US3695721A - Internally vibrated roller cutter apparatus for cutting earth and rock - Google Patents

Internally vibrated roller cutter apparatus for cutting earth and rock Download PDF

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Publication number
US3695721A
US3695721A US80398A US3695721DA US3695721A US 3695721 A US3695721 A US 3695721A US 80398 A US80398 A US 80398A US 3695721D A US3695721D A US 3695721DA US 3695721 A US3695721 A US 3695721A
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United States
Prior art keywords
roller cutter
work tool
cutter means
roller
head according
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Expired - Lifetime
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US80398A
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English (en)
Inventor
Heinrich Jungel
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Fried Krupp AG
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Fried Krupp AG
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    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S37/00—Excavating
    • Y10S37/904—Vibration means for excavating tool

Definitions

  • Driving devices of this type are known in the art. According to these driving devices, the bearing bodies of the roller chisels are mounted for instance at the lower ends of rods which are displaceably guided in vertical bores of the tool carrier against the thrust of springs. For each individual roller chisel there is provided an unbalance vibrator which is mounted on a platform at the upper end of the respective rod, which end protrudes beyond the tool carrier. According to another heretofore known working device of the above mentioned type, a plurality of unbalance vibrators are arranged on the tool carrier which is displaceably guided by a shank in vertical direction while a set of weights, through the intervention of springs, acts upon the upper end of the shank.
  • roller chisels especially a driving device for drifts, tunnels, shafts, and the like which will combine the above mentioned advantages inherent to the employment of vibrators for advancing devices, with roller chisels, without encountering the above mentioned drawbacks.
  • FIG. 1 diagrammatically illustrates a vertical axial section through a roller chisel and a portion of the tool carrier according to the present invention.
  • FIG. 2 represents a section taken along the line II-II of FIG. 1.
  • FIG. 3 is a section similar to that of FIG. 2 for two different positions of an unbalance mass.
  • FIG. 4 is a vertical axial section through a roller chisel and a portion of the tool carrier according to a modification of the present invention.
  • FIGS. 5 and 6 illustrate roller chisels and the structural elements carrying the same, according to a third and fourth embodiment respectively of the present invention.
  • the working device is characterized primarily in that the vibrators are mounted in the interior of the hollow roller chisels and act upon the same while bypassing the bearings.
  • vibrators known per se are employed which comprise housings with cylindrical roller paths provided in the interior of said housings for roller bodies serving as unbalancing mass, said housings being formed by the roller chisels.
  • This may be realized in a manner known per se in such a way that the roller path of a vibrator is formed by the circumferential surface of a shaft which extends through the housing and is fixedly connected thereto.
  • the roller body forms a circular ring and has its bore, the diameter is greater than the diameter of the shaft surrounded by the latter.
  • the roller path of a vibrator is formed by the circumferential surface of the hollow chamber of the housing.
  • the roller movement of the roller body on the roller path is produced by compressed air or the like introduced into the housing, i.e., into the interior of the roller chisel.
  • compressed air for driving unbalance masses within the roller chisel brings about the particular advantage that a cooling effect is obtained when the compressed air expands. This cooling effect has a favorable effect upon the roller chisel and the bearings therefor.
  • the air which leaves the roller chisels can be used for lubricating purposes and for protecting the bearings against dust, or the like.
  • roller paths each are arranged within said roller chisel for counter moving roller bodies, said roller paths being arranged adjacent to each other.
  • the guiding paths of said bearings are so designed that they are able to offer as high a resistance as possible to any radial movement of oscillation of the roller chisel in a direction transverse to the direction of movement of the bearings, i.e., parallel to the working face.
  • roller chisel there are provided adjacent to each other three or more roller tracks or roller paths for counter moving roller bodies in such a way that in all positions of the roller bodies, also the total of the moments exerted upon the roller chisel by the centrifugal force components respectively at a right angle to the direction of movement of the bearings, will at least approximately be zero.
  • the frequence of the oscillations of a roller chisel at least approximately equal to the fundamental frequency of the oscillation system which is formed by the masses taking part in the oscillating movement and by the springs between the pertaining bearings and the tool carrier.
  • the working frequency of the vibrator will, only at an approximate tuning of the system in the above mentioned way, adjust itself automatically in conformity with the fundamental frequency and will follow also slight changes in the fundamental frequency of the system.
  • the fundamental frequency of the system may also be selected much lower than the working frequency of the vibrator.
  • the hollow roller chisel 1 shown therein is passed through by a shaft 2 arranged co-axially with regard to the roller chisel l.
  • Shaft 2 is fixedly connected to the roller chisel 1.
  • the ends of shaft 2 protrude at both sides of the end walls 3 of the roller chisel l and are located in bearings 4.
  • These bearings form sliding bearings, but if desired, also antifriction bearings may be employed instead.
  • the bearings 4 are located in guiding bodies 5 which, by means of upwardly extending cylindrical studs 6 are displaceably guided in vertical bores of the tool carrier 7.
  • Tool carrier 7 is, in a manner known per se, rotatably journalled on the frame, for instance, of a shaft driving machine so as to be rotatable about the shaft axis.
  • the drives acting upon the tool carrier 7 for turning and for the feed may be realized in any standard manner.
  • strong dish springs 8 between the tool carrier 7 and below collars of the guiding body 5, which collars are arranged below said tool carrier 7, there are provided strong dish springs 8, by means of which, the roller chisel 1 is, by the tool carrier 7, pressed against the bottom 9 of the mine shaft.
  • the springs 8 are preferably by counter springs 8a preloaded by nuts 6a.
  • the roller chisel may act upon the ore in any other arrangement, for instance, may press against the face (Ortsbrust) of a drift or tunnel to be driven.
  • the individual roller chisels of the driving device are arranged with regard to each other. Depending upon the circumstances, they may be stepped in radial direction with regard to the axis of rotation of the tool carrier 7 and also in the direction of rotation of the tool carrier with regard to each other.
  • the roller chisel 1 has three cylindrical co-axial hollow chambers 10, 11, 12 which are separated from each other by partitions 13, 14 extending to the shaft 2.
  • three circular metallic rings l5, l6, 17 Arranged in the hollow chambers 10, 11, 12 there are provided three circular metallic rings l5, l6, 17 which form the unbalance masses. These unbalance masses have their end faces in close engagement with the end faces of the hollow chambers l0, ll, 12. They have the same outer diameter and by means of the walls defining their bores extend around the shaft 2.
  • the bores of the three rings have the same diameter, which is greater than the diameter of the shaft 2.
  • the rings 15 and 17 have the same width. They are half as wide as the ring 16.
  • the shaft 2 has one end provided with an extension or stud 18 which protrudes beyond a guiding body 5.
  • This guiding body is, through the intervention of seals 19, surrounded by an annular body 20 which is secured against rotation.
  • Body 20 comprises an annular chamber which, through the intervention of a nipple, is connected to a compressed air feeding line 21 and through radial bores in stud l8 communicates with an axial bore 22 of shaft 2.
  • This bore 22, which is closed at the end of the stud 18, extends into the region of the unbalance rings l7, l6, l5. Bore 22 communicates through radial slots 23, 24, 25 in shaft 2 with the hollow chambers 10, 11 and 12, respectively.
  • guiding members 26, 27, 28 are guided which, by means of their end faces closely engage the end faces of the hollow chambers 10, ll, 12 as well as the end faces of slots 23, 24, 25, which end faces are flush with the end faces of the hollow chambers 10, ll, 12. Furthermore, said sliding members 26, 27, 28 are in line contact with the cylindrical surfaces of the bores of the rings l5, 16, 17.
  • the sliding members are at one side thereof provided with grooves 29 through which compressed air may pass from the axial bore 22 into bores of rings 15, l6, 17.
  • the end walls 3 and the partitions l3, 14 are provided with radially extending grooves 30, which on one hand lead into the bores of the rings l5, 16, 17, and on the other hand lead into the hollow chambers l0, ll, 12 close to the circumferential surfaces thereof and, more specifically, outside the rings l5, 16, 17.
  • the radial grooves 30 are, through the intervention of passages 31, 32, provided in end walls 2 and in end walls 13, 14 respectively, in communication with the atmosphere.
  • the three rings l5, 16, 17 have the same position with regard to the shaft 2.
  • the said three rings engaging the cylindrical circumferential surface of shaft 2 at the highest mantle line 33 of said circumferential surface. Accordingly, the center line 34 of the rings, i.e., the line of gravity thereof is located below the center line 35 of shaft 2. It is assumed that the roller chisel 1 occupies such rotary position that the radial slots 23, 24, 25
  • the rolling movement of the intermediate ring 16 is directed opposite to the rolling movements of the rings 15 and 17. This is due to the fact that the grooves 29 of the slide 27 when viewing the starting position of FIG. 2, are located on that side opposite to that of grooves 29 of slides 26 and 28, and that consequently also the radial groove 30 in the partition 13 is located on that side of the slide which faces away from grooves 29, in other words, when looking at FIG. 2 on the right-hand side of the there illustrated slide.
  • the rotating speeds of all three rings 15, 16, 17 are the same.
  • the center lines, for instance 34, of rings 15, 16, 17 will, during the rotation of the rings, move on circular cylinders, the center lines of which co-incide with the center line 35.
  • FIG. 3 shows the rings in a position which they occupy when said rings have rolled on the shaft to such an extent that the mantle lines 30', 32 along which the rings l5, l7, l6 engage the circumferential surface of shaft 2 have moved out by 45 from the starting position 33.
  • the lines of gravity of the rings have moved into the positions designated with the reference numerals 34 and 34" respectively.
  • centrifugal forces F and F occur in the rings.
  • the directions of these centrifugal forces define together with the vertical line passing through the center line 35, angles of 45 each.
  • FIG. 3 shows the composition of the centrifugal force F and of the sum of the cen trifugal forces F and F of two horizontal components W and two vertical components L.
  • the horizontal components W cancel each other out whereas the vertical components L add to each other.
  • the total of the vertical components is the total force which is exerted upon the roller chisel 1 by the unbalance masses 15, 16, 17in their respective illustrated positions. Inasmuch as this force drives the cutting edges of the roller chisel downwardly into the ore 9, the ore will be blown up to a corresponding extent.
  • the roller chisel During the operation of the roller chisel, the latter rolls in conformity with the rotary movement of the tool carrier 7 on the ore.
  • the advancing direction of shaft 2 is designated by the arrow A.
  • the roller chisel 2 will, with regard to FIG. 2, rotate in a counterclockwise direction.
  • shaft 2 fixedly connected thereto which shaft 2 rotates in bearings 4.
  • the slides 26, 27, 28 and the radial grooves 30 take part in said rotary movement.
  • the rolling movements of the compressed airdriven rings l5, l6, and 17 about shaft 2 are not affected by the said rotation.
  • the speed of rotation of rings l5, l6, l7 greatly exceeds the circumferential speed of the roller chisel.
  • Unbalance-vibrators as formed with the described embodiment of the invention by rings 15, 16, 17 and the hollow roller chisel 1 with shaft 2 are, as mentioned above, known per se. It is also possible to employ a different type of likewise known unbalance vibrators for the roller chisel.
  • the unbalance masses are formed by balls or circular cylindrical bodies which roll on circular cylindrical inner surfaces of the roller chisel.
  • the drive for the rotary movements of these unbalance masses is likewise effected by compressed air which automatically is fed through the shafts of the roller chisels.
  • the compressed air is not controlled by slides or valves, but is, by nozzles in jets approximately tangential to the path of rotation directed toward the ball or cylinder-shaped unbalance masses.
  • the invention is not limited to embodiments in which the oscillations of the roller chisel are produced by unbalance masses rolling in the interior of the roller chisel.
  • FIG. 4 shows another embodiment of the present invention.
  • the roller chisel 40 is held in bearings of two guiding bodies 43 by means of hollow studs 41.
  • the said guiding bodies 43 similar to the guiding bodies 5 of the first embodiment described above are vertically displaceably guided in the bores of the tool carrier 7 and rest from below against the tool carrier by means of preferably pre-loaded dish springs 8.
  • a hollow chamber 44 of the expediently divided roller chisel 40 there is provided a housing 45 with studs 46 which, on both sides, extend through bores of the hollow stud 41 toward the outside where they are rigidly connected to the guiding body 43.
  • a bolt 47 In the lower portion of housing 45 there is vertically displaceably guided a bolt 47, the rounded end of which, protrudes downwardly out of the housing 45 and into a groove 48 of the roller chisel 40.
  • an impact bolt 49 Above the bolt 47 and co-axial therewith there is displaceably guided an impact bolt 49 which is held in its illustrated elevated position by means of a spring 50.
  • compressed air By compressed air, which is introduced through a passage 51 in housing 45 through one of the studs 46 into the chamber above the impact bolt 49, the latter is driven downwardly so that the impacts upon the bolt 47 with the result that the latter in groove 48 hits upon the roller chisel 40.
  • the compressed air may, for instance, by means of a discharge conduit 52 which is released in the lowermost position of the impact bolt 49, in combination with spring 50 placed into oscillations so that the roller chisel 40 will, in the rhythm of said oscillations receive downward shocks by the bolt 47, in other words, will be subjected to oscillations for breaking up the ore 9.
  • FIG. shows that the bearings of a roller chisel 1 which, in conformity with this invention, has vibrators 58 arranged in the interior thereof will not be located in vertically displaceable guiding bodies as is the case with the embodiment of FIGS. 1 4. Instead, a support 53 which comprises the bearings 54 of the roller chisel is arranged on a pivotable member 55 which is pivotally located below the tool carrier 7 on a support 56.
  • the arrangement is such that the pivot axis 57 is parallel to the center line of bearings 54 and is arranged in spaced relationship thereto. This brings about that transverse forces O which occur as horizontal components of the centrifugal forces of unbalance masses, for instance, of a ring 58, in conformity with ring in FIGS.
  • Springs 60 by means of which with the embodiment of FIG. 5, the bearing body 50 rests against the tool carrier are expediently located in a recess of the tool carrier above the bearing support 53. These springs are preloaded through the intervention of counter springs 61 and nuts 62.
  • the rocker or oscillatable member 55 may be formed by a leaf spring 63 having one end connected to the tool carrier 7. This embodiment is simpler and can produce an even greater rigidity in strength in a direction transverse to the working direction.
  • hollow roller cutter means for cutting engagement with a formation being worked, a work tool carrier, bearing means rotatably supporting said hollow roller cutter means, means resiliently supporting said bearing means on said work tool carrier, vibrator means for vibrating said hollow roller cutter means in the working direction thereof to augment the cutting action of the hollow roller cutter means, said vibrator means being unbalance mass means mounted inside said hollow roller cutter means and acting directly thereon, and means for driving said unbalance mass means in rotation thereby to develop vibrating forces on said hollow roller cutter means.
  • a work tool head which includes a shaft extending axially through said hollow roller cutter means and fixed thereto, said mass means surrounding said shaft with radial clearance and rolling thereon when driven in rotation.
  • a work tool head according to claim 2 in which said shaft extends from both ends of said hollow roller cutter means and is rotatably supported by said bearing means.
  • a work tool head which includes compressed air inlet means leading into said roller cutter means, and means for driving said mass means in rotation by compressed air supplied to said roller cutter means via said inlet means.
  • a work tool head according to claim I in which said mass means comprises at least two cylindrical mass elements in said roller cutter means adapted to rotate therein in opposite directions and at such phase relation to each other as to balance out vibrating forces developed on said roller cutter means which are at right angles to said working direction of said roller cutter means.
  • said mass means comprises three cylindrical masses in side by side relation in said roller cutter means with one mass rotating in one direction and the other two masses rotating in the opposite direction and with the phases of the masses being such that all vibrating forces developed on said roller cutter means which are at right angles to said working direction of said roller cutter means are balanced out.
  • a work too] head according to claim 1 in which said means supporting said bearing means on said carrier comprises an arm which at one end engages said bearing means and at the other end is supported on said carrier.
  • a work tool head in which said arm is a leaf spring and at said other end is fixed to said carrier.
  • a work tool head according to claim 9 in which said arm at said other end is pivotally supported on said carrier on an axis parallel to the axis of rotation of said roller cutter means.

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Earth Drilling (AREA)
  • Excavating Of Shafts Or Tunnels (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
US80398A 1969-10-24 1970-10-13 Internally vibrated roller cutter apparatus for cutting earth and rock Expired - Lifetime US3695721A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1953550A DE1953550C2 (de) 1969-10-24 1969-10-24 Mit Rollenmeißeln bestückter Arbeitskopfeiner Einrichtung zum Abtragen von Gestein, insbesondere einer Vortriebseinrichtung zum Auffahren von Strecken, Schächten od. dgl

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US80398A Expired - Lifetime US3695721A (en) 1969-10-24 1970-10-13 Internally vibrated roller cutter apparatus for cutting earth and rock

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US (1) US3695721A (sh)
JP (1) JPS4913121B1 (sh)
AT (1) AT304411B (sh)
CA (1) CA943981A (sh)
CH (1) CH534777A (sh)
DE (1) DE1953550C2 (sh)
FR (1) FR2065498B1 (sh)
GB (1) GB1304249A (sh)
NL (1) NL7014948A (sh)
NO (1) NO127363B (sh)
SE (1) SE359885B (sh)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3860292A (en) * 1971-11-30 1975-01-14 J C Soding & Halbach Rock boring cutter with internal vibrator
US4386663A (en) * 1981-02-25 1983-06-07 Hughes Tool Company Cooled journal bearing
EP0125232A1 (de) * 1983-04-11 1984-11-14 VOEST-ALPINE Aktiengesellschaft Verfahren zum Schrämen von Gestein sowie Vorrichtung zur Durchführung dieses Verfahrens
US7546883B1 (en) 2006-05-15 2009-06-16 Astec Industries, Inc. Vibratory plow
US20130082507A1 (en) * 2010-04-16 2013-04-04 Bomag Gmbh Method for operating a ground milling machine with height-adjustable milling roller
CN108128031A (zh) * 2018-01-25 2018-06-08 文弟陆 一种压克力钻石贴纸全自动筛钻印刷机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3791705A (en) * 1972-03-31 1974-02-12 Robbins Co Mounting structure for a rock cutter wheel
JPS5278520U (sh) * 1975-12-09 1977-06-11
JPS60117818U (ja) * 1984-01-18 1985-08-09 田淵　和久 分娩処置衣
CH672659A5 (sh) * 1984-04-19 1989-12-15 Bechem Hannelore
JPS6360410U (sh) * 1986-10-08 1988-04-22

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE347785C (de) * 1920-11-23 1922-01-24 Det Tekniske Forsoegsaktiesels Mechanischer Hammer
US2654586A (en) * 1950-02-04 1953-10-06 Goodman Mfg Co Digging machine for mining coal
US2659585A (en) * 1951-06-29 1953-11-17 Goodman Mfg Co Power drive connection for combined rotatable and oscillatable mining tools
US3082668A (en) * 1959-11-20 1963-03-26 Vibrator Mfg Company Surface-treating machine
US3151912A (en) * 1961-01-14 1964-10-06 Gewerk Eisenhuette Westfalia Impact planer device for extraction of mineral material
DE1205024B (de) * 1960-08-23 1965-11-18 Heinz J Bienert Rotationsvibrator fuer Erdbohrungen
US3544075A (en) * 1968-08-21 1970-12-01 Robbins & Assoc James S Vibrator systems

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE347785C (de) * 1920-11-23 1922-01-24 Det Tekniske Forsoegsaktiesels Mechanischer Hammer
US2654586A (en) * 1950-02-04 1953-10-06 Goodman Mfg Co Digging machine for mining coal
US2659585A (en) * 1951-06-29 1953-11-17 Goodman Mfg Co Power drive connection for combined rotatable and oscillatable mining tools
US3082668A (en) * 1959-11-20 1963-03-26 Vibrator Mfg Company Surface-treating machine
DE1205024B (de) * 1960-08-23 1965-11-18 Heinz J Bienert Rotationsvibrator fuer Erdbohrungen
US3151912A (en) * 1961-01-14 1964-10-06 Gewerk Eisenhuette Westfalia Impact planer device for extraction of mineral material
US3544075A (en) * 1968-08-21 1970-12-01 Robbins & Assoc James S Vibrator systems

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3860292A (en) * 1971-11-30 1975-01-14 J C Soding & Halbach Rock boring cutter with internal vibrator
US4386663A (en) * 1981-02-25 1983-06-07 Hughes Tool Company Cooled journal bearing
EP0125232A1 (de) * 1983-04-11 1984-11-14 VOEST-ALPINE Aktiengesellschaft Verfahren zum Schrämen von Gestein sowie Vorrichtung zur Durchführung dieses Verfahrens
AU568641B2 (en) * 1983-04-11 1988-01-07 Voest-Alpine Bergtechnik Gesellschaft Mbh Pick for cutting head
US7546883B1 (en) 2006-05-15 2009-06-16 Astec Industries, Inc. Vibratory plow
US20130082507A1 (en) * 2010-04-16 2013-04-04 Bomag Gmbh Method for operating a ground milling machine with height-adjustable milling roller
US8960806B2 (en) * 2010-04-16 2015-02-24 Bomag Gmbh Method for operating a ground milling machine with height-adjustable milling roller
CN108128031A (zh) * 2018-01-25 2018-06-08 文弟陆 一种压克力钻石贴纸全自动筛钻印刷机

Also Published As

Publication number Publication date
GB1304249A (sh) 1973-01-24
CA943981A (en) 1974-03-19
DE1953550B1 (de) 1971-04-01
SE359885B (sh) 1973-09-10
AT304411B (de) 1973-01-10
NO127363B (sh) 1973-06-12
DE1953550C2 (de) 1974-03-21
FR2065498B1 (sh) 1973-01-12
CH534777A (de) 1973-03-15
NL7014948A (sh) 1971-04-27
JPS4913121B1 (sh) 1974-03-29
FR2065498A1 (sh) 1971-07-30

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