EP0305658B1 - Milling device for slits - Google Patents

Milling device for slits Download PDF

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Publication number
EP0305658B1
EP0305658B1 EP88108726A EP88108726A EP0305658B1 EP 0305658 B1 EP0305658 B1 EP 0305658B1 EP 88108726 A EP88108726 A EP 88108726A EP 88108726 A EP88108726 A EP 88108726A EP 0305658 B1 EP0305658 B1 EP 0305658B1
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EP
European Patent Office
Prior art keywords
milling cutter
cutter according
slotted wall
damping element
cutting wheel
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.)
Expired - Lifetime
Application number
EP88108726A
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German (de)
French (fr)
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EP0305658A1 (en
Inventor
Maximilian Dipl.-Ing. Arzberger
Johann Dipl.-Ing. Haberer
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.)
Bauer Spezialtiefbau GmbH
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Bauer Spezialtiefbau GmbH
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Application filed by Bauer Spezialtiefbau GmbH filed Critical Bauer Spezialtiefbau GmbH
Priority to AT88108726T priority Critical patent/ATE54971T1/en
Publication of EP0305658A1 publication Critical patent/EP0305658A1/en
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D5/00—Bulkheads, piles, or other structural elements specially adapted to foundation engineering
    • E02D5/18—Bulkheads or similar walls made solely of concrete in situ
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D17/00—Excavations; Bordering of excavations; Making embankments
    • E02D17/13—Foundation slots or slits; Implements for making these slots or slits
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/18—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
    • E02F3/20—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with tools that only loosen the material, i.e. mill-type wheels
    • E02F3/205—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with tools that only loosen the material, i.e. mill-type wheels with a pair of digging wheels, e.g. slotting machines
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/001—Drilling a non circular hole

Definitions

  • the invention relates to a trench cutter with at least one drive unit according to the preamble of claim 1.
  • Such a trench cutter is such. B. from DE-OS 3 424 999.0.
  • the aim can be seen in realizing a power transmission from the corresponding drive unit to the cutting wheels that is as simple but functional as possible. It describes the power transmission using bevel gear and planetary gear as well as a simple chain drive.
  • the invention is therefore based on the object of designing a trench wall cutter of the generic type robustly and functionally simply in such a way that impulsive stresses on the cutting wheel gearbox are largely avoided both when the cutting wheels are blocked and in the start-up and switch-off phase, but at least a strong one Experience reduction.
  • a core idea of the invention can therefore be seen in this, in addition to one between the drive unit, e.g. a hydraulic motor, and the coupling provided for the cutting wheel gear to "integrate" a damping device directly into the cutting wheels, so to speak.
  • a torsionally elastic damping element preferably made of a highly elastic natural rubber, is provided at a radial distance from the output shaft, which, viewed radially, is arranged very close to the peripheral surface of the milling wheels.
  • This elastomeric damping element can be used e.g.
  • the delay caused by the damping element in the transmission and damping of the shock-like load on the cutter gear also enables the power coming from the drive unit to be disengaged, so that a permanent load in the direction of rotation is avoided when the cutting wheels are blocked.
  • the elastomer material of the damping element should be chosen with high shear strength, this also applies to the vulcanization and vulcanization process compared to the adjacent metal sleeves.
  • a particular advantage of the invention can be seen in the fact that the basic construction between the cutting wheel gear and cutting wheels could be retained. One could also say that this structure has to be maintained and that a solution to these conditions has to be found accordingly.
  • the measure according to the invention that the elastomeric damping element is provided with the largest possible diameter and a slight distance from the peripheral surface of the cutting wheel around the output shaft leaves the previous design of the cutting wheels almost unaffected. Since the damping element is, as it were, directly exposed to the corresponding ground conditions and, on the other hand, had to be adapted to the robust construction of the trench wall cutter, it was designed with a relatively low radial thickness. However, in order to avoid the high torques of e.g. In extreme cases, to dampen or absorb 30 kNm per cutting wheel set, the aim is to design the sleeve-like damping element with the largest possible circumferential circle.
  • shock-like loads can be damped, which means that the drive unit, e.g. a hydraulic motor, can be switched off due to a build-up of excess pressure.
  • the damping element is advantageously designed in the manner of a cylindrical bush which is vulcanized or vulcanized in between the inner hub ring, which is connected to the output shaft, and an outer metal sleeve.
  • the damping element including the inner hub ring and the radially outer metal sleeve or sheet metal segment is designed as an assembly, so that the damping unit can be replaced relatively easily and completely.
  • the damping's radially outer metal sleeve Unit is largely non-rotatably connected to the milling wheel via key-and-groove connections, which are distributed over the circumference at the same angular distance.
  • the rotationally fixed connections between the output shaft on the one hand and between the damping unit and the cutting wheel on the other hand consist of axial screw connections which are accessible from the end face of the output shaft.
  • the bush-like damping element extends largely over the entire axial extent of the cutting wheel, so that different radial forces acting on the output shaft from the cutting teeth are absorbed and transmitted over a larger axial area can.
  • the radial thickness of the damping element can be, for example, approximately 3 cm with an inner radius in the installed state of 50 cm, and the outer surface of the milling wheel can have a radius of approximately 65 cm.
  • the outer surface of the milling wheel is understood in this case so that the corresponding fastening devices for the milling teeth are attached and in particular welded on.
  • a particularly preferred solution consists in moving the damping element radially outward as far as possible to the circumference of the cutting wheel.
  • the metal sleeve can consist, for example, of four sheet metal segments, between which corresponding grooves are provided, in which the feather keys of the cutting wheel engage in a positive and non-positive manner.
  • a trench cutter 1 is shown in side view, as it is known in principle from DE-OS 34 24 999.0.
  • the trench wall cutter 1 has a support frame 5 which is held by a support cable 3.
  • drive motors 9 for the milling wheels 11 are fastened to the milling frame 5 and drive the milling wheels 11 via a schematically indicated gear 12.
  • the two milling wheels 11 shown are rotatably received in two bearing plates 13, which in turn are firmly connected to the milling frame 5.
  • the trench wall cutter 1 is moved forward according to the arrow 15 shown.
  • the trench wall cutter 1 also has two milling wheels on the other side of the end shields 13.
  • the respective milling wheel 11 usually has a plurality of milling tooth sets 10 on its circumferential surface, which are provided axially one behind the other on the output shaft.
  • the milling tooth sets 10 are generally somewhat offset in the direction of rotation, so that the corresponding milling teeth 18 cause the milling process with an angular offset.
  • the cutting wheels 11 shown in FIG. 1 are now equipped with an elastomeric damping element 17.
  • This damping element 17 is vulcanized at a radial distance around the output shaft 21 onto a corresponding hub ring 22.
  • the damping element 17 is surrounded radially outward by sheet metal segments 23, which can also be designed as a metal sleeve. In practical implementation, four sheet metal segments 23, which are spaced apart from one another in the circumferential direction via a corresponding groove, are sufficient. 2, a corresponding key 24 engages in this groove, which is connected at 25 to an outer hub part 26 or the sleeve-like milling wheel 11.
  • the damping element 17 consisting for example of an elastomer with a rubber hardness in the range of 55 Shore-A and a tensile strength in the range of 15 to 30 N / mm 2 , is firmly vulcanized between the inner hub ring 22 and the radially outer sheet metal segments 23. While the hub ring is non-rotatably connected to the output shaft 21 by means of screws 20, the sheet metal segments 23 are non-rotatably connected to an outer hub part 26 via parallel keys 24 (FIG. 2). The attachment of this hub part 26 is carried out from the end face of the output shaft 21 by means of stud bolts 19 which are in engagement with the cutting wheel 11.
  • the output shaft 21 is shown only schematically in the illustrations and not with its realistic diameter. In practical implementation, the diameter of the output shaft would have to be significantly larger than in the illustrations. However, the construction is such that the screw connections 20, 19 can be loosened from the end face 28 and the entire assembly of the damping unit 17, 22, 23 can also be removed in this direction.
  • the milling wheels 11 are shown in the illustrations according to FIGS. 2 and 3 without fastening devices with milling teeth welded onto the peripheral surface 27. A plurality of sets of milling teeth 10 are normally provided in the axial direction on the peripheral surface 27 of the milling wheels 11.
  • the torque coming from the output shaft 21 is absorbed in the damping element 17 in the circumferential direction, but at least strongly damped, so that an abrupt stress on the cutting gear 21 connected downstream in the direction of the motor 9 (not shown) is prevented.
  • the vulcanization of the damping element 17 is designed such that the deformation forces and shear forces that occur do not result in the vulcanization connection between the hub 22 and the sheet metal segments 23 being torn off.
  • this second alternative relates to a lamella-like arrangement of individual elastomer elements 70 with alternating metal rings 62 to 65.
  • the basic structure of this second alternative of the trench wall cutter with damping element 57 is that a segmented hub ring 51 is fastened by means of stud bolts 58 in the front edge region of the output shaft 21.
  • the hub ring 51 has a first, end-side segment 52 which covers the corner region of the output shaft 21.
  • This segment 52 has a ring segment 62 which is radially set back radially with respect to the end face and which has a thinner material thickness in the axis-parallel direction.
  • segments 53, 54, 55 are screwed together in a reversed order by means of a screw 59.
  • These segments 53 to 55 each have radially projecting ring segments 63, 64, 65.
  • the axially innermost segment 55 is welded to a spacer sleeve 76, which extends axially parallel on the outer circumference of the output shaft 21, a symmetrical arrangement of a hub ring with a damping element being located on the end face of the output shaft 21, not shown.
  • the elastomer rings 70 are fixed in terms of area in the example by means of an adhesive connection.
  • a suitable component is, for example, a component adhesive or, preferably, Loctite IS 496 adhesive.
  • the elastomer rings 70 have an approximately oblong, rectangular shape in radial section.
  • the counter surface of the axially innermost elastomer ring 70 is formed by the bonding surface 75 of a metal ring web 81 projecting radially inwards from the outside. This metal ring web 81 is part of an outer ring segment 69.
  • the outer region of the cutting wheel is formed by external ring segments 66, 67, 68 and 69, which have an approximately L-shape.
  • these ring segments 66 to 69 are held together in the axis-parallel direction by a clamping screw 60 and can also be pressed together.
  • the radially standing L-legs engage tooth-like in the spaces between the radial ring segments 62 to 65, the spaces created between corresponding inner radial ring segments 62 to 66 and the outer L-legs being occupied by individual elastomer rings 70.
  • the damping element 57 therefore resembles a “multi-plate clutch”, the corresponding damping forces being absorbed essentially on radial surfaces and in the elastomer ring 70 in the radial direction.
  • the milling teeth which are not shown in the example according to Fig. 4, are on the radial peripheral surface 83 e.g. welded.
  • the welding attachment is preferably provided over the entire axial extent of the circumferential surface 83, so that the force can be transmitted across all segments and elastomer rings 70.
  • FIG. 5 the example according to FIG. 4 is drawn out with a view of the end face 28 into a circumferential area of 90 ° .
  • the radially inner stud screws 58 serve to connect the hub ring 51 to the output shaft 21.
  • the clamping screws 60 are arranged radially on the outside, while the screws 59 for fixing the segments 52 to 55 of the hub ring 51 are shown in the central region.
  • a damping element is provided between the cutting wheels and their cutting gear, which absorbs sudden torques, e.g. by blocking the cutting wheels and thus preventing damage to the cutting wheel gear connected downstream in the direction of the drive unit.

Abstract

1. Slotted wall milling cutter with at least one drive unit, e.g. a hydraulic motor optionally driving by means of an upstream coupling, via a cutting wheel gear the driven shaft or shafts (21) of the cutting wheels (11) equipped with cutting teeth (18), characterized in that a rotation-elastic damping element (17, 57) is provided between the driven shaft (21) and the cutting wheel (11).

Description

Die Erfindung betrifft eine Schlitzwandfräse mit mindestens einem Antriebs-Aggregat gemäß Oberbegriff des Anspruches 1.The invention relates to a trench cutter with at least one drive unit according to the preamble of claim 1.

Eine derartige Schlitzwandfräse ist z. B. aus der DE-OS 3 424 999.0 bekannt. Bei dieser bekannten Schlitzwandfräse kann man die Zielrichtung darin sehen, eine möglichst einfach aber funktionell konstruierte Kraftübertragung vom entsprechenden Antriebs-Aggregat auf die Fräsräder zu realisieren. So ist darin die Kraftübertragung mittels Kegelradgetriebe und Planetengetriebe ebenso wie über einen einfachen Kettenantrieb beschrieben.Such a trench cutter is such. B. from DE-OS 3 424 999.0. With this known trench wall cutter, the aim can be seen in realizing a power transmission from the corresponding drive unit to the cutting wheels that is as simple but functional as possible. It describes the power transmission using bevel gear and planetary gear as well as a simple chain drive.

Auch kann bei derartigen Schlitzwandfräsen bereits der Einbau einer Kupplung zwischen dem eigentlichen Antriebs-Aggregat und dem Fräsrad- Getriebe vorgesehen sein. Dies entspricht nahezu der im Maschinenbau gängigen Praxis, um entsprechende Anfahr- und Abschaltvorgänge, aber auch die gewünschte Leistungsübertragung auf die Fräsräder schalten zu können.With such trench wall milling machines, the installation of a clutch between the actual drive unit and the cutting wheel gear can already be provided. This almost corresponds to the common practice in mechanical engineering, in order to be able to switch the corresponding start-up and shutdown processes, but also the desired power transfer to the milling wheels.

Es hat sich jedoch gezeigt, daß gerade bei den schwierigen Einsatzbedingungen und Bodenstrukturen, bei denen Schlitzwandfräsen überwiegend eingesetzt werden, starke Beschädigungen des Fräsrad-Getriebes auftreten. Diese Beschädigungen resultieren vor allen Dingen daraus, daß die Fräsräder während des Fräsvorganges plötzlich auf harte Materialien, wie Kies, Findlinge, Betonreste etc. stoßen können, wodurch häufig ein abruptes Blockieren der Fräsräder auftreten kann. Aufgrund dieser schlagartigen Blockierung der Fräsräder, müssen diese Kräfte stoßartig vom Fräsrad- Getriebe aufgefangen werden, wodurch dieses einer Überbeanspruchung unterliegt und dadurch einer starken Abnutzung ausgesetzt ist. In der Praxis bedeutet dies, daß man bei derartigen Schlitzwandfräsen nahezu nach jedem Bauloseinsatz, das Fräsrad-Getriebe ausbauen und mindestens warten, wenn nicht sogar ersetzen muß.However, it has been shown that, particularly in the difficult operating conditions and floor structures, in which diaphragm wall cutters are predominantly used, severe damage to the cutting wheel gear occurs. This damage results above all from the fact that the milling wheels can suddenly encounter hard materials such as gravel, boulders, concrete residues etc. during the milling process, which can often result in an abrupt blocking of the milling wheels. Due to this sudden blockage of the cutting wheels, these forces must be absorbed by the cutting wheel gear in a jerky manner, as a result of which it is subject to excessive stress and is therefore subjected to severe wear. In practice, this means that with such trench wall cutters, the cutter wheel gearbox must be removed and at least serviced, if not replaced, after almost every job lot.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Schlitzwandfräse der gattungsgemäßen Art robust und funktionell einfach so auszulegen, daß stoßartige Beanspruchungen des Fräsrad-Getriebes sowohl bei Blockierungsvorgängen der Fräsräder als auch in der Anfahr- und Ausschalt-Phase weitestgehend vermieden werden, zumindest aber eine starke Reduzierung erfahren.The invention is therefore based on the object of designing a trench wall cutter of the generic type robustly and functionally simply in such a way that impulsive stresses on the cutting wheel gearbox are largely avoided both when the cutting wheels are blocked and in the start-up and switch-off phase, but at least a strong one Experience reduction.

Diese Aufgabe wird erfindungsgemäß durch die Merkmale des kennzeichnenden Teils des Anspruches 1 gelöst.This object is achieved by the features of the characterizing part of claim 1.

Ein Kemgedanke der Erfindung kann daher darin gesehen werden, zusätzlich zu einer zwischen dem Antriebs-Aggregat, z.B. einem Hydromotor, und dem Fräsrad-Getriebe vorgesehenen Kupplung, eine Dämpfungseinrichtung sozusagen direkt in die Fräsräder zu "integrieren". In der Grundidee wird daher im radialen Abstand zur Abtriebswelle ein drehelastisches Dämpfungselement, bevorzugterweise aus einem hochelastischen Naturkautschuk, vorgesehen, das radial gesehen sehr nahe an der Umfangsfläche der Fräsräder angeordnet ist. Dieses elastomere Dämpfungselement kann bei stoßartigem Stillstand der Fräsräder z.B. infolge eines Verfangens der Fräszähne an einem Findling, das hohe plötzlich auftretende Drehmoment zumindest stark abdämpfen, so daß nahezu keine stoßartige Belastung von den Fräsrädern rückwirkend auf das Fräsrad-Getriebe übertragen wird. Diese Abdämpfung wird einerseits durch die hohe Elastizität des Dämpfungselementes bewirkt, das eine starke Verdrehung der angrenzenden ringförmigen Teile zuläßt. Andererseits wird auch ein Teil des in solchen Blockierungsfällen auftretenden Drehmomentes durch die Formänderungsarbeit im Elastomer vernichtet.A core idea of the invention can therefore be seen in this, in addition to one between the drive unit, e.g. a hydraulic motor, and the coupling provided for the cutting wheel gear to "integrate" a damping device directly into the cutting wheels, so to speak. In the basic idea, therefore, a torsionally elastic damping element, preferably made of a highly elastic natural rubber, is provided at a radial distance from the output shaft, which, viewed radially, is arranged very close to the peripheral surface of the milling wheels. This elastomeric damping element can be used e.g. as a result of the milling teeth getting caught on a boulder, at least strongly dampen the high suddenly occurring torque, so that almost no impact load is transmitted retrospectively from the milling wheels to the milling wheel gear. This damping is caused on the one hand by the high elasticity of the damping element, which allows the adjacent ring-shaped parts to be rotated strongly. On the other hand, part of the torque that occurs in such blocking cases is also destroyed by the deformation work in the elastomer.

Die Verzögerung, die durch das Dämpfungselement bei der Übertragung und Dämpfung der stoßartigen Belastung auf das Fräsrad-Getriebe hervorgerufen wird, ermöglicht auch ein Auskuppeln der vom Antriebs-Aggregat kommenden Leistung, so daß eine Dauerbelastung in Drehrichtung bei blockierenden Fräsrädern vermieden wird. Das Elastomermaterial des Dämpfungselementes ist aus diesem Grund mit hoher Scherfestigkeit zu wählen, wobei dies auch für den An- und Einvulkanisierungsvorgang gegenüber den angrenzenden Metallhülsen gilt.The delay caused by the damping element in the transmission and damping of the shock-like load on the cutter gear also enables the power coming from the drive unit to be disengaged, so that a permanent load in the direction of rotation is avoided when the cutting wheels are blocked. For this reason, the elastomer material of the damping element should be chosen with high shear strength, this also applies to the vulcanization and vulcanization process compared to the adjacent metal sleeves.

Ein besonderer Vorteil kann bei der Erfindung darin gesehen werden, daß der prinzipielle konstruktive Aufbau zwischen Fräsrad-Getriebe und Fräsrädern beibehalten werden konnte. Man könnte auch sagen, daß dieser Aufbau beibehalten werden muß und man dementsprechend eine sich diesen Bedingungen unterordnende Lösung finden mußte. Die erfindungsgemäße Maßnahme, daß das elastomere Dämpfungselement mit möglichst großen Durchmesser und geringfügigem Abstand zur Umfangsfläche des Fräsrades um die Abtriebswelle vorgesehen ist, läßt die bisherige Konstruktion der Fräsräder nahezu unberührt. Da das Dämpfungselement sozusagen direkt den entsprechenden Bodenverhältnissen ausgesetzt ist und andererseits dem robusten Aufbau der Schlitzwandfräse anzupassen war, wurde es mit relativ geringer radialer Stärke ausgelegt. Um jedoch die auftretenden hohen Drehmomente von z.B. 30 kNm pro Fräsradsatz im Extremfall dämpfen oder aufnehmen zu können, ist man bestrebt, das hülsenartige Dämpfungselement mit möglichst großem Umfangskreis auszulegen.A particular advantage of the invention can be seen in the fact that the basic construction between the cutting wheel gear and cutting wheels could be retained. One could also say that this structure has to be maintained and that a solution to these conditions has to be found accordingly. The measure according to the invention that the elastomeric damping element is provided with the largest possible diameter and a slight distance from the peripheral surface of the cutting wheel around the output shaft leaves the previous design of the cutting wheels almost unaffected. Since the damping element is, as it were, directly exposed to the corresponding ground conditions and, on the other hand, had to be adapted to the robust construction of the trench wall cutter, it was designed with a relatively low radial thickness. However, in order to avoid the high torques of e.g. In extreme cases, to dampen or absorb 30 kNm per cutting wheel set, the aim is to design the sleeve-like damping element with the largest possible circumferential circle.

Trotz enger Platzverhältnisse zwischen dem Fräsradgetriebe und dem eigentlichen Fräsrad ist somit eine Dämpfung stoßartiger Belastungen möglich, wodurch durch die Zeitverzögerung auch das Antriebs-Aggregat, z.B. ein Hydromotor, infolge eines sich aufbauenden Überdruckes abgeschaltet werden kann.Despite the limited space between the cutting gear and the actual cutting wheel, shock-like loads can be damped, which means that the drive unit, e.g. a hydraulic motor, can be switched off due to a build-up of excess pressure.

In vorteilhafter Weise ist das Dämpfungselement in Art einer zylindrischen Buchse ausgelegt, die zwischen dem inneren, mit der Abtriebswelle in Verbindung stehendem Nabenring und einer äußeren Metallhülse an- bzw. einvulkanisiert ist. Das Dämpfungselement einschließlich innerem Nabenring und radial äußerer Metallhülse bzw. Blechsegment ist als Baugruppe ausgelegt, so daß ein relativ einfacher, kompletter Austausch der Dämpfungseinheit erfolgen kann.The damping element is advantageously designed in the manner of a cylindrical bush which is vulcanized or vulcanized in between the inner hub ring, which is connected to the output shaft, and an outer metal sleeve. The damping element including the inner hub ring and the radially outer metal sleeve or sheet metal segment is designed as an assembly, so that the damping unit can be replaced relatively easily and completely.

Die radial äußere Metallhülse der Dämpfungseinheit steht dabei über Paßfeder-Nut-Verbindungen, die mit gleichem Winkelabstand über den Umfang verteilt sind, weitgehend drehfest mit dem Fräsrad in Verbindung. Um eine gute Zugänglichkeit zu gewährleisten bestehen die drehfesten Verbindungen zwischen Abtriebswelle einerseits und zwischen Dämpfungseinheit und dem Fräsrad andererseits aus axialen Schraubverbindungen, die von der Stirnseite der Abtriebswelle zugängig sind.The damping's radially outer metal sleeve Unit is largely non-rotatably connected to the milling wheel via key-and-groove connections, which are distributed over the circumference at the same angular distance. In order to ensure good accessibility, the rotationally fixed connections between the output shaft on the one hand and between the damping unit and the cutting wheel on the other hand consist of axial screw connections which are accessible from the end face of the output shaft.

Da die Fräsräder üblicherweise in axialer Richtung mit zwei oder drei Fräszahnsätzen ausgelegt sind, erstreckt sich das buchsenartige Dämpfungselement weitgehend über die gesamte axiale Erstreckung des Fräsrades, so daß unterschiedliche radiale von den Fräszähnen auf die Abtriebswelle einwirkende Kräfte aufgenommen und über eine größere axiale Fläche übertragen werden können.Since the cutting wheels are usually designed with two or three sets of cutting teeth in the axial direction, the bush-like damping element extends largely over the entire axial extent of the cutting wheel, so that different radial forces acting on the output shaft from the cutting teeth are absorbed and transmitted over a larger axial area can.

Die radiale Stärke des Dämpfungselementes kann beispielsweise etwa 3 cm betragen bei einem Innenradius im eingebauten Zustand von 50 cm, wobei die Außenfläche des Fräsrades einen Radius von ca. 65 cm aufweisen kann. Die Außenfläche des Fräsrades wird in diesem Fall so verstanden, daß darauf die entsprechenden Befestigungseinrichtungen für die Fräszähne angebracht und insbesondere aufgeschweißt werden. Man erkennt jedoch daraus, daß eine besonders bevorzugte Lösung darin besteht, das Dämpfungselement soweit dies möglich ist, nach radial außen zum Fräsrad-Umfang zu verlagern.The radial thickness of the damping element can be, for example, approximately 3 cm with an inner radius in the installed state of 50 cm, and the outer surface of the milling wheel can have a radius of approximately 65 cm. The outer surface of the milling wheel is understood in this case so that the corresponding fastening devices for the milling teeth are attached and in particular welded on. However, it can be seen from this that a particularly preferred solution consists in moving the damping element radially outward as far as possible to the circumference of the cutting wheel.

Die Metallhülse kann beispielsweise aus vier Blechsegmenten bestehen, zwischen denen entsprechende Nuten vorgesehen sind, in die Paßfedem des Fräsrades form- und kraftschlüssig eingreifen.The metal sleeve can consist, for example, of four sheet metal segments, between which corresponding grooves are provided, in which the feather keys of the cutting wheel engage in a positive and non-positive manner.

Die Erfindung wird nachstehend anhand eines Ausführungsbeispieles und schematischer Zeichnungen noch näher erläutert. Es zeigen:

  • Fig. 1 eine Seitenansicht auf eine Schlitzwandfräse mit stirnseitig dargestellten Fräsrädern;
  • Fig. 2 einen radialen Schnitt durch ein Fräsrad ohne Fräszähne im Bereich einer Paßfeder-NutVerbindung längs der Linie 11-11 mit dem Dämpfungselement und der Abtriebswelle;
  • Fig. 3 einen radialen Schnitt, vergleichbar zu dem nach Fig. 2, jedoch im Bereich der axialen Schraubverbindungen zwischen Fräsrad und Abtriebswelle längs der Linie 111-111;
  • Fig. 4 eine weitere Alternative des Dämpfungselementes in einem bruchstückartig dargestellten radialen Schnitt durch ein Fräsrad, wobei zur Vereinfachung die Fräszähne weggelassen sind; und
  • Fig. 5 eine stirnseitige Ansicht auf den bruchstückartigen Teil nach Fig. 4.
The invention is explained in more detail below using an exemplary embodiment and schematic drawings. Show it:
  • Figure 1 is a side view of a trench cutter with milling wheels shown on the end.
  • 2 shows a radial section through a milling wheel without milling teeth in the area of a feather key connection along the line 11-11 with the damping element and the output shaft;
  • 3 shows a radial section, comparable to that according to FIG. 2, but in the area of the axial screw connections between the cutting wheel and the output shaft along the line 111-111;
  • FIG. 4 shows a further alternative of the damping element in a radial section through a cutting wheel, shown in a fragmentary manner, the cutting teeth being omitted for simplification; FIG. and
  • 5 shows an end view of the fragment-like part according to FIG. 4.

In Fig. 1 ist eine Schlitzwandfräse 1 in Seitenansicht dargestellt, wie sie im Prinzip aus der DE-OS 34 24 999.0 bekannt ist. Die Schlitzwandfräse 1 weist einen Tragrahmen 5 auf, der von einem Tragseil 3 gehalten wird. Es ist eine Absaugvorrichtung mit Pumpe 7 vorhanden, über die das gelöste Bodenmaterial nach oben befördert wird. Des weiteren sind Antriebsmotoren 9 für die Fräsräder 11 am Fräsrahmen 5 befestigt, die über ein schematisch angedeutetes Getriebe 12 die Fräsräder 11 antreiben. Die beiden dargestellten Fräsräder 11 sind drehbar in zwei Lagerschildern13 aufgenommen, die wiederum fest mit dem Fräsenrahmen 5 verbunden sind. Die Schlitzwandfräse 1 wird bei ihrem Einsatz gemäß dem eingezeichneten Pfeil 15 vorwärtsbewegt. Üblicherweise weist die Schlitzwandfräse 1 auf der anderen Seite der Lagerschilder 13 ebenfalls zwei Fräsräder auf. Das jeweilige Fräsrad 11 hat auf seiner Umfangsfläche üblicherweise mehrere Fräszahnsätze 10, die axial hintereinander geordnet auf der Abtriebswelle vorgesehen sind. Die Fräszahnsätze 10 sind in der Regel in Drehrichtung etwas versetzt, so daß die entsprechenden Fräszähne 18 winkelversetzt den Fräsvorgang bewirken.In Fig. 1, a trench cutter 1 is shown in side view, as it is known in principle from DE-OS 34 24 999.0. The trench wall cutter 1 has a support frame 5 which is held by a support cable 3. There is a suction device with pump 7, via which the loosened soil material is conveyed upwards. Furthermore, drive motors 9 for the milling wheels 11 are fastened to the milling frame 5 and drive the milling wheels 11 via a schematically indicated gear 12. The two milling wheels 11 shown are rotatably received in two bearing plates 13, which in turn are firmly connected to the milling frame 5. When used, the trench wall cutter 1 is moved forward according to the arrow 15 shown. Usually, the trench wall cutter 1 also has two milling wheels on the other side of the end shields 13. The respective milling wheel 11 usually has a plurality of milling tooth sets 10 on its circumferential surface, which are provided axially one behind the other on the output shaft. The milling tooth sets 10 are generally somewhat offset in the direction of rotation, so that the corresponding milling teeth 18 cause the milling process with an angular offset.

Im Gegensatz zur aus der DE-OS 3 424 999 bekannten Schlitzwandfräse 1 sind die in Fig. 1 dargestellten Fräsräder 11 nunmehr mit einem elastomeren Dämpfungselement 17 ausgestattet. Dieses Dämpfungselement 17 ist mit radialem Abstand um die Abtriebswelle 21 auf einen entsprechenden Nabenring 22 aufvulkanisiert.In contrast to the trench wall cutter 1 known from DE-OS 3 424 999, the cutting wheels 11 shown in FIG. 1 are now equipped with an elastomeric damping element 17. This damping element 17 is vulcanized at a radial distance around the output shaft 21 onto a corresponding hub ring 22.

Unter Bezugnahme auf die Fig. 2 und 3 wird das Dämpfungselement 17 nach radial außen von Blechsegmenten 23 umgeben, die auch als Metallhülse ausgelegt sein können. In der praktischen Realisation genügen vier Blechsegmente 23, die über eine entsprechende Nut in Umfangsrichtung voneinander beabstandet sind. In diese Nut greift entsprechend der Fig. 2 eine entsprechende Paßfeder 24 ein, die bei 25 mit einem äußeren Nabenteil 26 bzw. dem hülsenartigen Fräsrad 11 verbunden ist.With reference to FIGS. 2 and 3, the damping element 17 is surrounded radially outward by sheet metal segments 23, which can also be designed as a metal sleeve. In practical implementation, four sheet metal segments 23, which are spaced apart from one another in the circumferential direction via a corresponding groove, are sufficient. 2, a corresponding key 24 engages in this groove, which is connected at 25 to an outer hub part 26 or the sleeve-like milling wheel 11.

Das z.B. aus einem Elastomer mit einer Gummihärte im Bereich von 55 Shore-A und einer Zugfestigkeit im Bereich von 15 bis 30 N/mm2 bestehende Dämpfungselement 17 ist zwischen dem inneren Nabenring 22 und den radial äußeren Blechsegmenten 23 fest einvulkanisiert. Während der Nabenring über Schrauben 20 mit der Abtriebswelle 21 drehfest verbunden ist, stehen die Blechsegmente 23 formschlüssig über Paßfedern 24 (Fig. 2) mit einem äußeren Nabenteil 26 drehfest in Verbindung. Die Befestigung dieses Nabenteils 26 ist von der Stirnseite der Abtriebswelle 21 mittels Bolzenschrauben 19 vorgenommen, die in Eingriff mit dem Fräsrad 11 stehen.The damping element 17, consisting for example of an elastomer with a rubber hardness in the range of 55 Shore-A and a tensile strength in the range of 15 to 30 N / mm 2 , is firmly vulcanized between the inner hub ring 22 and the radially outer sheet metal segments 23. While the hub ring is non-rotatably connected to the output shaft 21 by means of screws 20, the sheet metal segments 23 are non-rotatably connected to an outer hub part 26 via parallel keys 24 (FIG. 2). The attachment of this hub part 26 is carried out from the end face of the output shaft 21 by means of stud bolts 19 which are in engagement with the cutting wheel 11.

Die Abtriebswelle 21 ist in den Darstellungen nur schematisch und nicht mit ihrem realistischen Durchmesser aufgezeigt. Bei praktischer Realisation müßte der Durchmesser der Abtriebswelle wesentlich größer als in den Darstellungen sein. Die Konstruktion ist jedoch so getroffen, daß die Schraubverbindungen 20,19 von der Stirnseite 28 her gelöst werden können und in dieser Richtung auch die gesamte Baugruppe der Dämpfungseinheit 17, 22, 23 ausgebaut werden kann. Die Fräsräder 11 sind in den Darstellungen nach Fig. 2 und 3 ohne auf der Umfangsfläche 27 aufgeschweißte Befestigungseinrichtungen mit Fräszähnen gezeigt. Normalerweise werden in axialer Richtung auf der Umfangsfläche 27 der Fräsräder 11 mehrere Fräszahnsätze 10 vorgesehen.The output shaft 21 is shown only schematically in the illustrations and not with its realistic diameter. In practical implementation, the diameter of the output shaft would have to be significantly larger than in the illustrations. However, the construction is such that the screw connections 20, 19 can be loosened from the end face 28 and the entire assembly of the damping unit 17, 22, 23 can also be removed in this direction. The milling wheels 11 are shown in the illustrations according to FIGS. 2 and 3 without fastening devices with milling teeth welded onto the peripheral surface 27. A plurality of sets of milling teeth 10 are normally provided in the axial direction on the peripheral surface 27 of the milling wheels 11.

Bei einem abrupten Stillstand und Blockieren der Fräsräder 11 in Drehrichtung der eingezeichneten Pfeile (Fig. 1) wird daher das von der Abtriebswelle 21 anstehende Drehmoment im Dämpfungselement 17 in Umfangsrichtung aufgefangen, zumindest aber stark gedämpft, so daß eine schlagartige Beanspruchung des der Abtriebswelle 21 in Richtung zum Motor 9 nachgeschalteten Fräsradgetriebes (nicht dargestellt) verhindert wird. Die Anvulkanisierung des Dämpfungselementes 17 ist so ausgelegt, daß die auftretenden Verformungskräfte und Scherkräfte kein Abreißen der Vulkanisationsverbindung zwischen der Nabe 22 und den Blechsegmenten 23 bringt.In the event of an abrupt standstill and blocking of the Cutting wheels 11 in the direction of rotation of the arrows (FIG. 1), therefore, the torque coming from the output shaft 21 is absorbed in the damping element 17 in the circumferential direction, but at least strongly damped, so that an abrupt stress on the cutting gear 21 connected downstream in the direction of the motor 9 ( not shown) is prevented. The vulcanization of the damping element 17 is designed such that the deformation forces and shear forces that occur do not result in the vulcanization connection between the hub 22 and the sheet metal segments 23 being torn off.

In dem weiteren Ausführungsbeispiel des Dämpfungselementes nach Fig. 4 ist bruchstückartig in einem radialen Schnitt der untere Teil eines Fräsrades 21 dargestellt. Der prinzipielle Unterschied gegenüber dem vorausgehend beschriebenen ersten Ausführungsbeispiel besteht darin, daß diese zweite Alternative eine lamellenartige Aneinanderreihung einzelner Elastomerelemente 70 mit abwechselnden Metallringen 62 bis 65 betrifft. Der grundsätzliche Aufbau dieser zweiten Alternative der Schlitzwandfräse mit Dämpfungselement 57 besteht darin, daß im stirnseitigen Randbereich der Abtriebswelle 21 ein segmentierter Nabenring 51 mittels Bolzenschrauben 58 befestigt ist. Der Nabenring 51 weist ein erstes, stimseitiges Segment 52 auf, das den Eckbereich der Abtriebswelle 21 bedeckt. Dieses Segment 52 weist ein radial gegenüber der Stirnseite axial zurückversetzes Ringsegment 62 auf, das in achsparalleler Richtung dünnere Materialstärke hat.In the further exemplary embodiment of the damping element according to FIG. 4, the lower part of a milling wheel 21 is shown in fragments in a radial section. The basic difference compared to the first exemplary embodiment described above is that this second alternative relates to a lamella-like arrangement of individual elastomer elements 70 with alternating metal rings 62 to 65. The basic structure of this second alternative of the trench wall cutter with damping element 57 is that a segmented hub ring 51 is fastened by means of stud bolts 58 in the front edge region of the output shaft 21. The hub ring 51 has a first, end-side segment 52 which covers the corner region of the output shaft 21. This segment 52 has a ring segment 62 which is radially set back radially with respect to the end face and which has a thinner material thickness in the axis-parallel direction.

Über eine Schraube 59 sind montagemäßig in umgedrehter Reihenfolge weitere Segmente 53,54,55 gegeneinander verschraubt. Diese Segmente 53 bis 55 weisen jeweils radial abstehende Ringsegmente 63,64,65 auf.Further segments 53, 54, 55 are screwed together in a reversed order by means of a screw 59. These segments 53 to 55 each have radially projecting ring segments 63, 64, 65.

Das axial innerste Segment 55 ist an einer Abstandshülse 76 verschweißt, die sich achsparallel am Außenumfang der Abtriebswelle 21 erstreckt, wobei sich auf der nicht dargestellten Stirnseite der Abtriebswelle 21 eine symmetrische Anordnung eines Nabenringes mit Dämpfungselement befindet.The axially innermost segment 55 is welded to a spacer sleeve 76, which extends axially parallel on the outer circumference of the output shaft 21, a symmetrical arrangement of a hub ring with a damping element being located on the end face of the output shaft 21, not shown.

Auf den radialen Ringflächen 74 der radialen Ringsegmente 62 bis 65 sind im Beispiel mittels einer Klebeverbindung die Elastomerringe 70 flächenmä- βig befestigt. Als Klebemittel eignet sich beispielsweise ein Komponentenkleber oder vorzugsweise der Kleber Loctite IS 496. Die Elastomerringe 70 weisen im Radialschnitt etwa länglich-rechteckige Form auf. Die Gegenfläche des axial innersten Elastomerrings 70 wird durch die Verklebungsfläche 75 eines von außen radial nach innen ragenden Metallringsteges 81 gebildet. Dieser Metallringsteg 81 ist Teil eines äußeren Ringsegmentes 69.On the radial ring surfaces 74 of the radial ring segments 62 to 65, the elastomer rings 70 are fixed in terms of area in the example by means of an adhesive connection. A suitable component is, for example, a component adhesive or, preferably, Loctite IS 496 adhesive. The elastomer rings 70 have an approximately oblong, rectangular shape in radial section. The counter surface of the axially innermost elastomer ring 70 is formed by the bonding surface 75 of a metal ring web 81 projecting radially inwards from the outside. This metal ring web 81 is part of an outer ring segment 69.

In ähnlicher Weise wie vorausgehend beim Nabenring 51 beschrieben, wird der äußere Bereich des Fräsrades durch externe Ringsegmente 66, 67, 68 und 69 gebildet, die in etwa L-Form haben. Im Basisschenkel sind diese Ringsegmente 66 bis 69 durch eine Klemmschraube 60 in achsparalleler Richtung zusammengehalten und können auch zusammengepreßt werden. Die radial stehenden L-Schenkel greifen dabei zahnartig in die Zwischenräume zwischen den radialen Ringsegmenten 62 bis 65, wobei die dabei zwischen entsprechenden inneren radialen Ringsegmenten 62 bis 66 und den äußeren L-Schenkel entstehenden Räume durch einzelne Elastomerringe 70 eingenommen werden. Diese Elastomerringe sind an den radialen Flächen mit den anliegenden radialen Metallflächen verklebt, wobei jedoch im Hinblick auf eine achsparallele Verpressung, z.B. durch die Klemmschraube 60, ein minimaler radialer Abstand nach außen und innen am Elastomerring 70 existiert.In a similar way as described above for the hub ring 51, the outer region of the cutting wheel is formed by external ring segments 66, 67, 68 and 69, which have an approximately L-shape. In the base leg, these ring segments 66 to 69 are held together in the axis-parallel direction by a clamping screw 60 and can also be pressed together. The radially standing L-legs engage tooth-like in the spaces between the radial ring segments 62 to 65, the spaces created between corresponding inner radial ring segments 62 to 66 and the outer L-legs being occupied by individual elastomer rings 70. These elastomer rings are glued to the radial surfaces with the adjacent radial metal surfaces, but with regard to an axially parallel pressing, e.g. by the clamping screw 60, there is a minimal radial distance outwards and inwards on the elastomer ring 70.

Das Dämpfungselement 57 gleicht daher in der zweiten Ausführungsform einer "MehrscheibenKupplung"' wobei die entsprechenden Dämpfungskräfte im wesentlichen an radialen Flächen und im Elastomerring 70 in radialer Richtung aufgenommen werden.In the second embodiment, the damping element 57 therefore resembles a “multi-plate clutch”, the corresponding damping forces being absorbed essentially on radial surfaces and in the elastomer ring 70 in the radial direction.

Die Fräszähne, die im Beispiel nach Fig. 4 nicht dargestellt sind, werden an der radialen Umfangsfläche 83 z.B. verschweißt. Hierbei wird die Schweißbefestigung vorzugsweise über die gesamte axiale Erstreckung der Umfangsfläche 83 vorgesehen, damit die Kraftübertragung über sämtliche Segmente und Elastomerringe 70 erfolgen kann.The milling teeth, which are not shown in the example according to Fig. 4, are on the radial peripheral surface 83 e.g. welded. In this case, the welding attachment is preferably provided over the entire axial extent of the circumferential surface 83, so that the force can be transmitted across all segments and elastomer rings 70.

Im Falle einer abrupten Blockierung eines Fräszahns 18 gegenüber der Abtriebswelle 21 werden daher in den Elastomerringen 70 Scher- und Verformungskräfte aufgenommen, so daß die abrupte Krafteinwirkung durch ein Blockieren nur stark reduziert auf die Abtriebswelle 21 übertragen wird.In the event of an abrupt blocking of a milling tooth 18 with respect to the output shaft 21, shear and deformation forces are therefore absorbed in the elastomer rings 70, so that the abrupt action of the force is only transmitted to the output shaft 21 in a greatly reduced manner by blocking.

In Fig. 5 ist das Beispiel nach Fig. 4 mit Blick auf die Stirnseite 28 in einen Umfangsbereich von 90° herausgezeichnet. Es ist hierbei erkennbar, daß die radial inneren Bolzenschrauben 58 der Verbindung des Nabenringes 51 mit der Abtriebswelle 21 dienen. Die Klemmschrauben 60 sind radial außen angeordnet, während im mittleren Bereich die Schrauben 59 zur Festlegung der Segmente 52 bis 55 des Nabenringes 51 dargestellt sind.In FIG. 5, the example according to FIG. 4 is drawn out with a view of the end face 28 into a circumferential area of 90 ° . It can be seen here that the radially inner stud screws 58 serve to connect the hub ring 51 to the output shaft 21. The clamping screws 60 are arranged radially on the outside, while the screws 59 for fixing the segments 52 to 55 of the hub ring 51 are shown in the central region.

Erfindungsgemäß wird daher trotz engster Platzverhältnisse und in robuster einfacher Weise ein Dämpfungselement zwischen den Fräsrädern und deren Fräsradgetriebe vorgesehen, das stoßartig auftretende Drehmomente, z.B. durch Blockieren der Fräsräder auffängt und somit eine Beschädigung des in Richtung zum Antriebsaggregat nachgeschalteten Fräsradgetriebes verhindert.According to the invention, therefore, despite the tightest space and in a robust, simple manner, a damping element is provided between the cutting wheels and their cutting gear, which absorbs sudden torques, e.g. by blocking the cutting wheels and thus preventing damage to the cutting wheel gear connected downstream in the direction of the drive unit.

Claims (13)

1. Slotted wall milling cutter with at least one drive unit, e.g. a hydraulic motor optionally driving by means of an upstream coupling, via a cutting wheel gear the driven shaft or shafts (21) of the cutting wheels (11) equipped with cutting teeth (18), characterized in that a rotation-elastic damping element (17, 57) is provided between the driven shaft (21) and the cutting wheel (11).
2. Slotted wall milling cutter according to claim 1, characterized in that the damping element (17) is provided in the form of a cylindrical bush in radially spaced manner between the driven shaft (21) and the cutting wheel (11).
3. Slotted wall milling cutter according to claims 1 or 2, characterized in that the damping element (17) is an elastomer, particularly comprising a highly elastic natural rubber, which is vulcanized in between an inner hub ring (22) connected in non-rotary manner to the driven shaft (21), and a radially outer metal sleeve (23) with a substantially non-rotary connection to the cutting wheel (11).
4. Slotted wall milling cutter according to claim 3, characterized in that the metal sleeve (23) is in rotary connection with the cutting wheel (11) via several, circumferentially distributed fitting key and slot connections (24).
5. Slotted wall milling cutter according to one of the claims 1 to 4, characterized in that in the case of an outer radius of the circumferential surface (27) of the cutting wheel (11) without cutting teeth (18) of approximately 65 cm, in the fitted state the damping elements (17) has a radial thickness of approximately 3 cm for an inner radius of approximately 50 cm.
6. Slotted wall milling cutter according to one of the claims 1 to 5, characterized in that the damping element (17) extends roughly over the axial depth of the circumferential surface (27) of the cutting wheel (11).
7. Slotted wall milling cutter according to one of the claims 1 to 6, characterized in that the damping element (17) with hub ring (22) and metal sleeve (23) is arranged as a subassembly in radial form between the driven shaft (21) and the cutting wheel (11), particularly by means of axial screw connections.
8. Slotted wall milling cutter according to one of the claims 1 to 7, characterized in that the radial spacing. of the damping element (17) from the axis of the driven shaft (21) is as large as possible.
9. Slotted wall milling cutter according to one of the claims 1 to 8, characterized in that the damping element (17) is designed as a tangential force coupling means between hub ring (22) and an outer metal sleeve (23).
10. Slotted wall milling cutter according to claims 1 or 8, characterized in that the damping element (17) is designed as a radial force coupling means (65, 74, 70, 75, 81) between the cutting wheel (91) and the hub ring (51).
11. Slotted wall milling cutter according to claim 10, characterized in that the radial coupling means (65, 74, 70, 75, 81) has a plurality of elastomer rings (70) fixed between radial ring lands (81, 62, 63, 64) of hub ring (51).
12. Slotted wall milling cutter according to claim 11, characterized in that the elastomer rings (70) are axially and radially fixed between the radial ring lands.
13. Slotted wall milling cutter according to one of the claims 11 or 12, characterized in that the radial faces of the elastomer rings (70) and the ring segments (66, 62, 63, 64, 81) are connected and in particular bonded in nonrotary manner to one another.
EP88108726A 1987-08-28 1988-05-31 Milling device for slits Expired - Lifetime EP0305658B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88108726T ATE54971T1 (en) 1987-08-28 1988-05-31 DIAPHRAGM CUTTER.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873728866 DE3728866A1 (en) 1987-08-28 1987-08-28 SLOT WALL MILLING
DE3728866 1987-08-28

Publications (2)

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EP0305658A1 EP0305658A1 (en) 1989-03-08
EP0305658B1 true EP0305658B1 (en) 1990-07-25

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EP88108726A Expired - Lifetime EP0305658B1 (en) 1987-08-28 1988-05-31 Milling device for slits

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US (1) US4934978A (en)
EP (1) EP0305658B1 (en)
JP (1) JPS6483726A (en)
AT (1) ATE54971T1 (en)
DE (2) DE3728866A1 (en)
ES (1) ES2016668B3 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5056242A (en) * 1989-05-12 1991-10-15 Finic, B.V. Underground wall construction method and apparatus
JPH0477636U (en) * 1990-11-20 1992-07-07
DE9107187U1 (en) * 1991-06-11 1991-07-25 Bauer Spezialtiefbau
DE102005017754A1 (en) * 2005-04-15 2006-10-19 Wirtgen Gmbh Construction machine, in particular road milling machine, recycler or stabilizer, and drive train for such construction machines
JP6022865B2 (en) * 2012-09-10 2016-11-09 大成建設株式会社 Decontamination equipment for concrete
CN103321266B (en) * 2013-07-21 2015-05-20 日照市东港区水岩基础工程处 Curved knife groover
CN108978754A (en) * 2018-07-05 2018-12-11 河南黄河河务局焦作黄河河务局 A kind of continuous trough forming system and the method that continuous subterranean wall is built using it
DE202019100319U1 (en) * 2019-01-21 2020-04-22 Liebherr-Werk Nenzing Gmbh Trench cutter

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2956187A (en) * 1960-10-11 Nested flexible coupling for dynamoelectric machines
US1868818A (en) * 1930-06-21 1932-07-26 Budd Wheel Co Universal joint
US2262512A (en) * 1941-03-26 1941-11-11 Atlas Press Company Drill press
AT200934B (en) * 1954-03-30 1958-12-10 Hermann Happ Two-part, torsionally elastic shaft connection built between two universal joints of a cardan shaft, especially for motor vehicles
US2880599A (en) * 1957-07-15 1959-04-07 Goodman Mfg Co Vibration damping gear
US3304747A (en) * 1965-03-26 1967-02-21 Walker Neer Mfg Co Elastomer shock absorber for a drive system
DE1634487A1 (en) * 1966-12-06 1970-10-01 Masch Und Bohrgeraete Fabrik Drilling device for the production of slot holes
US4041730A (en) * 1976-02-11 1977-08-16 Dana Corporation Marine propeller bushing coupling
US4266830A (en) * 1977-07-21 1981-05-12 The United States Of America As Represented By The Secretary Of The Interior Auger construction providing reduced noise
DE2941921C2 (en) * 1979-10-17 1982-12-30 Gebr. Eickhoff, Maschinenfabrik U. Eisengiesserei Mbh, 4630 Bochum Dozer blade for drum shearers
DE2942874A1 (en) * 1979-10-24 1981-04-30 Gerhard Dipl.-Ing. 5600 Wuppertal Kirschey ELASTIC SHAFT COUPLING
US4467753A (en) * 1981-07-31 1984-08-28 Deere & Company Vibration dampener on engine shaft
DE3139012C2 (en) * 1981-10-01 1985-02-21 Gebr. Eickhoff Maschinenfabrik U. Eisengiesserei Mbh, 4630 Bochum Roller cutting machine for underground mining
DE3424999C2 (en) * 1984-07-06 1994-01-13 Bauer Spezialtiefbau Trench cutter

Also Published As

Publication number Publication date
DE3728866C2 (en) 1992-10-01
ES2016668B3 (en) 1990-11-16
US4934978A (en) 1990-06-19
DE3728866A1 (en) 1989-03-16
EP0305658A1 (en) 1989-03-08
ATE54971T1 (en) 1990-08-15
JPH0448903B2 (en) 1992-08-10
JPS6483726A (en) 1989-03-29
DE3860362D1 (en) 1990-08-30

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