EP0004946B1 - Marteau de forage, notamment marteau fond-de-trou - Google Patents

Marteau de forage, notamment marteau fond-de-trou Download PDF

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Publication number
EP0004946B1
EP0004946B1 EP79101125A EP79101125A EP0004946B1 EP 0004946 B1 EP0004946 B1 EP 0004946B1 EP 79101125 A EP79101125 A EP 79101125A EP 79101125 A EP79101125 A EP 79101125A EP 0004946 B1 EP0004946 B1 EP 0004946B1
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EP
European Patent Office
Prior art keywords
drill hammer
hammer according
slide tube
control means
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP79101125A
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German (de)
English (en)
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EP0004946A1 (fr
Inventor
Hans-Philipp Walter
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Individual
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Individual
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Publication date
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Publication of EP0004946A1 publication Critical patent/EP0004946A1/fr
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Expired 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, with an outer tube and through hole in an upper cap for connection to a compressed air source and optionally to a drill pipe, with the control device supported on the cap, control body and with the control device positively connected cylindrical slide tube which can be moved up and down along a drilled percussion piston in the outer tube, and with a radially divided lower retaining cap of disharmonious polygon inner profile, in which a likewise drilled-through polygon shaft of a drill bit provided with flushing bores is movably held up and down.
  • Such hammer drills are known from DE-A-26 09 376.
  • DE-A-23 62 724 and GB-A-1 419981 also describe deep hole drilling hammers, in which, however, the sliding tube itself is movably mounted up and down and protrudes into the head of the drill bit , which has considerable disadvantages.
  • the lower hammer parts experience wear relatively quickly, which can lead to canting of the drill bit with a risk of breakage for the end of the guide tube.
  • the serration of the drill bit shaft provided for rotary driving is deformed or jammed, at least when an eccentric position of the sliding tube causes a force transmission to the outer tube or from there.
  • an intermediate piston is arranged between the percussion piston and the drill bit head and is guided at least in part on the slide tube and that the lower part of the control device has or forms an insert, the surfaces of which in the slide tube are positively connected to it.
  • the hammer either runs in intermittent operation, the impact can be switched on and off, or overall continuously.
  • the impact of the impact piston is transferred to the drill bit by the intermediate piston, which has an important buffer function. It contributes significantly to the air flow and causes a vibration effect with continuous air strikes even when the percussion piston is intercepted by an air cushion with a deeply immersed intermediate piston or sagging drill bit and no longer strikes the intermediate piston. Cold forging deformation in idle mode is therefore excluded here as well as on the drill bit head. Due to the good guidance of the intermediate piston, in particular in a buffer sleeve which is inserted into the outer tube, a safe function with good control of the hammer operation is maintained for a long time, in contrast to embodiments according to US Pat. Nos. 2,661,928 and 2,851,251, where an upper and a lower piston can tilt very easily and the buffer effect caused by the invention is missing.
  • the casing body provided according to claims 4 and 5 and its outer groove profile allow the hammer to be opened much more easily than before in the event of malfunctions or chisel changes.
  • Conventional rotary hammers can sometimes not be loosened at all, while others in the casing are severely weakened and have predetermined breaking points.
  • the application of the necessarily heavy tool creates a high risk of accidents, since it slips and falls easily with conventional designs.
  • a closed tool can be used, which is temporarily fixed by one or more bolts on the circumference of the hammer, in particular the casing body.
  • the embodiment according to claim 6 creates a multi-channel inner tube control system that works extremely reliably with a simple and stable structure.
  • a four-channel system with intersecting pairs of opposite exhaust and return stroke channels is particularly favorable; this ensures that the air flows out very evenly and the piston cannot jam.
  • a particularly good coordination is achieved by the features of claims 7 and 8 between the buffering area and the lower opening to the return stroke channel.
  • the dimensioning can be such that the greatest performance is achieved with a half-sagging drill bit, while with increasing bit travel there is a gradual decrease in performance until pure buffer operation, which prevents the bit head and the stop parts from being smashed.
  • the buffer sleeve is provided with adapted ventilation grooves in order to transfer the impact energy to the maximum, whereby the buffer effect starts somewhat delayed, but the piston is not caught too early or too strongly.
  • An advantageous simplification further consists in the measures of claim 9, since - in contrast to the prior art - only minimal machining of the sliding tube is necessary.
  • Several, distributed over the length of the guide tube for each channel provides the embodiment according to claim 10, wherein an air extension takes place through the upper shut-off hole, which has a larger width than the lower shut-off hole leading into the return stroke channel, despite the intermediate piston located in the lower end position can. Therefore, the hammer can continue to run while the buffering effect persists, or the hammer is turned off and the air flows out.
  • the air which continues to flow intermittently or continuously, causes a good flushing on or around the drill bit, even while the percussion piston no longer comes into metallic contact with the intermediate piston due to the air spring formed.
  • the measure of claim 11 contributes to this, since the enlarged head of the intermediate piston exactly limits the buffer volume when entering an upper annular space of the buffer sleeve.
  • a check valve - if at all - was usually only arranged in the upper hammer part above the control unit, so that when the hammer was switched off, its lower part was fully exposed to the penetration of cuttings, dust, water, etc.
  • a threaded stopper provided according to claim 15 on the head of the lower control housing part can, if necessary, be designed as a nozzle which, with a predetermined cross-section, enables additional air passage if desired.
  • the control can be changed as required by replacing the threaded plug. It can be omitted if, for use as a hammer drill with water flushing, the entire control housing is penetrated by a central tube or bore through which water can be introduced.
  • the hammer drill 10 shown has an outer tube 12 and an upper cap 14, which is provided with a threaded connection 16 and wrench flats 18 and has a through hole 20.
  • a suitable connection can be attached to the rotary hammer 10 by simply changing the cap 14.
  • the cap 14 screws with a jacket body 22, which in turn is screwed to the outer tube 12 and comes into contact with the collar or shoulder 28 thereof.
  • a grooved profile 24 is provided on the outside of the jacket body 22, via which a closed key (not shown) can be pushed and fixed in the circumferential and axial directions by at least one socket pin.
  • the hammer drill 10 can also have a corresponding groove profile at other points, for example at its lower end.
  • the upper part 30 of a three-part control device is supported on the cap 14 in the jacket body 22 via buffer rings 26 and 27, which can be made of elastomers such as polyurethane.
  • the upper part 30 has a number of oblique channels 36 distributed over the circumference.
  • On its underside it has a valve seat 38 for a control body 40, which between a valve support 42 of the control device middle part 32 and the valve seat 38 of the upper part 30 in Movable axially back and forth and guided centrally in the central part 32.
  • the latter is provided with a number of oblique channels 44 distributed over the circumference and, following the control body 40, with a chamber 48.
  • outer and side channels 46 lead to the head of the lower part 34, at least one of which opens out at bores 52 which are machined into the head of the lower part 34 of the control device.
  • An axial section of the bores 52 is closed with a threaded plug 54 which, if necessary, can be replaced by a nozzle of a suitable diameter.
  • a number of passages 50 distributed over the circumference create a flow connection between the chamber 48 and an annular space 55 in the interior of the outer tube 12.
  • An insert 62 is integral with the control device lower part 34, on which a sliding tube 60 connected to it integrally is seated. To secure this attachment, a screw connection (not shown) may be present.
  • the lower part 34 or the insert 62 and the sliding tube 60 are penetrated by a cross section 58 with a precise fit just below a collar 35. This is dimensioned in length so that it fits into the inside width of a collar 56 of the casing body 22 and is thereby secured against movements in the direction of its axis.
  • the insert 62 has, as can be seen from FIGS. 2 and 3, partitions 64 which connect to one another in a star shape in cross-section and bear with surfaces 66 on the inside of the sliding tube 60. The length of the insert 62 can match that of the sliding tube 60 or, as drawn in FIGS. 1 b and 2, may be somewhat shorter.
  • an inwardly projecting collar 61 which is chamfered and serves as a valve seat for the valve body 59 of a check valve.
  • the body 59 is slidably supported on a pin 63 which extends the insert 62 coaxially and is supported against its end, to which nuts 63a can be screwed in a suitable manner, by means of a compression spring 65 which partially dips into the body 59.
  • the sliding tube 60 each has a preferably elongated outlet 69 (shown in broken lines in FIG. 1b) for two exhaust channels 67, which are formed by the four web walls 64 of the insert 62 together with two return stroke channels 68.
  • the arrangement is preferably such that the diametrically opposite exhaust ducts 67 have a larger cross section than the return stroke ducts 68; the ratio of the cross sections can be 3: 2, for example.
  • the sliding tube 60 At the lower end of the sliding tube 60, it has a lateral ventilation opening 74 for establishing a flow connection between each return stroke channel 68 and a compression space 76, which is provided between the outer tube 12 and the sliding tube 60 below a percussion piston 70.
  • a lateral ventilation opening 74 Above the ventilation openings 74, an upper idle or shut-off hole 71 leads to the exhaust ducts 67, while below the openings 74 a smaller lower shut-off hole 73 opens into a chamber 115, which is located in the sliding tube 60 at the lower end of the insert 62.
  • the percussion piston 70 is guided in the outer tube 12 and provided with circumferential grooves 72. Its lower end faces axially opposite the head 82 of an intermediate piston 80. Percussion piston 70 and intermediate piston 80 slide along tube 60.
  • the intermediate piston 80 is partially guided on the sliding tube 60 and in a buffer sleeve 78 which is inserted into the outer tube 12 from below and has adapted longitudinal grooves 79.
  • the intermediate piston 80 has two or more radial outlets 84; In the exemplary embodiment according to FIGS. 1 b, 5 and 6, there are three such radial outlets 84 which establish the flow connection to a lower annular space 88.
  • An upper annular space 86 connects to the compression space 76 in the buffer sleeve 78.
  • a retaining cap 90 which is formed in two parts, held together by pins 92 and screwed into the outer tube 12 from below, serves to fasten both the buffer sleeve 78 and a drill bit 94.
  • the holding cap 90 has a disharmonious polygonal profile, in particular of the PC4 type, as described in DE-A-26 09 376.
  • the drill bit 94 has a head 106 with an enlarged diameter and a shank 96 which - as can be seen in FIG. 4 - has a precisely adapted polygonal profile with slightly curved surfaces and strongly rounded edges.
  • axial grooves 98 which lead via an annular gap 100 to recesses 112, which are also in fluid communication with the space outside of the hammer drill 10 or the drill bit 94 when the latter is in contact with a collar 110 at the lower end of the holding cap 90 .
  • the chisel head 106 can move down to a stop 108 at which the polygon inner profile of the holding cap 90 ends at the top.
  • a through hole 102 of the drill bit 94 leads to the drill bit 104 and branches therein, as indicated by dashed lines in FIG. 1b.
  • the hammer drill 10 It is essential for the hammer drill 10 according to the invention that it enables a robust construction with high space utilization with simplified and improved control. Practical designs with outer tube diameters from 80 mm to 135 mm have achieved surprising drilling progress in operation with a pressure of 13 bar, even in unfavorable rock conditions. This contributes to the fact that the intermediate piston 80 guided in the buffer sleeve 78 is constantly on the drill bit head 106 and thus either releases the return air bore 74 or closes it (partially or completely). If the Head 82 of the intermediate piston 80 completely into the upper annular space 86, the compression space 76 located above prevents the impact piston 70 from striking through its air cushion.
  • the impact piston 70 springs back upwards, whereby - if the other requirements are met - drill bits 94 and intermediate piston 80 can also drive back.
  • the strokes of the percussion piston 70 which occur continuously with the hammer 10 running continuously, produce sequences of air blasts which, in addition to a vibration effect, bring about high gas accelerations and thereby substantially support the drilling work or enable intermittent operation with correspondingly dimensioned shut-off holes 71, 73.
  • the lower annular space 88 serves primarily for air distribution to the ventilation channels 98, 100, 112. This complete ventilation allows the drill bit head 106 to move down to the stop shoulder 108 of the retaining cap 90. Between this and the drill bit there is a practically wear-free polygon guide, which allows the transmission of torques over a wide range even with large axial forces.
  • the conventionally given risk of breakage for the lower end of the sliding tube is eliminated according to the invention in a simple and effective manner.
  • the sliding tube 60 is optimally protected by its connection to the insert 62 or the lower control housing part 34, especially since the drill bit 94 never comes into contact with the sliding tube 60.
  • the upper parts 30, 32 of the control device are greatly simplified, which not only greatly simplifies manufacture and assembly, but also increases functional reliability.
  • the available cross sections are used optimally.
  • effective assembly and disassembly aids are provided in the form of the key grooves 24 and key surfaces 18, which considerably shorten the set-up and downtimes compared to conventional rotary hammers.
  • the clear structure ultimately helps to facilitate and accelerate maintenance and repair work without the mechanical and wear resistance being impaired in any way. While the mode of operation largely corresponds to that of the deep hole hammer drill according to DE-A-26 09 376, the versatility of use and the cost-effectiveness of use are considerably increased.
  • a central tube 113 (shown in dashed lines in FIGS. 1b and 1b), which passes through the control device upper part 30 and middle part 32 and projects into the lower part 34, where a central bore 114 (indicated by dashed lines in FIG. 3) connects in the insert 62 , water can be introduced and the device can therefore also be used as a hammer drill with water flushing. It can be seen that no additional effort is required for this; the threaded plug 54 can be omitted or modified accordingly.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)

Claims (16)

1. Marteau de forage, en particulier, marteau de forage fond-de-trou, fonctionnant pneumati- quement et comportant un tube extérieur (12) et un trou de passage (20) pratiqué dans un chapeau supérieur (14) pour établir un raccordement avec une source d'air comprimé et éventuellement avec un train de tiges de forage, un dispositif de commande (30, 32, 34) prenant appui sur le chapeau (14), un corps de commande (40) et un tube cylindrique de glissement (60) assemblé solidairement au dispositif de commande et le long duquel un piston frappeur perforé (70) peut effectuer un mouvement ascendant et descendant dans le tube extérieur (12), de même qu'un chapeau de retenue inférieur (90) subdivisé radialement, ayant un profil intérieur polygonal disharmoni- que dans lequel une tige polygonale également perforée (96) d'un trépan (94) comportant des trous d'écurage est maintenue de façon à pouvoir effectuer également des mouvements ascendants et descendants, caractérisé en ce que, entre le piston frappeur (70) et la tête (106) du trépan, est installé un piston intermédiaire (80) guidé au moins partiellement sur le tube de glissement (60), tandis que la partie inférieure (34) du dispositif de commande comporte ou forme une pièce rapportée (62) dont les surfaces (66) venant s'appliquer sur le tube de glissement (60) sont assemblées solidairement à ce dernier.
2. Marteau de forage suivant la revendication 1, caractérisé en ce que le tube de glissement (60) et la partie inférieure (34) du dispositif de commande sont, en outre, assemblés l'un à l'autre par vissage.
3. Marteau de forage suivant la revendication 1 ou 2, caractérisé en ce qu'une broche (58) passe transversalement à travers l'extrémité supérieure de la pièce rapportée (62) formant une seule pièce avec la partie correspondante (34) du dispositif de commande, ainsi qu'à travers le tube de glissement (60) lui-même reposant sur cette pièce rapportée.
4. Marteau de forage suivant la revendication 3, caractérisé en ce que la partie inférieure (34) du dispositif de commande prend appui, par une bague tampon (27), sur un collet (56) dirigé vers l'intérieur et faisant partie d'un corps périphérique (22) vissé entre le tube extérieur (12) et le chapeau supérieur (14), tandis que la broche (58) s'étend radialement, à ses deux extrémités, jusqu'au collet (56).
5. Marteau de forage suivant la revendication 4, caractérisé en ce que le corps périphérique (22) comporte, extérieurement, un profil à gorges (24) sur lequel vient s'engager un outil à visser d'un contre-profil correspondant.
6. Marteau de forage suivant une des revendication précédentes, caractérisé en ce que les surfaces (66) venant s'appliquer contre le tube de glissement (60) et faisant partie de la pièce rapportée (62) de la partie inférieure (34) du dispositif de commande forment la terminaison radiale de plusieurs cloisons transversales (64) juxtaposées en une section transversale en étoile et entre lesquelles sont ménagés des canaux de circulation d'air (67, 68) s'étendant axialement.
7. Marteau de forage suivant au moins une des revendications précédentes, caractérisé en ce que le piston intermediaire (80) est guidé dans une douille tampon (78) introduite dans le tube extérieur (12) et comportant des rainures longitudinales (79).
8. Marteau de forage suivant la revendication 6 ou 7, caractérisé en ce que, à l'extrémité inférieure du canal (68) prévu pour la course de retour dans le tube de glissement (60), est pratiquée au moins une ouverture d'évacuation d'air (74) dont les dimensions sont calculées de telle sorte qu'il n'y ait aucune communication pour l'écoulement vers le bas lorsque le piston intermédiaire (80) occupe sa position inférieure de fin de course.
9. Marteau de forage au moins suivant la revendication 8, caractérisé en ce que, outre l'ouverture d'évacuation d'air (74) du canal (68) prévu pour la course de retour, le tube de glissement (60) comporte, pour chaque canal d'échappement (67), une sortie d'évacuation (69) réalisée, en particulier, sous forme d'un trou oblong ou d'une fente d'une longueur déterminée en fonction de la course du piston frappeur (70).
10. Marteau de forage suivant les revendications 8 et 9, caractérisé en ce que, entre la sortie d'échappement/évacuation (69) et l'ouverture d'évacuation d'air (74), le tube de glissement (60) comporte un passage supérieur d'arrêt (71) débouchant dans les canaux d'échappement (67) tandis que, en dessous de cette ouverture d'évacuation d'air (74), ce tube de glissement (60) comporte un passage inférieur d'arrêt (73) débouchant dans les cannaux (68) de la course de retour, ce passage inférieur d'arrêt étant plus petit que le passage supérieur (71).
11. Marteau de forage suivant au moins une des revendications 1 à 10, caractérisé en ce que le piston intermédiaire (80) comporte une tête (82) dont le diamètre augmente vers l'extérieur, tandis que son corps cylindrique plus étroit comporte, à son extrémité inférieure, des sorties d'évacuation radiales (84).
12. Marteau de forage suivant au moins une des revendications 1 à 11, caractérisé en ce que le trépan (94) comporte des canaux axiaux (98) à profil polygonal, ces canaux reliant un compartiment annulaire (88) formé à l'extrémité inférieure du piston intermédiaire (80) à un espace annulaire (100) dans lequel il y a une communication continue pour l'écoulement vers l'extérieur grâce à des évidements (112) ménagés à l'extrémité inférieure du chapeau de retenue (90) face à un collet inférieur (110) du trépan (94).
13. Marteau de forage suivant la revendication 12, caractérisé en ce que les canaux axiaux (98) sont prévus aux angles ou aux bords arrondis du profil polygonal de la tige (96) du trépan.
14. Marteau de forage suivant au moins une des revendications 1 à 13, caractérisé en ce que, à l'extrémité du tube de glissement (60), est prévu un collet (61) formant une soupape de retenue conjointement avec un corps de soupape (59) pouvant se déplacer coaxialement par rapport à ce tube de glissement (60).
15. Marteau de forage suivant au moins une des revendications 1 à 14, caractérisé en ce que, à la tête de la partie inférieure (34) du dispositif de commande, sont pratiqués des passages de guidage d'air (52) dont la partie axiale est fermée entièrement ou partiellement, côté frontal, par un bouchon fileté (54).
16. Marteau de forage suivant au moins une des revendications 1 à 15, caractérisé en ce qu'un tube ou un passage central (113, 114) traverse le dispositif de commande (30, 32, 34).
EP79101125A 1978-04-18 1979-04-12 Marteau de forage, notamment marteau fond-de-trou Expired EP0004946B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2816737A DE2816737C3 (de) 1978-04-18 1978-04-18 Bohrhammer, Insbesondere Tieflochhammer
DE2816737 1978-04-18

Publications (2)

Publication Number Publication Date
EP0004946A1 EP0004946A1 (fr) 1979-10-31
EP0004946B1 true EP0004946B1 (fr) 1981-10-14

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EP79101125A Expired EP0004946B1 (fr) 1978-04-18 1979-04-12 Marteau de forage, notamment marteau fond-de-trou

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US (1) US4280570A (fr)
EP (1) EP0004946B1 (fr)
AT (1) AT363427B (fr)
DE (1) DE2816737C3 (fr)

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US4030554A (en) * 1975-07-07 1977-06-21 Bakerdrill, Inc. Bore hole airhammer and anvil bit
DE2551303C3 (de) * 1975-11-14 1981-04-02 Institut gornogo dela Sibirskogo otdelenija Akademii Nauk SSSR, Novosibirsk Druckluftbetriebene Tiefloch-Schlagbohrmaschine
DE2609376C3 (de) * 1976-03-06 1978-09-07 H.P. Walter Gmbh + Co Drucklufttechnik Kg, 3570 Stadt Allendorf Tieflochbohrhammer
GB1585086A (en) * 1976-07-28 1981-02-25 Compair Constr Mining Ltd Down-the-hole percussion drills
US4163478A (en) * 1978-09-15 1979-08-07 Adcock Gerald L Self aligning impact rock drilling tool

Also Published As

Publication number Publication date
DE2816737B2 (de) 1980-07-10
AT363427B (de) 1981-08-10
US4280570A (en) 1981-07-28
DE2816737A1 (de) 1979-10-25
ATA277979A (de) 1981-01-15
EP0004946A1 (fr) 1979-10-31
DE2816737C3 (de) 1981-03-19

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