US20060000646A1 - Down-the hole hammer - Google Patents
Down-the hole hammer Download PDFInfo
- Publication number
- US20060000646A1 US20060000646A1 US10/529,614 US52961405A US2006000646A1 US 20060000646 A1 US20060000646 A1 US 20060000646A1 US 52961405 A US52961405 A US 52961405A US 2006000646 A1 US2006000646 A1 US 2006000646A1
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- Prior art keywords
- inner cylinder
- distributor
- wear sleeve
- air
- tool
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- Abandoned
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- 230000000295 complement effect Effects 0.000 claims abstract description 10
- 238000009527 percussion Methods 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 6
- 239000000523 sample Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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 “down-the-hole” hammers or fluid-operated percussion drill tools operated by a supply of compressed air.
- Some designs of conventional down-the-hole hammers and fluid-operated percussion drill tools comprise an external cylinder or outer wear sleeve, within which is mounted an inner cylinder which in turn engages with a backhead assembly.
- a sliding reciprocating piston co-operates with the inner cylinder and backhead assembly, which when air pressure is supplied through the backhead assembly, acts with a percussive effect on a drill bit retained within a chuck on the outer wear sleeve.
- the inner cylinder is effectively suspended within the outer wear sleeve by means of a compressible retaining ring, such as a circlip, which has to be slid up the inner cylinder so as to seat against a shoulder or lip at one end thereof, being compressed when the inner cylinder is dropped down within the outer wear sleeve, and then expanding outwardly into a groove or shoulder formed on the inner diameter of the outer wear sleeve with a snap action.
- a compressible retaining ring such as a circlip
- EP1004744A discloses a segmented ring mounting for retaining the inner cylinder within the outer wear sleeve in a fluid-operated percussion drill tool, such as a down-the-hole hammer.
- the retaining ring seats the smaller diameter inner cylinder within the larger diameter outer wear sleeve.
- the outer wear sleeve is formed with a groove cut on its inside diameter, or a shoulder for seating the retaining ring against a lip of the inner cylinder.
- the ring is capable of radial compression and expansion so as to expand radially into the seating groove or shoulder for retaining the components one within the other in use.
- the retaining ring comprises at least three segments, which when touching end to end form a complete circle, and an expansible O-ring, for holding the segments together but allowing the segments to expand radially and move apart by sufficient amount so as to seat the segments in the groove or against the shoulder.
- the inner cylinder of EP1004744A is integral to the porting of the hammer.
- the piston runs on the inner diameter of the inner cylinder and also on the inner diameter of the outer wear sleeve. It is essential that the fit between the outer diameter of the inner cylinder and the bore of the outer wear sleeve be a tight/close fit to ensure optimum alignment of the two bores. This means that the clearance and hence the efficiency of the hammer is optimised because the operation of the hammer relies on a partial seal between the piston and the top and bottom chambers, i.e. the tighter the clearance the greater the energy (within reason).
- the inner cylinder is mounted within the outer wear sleeve by means of a compressible retaining ring, such as a circlip, which is expanded outwardly to seat into the groove or shoulder formed on the inner diameter of the outer wear sleeve.
- a compressible retaining ring such as a circlip
- the outer wear sleeve of down-the-hole hammers is subject to very strong abrasive forces when in use causing significant wear of, and removal of metal from, the outer sleeve. This weakens the outer wear sleeve to the point where it has to be replaced.
- the prior art hammers described the provision of circumferential seating grooves for circlips, seating rings and the like, in the inner face of the wear sleeve reduce the wear thickness of the outer sleeve. This means that the outer wear sleeve has to be replaced more quickly than would be the case if the wear sleeve contained no more grooves.
- the invention provides a fluid-operated percussion drill tool, in particular a down-the-hole hammer, comprising an external cylindrical outer wear sleeve, an inner cylinder mounted co-axially within the outer wear sleeve, a sliding piston mounted for reciprocating movement within the inner cylinder and the outer wear sleeve, to strike a hammer bit mounted at the lower end of the outer wear sleeve, characterised in that the inner cylinder is formed with an inwardly-directed abutment which in the assembled tool is clamped between a complementary engagement means and a locking means such that the inner cylinder is rigidly mounted and held in the drill tool assembly relative to the outer wear sleeve.
- an elongate cylindrical air distributor is positioned within the hammer assembly, and a lower end of the air distributor is positioned substantially concentrically within the upper end of the inner cylinder and an abutment on the air distributor engages the underside of a complementary abutment on the inner cylinder.
- the top end of the outer wear sleeve is screw-threadably engaged with the lower end of an annular air distributor mount, and the top end of the inner cylinder abuts the lower end of the distributor mount such that the inner cylinder is rigidly mounted in the drill assembly relative to the outer wear sleeve when a top locking member is threadably mounted onto the air distributor.
- the air distributor is threadably engaged at its upper end with a top locking member which abuts the top of the air distributor mount.
- the inner cylinder is rigidly held relative to the outer wear sleeve.
- FIG. 1 is a sectional side elevation of a first embodiment of a down-the-hole hammer of the invention, showing the piston in the strike position;
- FIG. 2 is a sectional side elevation of the down-the-hole hammer of FIG. 1 , showing the piston in the top of stroke position;
- FIG. 3 is a sectional side elevation of the top part of the hammer of FIG. 1 to a larger scale
- FIG. 4 is a sectional side elevation, to an enlarged scale, showing a detail of FIG. 3 ;
- FIG. 5 is a cross-sectional plan view of the down-the-hole hammer of FIG. 1 , on the line C-C of FIG. 3 ;
- FIG. 6 is a cross-sectional plan view of the down-the-hole hammer of FIG. 1 , on the line B-B of FIG. 3 ;
- FIG. 7 is a cross-sectional plan view of the down-the-hole hammer of FIG. 1 , on the line D-D of FIG. 3 ;
- FIG. 8 is a cross-sectional plan view of the down-the-hole hammer of FIG. 1 , on the line E-E of FIG. 3 ;
- FIG. 9 is a cross-sectional plan view of the down-the-hole hammer of FIG. 1 , on the line F-F of FIG. 3 ;
- FIG. 10 is a sectional side elevation of a second embodiment of a down-the hole hammer of the invention, showing the piston in the strike position;
- FIG. 11 is sectional side elevation of the top part of the hammer of FIG. 10 to a larger scale.
- a first embodiment of a down-the-hole hammer of the invention comprises an external cylindrical outer wear sleeve 10 .
- An inner cylinder 9 is mounted co-axially within the outer wear sleeve 10 .
- a sliding piston 11 is mounted for reciprocating movement within the inner cylinder 9 and the outer wear sleeve 10 , to strike a hammer bit 36 mounted for sliding movement in a chuck 41 located at the forward end of the outer wear sleeve 10 , in well known manner.
- a top locking member 1 is screw-threadably mounted on an annular air distributor 3 .
- Air distributor 3 is fitted concentrically through inner cylinder 9 and a distributor mount 2 and when assembled an outwardly-directed annular flange 38 on the lower end of air distributor 3 abuts the underside of an inwardly-directed annular shoulder 15 in inner cylinder 9 .
- the top end 14 of inner cylinder 9 above the shoulder 15 , in turn abuts the lower end of the distributor mount 2 .
- the distributor mount 2 is substantially cylindrical and open at both ends.
- the mount 2 has an upper part 2 a having an outer diameter which is the same as the outer diameter of the outer wear sleeve 10 , such that when the mount 2 is engaged with the wear sleeve (as described below) the outer cylindrical wall of the mount 2 is flush with the outer wall of the wear sleeve 10 .
- the mount 2 has a lower part 2 b of reduced diameter which fits within the top end of the wear sleeve 10 , and is screw-threadably engaged with the inner wall of the wear sleeve 10 , by means of screw threads 39 (see also FIG. 8 ).
- the transition between the upper and lower parts of the distributor mount 2 is defined by a downwardly facing annular shoulder 23 , against which the top annular rim of the wear sleeve 10 abuts, and is locked in place when the mount 2 is fully engaged with the wear sleeve 10 .
- the bottom of the top locking member I has a flat annular rim 12 which engages a complementary flat shoulder 13 on the top end of the distributor mount 2 .
- the inner cylinder 9 is thus effectively locked between a shoulder 13 (between top locking member 1 and mount 2 ) and shoulder 15 (between air distributor 3 and inner cylinder 9 ). Shoulder 15 may be tapered if required.
- the inner cylinder 9 at its upper end, has an inwardly extending annular shoulder or flange 14 which is rigidly held between the shoulder 15 and the lower end of the distributor mount 2 , when the distributor mount 2 has been screwed into position in the top end of the wear sleeve 10 , and the top locking member 1 has been screwed on to the air distributor.
- the top-locking member 1 is screwed down, by screw-threadably engaging it with the top of the air-distributor 3 , this acts to pull the air-distributor 3 upwardly against the shoulder 15 , and in turn pulls the inner cylinder 9 upwardly against the shoulder 14 .
- the whole assembly then locks down on shoulder 13 .
- air distributor 3 When screw engaging top locking member 1 to air distributor 3 , air distributor 3 is prevented from turning by means of dowels 8 positioned between mount 2 and air distributor 3 .
- An annular circlip 7 (see FIGS. 3 and 4 ) is positioned in a chamber 24 formed between locking member 1 and mount 2 and a groove 25 machined on air distributor 3 . The circlip 7 serves to retain air distributor 3 loosely in position when assembling the hammer.
- the air distributor 1 may be provided with external flats (flat surface) which mate with complementary flats milled internally in the distributor mount 2 .
- the fit must be as close to size for size as possible. Due to tolerance restrictions this means that the fit could be a very close sliding fit, a size for size fit, or a slight interference fit.
- the efficiency of the hammer is partly dependent upon the clearance between the piston 11 and the wear sleeve 10 , because the sliding contact between the piston 11 and the inner diameter of the wear sleeve 10 acts as a pneumatic seal. The clearance between these parts is of the order of 0.1 mm. It will be appreciated that the piston 11 is running in the bore of the wear sleeve 10 at the lower end of its stroke (see FIG.
- the tolerance on the bore of the outer wear sleeve 10 relative to the piston 11 is about 20 microns and a tolerance of about 10 microns in the outer diameter of the inner cylinder 9 , relative to the outer diameter of the piston 11 .
- the clearance between these parts should be in the range of 0.11 mm and 0.14 mm. If the clearance is greater than about 0.14 mm there is a loss of efficiency of the hammer because compressed air bypasses the piston.
- the mount 2 is screw-threadably engaged with the top of wear sleeve 10 by means of screw threads 39 (see FIGS. 3 and 8 ) which are cut into the inner face of the wear sleeve 10 .
- the axial depth of cut of the screw thread 39 is kept to a minimum to minimise the stress on the wear sleeve.
- the minimum thread depth would increase. In the case of 3′′ and 4′′ hammers the minimum depth could be in the range of 1.0 to 1.4 mm. On the larger sizes, e.g. 8′′, this minimum depth could be in the range of 1.6 mm to 2.0 mm.
- the bottom end of the hammer is assembled first.
- the hammer is then placed upright.
- the piston 11 is placed into the wear sleeve 10 .
- the air distributor 3 is placed into the wear sleeve 10 such that the probe 6 is sitting within piston 11 .
- the inner cylinder 9 is pushed into the wear sleeve 10 .
- the distributor mount 2 is screwed into the wear sleeve 10 .
- the assembly is then tipped on end so that distributor 3 falls down through mount 2 Where the dowels 8 are used these are assembled, and an O-ring is placed on distributor 3 .
- the check valve 4 and a spring are put in position.
- the top locking member 1 is then screwed onto the end of distributor 3 .
- the air distributor 3 is inserted into inner cylinder 9 (the probe 6 has already been inserted in air distributor 3 ).
- the distributor mount 2 is placed over air distributor 3 .
- Dowels 8 are inserted in position in grooves 26 in distributor mount 2 , and complementary grooves 27 in air distributor 3 (see FIG. 6 ). Once the dowels are in place the air distributor 3 cannot rotate.
- the circlip 7 is assembled in groove 25 on air distributor 3 (see FIGS. 3 and 4 ). If the assembly at this stage is stood on inner cylinder 9 , then air distributor 3 can fall as far as circlip 7 allows it. In this position circlip 7 is in groove 24 (in distributor mount 2 ) and cannot come out.
- the assembly can be inserted into wear sleeve 10 by applying force until the distributor mount 2 is in position to screw into wear sleeve 10 .
- the inner cylinder 9 will be gradually pushed into position.
- the top locking member 1 is screwed to air distributor 3 by screw threads 42 (see FIG. 7 ).
- the inner cylinder 9 is held securely in position, and circlip 7 has pulled up in space 24 to a top position.
- the function of the circlip 7 is to prevent the air distributor 3 from falling down into the hammer assembly before the locking member 1 is in place.
- the air distributor 3 is firmly held in position and the circlip 7 becomes redundant.
- the operation of the hammer is as follows. Referring to FIG. 3 , compressed air is supplied through top locking member 1 and forces check valve 4 open by pushing down on a compression spring 5 . The compressed air is then supplied through an annular chamber 16 formed between air distributor 3 and probe 6 (see FIGS. 3 and 7 ). The air then passes through ports 17 in air distributor 3 and into four chambers 18 (see FIGS. 3 and 8 ), which are segmental in plan, and are formed between distributor mount 2 and air distributor 3 . From there the compressed air passes down through ports 19 in inner cylinder 9 and into the segmentally-shaped chambers 20 (see FIG. 9 ) between the inner cylinder 9 and the wear sleeve 10 . From here the air is supplied through ports 21 in the inner cylinder 9 .
- FIGS. 10 and 11 of the drawings A second embodiment of the down-the hole hammer is now described with reference to FIGS. 10 and 11 of the drawings.
- This embodiment is substantially similar in construction and operation to the first embodiment of FIGS. 1 to 9 , and like reference numerals denote like parts.
- the stop is provided by means of an annular flat shoulder 50 on the inner surface of the top locking member 1 , which abuts the top flat annular end 51 of the air-distributor 3 , when the inner cylinder 9 is locked in position.
- the locking is achieved, by arranging the length tolerances to be such that, as the inner cylinder 9 , is locked, there is a small gap between the end 51 of the air-distributor 3 and shoulder 50 . As the hammer tightens due to applied torque in operation, this gap is closed.
- a compression ring (not shown) may be positioned between the end 51 and the shoulder 50 which absorbs forces as the assembly tightens. This also makes up for variation in lengths due to tolerances.
- the length tolerances referred to are the length of distributor 3 from end 51 to shoulder 15 ; the length of inner cylinder 9 from shoulder 15 to the top end 14 of the inner cylinder; the overall length of mount 2 , and the length from shoulder 12 on top locking member 1 to shoulder 50 . These lengths are chosen to achieve a small gap between the shoulder 50 and the flat end 51 . As explained about, this gap closes in operation of the hammer. If it is not desired to be restricted to tight length tolerances then a compression ring may be inserted between shoulder 50 and the flat end 51 as explained above.
- the air distributor 3 is all in one piece which improves the strength of the assembly.
- annular circlip 7 shown in FIGS. 3 and 4 is replaced by a rubber O-ring 53 positioned between the lower inner end of the locking member 1 and the air-distributor 3 .
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Abstract
A down-the-hole hammer is described. It comprises an external cylindrical outer wear sleeve (10), an inner cylinder (9) mounted co-axially within the outer wear sleeve (10), a sliding piston (11) mounted for reciprocating movement within the inner cylinder (9) and the outer wear sleeve (10), to strike a hammer bit (40) mounted at the lower end of the outer wear sleeve (10) and an elongate cylindrical air distributor (3) positioned within the hammer assembly. The lower end of the air distributor (3) is positioned substantially concentrically within the upper end of the inner cylinder (9). A shoulder (38) on the air distributor (3) engages the underside of a complementary shoulder (15) on the inner cylinder (9). The top end of the outer wear sleeve (10) is screw-threadably engaged with the lower end of an annular air distributor mount (2), and the top end of the inner cylinder (9) abuts the lower end of the distributor mount (2) such that the inner cylinder is rigidly mounted in the drill assembly relative to the outer wear sleeve (10).
Description
- The present invention relates to “down-the-hole” hammers or fluid-operated percussion drill tools operated by a supply of compressed air.
- Some designs of conventional down-the-hole hammers and fluid-operated percussion drill tools comprise an external cylinder or outer wear sleeve, within which is mounted an inner cylinder which in turn engages with a backhead assembly. A sliding reciprocating piston co-operates with the inner cylinder and backhead assembly, which when air pressure is supplied through the backhead assembly, acts with a percussive effect on a drill bit retained within a chuck on the outer wear sleeve.
- In down-the-hole hammers the energy created is in part dependent on the cross sectional area of the reciprocating piston. This is because the force is determined by the formula P×A (where P=air pressure and A=cross sectional area of the piston). In most modern down-the-hole hammers the piston is a sliding valve, which reciprocates between a strike position on a bit and a top of stroke position. The length and timing of the stroke is determined by the supply and exhaust of air to a lift chamber and top pressure chamber.
- In known conventional arrangements, the inner cylinder is effectively suspended within the outer wear sleeve by means of a compressible retaining ring, such as a circlip, which has to be slid up the inner cylinder so as to seat against a shoulder or lip at one end thereof, being compressed when the inner cylinder is dropped down within the outer wear sleeve, and then expanding outwardly into a groove or shoulder formed on the inner diameter of the outer wear sleeve with a snap action. When in this position, the circlip seats within the groove and abuts against the lip of the inner cylinder, by which the inner cylinder is suspended within the outer wear sleeve.
- EP1004744A, of the same applicant, discloses a segmented ring mounting for retaining the inner cylinder within the outer wear sleeve in a fluid-operated percussion drill tool, such as a down-the-hole hammer.
- The retaining ring seats the smaller diameter inner cylinder within the larger diameter outer wear sleeve. The outer wear sleeve is formed with a groove cut on its inside diameter, or a shoulder for seating the retaining ring against a lip of the inner cylinder. The ring is capable of radial compression and expansion so as to expand radially into the seating groove or shoulder for retaining the components one within the other in use. The retaining ring comprises at least three segments, which when touching end to end form a complete circle, and an expansible O-ring, for holding the segments together but allowing the segments to expand radially and move apart by sufficient amount so as to seat the segments in the groove or against the shoulder.
- The inner cylinder of EP1004744A is integral to the porting of the hammer. In the system the piston runs on the inner diameter of the inner cylinder and also on the inner diameter of the outer wear sleeve. It is essential that the fit between the outer diameter of the inner cylinder and the bore of the outer wear sleeve be a tight/close fit to ensure optimum alignment of the two bores. This means that the clearance and hence the efficiency of the hammer is optimised because the operation of the hammer relies on a partial seal between the piston and the top and bottom chambers, i.e. the tighter the clearance the greater the energy (within reason). In the seating ring system of EP1004744A effective operation relies on a difference in wear sleeve bore diameter above and below the seating ring groove. This means the usable diameter for the piston, and thus the energy, is reduced. This is because the inner diameter of the wear sleeve above the seating ring has to be larger than below to ensure that the seating ring is located in position. This results in an effective reduction in the cross-sectional diameter of the piston, which reduces the force on the piston.
- Other manufacturers have in the past made the inner cylinder as part of a threaded component which screws into the outer wear sleeve. The disadvantage of this is that the hammer wears externally and in many cases it is rebuilt by replacing all external components. This would obviously be extremely expensive in the above scenario. There is also the issue of the clearance which would be necessary, between the external diameter of the inner cylinder portion and the bore of the wear sleeve, to allow the component to screw into the wear sleeve. As will be explained below the clearance needs to be minimised to optimise the concentricity of the inner cylinder bore and the wear sleeve bore.
- In other known prior art percussion hammers the inner cylinder is mounted within the outer wear sleeve by means of a compressible retaining ring, such as a circlip, which is expanded outwardly to seat into the groove or shoulder formed on the inner diameter of the outer wear sleeve.
- The outer wear sleeve of down-the-hole hammers is subject to very strong abrasive forces when in use causing significant wear of, and removal of metal from, the outer sleeve. This weakens the outer wear sleeve to the point where it has to be replaced. In the prior art hammers described the provision of circumferential seating grooves for circlips, seating rings and the like, in the inner face of the wear sleeve reduce the wear thickness of the outer sleeve. This means that the outer wear sleeve has to be replaced more quickly than would be the case if the wear sleeve contained no more grooves.
- In other prior art down-the-hole hammers (e.g. those having a seating ring) the inner cylinder is located on a shoulder provided by a groove in the wear sleeve. It is then locked in position by the application of torque at the backhead, which locks down on a compression ring or the like. The result is that there is a significant locking force which acts between the shoulder and the threads of the wear sleeve. The possibility that this force could cause distortion on the wear sleeve will increase as the external wear on the wear sleeve outer diameter increases.
- Another type of locking system relies on a collet type system (e.g. WO9967065 Azuko). This system applies not only a force down an shoulder on the wear sleeve but also an outward force on the wear sleeve. Again the effect of these forces increases as the wear sleeve wears.
- In summary, the disadvantages of the prior art systems are as follows.
- Where a seating ring is used this results in:
-
- a reduction of the available piston cross-section due to shoulder requirements for the seating ring;
- a reduction of wear sleeve cross-section due to the requirement to provide a seating ring groove;
- high locking forces required on the seating ring shoulder of the wear sleeve.
Where a compressible/expandable circlip is used this results in: - a reduction of the wear sleeve cross-section due to the requirement to provide a seating ring groove;
- high locking forces required on the seating ring shoulder of the wear sleeve.
Where an integral inner cylinder and threaded component is used, this results in: - a requirement for clearance between the inner cylinder and the wear sleeve resulting in concentricity problems;
- it is expensive to rebuild.
- It is an object of the invention to provide a down-the-hole hammer, or other fluid operated percussion drill tool, having means for rigidly mounting the inner cylinder in the outer wear sleeve while still maximising the bore of the wear sleeve. It is also an object of the invention to obviate the need for a seating groove in the outer wear sleeve, and to minimise areas of weakness in the outer wear sleeve.
- The invention provides a fluid-operated percussion drill tool, in particular a down-the-hole hammer, comprising an external cylindrical outer wear sleeve, an inner cylinder mounted co-axially within the outer wear sleeve, a sliding piston mounted for reciprocating movement within the inner cylinder and the outer wear sleeve, to strike a hammer bit mounted at the lower end of the outer wear sleeve, characterised in that the inner cylinder is formed with an inwardly-directed abutment which in the assembled tool is clamped between a complementary engagement means and a locking means such that the inner cylinder is rigidly mounted and held in the drill tool assembly relative to the outer wear sleeve.
- Preferably, an elongate cylindrical air distributor is positioned within the hammer assembly, and a lower end of the air distributor is positioned substantially concentrically within the upper end of the inner cylinder and an abutment on the air distributor engages the underside of a complementary abutment on the inner cylinder. Preferably, the top end of the outer wear sleeve is screw-threadably engaged with the lower end of an annular air distributor mount, and the top end of the inner cylinder abuts the lower end of the distributor mount such that the inner cylinder is rigidly mounted in the drill assembly relative to the outer wear sleeve when a top locking member is threadably mounted onto the air distributor.
- The air distributor is threadably engaged at its upper end with a top locking member which abuts the top of the air distributor mount.
- Thus, in the drill assembly of the invention, the inner cylinder is rigidly held relative to the outer wear sleeve.
- There is no requirement for a mounting groove for the inner cylinder within the outer wear sleeve, which can be a weak point in the assembly.
- Embodiments of a down-the-hole hammer in accordance with the invention will now be described with reference to the accompanying drawings, wherein:
-
FIG. 1 is a sectional side elevation of a first embodiment of a down-the-hole hammer of the invention, showing the piston in the strike position; -
FIG. 2 is a sectional side elevation of the down-the-hole hammer ofFIG. 1 , showing the piston in the top of stroke position; -
FIG. 3 is a sectional side elevation of the top part of the hammer ofFIG. 1 to a larger scale; -
FIG. 4 is a sectional side elevation, to an enlarged scale, showing a detail ofFIG. 3 ; -
FIG. 5 is a cross-sectional plan view of the down-the-hole hammer ofFIG. 1 , on the line C-C ofFIG. 3 ; -
FIG. 6 is a cross-sectional plan view of the down-the-hole hammer ofFIG. 1 , on the line B-B ofFIG. 3 ; -
FIG. 7 is a cross-sectional plan view of the down-the-hole hammer ofFIG. 1 , on the line D-D ofFIG. 3 ; -
FIG. 8 is a cross-sectional plan view of the down-the-hole hammer ofFIG. 1 , on the line E-E ofFIG. 3 ; -
FIG. 9 is a cross-sectional plan view of the down-the-hole hammer ofFIG. 1 , on the line F-F ofFIG. 3 ; -
FIG. 10 is a sectional side elevation of a second embodiment of a down-the hole hammer of the invention, showing the piston in the strike position; and -
FIG. 11 is sectional side elevation of the top part of the hammer ofFIG. 10 to a larger scale. - Referring to FIGS. 1 to 4 of the drawings a first embodiment of a down-the-hole hammer of the invention comprises an external cylindrical
outer wear sleeve 10. Aninner cylinder 9 is mounted co-axially within theouter wear sleeve 10. A slidingpiston 11 is mounted for reciprocating movement within theinner cylinder 9 and theouter wear sleeve 10, to strike ahammer bit 36 mounted for sliding movement in achuck 41 located at the forward end of theouter wear sleeve 10, in well known manner. - Referring now to
FIG. 3 , at the back end of the hammer, atop locking member 1 is screw-threadably mounted on anannular air distributor 3.Air distributor 3 is fitted concentrically throughinner cylinder 9 and adistributor mount 2 and when assembled an outwardly-directedannular flange 38 on the lower end ofair distributor 3 abuts the underside of an inwardly-directedannular shoulder 15 ininner cylinder 9. Thetop end 14 ofinner cylinder 9, above theshoulder 15, in turn abuts the lower end of thedistributor mount 2. Thedistributor mount 2 is substantially cylindrical and open at both ends. It has anupper part 2 a having an outer diameter which is the same as the outer diameter of theouter wear sleeve 10, such that when themount 2 is engaged with the wear sleeve (as described below) the outer cylindrical wall of themount 2 is flush with the outer wall of thewear sleeve 10. Themount 2 has alower part 2 b of reduced diameter which fits within the top end of thewear sleeve 10, and is screw-threadably engaged with the inner wall of thewear sleeve 10, by means of screw threads 39 (see alsoFIG. 8 ). The transition between the upper and lower parts of thedistributor mount 2 is defined by a downwardly facingannular shoulder 23, against which the top annular rim of thewear sleeve 10 abuts, and is locked in place when themount 2 is fully engaged with thewear sleeve 10. The bottom of the top locking member I has a flatannular rim 12 which engages a complementaryflat shoulder 13 on the top end of thedistributor mount 2. Theinner cylinder 9 is thus effectively locked between a shoulder 13 (between top lockingmember 1 and mount 2) and shoulder 15 (betweenair distributor 3 and inner cylinder 9).Shoulder 15 may be tapered if required. - Stated differently, the
inner cylinder 9, at its upper end, has an inwardly extending annular shoulder orflange 14 which is rigidly held between theshoulder 15 and the lower end of thedistributor mount 2, when thedistributor mount 2 has been screwed into position in the top end of thewear sleeve 10, and thetop locking member 1 has been screwed on to the air distributor. When the top-lockingmember 1 is screwed down, by screw-threadably engaging it with the top of the air-distributor 3, this acts to pull the air-distributor 3 upwardly against theshoulder 15, and in turn pulls theinner cylinder 9 upwardly against theshoulder 14. The whole assembly then locks down onshoulder 13. - When screw engaging top locking
member 1 toair distributor 3,air distributor 3 is prevented from turning by means ofdowels 8 positioned betweenmount 2 andair distributor 3. An annular circlip 7 (seeFIGS. 3 and 4 ) is positioned in achamber 24 formed between lockingmember 1 andmount 2 and agroove 25 machined onair distributor 3. Thecirclip 7 serves to retainair distributor 3 loosely in position when assembling the hammer. - Instead of the
dowels 8, other means (not shown) may be provided to prevent theair distributor 3 from turning as thetop locking member 1 is being screwed in place in assembling the hammer. For example, theair distributor 1 may be provided with external flats (flat surface) which mate with complementary flats milled internally in thedistributor mount 2. - To ensure maximum alignment between the
inner cylinder 9 and thewear sleeve 10 the fit must be as close to size for size as possible. Due to tolerance restrictions this means that the fit could be a very close sliding fit, a size for size fit, or a slight interference fit. The efficiency of the hammer is partly dependent upon the clearance between thepiston 11 and thewear sleeve 10, because the sliding contact between thepiston 11 and the inner diameter of thewear sleeve 10 acts as a pneumatic seal. The clearance between these parts is of the order of 0.1 mm. It will be appreciated that thepiston 11 is running in the bore of thewear sleeve 10 at the lower end of its stroke (seeFIG. 1 ) and runs in the bore of theinner cylinder 9 at the top of the stroke (seeFIG. 2 ). Again the clearance is of the order of 0.1 mm. It is also important to ensure that the bore of theinner cylinder 9 is concentric with the bore of theouter wear sleeve 10, and that there is no sideways (i.e. radial) movement. This is achieved by having theinner cylinder 9 as a very snug, or interference, fit within the bore of theouter sleeve 10. - The tolerance on the bore of the
outer wear sleeve 10 relative to thepiston 11 is about 20 microns and a tolerance of about 10 microns in the outer diameter of theinner cylinder 9, relative to the outer diameter of thepiston 11. The clearance between these parts should be in the range of 0.11 mm and 0.14 mm. If the clearance is greater than about 0.14 mm there is a loss of efficiency of the hammer because compressed air bypasses the piston. - As mentioned above, the
mount 2 is screw-threadably engaged with the top ofwear sleeve 10 by means of screw threads 39 (seeFIGS. 3 and 8 ) which are cut into the inner face of thewear sleeve 10. The axial depth of cut of thescrew thread 39 is kept to a minimum to minimise the stress on the wear sleeve. When considering the axial depth ofscrew thread 39 it is important to note that as the diameter of the hammer increases (hammer models are generally denoted by the nominal size which they are designed to drill e.g. 3″, 4″, 5″, 6″, 8″ etc.) the minimum thread depth would increase. In the case of 3″ and 4″ hammers the minimum depth could be in the range of 1.0 to 1.4 mm. On the larger sizes, e.g. 8″, this minimum depth could be in the range of 1.6 mm to 2.0 mm. - In a preferred method of assembly of the hammer, the bottom end of the hammer is assembled first. The hammer is then placed upright. The
piston 11 is placed into thewear sleeve 10. Theair distributor 3 is placed into thewear sleeve 10 such that theprobe 6 is sitting withinpiston 11. Theinner cylinder 9 is pushed into thewear sleeve 10. Thedistributor mount 2 is screwed into thewear sleeve 10. The assembly is then tipped on end so thatdistributor 3 falls down throughmount 2 Where thedowels 8 are used these are assembled, and an O-ring is placed ondistributor 3. Thecheck valve 4 and a spring are put in position. Thetop locking member 1 is then screwed onto the end ofdistributor 3. - There are other ways of assembling hammer but the above method has been found to be convenient.
- For example, in an alternative method of assembly, the
air distributor 3 is inserted into inner cylinder 9 (theprobe 6 has already been inserted in air distributor 3). Thedistributor mount 2 is placed overair distributor 3.Dowels 8 are inserted in position ingrooves 26 indistributor mount 2, andcomplementary grooves 27 in air distributor 3 (seeFIG. 6 ). Once the dowels are in place theair distributor 3 cannot rotate. Thecirclip 7 is assembled ingroove 25 on air distributor 3 (seeFIGS. 3 and 4 ). If the assembly at this stage is stood oninner cylinder 9, thenair distributor 3 can fall as far ascirclip 7 allows it. In thisposition circlip 7 is in groove 24 (in distributor mount 2) and cannot come out. Thus the assembly can be inserted intowear sleeve 10 by applying force until thedistributor mount 2 is in position to screw intowear sleeve 10. On screwing thedistributor mount 2 into thewear sleeve 10, theinner cylinder 9 will be gradually pushed into position. When thedistributor mount 2 abuts wearsleeve 10 atshoulder 23, thetop locking member 1 is screwed toair distributor 3 by screw threads 42 (seeFIG. 7 ). When the lockingmember 1 is locked onshoulder 13, theinner cylinder 9 is held securely in position, andcirclip 7 has pulled up inspace 24 to a top position. Thus, the function of thecirclip 7 is to prevent theair distributor 3 from falling down into the hammer assembly before the lockingmember 1 is in place. After the lockingmember 1 has been screwed into position theair distributor 3 is firmly held in position and thecirclip 7 becomes redundant. - The operation of the hammer is as follows. Referring to
FIG. 3 , compressed air is supplied through top lockingmember 1 and forces checkvalve 4 open by pushing down on acompression spring 5. The compressed air is then supplied through anannular chamber 16 formed betweenair distributor 3 and probe 6 (seeFIGS. 3 and 7 ). The air then passes throughports 17 inair distributor 3 and into four chambers 18 (seeFIGS. 3 and 8 ), which are segmental in plan, and are formed betweendistributor mount 2 andair distributor 3. From there the compressed air passes down throughports 19 ininner cylinder 9 and into the segmentally-shaped chambers 20 (seeFIG. 9 ) between theinner cylinder 9 and thewear sleeve 10. From here the air is supplied throughports 21 in theinner cylinder 9. - When the
piston 11 is in the strike position (FIG. 1 ), air is supplied from theports 21 into thechamber 28 between thepiston 11 and thewear sleeve 10. From here it is supplied through thechannels 29 in thepiston 11 to undercut 30 and intolift chamber 31. - At the back end of the piston, in a
top chamber 32, air is free to exhaust through piston bore 33 and bit bores 34 and 35 to atmosphere. As a result a pressure differential exists between thelift chamber 31 and thetop chamber 32 and the piston lifts to the top of stroke position (FIG. 2 ). - In this position air is cut-off from entering
chamber 31, and air can exhaust fromchamber 31 through bit bores 34 and 35 to atmosphere. Pressurised air is supplied fromports 21 to achamber 38 betweenpiston 11 andinner cylinder 9. From here it is supplied thoughchannels 37 ininner cylinder 9 totop chamber 32 which is prevented from exhausting byprobe 6 which is in piston bore 33. As there is now a pressure differential betweenchambers bit 36 and the cycle repeats itself. - A second embodiment of the down-the hole hammer is now described with reference to
FIGS. 10 and 11 of the drawings. This embodiment is substantially similar in construction and operation to the first embodiment of FIGS. 1 to 9, and like reference numerals denote like parts. - It has been found in use of the first embodiment that there is a risk that the
distributor mount 2 may crack if excessive force is applied to it from thetop locking member 1 due to torqueing up of the assembly in operation. This risk may be avoided by providing a stop for the downward movement of thetop locking member 1 on the top end of theair distributor 3. - As shown in
FIG. 11 , the stop is provided by means of an annularflat shoulder 50 on the inner surface of thetop locking member 1, which abuts the top flatannular end 51 of the air-distributor 3, when theinner cylinder 9 is locked in position. In practice the locking is achieved, by arranging the length tolerances to be such that, as theinner cylinder 9, is locked, there is a small gap between theend 51 of the air-distributor 3 andshoulder 50. As the hammer tightens due to applied torque in operation, this gap is closed. Alternatively, a compression ring (not shown) may be positioned between theend 51 and theshoulder 50 which absorbs forces as the assembly tightens. This also makes up for variation in lengths due to tolerances. - The length tolerances referred to are the length of
distributor 3 fromend 51 toshoulder 15; the length ofinner cylinder 9 fromshoulder 15 to thetop end 14 of the inner cylinder; the overall length ofmount 2, and the length fromshoulder 12 on top lockingmember 1 toshoulder 50. These lengths are chosen to achieve a small gap between theshoulder 50 and theflat end 51. As explained about, this gap closes in operation of the hammer. If it is not desired to be restricted to tight length tolerances then a compression ring may be inserted betweenshoulder 50 and theflat end 51 as explained above. - In this embodiment, the
air distributor 3 is all in one piece which improves the strength of the assembly. - As shown in
FIG. 11 , in this embodiment theannular circlip 7 shown inFIGS. 3 and 4 , is replaced by a rubber O-ring 53 positioned between the lower inner end of the lockingmember 1 and the air-distributor 3. - From the foregoing, it will be apparent that numerous modifications and variations can be effected without departing from the true spirit and scope of the novel concept of the present invention. It will be appreciated that the present disclosure is intended to set forth the exemplifications of the invention which are not intended to limit the invention to the specific embodiments illustrated. The disclosure is intended to cover by the appended claims all such modifications as fall within the scope of the claims.
- Where technical features mentioned in any claim are followed by reference signs, these reference signs have been included for the sole purpose of increasing the intelligibility of the claims and accordingly, such reference signs do not have any limiting effect on the scope of each element identified by way of example by such reference signs.
- The words “comprises/comprising” and the words “having/including” when used herein with reference to the present invention are used to specify the presence of stated features, integers, steps or components but does not preclude the presence or addition of one or more other features, integers, steps, components and groups thereof.
Claims (12)
1. A fluid-operated percussion drill tool, in particular a down-the-hole hammer, comprising an external cylindrical outer wear sleeve (10), an inner cylinder (9) mounted co-axially within the outer wear sleeve (10), a sliding piston (11) mounted for reciprocating movement within the inner cylinder (9) and the outer wear sleeve (10), to strike a hammer bit (36) mounted at the lower end of the outer wear sleeve (10), characterised in that the inner cylinder (9) has an abutment (15) which in the assembled tool is clamped between a complementary engagement means (38) and a locking means (2) such that the inner cylinder (9) is rigidly mounted and held in the drill tool assembly relative to the outer wear sleeve (10).
2. A fluid-operated percussion drill tool as claimed in claim 1 , characterised in that the top end of the outer wear sleeve (10) is screw-threadably engaged with the lower end of an annular air distributor mount (2), the top end of the inner cylinder (9) abuts the lower end of the distributor mount (2), a lower end of the air distributor (3) abuts a shoulder (15) in the inner cylinder (9) and is threadably engaged at its upper end with a top locking member (1). which in its locked position abuts the top of the air distributor mount (2).
3. A tool as claimed in claim 1 , characterised in that there is an elongate cylindrical air distributor (3) positioned within the hammer assembly and an abutment (15) on the inner cylinder (9) engages with a complementary abutment (38) on the air distributor (3) and locking means (2) connected to the outer wear sleeve (10) are provided to clamp the abutment (15) between the abutment (38) on the air distributor (3), and the locking means is such that the inner cylinder (9) is rigidly mounted in the drill assembly relative to the outer wear sleeve (10).
4. A tool as claimed in claim 1 or claim 3 , characterised in that the locking means comprises an annular air distributor mount (2) the lower end of which is screw-threadably engaged with the top end of the outer wear sleeve (10).
5. A tool as claimed in claim 4 characterised in that the air distributor (3) is threadably engaged at its upper end with a top locking member (1) which abuts the top of the air distributor mount (2).
6. A tool as claimed in any of the preceding claims characterised in that the inner cylinder (9) is formed with an inwardly directed abutment which is clamped between the complementary engagement means (38) and the locking means (2).
7. A tool as claimed in any one of the preceding claims characterised in that it comprises a top locking member (1) screw threadably mounted on an annular air-distributor 3, which is fitted concentrically through an inner cylinder (9) and an annular distributor mount (2), and an annular flange (38) on the lower end of the air-distributor (3) abuts the underside of an inwardly-directed abutment (15) in inner cylinder (9), and a top end (14) of the inner cylinder (9) abuts a lower end of the distributor mount (2) whereby the inner cylinder (9) is locked in position.
8. A tool as claimed in claim 7 , characterised in that the top end of the inner cylinder (9) comprises an annular shoulder or flange (14) which is rigidly held between an annular flange (38) on the lower end of air-distributor (3) which abuts an annular shoulder (15) of the inner cylinder (9), and the lower end of the distributor mount (2).
9. A tool as claimed in any one of claims 2 to 8 , characterised in that the bottom of the top locking member (1) has a flat annular rim (12) which engages a complementary flat shoulder (13) on the top end of the distributor mount (2).
10. A tool as claimed in any one of claims 2 to 9 characterised in that downward movement of the top locking member 1 against the distributor mount (2) is controlled by means of a stop (51) on the air-distributor (3).
11. A tool as claimed in claim 10 characterised in that the stop is provided by means of an annular surface (51) on the top of the air-distributor 3 which engages with an annular shoulder (50) on the inner surface of the top locking member (1).
12. A tool as claimed in claim 11 , characterised in that a compression ring is positioned between the annular surface (51) and the annular shoulder (50).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IES20020794 | 2002-10-04 | ||
IE20020794A IES20020794A2 (en) | 2002-10-04 | 2002-10-04 | A down-the-hole hammer |
PCT/IE2003/000132 WO2004031530A1 (en) | 2002-10-04 | 2003-09-30 | A down-the hole hammer |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060000646A1 true US20060000646A1 (en) | 2006-01-05 |
Family
ID=27638011
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/529,614 Abandoned US20060000646A1 (en) | 2002-10-04 | 2003-09-30 | Down-the hole hammer |
Country Status (9)
Country | Link |
---|---|
US (1) | US20060000646A1 (en) |
EP (1) | EP1549819B1 (en) |
AT (1) | ATE323210T1 (en) |
AU (1) | AU2003273513A1 (en) |
CA (1) | CA2500949A1 (en) |
DE (1) | DE60304593D1 (en) |
IE (1) | IES20020794A2 (en) |
WO (1) | WO2004031530A1 (en) |
ZA (1) | ZA200502866B (en) |
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US20090071725A1 (en) * | 2005-09-20 | 2009-03-19 | Joseph Purcell | Percussion Hammer for Enlarging Drilled Holes |
US20090260889A1 (en) * | 2005-11-03 | 2009-10-22 | Rockmore International, Inc. | Backhead and drill assembly with backhead |
US20100300763A1 (en) * | 2006-10-20 | 2010-12-02 | Drillroc Pneumatic Pty Ltd | Down-the-Hole Hammer Drill |
US20110192009A1 (en) * | 2009-02-05 | 2011-08-11 | Plunkett Timothy J | Method for assembling a down hole drill |
KR101092873B1 (en) | 2009-11-05 | 2011-12-15 | 주식회사 에버다임락툴 | A ground drilling hammer and its driving process |
US20140076638A1 (en) * | 2012-09-14 | 2014-03-20 | Drillco Tools S.A. | Pressurized fluid flow system having multiple work chambers for a down-the-hole drill hammer and normal and reverse circulation hammers thereof |
US20150129269A1 (en) * | 2013-11-13 | 2015-05-14 | Sandvik Mining And Construction Oy | Impact device and method of dismounting the same |
US9068399B2 (en) | 2006-10-20 | 2015-06-30 | Drillroc Pneumatic Pty Ltd | Down-the-hole hammer drill |
CN106150345A (en) * | 2016-08-29 | 2016-11-23 | 山东天瑞重工有限公司 | The well air distribution system of fast energy-saving down-hole hammer |
US20180195991A1 (en) * | 2017-01-09 | 2018-07-12 | Mobiosense Corp. | Biosensor device |
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CN108590608A (en) * | 2018-01-17 | 2018-09-28 | 大庆市天德忠石油科技有限公司 | Downhole intelligent distributor |
WO2018198017A1 (en) * | 2017-04-25 | 2018-11-01 | Drillco Tools S.A. | Backhead assembly for dth hammer |
US20220018386A1 (en) * | 2020-07-14 | 2022-01-20 | Terelion, Llc | Integrated retaining ring and bushing |
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IES20040482A2 (en) * | 2004-07-16 | 2006-01-25 | Minroc Techn Promotions Ltd | A down-the-hole hammer |
IES20060005A2 (en) * | 2006-01-04 | 2007-02-21 | Minroc Techn Promotions Ltd | A drill bit assembly for fluid-operated percussion drill tools |
IES20090701A2 (en) | 2009-08-31 | 2010-05-12 | Minroc Techn Promotions Ltd | A drill bit assembly for fluid-operated percussion drill tools |
IES20100666A2 (en) | 2010-10-15 | 2011-06-22 | Minroc Techn Promotions Ltd | A down-the-hole hammer |
CN107217982B (en) * | 2017-07-11 | 2019-03-05 | 中煤科工集团西安研究院有限公司 | The multistage deslagging air screw motor of underground coal mine drilling |
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Also Published As
Publication number | Publication date |
---|---|
ATE323210T1 (en) | 2006-04-15 |
EP1549819A1 (en) | 2005-07-06 |
DE60304593D1 (en) | 2006-05-24 |
EP1549819B1 (en) | 2006-04-12 |
AU2003273513A1 (en) | 2004-04-23 |
WO2004031530A1 (en) | 2004-04-15 |
ZA200502866B (en) | 2006-06-28 |
CA2500949A1 (en) | 2004-04-15 |
IES20020794A2 (en) | 2003-02-19 |
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