EP0305658B1 - Schlitzwandfräse - Google Patents

Schlitzwandfräse 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
Authority
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
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0305658A1 (de
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
Original Assignee
Bauer Spezialtiefbau 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 Bauer Spezialtiefbau GmbH filed Critical Bauer Spezialtiefbau GmbH
Priority to AT88108726T priority Critical patent/ATE54971T1/de
Publication of EP0305658A1 publication Critical patent/EP0305658A1/de
Application granted granted Critical
Publication of EP0305658B1 publication Critical patent/EP0305658B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Paleontology (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Pit Excavations, Shoring, Fill Or Stabilisation Of Slopes (AREA)
  • Vehicle Step Arrangements And Article Storage (AREA)
  • Soil Working Implements (AREA)
  • Working Measures On Existing Buildindgs (AREA)
  • Milling Processes (AREA)
EP88108726A 1987-08-28 1988-05-31 Schlitzwandfräse Expired - Lifetime EP0305658B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88108726T ATE54971T1 (de) 1987-08-28 1988-05-31 Schlitzwandfraese.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3728866 1987-08-28
DE19873728866 DE3728866A1 (de) 1987-08-28 1987-08-28 Schlitzwandfraese

Publications (2)

Publication Number Publication Date
EP0305658A1 EP0305658A1 (de) 1989-03-08
EP0305658B1 true EP0305658B1 (de) 1990-07-25

Family

ID=6334749

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88108726A Expired - Lifetime EP0305658B1 (de) 1987-08-28 1988-05-31 Schlitzwandfräse

Country Status (6)

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

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 (da) * 1990-11-20 1992-07-07
DE9107187U1 (de) * 1991-06-11 1991-07-25 Bauer Spezialtiefbau GmbH, 8898 Schrobenhausen Fräsrahmen für eine Schlitzwandfräse mit einer Druckausgleichsvorrichtung für die Lagerdichtungen
DE102005017754A1 (de) 2005-04-15 2006-10-19 Wirtgen Gmbh Baumaschine insbesondere Strassenfräsmaschine, Recycler oder Stabilisierer, sowie Antriebsstrang für derartige Baumaschinen
JP6022865B2 (ja) * 2012-09-10 2016-11-09 大成建設株式会社 コンクリート用除染装置
CN103321266B (zh) * 2013-07-21 2015-05-20 日照市东港区水岩基础工程处 曲形刀挖槽机
CN108978754A (zh) * 2018-07-05 2018-12-11 河南黄河河务局焦作黄河河务局 一种连续成槽装置及采用其建造连续地下墙的方法
DE202019100319U1 (de) * 2019-01-21 2020-04-22 Liebherr-Werk Nenzing Gmbh Schlitzwandfräse

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 (de) * 1954-03-30 1958-12-10 Hermann Happ Zweiteilige, zwischen zwei Wellengelenken einer Kardanwelle eingebaute drehelastische Wellenverbindung, insbesondere für Kraftfahrzeuge
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 (de) * 1966-12-06 1970-10-01 Masch Und Bohrgeraete Fabrik Bohrvorrichtung zur Herstellung von Schlitzloechern
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 (de) * 1979-10-17 1982-12-30 Gebr. Eickhoff, Maschinenfabrik U. Eisengiesserei Mbh, 4630 Bochum Räumschild für Walzenschrämmaschinen
DE2942874A1 (de) * 1979-10-24 1981-04-30 Gerhard Dipl.-Ing. 5600 Wuppertal Kirschey Elastische wellenkupplung
US4467753A (en) * 1981-07-31 1984-08-28 Deere & Company Vibration dampener on engine shaft
DE3139012C2 (de) * 1981-10-01 1985-02-21 Gebr. Eickhoff Maschinenfabrik U. Eisengiesserei Mbh, 4630 Bochum Walzenschrämmaschine für den Untertagebergbau
DE3424999C2 (de) * 1984-07-06 1994-01-13 Bauer Spezialtiefbau Schlitzwandfräse

Also Published As

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

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