent, but at the same time the tool carrier 116A relative to the tool carrier 116B receives a 180 ° out of phase oscillation overlay, so that a dynamic balancing of the drive device 110 by means of additional balancing weights is not required.
  • FIGs. 6A-6D schematically shows a drive device 210 according to a third embodiment, the arrangement of the tool carrier 216A, 216B and the arrangement of the eccentric 232 of the intermediate shafts, the individual representations A to D respectively represent the relative position of the tool carrier after a 90 ° rotation of the intermediate waves, without the simultaneous rotation of the sleeve carrier and thus both tool carriers about the axis of rotation D is taken into account.
  • the drive device 210 is in turn provided with two half-disc-shaped tool carriers 216A, 216B, although each tool carrier 216A or 216B is assigned only two intermediate shafts with eccentric parts 232.
  • the axes of rotation 231 of the intermediate shafts 230 and the axis of rotation D of the carrier sleeve and the drive shaft are also in Fig. 6A located.
  • the oscillation excitation means effected by means of the eccentric members 232 and the intermediate shafts
  • the tool carriers 216A, 216B each undergo a 180 ° out of phase pulse I, this angular momentum 1 being phase-shifted by 180 ° at any one time for the one tool carrier 216A to the pulse I for the other tool carrier 216B, whereby the two tool carriers 216A, 216B are dynamically balanced against each other like the drain over the Figs. 6B, 6C and 6D shows particularly clearly, since between the individual representations, the intermediate waves in each case by 90 ° have turned further. All intermediate shafts rotate in the same direction as indicated by the arrows.
  • a total of four quarter-blade segmented tool carriers 316A, 316B, 316C, 316D are coupled to the eccentric portions 332 of two intermediate shafts, respectively.
  • Each of the opposing tool carriers 316A and 316C or 316B, 316D form a pair and are excited with a 180 ° phase-shifted oscillation, so that in each case the pair of tool carriers 316A, 316C and 316D, 316B balances each other dynamically.
  • a further phase shift of 90 ° is also provided between the pairs, as the respective different positions of the eccentric 232 show relative to the shaft shafts 331 of the intermediate shafts.
  • the individual figures in turn show a movement over a 360 ° rotation of the intermediate shafts, each view shows a shifted by 90 ° to the previous view position of the position of the tool carrier and the rotation of the support sleeve about the rotation axis D is not taken into account.
  • a drive device 410 has these three disk-segment-shaped tool carrier 416A, 416B, 416C, which are each associated with two concentrically rotating about the axis of rotation D intermediate shafts for Oszillationsüberlagerung.
  • the eccentric portions 432 of the intermediate shafts of the tool holder 416A are respectively phase-shifted and rotated by 120 ° relative to the eccentric portions 432 of the intermediate shafts of the tool carriers 416B and 416C, so that each tool carrier 416A provides an oscillation overlap shifted 120 ° out of phase with the other two tool carriers 416C, 416D receives.
  • the three tool carriers 416A, 416B and 416C lying in one plane also dynamically balance one another with respect to their impact pulse.
  • Fig. 9 shows a sixth embodiment of a drive device 510 according to the invention with two tool carriers 516A and 516B, wherein the tool carrier 516B is disposed in a plane behind the tool carrier 516A.
  • Each of the tool carriers 516A, 516B is associated with three intermediate shafts with eccentric parts 532, respectively, and the tool carrier 516A is superimposed with an oscillation pulse which is 180 ° out of phase with the oscillation pulse for the tool carrier 516B.
  • Both tool carriers 516A, 516B have an approximately spade-like contour and in each case one intermediate shaft assigned to the tool carrier 516B is arranged between two intermediate shafts assigned to the tool carrier 516A.
  • the pressure forces can be minimized by the tool carriers 516A and 516B located in different planes, since the individual tool carriers 516A, 516B are never in the same plane at the same time in engagement with the stone to be removed, but always alternately and attack the rock at different levels Solve material there.
  • two tool carriers 616A, 616B are set in rotation and excited with oscillation superimposition.
  • the tool carrier can either be substantially plate-shaped and arranged with their central surfaces one behind the other, so that they and the attachable to them processing tools lie in different planes.
  • the tool carriers 616A, 616B are provided with a corresponding and suitable interleaving, so that the areas of the tool carriers 616A, 616B receiving the processing tools lie in one plane and only the central regions of both tool carriers are arranged in successive planes.
  • the nesting can be achieved, for example, with forwardly projecting offsets on the rear tool carrier 616B and possibly additionally with backward offset offsets on the front tool carrier.
  • each of the intermediate shafts for the one tool support 616A of two intermediate shafts adjacent to the other shaft support 616B and the eccentric portions 632 of the individual intermediate shafts are arranged such that the two tool carriers 616A, 616B are superimposed 180 ° out of phase with each other with the impact pulse.
  • Both tool carriers 616A, 616B have a substantially star-shaped or propeller-shaped contour and on each tool carrier 616 A, 616 B, a partial ring segment-shaped tool holder can be attached to the screw fasteners 651.
  • Each tool carrier 616A, 616B is coupled to three intermediate shafts, respectively. The ends of the individual struts of prppeller- or star-shaped tool carrier can then be provided with the cranks.
  • FIGS. 11 and 12 show yet an eighth embodiment of a drive device 710 according to the invention in a view corresponding to the 3 and 4 ,
  • a drive shaft 713 and a support sleeve 715 are rotatably supported about the same rotation axis D in a drive housing 711.
  • the head 715A of the support sleeve 715 is made more massive than in the first embodiment and between the head 715A and the shutter disc 720 are in addition to a here relatively small-sized and rotatably coupled to the drive shaft 713 central gear 723 and the rotationally fixed to the intermediate shafts 730 planetary gears 734 still intermediate gears 738 stored.
  • All intermediate shafts 730 here have an eccentric part, which consists of a shaft extension 732 arranged eccentrically to the shaft axis 731 of the intermediate shafts 730, which has a conical pin projection 742 which dips into a likewise conical recess 743 in the intermediate shafts 730.
  • the projection 742 and the recess 743 are secured by means of a screw lock, which can be released from the front of the tool holder 716 after removal of the closure flaps 706. As a result, the entire tool carrier 716 can be pulled forwards from the drive housing 711.
  • the drive device 710 has only a single tool carrier 716, which is superimposed with a total of six intermediate waves with the impact pulse.
  • a balance weight 760 is non-rotatably coupled to the drive shaft 713, which is arranged 180 ° out of phase with the arrangement or the eccentric offset of the eccentric parts and rotates in phase in the same direction 180 ° out of phase due to the reduction ratio of the gear mechanism that the balance weight 716 balances the impact movement of the tool carrier 716.
  • the balance weight 760 rotates in a central recess 739 on the inner circumference of the tool carrier 716.
  • each tool carrier can also be assigned three or more intermediate shafts.
  • the particular advantage remains that the intermediate shafts with the eccentric parts build much smaller than in drive devices with eccentrically drilled carrier sleeves, completely preserved. It is not shown that the drives for the drive shafts and the drives for the carrier sleeve can be coupled directly to each other via a suitable Gereteanordriung.
  • the speed of the intermediate shaft drive, the speed of the carrier sleeve drive and the feed rate for the entire tool matched and in particular can be controlled based on the speed of vitewellenancriebs.
  • the eccentric offset can be, for example, 7.5 mm at a peripheral speed of the carrier sleeve of 100-150 revolutions / min and a beat overlay or oscillation of about 3200 / min, so that a speed ratio N 2 of the intermediate shafts and N T of the carrier sleeve of about 20: 1 to 35: 1 can result.
  • the releasable attachment between the eccentric and the intermediate shafts can also be effected by means of a ⁇ lpreß concernedes.
  • 8 processing tools with an angular offset of 45 ° to each other can be attached to the tool carriers.
  • Torsionally flexible couplings can be installed, which may additionally be equipped with an overload function to prevent damage to the drive devices or drives in case of blockages.
  • the editing tools such as round shank chisel, discs, flat chisel or the like. can also be attached directly to the tool carrier.
  • the gap between the segment-shaped tool carriers can with plates or the like. be covered.

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Environmental & Geological Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Earth Drilling (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Excavating Of Shafts Or Tunnels (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Grinding-Machine Dressing And Accessory Apparatuses (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Jigs For Machine Tools (AREA)
  • Harvester Elements (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
  • Turning (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
EP06010277A 2005-06-18 2006-05-18 Antriebsvorrichtung für rotierende, mit Oszillationsüberlagerung arbeitende Werkzeuge und Werkzeug hiermit Not-in-force EP1734224B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL06010277T PL1734224T3 (pl) 2005-06-18 2006-05-18 Urządzenie napędowe do narzędzi obrotowych, współpracujących z generatorem drgań i narzędzie obrotowe

Applications Claiming Priority (1)

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DE102005028277A DE102005028277A1 (de) 2005-06-18 2005-06-18 Antriebsvorrichtung für rotierende, mit Oszillationsüberlagerung arbeitende Werkzeuge und Werkzeug hiermit

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EP1734224A1 EP1734224A1 (de) 2006-12-20
EP1734224B1 true EP1734224B1 (de) 2008-07-16

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EP (1) EP1734224B1 (ru)
JP (1) JP5207339B2 (ru)
CN (1) CN1880724B (ru)
AT (1) ATE401492T1 (ru)
AU (1) AU2006202562B2 (ru)
CA (1) CA2550348C (ru)
DE (2) DE102005028277A1 (ru)
ES (1) ES2310874T3 (ru)
PL (1) PL1734224T3 (ru)
RU (1) RU2391504C2 (ru)
ZA (1) ZA200604924B (ru)

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CN101796263B (zh) * 2007-09-18 2013-01-09 布西鲁斯欧洲有限公司 牙轮钻具或牙轮钻头
JP5330673B2 (ja) 2007-11-01 2013-10-30 王子ホールディングス株式会社 スプレー製品
EP2803817B1 (en) 2013-05-13 2019-02-27 Caterpillar Global Mining Europe GmbH Milling device
CN103696694B (zh) * 2014-01-06 2017-02-08 上海金泰工程机械有限公司 超深碎石桩钻具
CN108798503B (zh) * 2018-07-31 2023-08-08 西南石油大学 螺杆式周向冲击钻井工具
CN117246507B (zh) * 2023-11-02 2024-03-12 常州市中海船舶螺旋桨有限公司 一种具有触发机构的自动矫正螺旋桨

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CN1880724B (zh) 2012-06-27
ZA200604924B (en) 2007-04-25
RU2006121387A (ru) 2007-12-27
PL1734224T3 (pl) 2009-02-27
JP2006348736A (ja) 2006-12-28
CA2550348C (en) 2012-11-20
ATE401492T1 (de) 2008-08-15
EP1734224A1 (de) 2006-12-20
AU2006202562A1 (en) 2007-01-11
ES2310874T3 (es) 2009-01-16
CN1880724A (zh) 2006-12-20
DE102005028277A1 (de) 2006-12-21
JP5207339B2 (ja) 2013-06-12
DE502006001107D1 (de) 2008-08-28
RU2391504C2 (ru) 2010-06-10
AU2006202562B2 (en) 2010-11-25
CA2550348A1 (en) 2006-12-18

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