EP0778100A1 - Foret héliocoidal de percussion - Google Patents

Foret héliocoidal de percussion Download PDF

Info

Publication number: EP0778100A1
Authority: EP; European Patent Office
Prior art keywords: shaft; cutting tip; cutting; cutting edge; central
Prior art date: 1995-12-07
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.): Granted

Application number

EP96810630A

Other languages

German (de)

English (en)

Other versions

EP0778100B1 (fr

Inventor

Werner Kleine

Werner Bongers

Axel Neukirchen

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.)

Hilti AG

Original Assignee

Hilti AG

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.)

1995-12-07

Filing date

1996-09-25

Publication date

1997-06-11

1996-09-25 Application filed by Hilti AG filed Critical Hilti AG

1997-06-11 Publication of EP0778100A1 publication Critical patent/EP0778100A1/fr

1998-12-23 Application granted granted Critical

1998-12-23 Publication of EP0778100B1 publication Critical patent/EP0778100B1/fr

2016-09-25 Anticipated expiration legal-status Critical

Status Expired - Lifetime legal-status Critical Current

Images

Classifications

- 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
- E21B10/00—Drill bits
- E21B10/46—Drill bits characterised by wear resisting parts, e.g. diamond inserts
- E21B10/58—Chisel-type inserts
- 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
- E21B10/00—Drill bits
- E21B10/44—Bits with helical conveying portion, e.g. screw type bits; Augers with leading portion or with detachable parts
- E21B10/445—Bits with helical conveying portion, e.g. screw type bits; Augers with leading portion or with detachable parts percussion type, e.g. for masonry
- 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
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T408/00—Cutting by use of rotating axially moving tool
- Y10T408/89—Tool or Tool with support
- Y10T408/905—Having stepped cutting edges
- Y10T408/906—Axially spaced
- 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
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T408/00—Cutting by use of rotating axially moving tool
- Y10T408/89—Tool or Tool with support
- Y10T408/905—Having stepped cutting edges
- Y10T408/906—Axially spaced
- Y10T408/9065—Axially spaced with central lead
- 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
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T408/00—Cutting by use of rotating axially moving tool
- Y10T408/89—Tool or Tool with support
- Y10T408/909—Having peripherally spaced cutting edges
- 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
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T408/00—Cutting by use of rotating axially moving tool
- Y10T408/89—Tool or Tool with support
- Y10T408/909—Having peripherally spaced cutting edges
- Y10T408/9095—Having peripherally spaced cutting edges with axially extending relief channel
- Y10T408/9097—Spiral channel

Definitions

the invention relates to a rotary impact twist drill according to the generic preamble of claim 1.
Rotary impact twist drills are drilling tools that are used in connection with axial impact supported rotary drilling rigs.
these are generally rock or masonry drills that can be used for the rotary striking drilling or breakthroughs in concrete or masonry.
a rotary impact twist drill of the generic type is known for example from EP-A-0 322 565. It comprises a shank which has at least one discharge groove in its jacket, which runs spirally from the shank end in the direction of the insertion end of the tool. At the end of the shaft, a groove is provided in the end face of the shaft, which extends over a diameter of the shaft and runs continuously.
a cutting tip with at least one hard metal cutting edge is inserted with its foot part into the groove and fixed there. For example, the cutting tip is soldered into the end of the shaft.
the cutting tip is chamfered in a roof shape with a central tip and axially recessed areas towards the periphery and carries hard metal blades that remove material during operation.
the material is removed by two mechanisms.
the raised central tip of the rotary impact twist drill is hammered into the ground like a chisel by the axial impact.
the rotating movement of the tool causes the material to snap off and shear off.
the cuttings are transported out of the borehole via the at least one main production groove in the shaft. Due to the cutting edge geometry, the central tip of the cutting tip is subjected to particularly high stress during operation. Especially when drilling, when the peripheral areas of the cutting tip are not yet in engagement with the surface, the entire energy of the axial strokes must be absorbed by the central tip.
the tips of the known rotary impact twist drills are often worn out prematurely.
the drilling tool becomes blunt, which manifests itself in unfavorable drilling and centering properties; in addition, the drilling performance often drops sharply after a short time.
the excessive stress on the tip of the cutting tip particularly during drilling, can lead to a break in the edge of the cutting tip in the shaft end or the cutting tip itself, which is preferably made of hard metal.
Another disadvantage of the known rotary impact twist drills is that a relatively great effort has to be made to position the cutting tip exactly in the continuous groove in the shaft end. It must be exactly centered, its protrusion on both sides of the sheath of the shank must be exactly the same in order to ensure a uniform concentricity and to avoid jamming of the drilling tool in the borehole.
the drilling device should be prepared in such a way that modifications, for example of the cutting edge geometry, to improve the degradation properties and the service life of the rotary impact twist drill can be carried out easily.
the base part of the cutting tip is reinforced in the area of its diameter, preferably in the central area of its longitudinal extent, in such a way that its cross section has at least one substantially part-circular bulge.
the continuous groove in the shaft end has a recess designed to reinforce the foot part of the cutting tip.
the base part of the cutting tip is centered in the end of the shaft by positive locking.
the reinforcement in the area of the circumference, preferably in the central area, of the foot part of the cutting tip makes it particularly the one that is particularly heavily loaded by the axial shocks Center area of the drilling tool reinforced.
the reinforced cutting tip can absorb the energy of the axial hits better, especially when drilling into the ground.
the drilling tool does not become blunt prematurely and has an advantageous service life.
the cutting plate is centered in a form-fitting manner due to the thickening in the cross-section, which is essentially partially circular, in the central region of the base of the cutting tip and due to the correspondingly designed recess in the central area of the continuous groove extending over a diameter of the shaft. In this way, the insertion of the cutting tip into the continuous groove is significantly facilitated.
the fact that the central area of the cutting tip is fixed by positive locking also ensures that the cutting tip has the same protrusion on both sides of the mouth of the groove in the casing of the shaft. This makes it easy to manufacture drilling tools with excellent concentricity.
the shape of the recess corresponding to the reinforcement can be made in a simple working step, for example after the creation of the continuous groove.
the form-fitting centering of the cutting tip used also facilitates the subsequent fixing by soldering and the subsequent hardening.
the central region of the base of the cutting tip has two symmetrically arranged, essentially part-circular thickenings, which are held in a correspondingly designed recess symmetrically on both sides of the longitudinal extent of the continuous groove by positive locking.
the symmetrical arrangement of the recesses facilitates the production of the recesses. Due to the symmetrical design of its base part, the cutting tip can also be inserted into the recess in a position rotated by 180 °, which overall further simplifies the manufacture of the rotary impact twist drill.
the reinforcement is essentially cylindrical in the axial direction of the shaft.
the central recess can simply be created by means of a cylindrical bore which is made in front of, simultaneously with or immediately after the milling of the groove in the end face of the shaft end.
the reinforcement can also be essentially conical in the axial direction of the shaft, the tip of the cone lying opposite the hard metal cutting edge and being embedded in the shaft.
the conical bore in the shaft end can be made, for example, similar to a countersink, but it can also be created in a forming process, for example in a stamping process.
the maximum cross section of the reinforcement is approximately 1.2 times to approximately 2 times, preferably approximately 1.5 times, the thickness of the cutting tip, which is preferably made of hard metal. This ensures that the cutting tip is surrounded on all sides by a sufficiently thick material layer of the shaft even in the area of the reinforcement, which is circular in cross section, so that the shaft material cannot fail in the border region.
the cutting tip is segmented and comprises a central cutting edge and two peripheral segments which are connected to one another via thin connecting webs.
the thickness of the connecting webs is less than the thickness of the central cutting edge or the segments.
the central cutting edge rises above the reinforcement of the base part of the cutting tip and projects above the peripheral segments.
the peripheral segments are arranged at a distance from the central cutting edge that is greater than the length of the connecting webs, preferably greater than the thickness of the cutting tip, and smaller than half the circumferential diameter of the central cutting edge.
This embodiment variant of the rotary impact twist drill according to the invention is particularly advantageous in particular in the case of drilling tools of large diameter.
the segmentation of the cutting tip divides the hard metal cutting edge into a central cutting edge with reinforcement and into peripheral segments.
the peripheral segments can perform cutting functions. It turns out that it is not necessary to cut the entire diameter of the mounting hole. It is sufficient if the substrate is processed and crushed in the manner of a breakthrough drill in concentric areas. The remaining standing areas have little stability due to the brittleness of the material and break due to the shocks of the axial shocks. By working the subsurface in concentric areas, the large diameter that occurs when creating a locating hole becomes Reactive powers reduced.
the rotary impact twist drills designed in accordance with the invention, in particular with large diameters, can accordingly also be operated with drilling devices of only medium or low power with satisfactory removal capacities, since the required extraction energy is reduced. Given the available mining energy, the inventive design of the rotary impact twist drill increases the mining speed compared to a conventional tool according to the prior art.
the subdivision of the cutting tip, which is preferably made of hard metal, into segments connected by thin webs has the advantage that it is possible to save on expensive and relatively difficult to machine hard metal in the manufacture of the rotary impact twist drill.
a coherent cutting tip for assembly which can be inserted in one piece and in a form-fitting manner into the continuous groove in the end face of the shaft end.
Another advantage of the thin webs connecting the central cutting edge and the peripheral segments is that they act as predetermined breaking points in the event of excessive shear stress, in particular of the peripheral segments.
the cutting tip thus does not break in an uncontrolled manner in the area of cutting-bearing segments, but specifically only at the connecting webs of the segments which, after the cutting tip has been fixed in the groove in the shaft end, no longer fulfill a supporting or holding function.
the rotary impact twist drill designed according to the invention remains fully operational even with broken webs.
the longitudinal extent of the central cutting edge is at least the same, preferably larger than the largest cross-sectional diameter of the thickening.
the end of the shaft carrying the hard metal cutting edge (s) is equipped with guide elements which are fixed in the stimulating or in the jacket of the shaft and protrude beyond the jacket of the shaft.
the protrusion of the guide elements is the same or preferably less than the protrusion of the cutting tip. Due to their lower overhang, the guide elements hardly contribute to shredding the surface and are practically not stressed by the axial shocks. As a result, they can fully perform their role as management elements be optimized.
the peripheral contour of the guide elements is largely adapted to the contour of the shaft casing.
the axial boundary surface of the guide elements is a cylindrical surface, the radius of curvature of which is equal to the radius of curvature of the jacket of the shaft.
the peripheral segments connected to the central cutting edge via connecting webs are set back axially and radially in relation to additional cutting edges embedded in the end face of the shaft and projecting beyond the shaft jacket. In this way, they serve as guide elements, while the cutting tasks of the peripheral areas up to the borehole wall are taken over by the additional cutting edges. In this case, at least one of the additional cutting edges is assigned a main task.
the advantage of this embodiment variant of the invention lies in the fact that the main load on the cutting tip essentially lies only in the transmission of the axial impacts, and it can be specifically optimized for this loading without having to take the peripheral areas of the cutting tip into account.
the one-piece cutting tip can therefore be made very robust, while the additional cutting edges can be optimized in a manner known per se with regard to their cutting task with regard to their thickness, the cutting edges and angles.
the guide elements or additional cutting edges provided in addition to the cutting tip at the shaft end are each arranged at an acute angle to the continuous groove for the cutting tip.
the additional cutting edges can lie on one diameter, but they can also be arranged completely asymmetrically.
the free space between a guide element or an additional cutting edge and the peripheral section of the cutting tip that extends in the circumferential direction is increased and can be used for a larger dimensioning of the main discharge grooves for the drilling dust.
an additional procedure for the drilling dust can additionally be arranged.
the cutting tip consists of impact-resistant Material and the additional blades are made of a harder material than the cutting tip.
the reinforced central cutting edge and the additional cutting edges can be selected exactly according to their loads and tasks and can be formed from hard metal materials that are particularly suitable for the respective application.
the simple mounting of the cutting tip and the additional cutting edges is retained.
the shaft only has to be provided with a continuous groove which has at least one part-circular recess in the central region. The incisions for the minor cutting edges can, for example, be made in the same operation.
the exemplary embodiment of the rotary impact twist drill according to the invention shown in FIGS. 1 and 2 comprises a shaft 1 which is equipped with two main extraction grooves 4, 5 for cuttings which run in a spiral in its casing 2.
a cutting plate 6 is arranged, which is equipped with hard metal blades 7.
the cutting tip 6 is fixed in a groove 9 which extends over the diameter of the shaft 1.
the cutting tip 6 is fixed in the groove 9 by soldering.
the central region 11 of the foot part 10 of the cutting tip 6 is provided with a thickening which in cross section has the shape of an essentially part-circular Bulge 12 has on the lateral longitudinal contour of the cutting tip 6.
the cutting tip 6 has such a bulge 12 on either side of its longitudinal extent, which are symmetrically opposite one another.
the continuous groove 9 in the end 3 of the shaft 1 has correspondingly shaped recesses 13 which are provided on both sides of the longitudinal extent of the groove 9 in the central region of the cross section of the shaft 1.
the cutting plate 6 inserted into the groove 9 is held against radial displacement by positive locking of its bulges 12 in the central region 11 of its foot part 10 in the recesses 13 of the continuous groove 9.
the cutting plate 6 is axially fixed in a manner known per se, for example by soldering into the groove 9.
the maximum cross section of the foot part 10 in the region of the reinforcement is approximately 1.2 times to approximately 2 times, preferably approximately 1.5 times the thickness of the cutting tip 6.
the reinforcement of the central region 11 of the foot part 10 comprises two symmetrically arranged bulges 12, it goes without saying that the bulges can also be arranged axially offset from one another on both sides of the longitudinal extent of the cutting plate 6. It is also possible to provide only a single, substantially part-circular bulge 12 on one side of the longitudinal extension of the cutting tip 6.
the continuous groove 9, which is provided in the end 3 of the shaft 1 and extends over its diameter, is provided with one or more recesses 13 corresponding to the arrangement of the bulges 12.
FIG. 3 and 4 show a variant of a cutting tip 16 with reinforcement of the central region 11 of its foot part 10 designed according to the invention.
the strengthening of the foot part 10, which is embedded in the shaft 1 when the cutting tip 16 is inserted, can be designed in different ways.
the reinforcement can be cylindrical in the axial direction.
the reinforcement in the axial direction can also be essentially conical.
the reinforcement can end in a cone tip opposite the tip 20 of the hard metal cutting edge, but it can also have the shape of a truncated cone.
the cutting tip 6 is designed to be continuous and carries two continuous carbide cutting edges 7, which axially fall back from a cutting tip 8, the cutting tip 16 shown in FIGS. 3 and 4 is 16 segmented.
the cutting tip 16 comprises a central cutting edge 17 and two peripheral segments 18 which are connected to one another via thin connecting webs 19. The thickness of the connecting webs 19 is less than the thickness of the central cutting edge 17 or the peripheral segments 18.
the central cutting edge 17 is configured similarly to the hard metal cutting edges 7 on the continuous cutting tip 6 according to FIGS. 1 and 2.
the tip 20 of the central cutting edge 17 rises just above the reinforcement with the bulges 12 on both sides of the longitudinal extent of the cutting tip 16.
Two hard metal cutting edges 21 of roof-shaped configuration extend from the tip 20 and run axially recessed in the direction of the connecting webs 19.
the tip 20 of the central cutting edge 17 axially projects beyond the peripheral segments 18 adjoining both sides in the direction of the jacket 2 of the shaft 1.
the distance a, in which the peripheral segments 18 are arranged from the central cutting edge 17, is greater than the length b of the connecting webs 19.
the distance a is greater than the thickness of the cutting tip 16 in the area outside the Thickening and smaller than half the enveloping circle diameter h of the central cutting edge 17.
the longitudinal extent of the central cutting edge 17 is at least the same, preferably larger, than the largest cross-sectional diameter of the foot part 10 in the region of the thickening.
guide elements are provided on the end 3 of the shaft 1 in addition to the hard metal cutting edges 7 and 21.
the guide elements are designed as pins 22 which are fixed in the jacket 2 of the shaft 1 and protrude above it. As indicated, the protrusion of the guide pins 22 over the jacket 2 of the shaft is less than the protrusion of the cutting tip 6.
the envelope circle of the cutting tip 6 is indicated in FIG. 2 by the dashed line h.
the contour of the guide surface 23 of the guide pins 22 is aligned with the contour of the jacket 2 of the shaft 1.
the guide pins 22 from the jacket 2 of the Protrude shaft 1 can also be embedded in the stimulating end 3 of the shaft and project radially and axially, for example, by suitable inclination of the pins 22. It can also be provided that the guide pins 22 are embedded in the peripheral region of the shaft 1 in such a way that part of the outer contour of the guide pins 22 projects beyond the jacket. Instead of guide pins 22 with a circular cross section, those with a polygonal cross section can also be provided.
the guide elements can also be of plate-like shape and have the shape of secondary cutting edges.
FIG. 5 shows a variant of the rotary impact twist drill according to the invention, in which a segmented cutting tip 16 with reinforcement in its base part 10 is inserted into a groove 9 with symmetrically arranged recesses 12.
the cutting tip 16 is, for example, one according to the illustrations in FIGS. 3 and 4.
additional tip-shaped blades 26 are embedded in the end 3 of the shaft 1, for example.
the additional cutting edges 26 project beyond the peripheral segments 18 both axially and radially and define the enveloping circle h.
the peripheral segments 18 merely perform management functions, while the cutting function passes to the additional cutting edges 26. Since the actual material-removing function is performed by the additional cutting edges 26, the main removal grooves 4, 5 are arranged in such a way that they are positioned upstream of the additional cutting edges 26 in the direction of rotation R.
the additional cutting edges 26 are displaced in the direction of the peripheral segments 18. In this way, they form an acute angle with the cutting tip 16. As shown in FIG. 5, the additional cutting edges 26 can lie opposite one another on a diameter, but they can also be arranged in a different manner. Instead of a pair of additional cutting edges 26, only a single additional cutting edge can be provided, which is assigned a main removal groove. In the exemplary embodiment shown, the peripheral segments 18 merely perform a guiding function.
a secondary discharge groove 24, 25 can be provided in the area between the additional cutting edges 26 and the peripheral segments 18, which lead into the main discharge grooves 4, 5 along the axial extension of the shaft 1.
additional cutting edges 26 take over the actual material-removing functions it is advantageous if the cutting plate 6 or 16 consists of an impact-resistant material.
the additional cutting edges 26 are made of a harder and more abrasive material than the cutting tip 6 or 16.
the reinforcement according to the invention in the central region of the foot part of the cutting tip reinforces the central region of the drilling tool which is particularly heavily loaded by the axial shocks. Even in the case of reinforcement hits, the risk of the drilling tool failing in the region of the edge of the cutting tip or of the cutting tip itself is significantly reduced by the reinforcement of the central area.
the reinforced cutting tip can absorb the energy of the axial hits better, especially when drilling into the ground.
the drilling tool does not become blunt prematurely and has an advantageous service life.
the cutting plate is centered in a form-fitting manner due to the thickening in the cross-section, which is essentially partially circular, in the central region of the base of the cutting tip and due to the correspondingly designed recess in the central area of the continuous groove extending over a diameter of the shaft.

Landscapes

Engineering & Computer Science (AREA)
Geology (AREA)
Life Sciences & Earth Sciences (AREA)
Mining & Mineral Resources (AREA)
Physics & Mathematics (AREA)
Environmental & Geological Engineering (AREA)
Fluid Mechanics (AREA)
Mechanical Engineering (AREA)
General Life Sciences & Earth Sciences (AREA)
Geochemistry & Mineralogy (AREA)
Earth Drilling (AREA)
Drilling Tools (AREA)
Processing Of Stones Or Stones Resemblance Materials (AREA)
Percussive Tools And Related Accessories (AREA)

EP96810630A 1995-12-07 1996-09-25 Foret héliocoidal de percussion Expired - Lifetime EP0778100B1 (fr)

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
DE19545647A DE19545647A1 (de)	1995-12-07	1995-12-07	Drehschlag-Wendelbohrer
DE19545647		1995-12-07

Publications (2)

Publication Number	Publication Date
EP0778100A1 true EP0778100A1 (fr)	1997-06-11
EP0778100B1 EP0778100B1 (fr)	1998-12-23

Family

ID=7779438

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP96810630A Expired - Lifetime EP0778100B1 (fr)	1995-12-07	1996-09-25	Foret héliocoidal de percussion

Country Status (6)

Country	Link
US (1)	US5779403A (fr)
EP (1)	EP0778100B1 (fr)
JP (1)	JP3907757B2 (fr)
CN (1)	CN1081117C (fr)
DE (2)	DE19545647A1 (fr)
DK (1)	DK0778100T3 (fr)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE19724373A1 (de) *	1997-06-10	1998-12-17	Hilti Ag	Gesteinsbohrer
DE19810193A1 (de) *	1998-03-10	1999-09-16	Hilti Ag	Bohrwerkzeug
DE19827536A1 (de) *	1998-06-20	1999-12-23	Hilti Ag	Bohrwerkzeug
US6338390B1 (en)	1999-01-12	2002-01-15	Baker Hughes Incorporated	Method and apparatus for drilling a subterranean formation employing drill bit oscillation
DE19942987A1 (de) *	1999-09-09	2001-03-15	Hilti Ag	Bohrwerkzeug
DE19942985A1 (de) *	1999-09-09	2001-03-15	Hilti Ag	Bohrwerkzeug
DE19942986A1 (de) *	1999-09-09	2001-03-15	Hilti Ag	Bohrwerkzeug
DE10011108A1 (de) *	2000-03-09	2001-09-13	Hawera Probst Gmbh	Gesteinsbohrer
DE10053344A1 (de) *	2000-10-27	2002-05-08	Hilti Ag	Gesteinsbohrer
DE10117262A1 (de) *	2001-01-17	2002-07-18	Hilti Ag	Gesteinsbohrer
LU90862B1 (de) *	2001-12-17	2003-06-18	Cerametal Sarl	Schlag-oder Hammerbohrer
GB2400337A (en) *	2003-04-10	2004-10-13	Black & Decker Inc	A cutting plate for a drill bit
USD525272S1 (en) *	2003-12-24	2006-07-18	Robert Bosch Gmbh	Rotary impact drill bit
US7540696B1 (en) *	2004-01-15	2009-06-02	Century Tool & Design, Inc.	Spot drilling insert
DE102004028098A1 (de) *	2004-06-09	2005-12-29	Hilti Ag	Bohrer
JP4917471B2 (ja) *	2007-04-02	2012-04-18	ユニタック株式会社	深穴切削装置
US7740088B1 (en) *	2007-10-30	2010-06-22	The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration	Ultrasonic rotary-hammer drill
DE102009013069B4 (de) *	2008-08-13	2010-10-21	Iml Instrumenta Mechanik Labor Gmbh	Verfahren und Vorrichtung zur Beschaffenheitsuntersuchung von säulenförmigen oder zylindrischen Abschnitten von Körpern
DE102011076365A1 (de) *	2011-05-24	2012-11-29	Robert Bosch Gmbh	Gesteinsbohrer
CN102717127A (zh) *	2012-07-04	2012-10-10	邱立华	能够形成柱锥形孔的钻头
CN105312633A (zh) *	2014-08-04	2016-02-10	丹阳市博上工具有限公司	一种打孔钻
WO2016109116A1 (fr)	2014-12-31	2016-07-07	Smith International, Inc.	Éléments de coupe et outils de forage les incorporant
US9981406B2 (en)	2015-06-25	2018-05-29	Black & Decker Inc.	Drill bit

Citations (3)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US3447616A (en) *	1966-12-29	1969-06-03	Zigmund E Granat	Drills
US4314616A (en) *	1980-01-28	1982-02-09	Acme-Cleveland Corporation	Die-cast masonry drill with leading hard insert
US5287937A (en) *	1992-06-30	1994-02-22	The Sollami Company	Drill bits and the blades therefor

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE118806C (fr) *
US748890A (en) *		1904-01-05		Metal-boring tool
DE2416157C2 (de) *	1974-04-03	1982-08-12	Gebrüder Heller GmbH Werkzeugfabrik, 2807 Achim	Bohrwerkzeug
JPS5439290A (en) *	1977-09-03	1979-03-26	Mitsubishi Metal Corp	Boring tool
DE2903814C2 (de) *	1979-02-01	1982-08-19	Mapal Fabrik für Präzisionswerkzeuge Dr.Kress KG, 7080 Aalen	Bohrkopf
DE3014693A1 (de) *	1980-04-16	1981-10-22	Hilti AG, 9494 Schaan	Gesteinsbohrer
DE3226799C1 (de) *	1982-07-17	1990-04-19	Mapal Fabrik für Präzisionswerkzeuge Dr.Kress KG, 7080 Aalen	Einmesser-Reibahle
JPS6067012A (ja) *	1983-09-26	1985-04-17	Mitsubishi Heavy Ind Ltd	深穴加工用工具
DE3544433C2 (de) *	1985-12-16	1995-12-14	Hilti Ag	Gesteinsbohrer
EP0443517B1 (fr) *	1990-02-20	1995-09-06	Sumitomo Electric Industries, Ltd.	Foret à embout jetable
US5265688A (en) *	1990-04-09	1993-11-30	Hilti Aktiengesellschaft	Rock drill
US5443337A (en) *	1993-07-02	1995-08-22	Katayama; Ichiro	Sintered diamond drill bits and method of making

1995
- 1995-12-07 DE DE19545647A patent/DE19545647A1/de not_active Withdrawn
1996
- 1996-09-25 EP EP96810630A patent/EP0778100B1/fr not_active Expired - Lifetime
- 1996-09-25 DK DK96810630T patent/DK0778100T3/da active
- 1996-09-25 DE DE59601040T patent/DE59601040D1/de not_active Expired - Fee Related
- 1996-11-27 CN CN96121779A patent/CN1081117C/zh not_active Expired - Fee Related
- 1996-12-09 US US08/762,181 patent/US5779403A/en not_active Expired - Fee Related
- 1996-12-09 JP JP32869296A patent/JP3907757B2/ja not_active Expired - Fee Related

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US3447616A (en) *	1966-12-29	1969-06-03	Zigmund E Granat	Drills
US4314616A (en) *	1980-01-28	1982-02-09	Acme-Cleveland Corporation	Die-cast masonry drill with leading hard insert
US5287937A (en) *	1992-06-30	1994-02-22	The Sollami Company	Drill bits and the blades therefor

Also Published As

Publication number	Publication date
CN1159383A (zh)	1997-09-17
DK0778100T3 (da)	1999-08-23
JPH09177467A (ja)	1997-07-08
US5779403A (en)	1998-07-14
JP3907757B2 (ja)	2007-04-18
DE19545647A1 (de)	1997-06-12
EP0778100B1 (fr)	1998-12-23
CN1081117C (zh)	2002-03-20
DE59601040D1 (de)	1999-02-04

Publication	Publication Date	Title
EP0778100B1 (fr)	1998-12-23	Foret héliocoidal de percussion
EP0281997B1 (fr)	1991-10-02	Fleuret à rocher
EP0778391B1 (fr)	2003-08-20	Perceuse rotative hélicoidale à percussion
EP1008721B1 (fr)	2002-08-21	Outil de coupe ou de creusement et plaquette de coupe associée
DE2945766C2 (de)	1983-10-20	Bohrkrone und Bohrwerkzeug mit einer solchen Bohrkrone
DE3820695C2 (de)	1996-07-25	Gesteinsbohrer
EP0884448B1 (fr)	2004-12-08	Trépan de roche avec rainures d'évacuation hélicoidales
EP1045112B1 (fr)	2005-07-27	Broche à pierre
DE2414354A1 (de)	1975-10-16	Gesteinsbohrer
EP0657617A1 (fr)	1995-06-14	Trépan de roche
EP0707129A2 (fr)	1996-04-17	Outil de forage avec support et éléments de coupe
EP1316669A2 (fr)	2003-06-04	Outil de forage pour roche
EP0655547A2 (fr)	1995-05-31	Trépan de roche avec partie transporteuse hélicoidale
EP1083294A1 (fr)	2001-03-14	Outil de forage
DE3020284C2 (fr)	1987-10-15
EP1083295B1 (fr)	2005-11-16	Outil de forage
EP1455978A1 (fr)	2004-09-15	Outil de per age par percussion ou par martelage
EP3445519B1 (fr)	2022-11-09	Foret
EP1083293B1 (fr)	2005-11-02	Outil de forage
EP0778390B1 (fr)	2003-10-01	Perceuse rotative hélicoidale à percussion
EP0334806B1 (fr)	1993-10-13	Couronne de forage de roche
DE3825107C2 (de)	1996-07-11	Gesteinsbohrer mit Schneidplatte
EP0965406B1 (fr)	2008-11-19	Outil de forage
EP0965405B1 (fr)	2005-04-20	Outil de forage
EP1188897B1 (fr)	2006-06-28	Trépan de forage de roche

Legal Events

Date	Code	Title	Description
1997-04-25	PUAI	Public reference made under article 153(3) epc to a published international application that has entered the european phase	Free format text: ORIGINAL CODE: 0009012
1997-06-11	AK	Designated contracting states	Kind code of ref document: A1 Designated state(s): CH DE DK FR GB IT LI SE
1998-02-04	17P	Request for examination filed	Effective date: 19971211
1998-04-29	17Q	First examination report despatched	Effective date: 19980312
1998-05-25	GRAG	Despatch of communication of intention to grant	Free format text: ORIGINAL CODE: EPIDOS AGRA
1998-06-24	GRAG	Despatch of communication of intention to grant	Free format text: ORIGINAL CODE: EPIDOS AGRA
1998-06-24	GRAH	Despatch of communication of intention to grant a patent	Free format text: ORIGINAL CODE: EPIDOS IGRA
1998-10-20	GRAH	Despatch of communication of intention to grant a patent	Free format text: ORIGINAL CODE: EPIDOS IGRA
1998-11-06	GRAA	(expected) grant	Free format text: ORIGINAL CODE: 0009210
1998-12-23	AK	Designated contracting states	Kind code of ref document: B1 Designated state(s): CH DE DK FR GB IT LI SE
1998-12-31	REG	Reference to a national code	Ref country code: CH Ref legal event code: EP
1999-02-04	REF	Corresponds to:	Ref document number: 59601040 Country of ref document: DE Date of ref document: 19990204
1999-02-19	ET	Fr: translation filed
1999-04-14	GBT	Gb: translation of ep patent filed (gb section 77(6)(a)/1977)	Effective date: 19990319
1999-08-23	REG	Reference to a national code	Ref country code: DK Ref legal event code: T3
1999-10-29	PLBE	No opposition filed within time limit	Free format text: ORIGINAL CODE: 0009261
1999-10-29	STAA	Information on the status of an ep patent application or granted ep patent	Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT
1999-12-15	26N	No opposition filed
2002-01-01	REG	Reference to a national code	Ref country code: GB Ref legal event code: IF02
2002-09-25	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: GB Payment date: 20020925 Year of fee payment: 7
2003-09-25	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20030925
2004-05-12	GBPC	Gb: european patent ceased through non-payment of renewal fee	Effective date: 20030925
2008-10-31	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: DK Payment date: 20080912 Year of fee payment: 13
2008-11-28	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: IT Payment date: 20080926 Year of fee payment: 13 Ref country code: FR Payment date: 20080915 Year of fee payment: 13
2009-01-30	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: DE Payment date: 20080829 Year of fee payment: 13 Ref country code: CH Payment date: 20081016 Year of fee payment: 13
2009-02-27	PGFP	Annual fee paid to national office [announced via postgrant information from national office to epo]	Ref country code: SE Payment date: 20080908 Year of fee payment: 13
2010-04-30	REG	Reference to a national code	Ref country code: CH Ref legal event code: PL
2010-05-05	EUG	Se: european patent has lapsed
2010-05-10	REG	Reference to a national code	Ref country code: DK Ref legal event code: EBP
2010-06-25	REG	Reference to a national code	Ref country code: FR Ref legal event code: ST Effective date: 20100531
2010-07-30	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090930 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100401
2010-10-29	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090930 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090930
2011-01-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: DK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090930
2011-03-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090925
2011-05-31	PG25	Lapsed in a contracting state [announced via postgrant information from national office to epo]	Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090926