EP0658681A2 - Marteau à forage - Google Patents

Marteau à forage Download PDF

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Publication number
EP0658681A2
EP0658681A2 EP94119216A EP94119216A EP0658681A2 EP 0658681 A2 EP0658681 A2 EP 0658681A2 EP 94119216 A EP94119216 A EP 94119216A EP 94119216 A EP94119216 A EP 94119216A EP 0658681 A2 EP0658681 A2 EP 0658681A2
Authority
EP
European Patent Office
Prior art keywords
hammer drill
bores
adapter
outer tube
hammer
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.)
Granted
Application number
EP94119216A
Other languages
German (de)
English (en)
Other versions
EP0658681B1 (fr
EP0658681A3 (fr
Inventor
Hans-Phillip Walter
Ralf Buczeck
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.)
Walter Hans-Philipp
Original Assignee
Walter Hans-Philipp
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 Walter Hans-Philipp filed Critical Walter Hans-Philipp
Publication of EP0658681A2 publication Critical patent/EP0658681A2/fr
Publication of EP0658681A3 publication Critical patent/EP0658681A3/fr
Application granted granted Critical
Publication of EP0658681B1 publication Critical patent/EP0658681B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers

Definitions

  • the present invention relates to a pneumatically driven hammer drill, in particular a deep hole hammer, according to the preamble of claim 1.
  • DE-U-9 202 336 describes a hammer drill of the type mentioned at the outset, which can also be used well in difficult rock. It has a rotatably driven tubular body for metering the blown air and a shaft which can be displaced therein and has a central passage, the lower end of which forms a shut-off element with the tubular body (or a sleeve part), for example a rotary or parallel slide, which releases an air deflection space as required or - possibly partially - closed.
  • the neck of the shaft which is connected to the tubular body and a leading shaft can have a number of bores on the circumference provided pipe head are at risk of breakage due to relatively weak cross sections, especially since the length of the hammer drill acts on it with a large lever arm.
  • the invention aims to create a rotary hammer of the type mentioned, which is simple in construction and economical to manufacture and which provides long service lives with great performance.
  • the hammer should also be further developed so that it works relatively quietly even at an increased stroke frequency with low compressed air consumption.
  • a pneumatically driven hammer drill in particular a deep hole hammer, with an upper cap for connection to a compressed air source and, if appropriate, to a drill pipe, with an outer tube and a central tube with radial passages, which has a check valve upstream and which is firmly connected to a control housing, and with one on the outer tube at the bottom axially displaceably held drill bit, the head of which can be slid onto the lower end of the central tube, which leads a percussion piston guided in a cylinder liner
  • the invention provides according to claim 1 that the cylinder liner and the control housing casing with the outer tube at least partially form-fitting are firmly connected to a unit.
  • the cylinder liner can connect to a shoulder in the outer tube with the same diameter and be fixed concentrically to the control housing jacket, e.g. by fitting the lower end of a tubular body, which advantageously contributes to the concentric anchoring of the cylinder liner.
  • control housing jacket is circumferentially welded flush with the outer tube without welding additives over an axial region, the length of the welding zone being the outer diameter of the outer tube is in a ratio of 1: 1 to 1: 2, preferably in a ratio of 1: 1.5 to 1: 1.8.
  • the outer grooves provided in claim 4 enable the attachment of screwing tools, which has great advantages in practical handling compared to the largely conventional clamping jaws.
  • the cylinder liner has outer ribs offset from one another in sections, which at the same time ensure reliable support on the outer tube.
  • they are arranged axially parallel and in uniform ring arrangements so that their circumferential distance from the adjacent outer rib is two to five times, preferably about three times the width of the rib. Thanks to this dimensioning, there are large free cross sections in the contact area to the outer tube, which has an extremely advantageous effect on hammer operation.
  • the air distribution is further favored by the measure of claim 7 that the outer ribs of axially successive ring arrangements are in a gap with each other, whereby partial deflections in the circumferential direction are possible, while at the same time ensuring good contact with the inner tube inner wall.
  • the ring arrangements preferably have axial distances from one another of the order of magnitude of the rib length, so that to a certain extent compensation chambers are formed which contribute to the uniformity of the air flow.
  • control housing jacket is screwed directly to the top of the cap or to a lower part of an adapter, the threaded connection of which is parallel to the welding zone essentially over its axial length or extends beyond.
  • the adapter can have circumferential upper air ducts which open outward towards a sieve ring which is gripped by a filter ring resting on a shoulder of the adapter.
  • This can according to claim 11 on the circumference upward, in particular evenly distributed bores, nozzles or the like. have, which open obliquely or curved in an upper outer region where the filter ring tapers, preferably conically protruding is. In this way, a blow ring is created which generates a suction in the manner of a jet pump through air deflection. As a result, the cuttings are quickly moved up and out.
  • Claim 16 provides as a variant that the shaft has a control slide with passages and an annular surface below, which cooperates with a collar in the upper part of the adapter in an air-controlling manner, that a central passage in the sliding piece is connected to the flow with essentially axially parallel upper air ducts of the upper part of the adapter and that at least some of the passages communicate with the upper air ducts in an upper position of the shaft.
  • the air control formed in this way is as simple as it is effective. With little effort, flow conditions can be established that both Intermittent as well as continuous operation of the rotary hammer make a significant contribution to economic efficiency.
  • a valve seat for a check valve arranged on the control housing is present in the adapter, which can be held together with the associated valve spring on a base which has channels leading from the passage to a control housing chamber.
  • This structure is as simple as it is stable.
  • the valve holder through the base which connects directly to the lower part of the adapter, has proven its worth.
  • the further passages, channels, recesses etc. serve to supply air to the lower part of the hammer drill.
  • the tubular body has radial bores which are connected to one another and to control housing radial bores by a puncture or annular space and which open into an annular chamber between the outer tube and the cylinder liner.
  • the number, size and arrangement of these radial bores and the puncture assigned to them ensure perfect air flow for loading the piston.
  • the annular chamber between the outer tube and the cylinder liner is very advantageous, the free cross-section according to claim 19 being at least as large as the narrowest under the central bores in the passage components of the hammer drill. This dimensioning ensures good air passage with at least substantially uniform flow resistance.
  • the cylinder liner and the central tube have transverse or radial bores which are assigned to one another and can be released or closed by movement of the piston.
  • Important improvements to the hammer drill operation can be achieved according to claim 21 in that channels, grooves, axial bores or the like, close to the circumference, of recesses, annular grooves or the like, which are delimited by control edges.
  • the piston which open on one of its end faces. It is of great advantage that the required passages can be manufactured very precisely in a relatively simple manner, the number, size and arrangement of the passages in turn influencing the impact characteristics as required.
  • the amount of under air attacking on the underside of the piston can be controlled very appropriately so that the piston accelerates more upwards and less downwards is braked, whereby a high impact frequency is achieved and the impact force on the drill bit is increased.
  • a hammer drill 10 is shown with a connection or screw cap 11 and a central passage 12, furthermore a threaded connection 13 with a subsequent sealing ring 14 to a screw sleeve 16 inside a sleeve 15, which guides a shaft 20.
  • the head 19 is screwed to the sleeve 16, a central passage 17 being designed as a hexagon for inserting a screwing tool.
  • the shaft 20 carries spline-like ribs 21, which cooperate in a form-fitting manner with an opposite profile (counter ribs 31) in the upper part of a sliding piece 30.
  • a central passage 22 leads to the lower end 23 of the shaft 20, where it has a collar 26 and a sliding opening 27 on the inside.
  • a sliding guide 25 at the lower end 24 of the sleeve 15 guides a neck 35 of the sliding piece 30. This as well as the sleeve 15 and the screw cap 11 are provided with outer grooves R for attaching a screwing tool.
  • the lower end 24 of the sleeve 15 is opposite a shoulder 34 of the sliding piece 30, which also has an inner stop 36 which faces the collar 26 of the shaft 20.
  • a transition space 32 connects to the upper part 41 of an adapter 40, with a flow connection to its central passage 42 and to the outside air channels 43.
  • an upwardly projecting connecting piece 44 is formed on the upper part 41.
  • a blow ring 50 sits on a shoulder 46, the structure of which can be seen in detail from FIGS. 5a to 5d.
  • the sleeve 15 encloses an annular space in which an annular distributor 103 with channels 104 for permanent blowing air can be located (FIG. 3).
  • the passage 42 is flared until it merges into a chamber 47, the upper limit of which is designed as a valve seat 49. While the upper part 41 is screwed to the sliding piece 30 by a threaded connection 38, a threaded connection 48 on the lower part 45 serves for connection to an outer tube 55 which, like the adapter 40, has outer grooves R.
  • the outer tube 55 is welded on its upper part 56 in a welding zone S to a control housing jacket 60, specifically over an axial region of length l, which corresponds approximately to that of the thread 38.
  • a base 54 connects directly to the lower part 45 of the adapter 40 and serves as a holder for a check valve 59 with valve spring 58 and has channels 63 which open into a chamber 62 of the central tube 80.
  • the control housing casing 60 has radial bores 64 which can be offset from one another in the axial and circumferential directions. They open into a recess or annular space 65, which is connected in terms of flow via radial bores 67 to an annular chamber 68 which is located between the unit of outer tube 55 and cylinder liner 70 welded at the upper end. This ends at a shoulder 57 in the outer tube 55. It has upper radial bores 71 and middle radial bores 72.
  • a tubular body 61 which merges into the central tube 80, which has transverse bores 81 in the upper region and radial bores 83 in the lower region.
  • the central tube 80 Immediately above the lower end 84 of the central tube 80, it generally has a section 107 of reduced outer diameter (FIGS. 8a, 8b, 8c), but a uniformly shaped central tube 80 is also possible (FIG. 1b).
  • a piston 75 slides on it, which is also guided in the cylinder liner 70. It has recesses or annular grooves 76, 76 'and axial bores 78, 78' close to the circumference.
  • Its top surface 74 faces the bottom surface 69 of the tubular body 61.
  • the bottom surface 79 of the piston 75 periodically strikes the opposing impact surface 89 of a drill bit 90 during operation.
  • the drill bit 90 has a shaft 87 with a shoulder 88 which is supported on a retaining ring 86.
  • a buffer sleeve 85 is used to guide the upper part of the shaft 87.
  • a passage 92 is designed towards the impact surface 89 as a sliding bore 91 which cooperates with the lower central tube end 84 in an air-controlling manner, which - as mentioned - is preferably offset in diameter.
  • the drill bit 90 also has a retaining cap 93 with outer grooves R.
  • the base of the drill bit 90 is provided in the usual way with passages and pins (not designated) or hard metal inserts.
  • the lower part of the hammer drill 10 is shown in Fig. 1 in the blow-out position, i.e. with the hammer raised in the borehole B and therefore the drill bit 90 hanging without basic contact.
  • the collar 26 of the lower shaft end 23 bears against the stop 36 of the sliding piece 30 and has thus released the pin 44 of the adapter 40.
  • the air flow supplied through the central bores 12, 22 of the cap 11 and shaft 20 divides, so that a partial amount of air passes through the passage 42 in the adapter 40 and loads the check valve 59 downwards, i.e.
  • the hammer drill 10 In the blow-out position of FIG. 1, the hammer drill 10 is lifted off the bottom of the borehole, so that the drill bit 90 hangs on the retaining ring 86 with the shoulder 88 under the air pressure present and the piston 75 rests on the buffer sleeve 85. As a result, its top surface 74 exposes the radial bores 71 of the cylinder liner 70.
  • the compressed air therefore flows through the channels 63 into the chamber 62 of the central tube 80 and via the bores 64/65/67 into the annular space 68, further along the outer tube 55 to the radial bores 71 and into the channels or axial bores 78, but also through the transverse bores 81 and through the central bore 82 of the control or central tube 80 and the passage 92 in the shaft 87 of the drill bit 90, so that the bottom of the borehole is blown free underneath.
  • the lower shaft end 23 surrounds the pin 44 of the adapter 40 in the upper part of the hammer drill 10, and the collar 26 closes the upper air channels 43.
  • the compressed air supplied flows through the central bores or passages as a whole 12, 22, 42/47, 62, 82, 92 of components 11, 20, 30, 40, 61, 80, 87/90; as a result, the drill bit 90 of the hammer drill 10 processes the bottom of the borehole.
  • partial air quantities can be passed into the blow ring 50 by appropriately measuring or adjusting the annular gap between the collar 26 of the shaft 20 acting as a control slide and the pin 44 of the adapter 40.
  • the lower part of the hammer drill 10 is in its working position (FIG. 2b on the left), in which the drill bit 90 is pressed into the bottom of the borehole and thus the piston 75 is raised. Its head surface 74 is above the thus closed radial bores 71, and the head of the drill bit shank 87 surrounds the lower end 84 of the central tube 80.
  • Under air passes through the channels or axial bores 78 from the lower one Recess 76 of the piston 75. It is moved upwards until the supply of under air ceases as soon as the lower control edge 77 has passed over the radial bores 72 of the cylinder liner 70 (on the right in FIG. 2b). The air above the piston 75 is pushed out through the transverse bores 81 of the central tube 80 during the upward movement.
  • Fig. 3 shows the upper part of a design of the hammer drill 10, which is simplified by omitting the shaft 20 and sliding piece 30.
  • the sleeve 15 attached to the cap 11 is screwed directly to the adapter 40 by the threaded connection 38.
  • the compressed air supplied in this exemplary embodiment via the ring distributor 103 and its channels 104 flows in continuous blow mode via the passages 12, 42 into the lower part of the hammer drill (not shown here), the blowing again taking place through the upper air channels 43 and the blow ring 50.
  • the dimensioning and number of channels or bores determines the ratio of the partial air quantities.
  • the lower end 23 of the shaft 20 forms a control slide with e.g. two ring surfaces 29, 29 'arranged one above the other at a predetermined distance and a number of passages 28, 28', 28 '' located next to them.
  • the upper annular surface 29 ' closes the entrance of the passage 42 in the adapter 40. The entire air flow therefore passes through the passages 12, 22, 28' / 28, 42 of the components 11, 20/23, 40 in the screwed lower part of the rotary hammer 10 (not shown here).
  • the air flow introduced via the passage 22 is divided. Then the upper air flows partly through the passages 28 ', 43, 53 upwards into the open and a partial flow goes down through the bottom passage 28 and through a narrow annular space which is present between the annular surface 29 and the collar 37 the lower part of the hammer drill.
  • the partial air volumes can be adjusted as required by suitable dimensioning of the ducts or bores and the annular spaces.
  • Fig. 6 shows a further version of a hammer drill 10 with valve control and with adjustable under air. Components of the same type are identified with the same reference numbers as before.
  • a central tube 80 is also provided, but a ribbed cylinder liner 70 and a control valve 97 in a control housing jacket 60 which is axially welded to the outer tube 55. If the hammer 10 is not pressed against the bottom of the borehole, the lower edge 79 of the piston 75 lies on top of it Buffer sleeve 85 on. However, as soon as the hammer 10 is pressed on, the drill bit 90 lifts the piston 75.
  • valve 97 (of the flapper valve type) in a neutral position; however, other control valves are also readily usable. If the valve plate mounted on a central support, a kind of cutting edge 98, of the control housing 96 tilts to the right, the left side opens and the air can enter the chamber 62 of the central tube 80 and through holes (not shown) which are provided in the control housing 96 Flow through holes 99 in the space between the upper edge 74 of the piston 75 and the lower edge 69 of the control housing casing 60. When the piston 75 moves down, the space above the piston relaxes as soon as its top edge 74 hits the The upper edge of the outlet bores 81 overflows in the central tube 80.
  • the valve plate tilts to the left; it closes the blow air bores and opens the return stroke bores (not shown) in the control housing 96 on the right.The latter open into a collecting bore 100. From there, the air enters a puncture or annular space 65 and through radial bores 67 into the annular chamber 68, which is between the cylinder liner 70 and the outer tube 55 is formed. Finally, the air flows through the bores 72 of the cylinder liner 70 into the recess 76 of the piston 75, so that a new work cycle begins.
  • the control of the hammer drill according to the invention via the central tube 80 allows a high number of strokes regardless of the shaft length of the piston 75, namely because of the large-area attack of the full amount of under air on the piston underside with a correspondingly rapid upward acceleration.
  • This is in positive contrast to conventional rotary hammers, which only have a relatively narrow annular space available for the sub-air - either with a piston without a bore or one with a bore but without a central tube - and strive for high individual impact force, which is associated with a lower working frequency .
  • the under air can be controlled so that the piston 75 e.g. closes the under-air inlet 72 after a third of its return stroke.
  • a variant of this is a massive piston design (not shown) without axial bores or annular grooves, the under-air inlet 72 being pulled down so far that the air flowing in when the drill bit 90 is pressed in engages under the piston 75.
  • the invention is not limited to the described embodiments, but can be modified in many ways.
  • some grooves on the outside of the thread 38 can be made up to the height of the blow ring 50.
  • 7 shows a modified cylinder liner 70 which is provided with a multiplicity of outer ribs 101. These are arranged in ring arrangements 102 at axial distances p from one another in such a way that, with good support on the outer tube inner wall, a large through-flow volume is ensured.
  • the individual ring arrangements 102 are preferably set to one another with a gap, that is to say offset to one another in the circumferential direction, preferably by half the circumferential distance w. This is a multiple of the rib width n, in particular two to five times.
  • the axial distance p can correspond approximately to the rib length m, but can also be shorter, so that the ring arrangements 102 follow one another more closely.
  • FIG. 6a shows the central part of a rotary hammer designed for intermittent operation.
  • the piston 75 rests on the buffer sleeve 85, closes the under-air inlet 72 and has cleared shut-off and blow-out holes 106 at the top .
  • FIGS. 8b and 8c - analogously to FIGS. 4 and 6 - show the central part of a continuously striking rotary hammer, with the drill bit 90 still sagging in FIG. 8b, so that the elongated and thickened lower end 84 of the central tube 80 the sliding bore 91 of the Shaft 87 closes.
  • the top of the rotary hammer (Fig. 4) delivers a reduced amount of air. It is expediently metered in such a way that the piston 75, when moving downwards, itself generates a buffering in the closed space 94, which prevents the piston 75 from touching the buffer sleeve 85 and the drill bit 90.
  • the incoming under air then drives the piston 75 upward (FIG. 8c); as soon as it closes the outlet 81 in the buffer space 95, the oscillating piston movement occurs.
  • a pneumatically driven deep hole hammer generally has an outer tube 55, a control housing jacket 60 together with a check valve 59 and a central tube 80 having radial passages 81, 83 on which a percussion piston 75 slides.
  • the head of an axially displaceable The drill bit 90 can be slid onto the lower, preferably stepped central tube end 84.
  • a possibly ripped cylinder liner 70 guiding the piston 75 and the control housing jacket 60 are circumferentially welded to the outer tube 55 over an axial region (welding zone S, length l).
  • Above the control housing there is an adapter 40 which has upper air channels 42 and which carries a blow ring 50 with upward-directed nozzles 53.
  • a drive-transmitting sleeve 15 is connected to the adapter 40 directly or via a sliding piece 30 with a shaft 20 guided therein.
  • the lower end 23 thereof can form a control slide relative to the adapter upper part 41, from which passages 42, 47 lead to a control housing chamber 62 with channels 63.

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  • 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)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
EP94119216A 1993-12-15 1994-12-06 Marteau à forage Expired - Lifetime EP0658681B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9319223U 1993-12-15
DE9319223U DE9319223U1 (de) 1993-12-15 1993-12-15 Bohrhammer

Publications (3)

Publication Number Publication Date
EP0658681A2 true EP0658681A2 (fr) 1995-06-21
EP0658681A3 EP0658681A3 (fr) 1997-01-02
EP0658681B1 EP0658681B1 (fr) 2000-03-22

Family

ID=6902000

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94119216A Expired - Lifetime EP0658681B1 (fr) 1993-12-15 1994-12-06 Marteau à forage

Country Status (9)

Country Link
US (1) US5564510A (fr)
EP (1) EP0658681B1 (fr)
AT (1) ATE191055T1 (fr)
AU (1) AU677874B2 (fr)
CA (1) CA2138086A1 (fr)
CZ (1) CZ285685B6 (fr)
DE (2) DE9319223U1 (fr)
ES (1) ES2147212T3 (fr)
ZA (1) ZA949802B (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0933169A2 (fr) * 1998-02-03 1999-08-04 Krupp Berco Bautechnik GmbH Dispositif de percussion actionné par un fluide
DE102005015886A1 (de) * 2005-04-06 2006-10-26 Hans-Philipp Walter Bohrhammer
CN102482917A (zh) * 2009-08-24 2012-05-30 Tracto技术有限责任两合公司 冲击钻设备
CN104278948A (zh) * 2014-09-28 2015-01-14 扬州天业石油机械有限公司 一种螺杆钻具传动轴总成

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US5680904A (en) * 1995-11-30 1997-10-28 Patterson; William N. In-the-hole percussion rock drill
US5937956A (en) * 1995-12-08 1999-08-17 Tracto-Technik Paul Schmidt Spezialmaschinen Ram boring machine
DE29618066U1 (de) * 1996-10-18 1996-12-19 Walter, Hans-Philipp, 74251 Lehrensteinsfeld Bohrhammer
CA2260612C (fr) 1999-02-03 2005-04-26 Dresser Industries, Inc. Marteau pneumatique a forage dirige
US6499544B1 (en) * 2000-11-15 2002-12-31 Sandvik Ab Percussive down-the-hole hammer for rock drilling, and a one-way valve used therein
US6986394B2 (en) * 2004-04-29 2006-01-17 Varco I/P, Inc. Reciprocable impact hammer
US6883618B1 (en) * 2004-06-15 2005-04-26 Numa Tool Company Variable timing for front chamber of pneumatic hammer
WO2006062309A1 (fr) * 2004-12-07 2006-06-15 Byung-Duk Lim Marteau perforateur et procede d'entrainement associe
US9068399B2 (en) 2006-10-20 2015-06-30 Drillroc Pneumatic Pty Ltd Down-the-hole hammer drill
EA017936B1 (ru) * 2006-10-20 2013-04-30 Дриллрок Пнеуматик Пти Лтд. Скважинный бурильный молоток
CN107829689B (zh) * 2017-11-21 2023-10-31 中南大学 多向喷射气动潜孔锤钻头
PE20201129A1 (es) * 2017-12-13 2020-10-26 Jaime Andres Aros Sistema de flujo de fluido presurizado con multiples camaras de trabajo para un martillo de fondo y un martillo de fondo de circulacion normal con dicho sistema
SE543090C2 (en) * 2019-01-15 2020-10-06 Pml Energy Ab A rock drilling system for geothermal drilling, a method and use of such a rock drilling system
TWI719396B (zh) * 2019-01-25 2021-02-21 銳力工業股份有限公司 氣動錘之閥座

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EP0154778A1 (fr) * 1984-02-07 1985-09-18 Hans-Philipp Walter Perforateur à percussion
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DE9202336U1 (de) * 1992-02-22 1992-05-07 Walter, Hans-Philipp, 7102 Lehrensteinsfeld Bohrhammer-Gerät

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US4312412A (en) * 1979-08-06 1982-01-26 Dresser Industries, Inc. Fluid operated rock drill hammer
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US3225841A (en) * 1962-08-31 1965-12-28 Joy Mfg Co Drilling apparatus
US3924690A (en) * 1973-01-09 1975-12-09 Halifax Tool Co Ltd Percussion drill control means
US3964551A (en) * 1974-09-20 1976-06-22 Reed Tool Company Pneumatic impact drilling tool
US4280570A (en) * 1978-04-18 1981-07-28 Walter Hans Philipp Drill hammer
EP0154778A1 (fr) * 1984-02-07 1985-09-18 Hans-Philipp Walter Perforateur à percussion
US5090487A (en) * 1991-02-22 1992-02-25 Masse Roger F Drill head with integral impact hammers
DE9202336U1 (de) * 1992-02-22 1992-05-07 Walter, Hans-Philipp, 7102 Lehrensteinsfeld Bohrhammer-Gerät

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0933169A2 (fr) * 1998-02-03 1999-08-04 Krupp Berco Bautechnik GmbH Dispositif de percussion actionné par un fluide
EP0933169A3 (fr) * 1998-02-03 2000-11-15 Krupp Berco Bautechnik GmbH Dispositif de percussion actionné par un fluide
DE102005015886A1 (de) * 2005-04-06 2006-10-26 Hans-Philipp Walter Bohrhammer
DE102005015886B4 (de) * 2005-04-06 2008-06-19 Hans-Philipp Walter Bohrhammer
CN102482917A (zh) * 2009-08-24 2012-05-30 Tracto技术有限责任两合公司 冲击钻设备
US9016404B2 (en) 2009-08-24 2015-04-28 Tracto-Technik Gmbh & Co. Kg Ram boring device
CN104278948A (zh) * 2014-09-28 2015-01-14 扬州天业石油机械有限公司 一种螺杆钻具传动轴总成
CN104278948B (zh) * 2014-09-28 2016-07-06 扬州天业石油机械有限公司 一种螺杆钻具传动轴总成

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ATE191055T1 (de) 2000-04-15
AU8046794A (en) 1995-06-22
EP0658681B1 (fr) 2000-03-22
CZ316194A3 (en) 1995-07-12
CZ285685B6 (cs) 1999-10-13
ES2147212T3 (es) 2000-09-01
DE9319223U1 (de) 1994-02-24
US5564510A (en) 1996-10-15
ZA949802B (en) 1995-10-02
DE59409229D1 (de) 2000-04-27
EP0658681A3 (fr) 1997-01-02
AU677874B2 (en) 1997-05-08
CA2138086A1 (fr) 1995-06-16

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