United States Patent
`
`[19]
`
`[11]
`
`Patent Number:
`
`5,415,240
`
`
`[45] Date of Patent: May 16, 1995
`Mundjar
`
`US00541524OA
`
`. ..... 173/ 105
`3/1967 Kurt ........ .. .. .
`3,307,638
`173/48
`3,403,738 10/1968 Burkhart et al. .
`4,006,783 2/1977 Granholm ................. .. 173/105
`5,060,734 10/1991 Anderson et al.
`.. . .
`.. .. .. 173/206
`5,064,003 11/1991 Nerozhikov et al.
`............... 173/105
`
`
`
`Primary Examitzer—Scott A. Smith
`Attorney, Agent, or Firm—Browdy and Neimark
`
`[57]
`
`ABSTRACT
`
`The invention concerns a rock drill (2) for activating a
`rotatable and reciprocable drill steel assembly (FIG. 1 ).
`A reversible motor (50) is coupled to a striking bar (3)
`for rotating the drill steel. The striking bar is struck by
`a percussion piston (10). A rotary fluid valve (15) is
`operating the piston. A disconnectable
`coupling
`(37,38,43) in normal operation couples both the valve
`(15) and the striking bar (3) with the motor (50). In
`special modes the motor operates only the percussion
`piston, e.g. for retracting a drill rod, or only rotates the
`striking bar (3), e.g. for connecting and disconnecting
`drill rods.
`
`13 Claims, 3 Drawing Sheets
`
`[54] DRILLING DEVICE FOR A ROCK DRILL
`
`[75]
`
`Inventor: Marjan Mundjar, Lohningen,
`Switzerland
`
`[73] Assignee:
`
`SIG Schweizerische
`Industrie-Gesellschaft, Neuhaussen
`am Rheinfall, Switzerland
`
`[21] Appl. No.: 113,648
`
`[22] Filed:
`
`Aug. 31, 1993
`
`Foreign Application Priority Data
`[30]
`Aug. 31, 1992 [JP]
`Japan .................................. 4.232294
`
`Int. Cl.5 ........ ., ................................... .. B25D 9/20
`[51]
`[52] U.S. Cl. .................................... .. 173/48; 173/ 105;
`.
`173/206
`[58] Field of Search ................ .. 173/48, 206, 207, 105
`
`[56]
`
`References Cited
`U.S. PATENT DOCUMENTS
`
`3/1921 Smith .................................. 173/105
`1,372,915
`1,658,330 2/1928 Gilman .. ..... ....
`..... 173/ 105
`3,044,448
`7/1962 Curtis et al.
`........................ 173/ 105
`
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`NOV
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`Exhibit 2009
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` NOV
`Exhibit 2009
`
`

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`U.S. Patent
`
`May 16, 1995
`
`Sheet 1 of 3
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`5,415,240
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`NOV
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`Exhibit 2009
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` NOV
`Exhibit 2009
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`

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`U.S. Patent
`
`May 16, 1995
`
`Sheet 2 of 3
`
`5,415,240
`
`‘9
`
`28
`
`25,26
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`27
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`28
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`NOV
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`Exhibit 2009
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`Exhibit 2009
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` NOV
`Exhibit 2009
`
`
`

`
`1
`
`DRILLING DEVICE FOR A ROCK DRILL
`
`BACKGROUND OF THE INVENTION
`
`5,415,240
`
`2
`vance encounters rock formations of different proper-
`ties and hardness.
`
`This automatic internal adjustment of the percussion
`frequency, therefore, guarantees maximum drill perfor-
`mance in different rock formations.
`If the drill steel for some reason gets jammed in the
`rock then the percussion stops immediately. It is there-
`fore possible to reverse the direction of force on the
`drill steel and retract it. This saves considerable time
`and drilling equipment.
`When retracting a drill steel which is assembled from
`a number of sections, these sections must be discon-
`nected successively. To that end, the rear end of a fol-
`lowing section still partly inserted in the drill bore is
`clamped. The threaded connection between that section
`and the previous section that is still clamped in the
`drilling device, can now be rattled loose by indepen-
`dently operating only the percussion mechanism. The
`previous section can now be unscrewed by operating
`the drill motor in the proper rotation sense which is
`contra to the drilling mode.
`All these operations must be performed under remote
`control because generally operators are not permitted
`near the drilling process because of safety reasons due
`to the hazard of falling rock.
`For the above reasons the drilling device according
`to the present invention guarantees an optimum use of
`the rock drills under various rock conditions. At the
`same time it allows remote control of coupling and
`uncoupling in the event of long hole drilling.
`BRIEF DESCRIPTION OF THE DRAWINGS
`
`Embodiments of the present invention will now be
`described with reference to the drawings, in which
`FIG. 1 shows a longitudinal section through a first
`embodiment,
`FIG. 2 shows a detail of the rotary valve, and
`FIG. 3 shows a longitudinal section through a second
`embodiment.
`
`DETAILED DESCRIPTION OF PREFERRED
`EMBODIMENTS
`
`The drilling device 1 according to FIG. 1 comprises
`a housing 2 which reciprocatingly and rotably activates
`a striking bar 3. On its forward end the striking bar 3
`may have a male thread 4 for connecting the drill steel
`(not shown). The striking bar 3 also has an internal bore
`5 for supplying a flushing fluid to the drill face via a
`connection (not shown) to the housing 2.
`Coaxial with the striking bar a percussion piston 10 is
`reciprocatingly received in the housing 2. In operation
`the front face 11 of the piston rod 12 of piston 10 strikes
`against the rear face of the striking bar 3. The piston 10
`slides in a bore 13 of a cylinder 14. The cylinder 14 is
`rotably supported in housing 2 and forms a first valve
`member of a rotary valve 15. On its forward end it bears
`gear teeth 16 linking with a pinion 17. The cylinder 14
`has two sets of openings 18, 19 in two radial planes. The
`openings 18, 19 are regularly spaced in the circumferen-
`tial direction, and the openings 18 are angularly offset
`against the openings 19.
`The outer surface 20 of the cylinder 14 bears against
`a cylindrical, meander shaped second valve member 25
`of rotary valve 15. A developed projection on the outer
`cylindrical surface 26 of part of valve member 25 and
`cylinder 14 is shown in FIG. 2. One axial face 27 and
`therefore half of the slots 28 of the meander is pressu-
`rised with supply pressure and connected to a high
`
`NOV
`
`Exhibit 2009
`
`5
`
`10
`
`15
`
`20
`
`25
`
`30
`
`35
`
`This invention relates to a drilling device for a rock
`drill with a rotary drive for the drill steel and a percus-
`sion mechanism.
`
`A hydraulic rock drill is known through U.S. Pat. ‘
`No. 4,064,950 in which the control valves for percus-
`sion power and rotation speed are located in the control
`panel apart from the rock drill itself. Furthermore, the
`percussion apparatus and the rotation motor have sepa-
`rate hydraulic circuits. The maximum percussion power
`is adjusted by a pressure relief valve in the hydraulic
`circuit of the percussion mechanism and the maximum
`rotation power is adjusted by a pressure relief valve in
`the hydraulic circuit of the percussion mechanism.
`With such drilling devices it sometimes happens that
`the drill steel gets jammed and cannot be rotated fur-
`ther. When under such conditions the percussion mech-
`anism continues to strike the drill steel, it can happen
`that the latter is driven into the rock and cannot be
`retracted any more.
`In the German Offenlegungsschrift No. 34 39 268 a
`similar drilling device has been proposed where the
`percussion mechanism and the hydraulic motor are
`arranged in series. This device does not have the draw-
`back mentioned above: When the hydraulic fluid cannot
`flow through the motor because the motor is stopped by
`the drill then no flow passes through the percussion
`mechanism. Therefore, percussion stops when the drill
`rod gets jammed. However, this prior art device has
`other drawbacks: The sum of the power output of the
`hydraulic motor and the percussion mechanism is con-
`stant but the power distribution between the two is
`indetermined.
`In Swiss Patent No. 559 088 it was proposed to di-
`rectly couple the percussion frequency with the rota-
`tion rate of the motor. However, with this proposal it is
`not possible to operate the percussion mechanism and
`the motor independently.
`SUMMARY OF THE INVENTION
`
`The object of the present invention is to create a
`drilling device which does not have the drawbacks
`mentioned above.
`
`The drilling device of the present invention has a
`housing in which a striking bar is rotatably and recipro-
`cably supported. The output shaft of a reversible fluid
`motor is coupled to the striking bar for rotating the drill
`~steel. A percussion piston reciprocatingly received in a
`cylinder strikes on to the striking bar. A rotary fluid
`valve is connected to the cylinder. A releasable cou-
`pling selectively couples the output shaft with the ro-
`tary valve.
`The rotary valve may have an additional independent
`drive motor or a second releasable coupling may be
`arranged between the output shaft and the striking bar.
`During normal operation the rotary valve is directly
`coupled with the output shaft of the drill motor. The
`percussion frequency is exactly proportional
`to the
`rotation rate of the drill steel. The angle which the drill
`head shifts between two successive blows by the per-
`cussion piston is always the same regardless of the rota-
`tion rate. It can be shown that this represents about the
`optimum adjustment of percussion frequency to the
`rotation ratewhich varies as the drill steel on its ad-
`
`45
`
`50
`
`55
`
`65
`
` NOV
`Exhibit 2009
`
`

`
`3
`pressure hydraulic accumulator H and to a supply line
`S. The other axial face 29 and the other slots 30 are
`connected to a low pressure accumulator L and a return
`line R.
`
`5,415,240
`
`4
`
`l0
`
`15
`
`20
`
`25
`
`The above is a somewhat simplified description of 5
`rotary valve 15. A more detailed description is con-
`tained in Swiss Patent No. 559 088.
`In operation the valve member 25 remains fixed with
`housing 2. When the cylinder 14 rotates the openings 18
`communicate alternatively with the supply and the
`return and the openings 19 alternatively with the return
`and the supply so that by periodic pressure changes
`piston 10 reciprocates and hits on to the striking bar
`with a frequency proportional to the rotation rate of
`cylinder 14.
`The striking bar 3 has a splined shaft section 35 which
`communicates with a splined bushing 36 connected to a
`gear 37. Gear 37 communicates with a further gear 38
`which can be axially shifted from the normal position
`shown in FIG. 1 in two switch positions by supplying
`one or the other input line 39, 40 of a hydraulic cylinder
`41 with pressure fluid. When pressure is released from
`both inputs 39, 40 the gear 38 returns to the neutral
`position by a centering spring 42. In the neutral position
`the gear 38 links with gear 37 and a pinion 43 which is
`coupled to pinion 17 by a shaft 44.
`The internal bore of gear 38 is splined and sits on the
`splined end of an output shaft 49 of a reversible hydrau-
`lic motor 50. When gear 38 is shifted in its one end
`position it links with pinion 43 only and therefore only 30
`the percussion mechanism is in operation. This mode of
`operation is useful for transferring impacts to the
`threaded ends between two drill steels for loosening the
`coupling. When the gear 38 is shifted to the opposite
`end position it links exclusively with gear 37 so that the
`drill steel is rotated and the percussion mechanism is not
`operative. This mode of operation is useful for connect-
`ing and disconnecting drill rods and in some particular
`rock formations, for rotational drilling only.
`In normal application, however, the gear 38 is in the
`neutral position shown in FIG. 1 so that the percussion
`frequency is proportional to the rotation rate of the drill
`rod. This proportionality provides optimum perfor-
`mance in most drilling applications, irrespective of the
`rock conditions.
`
`35
`
`45
`
`50
`
`55
`
`In the embodiment shown in FIG. 3 like parts are
`designated with like reference numerals so that a de-
`tailed description of those parts need not be repeated.
`The basic difference between the two embodiments is
`that in the FIG. 3 embodiment percussion and drill
`rotation can additionally be performed with individual
`motors 50, 60. To that end, a pinion 61 on an output
`shaft 62 of hydraulic motor 60 links with gear 37. Gears
`37, 38 normally link so that motor 60 is the main motor.
`In normal operation motor 50 is idling, its two lines
`being connected to the return.
`If pressure is applied to input 39 the piston 41 pulls
`gear 38 out of engagement with gear 37. The rotary
`valve 15 can now either be kept at rest (no percussion),
`or it can be operated at a frequency independent of the
`rotation rate of the drill rod by operating motor 50 via
`gears 63, 17. This may be of advantage in some particu-
`lar rock formations.
`The embodiment of FIG. 3 is therefore somewhat
`more versatile whereas the embodiment of FIG. 1 is less 65
`expensive.
`What is claimed is:
`1. A drilling device for a drill steel, comprising:
`
`60
`
`a housing (2);
`a striking bar (3) for holding a rear end of said drill
`steel, said striking bar being supported in said hous-
`ing (2) for rotation around an axis of said striking
`bar and for reciprocal movement along said axis;
`a reversible first fluid motor (50, 60) having an output
`shaft (49, 62) coupled to said striking bar (3) for
`rotating said striking bar;
`a percussion piston (10) for striking said striking bar
`(3), said piston being reciprocatingly received in a
`cylinder (14); and
`a fluid valve (15) connected to said cylinder (14) for
`reciprocating said piston (10) by periodic pressure
`changes; and
`a disconnectable first mechanical coupling (37, 38)
`between said output shaft (49, 62) and said fluid
`valve (15) for coupling a valve member of said fluid
`valve (15) with said output shaft.
`2. The drilling device according to claim 1, further
`including a disconnectable second mechanical coupling
`(38, 37) connecting said output shaft (49) with said strik-
`ing bar (3).
`I
`3. The drilling device according to claim 1, further
`comprising a second fluid motor (50) coupled to said
`fluid valve (15).
`4. A drilling device for a drill steel, comprising:
`a housing (2);
`a striking bar (3) for holding a rear end of said drill
`steel, said striking bar being supported in said hous-
`ing for rotation around a striking bar axis and for
`reciprocal movement along said axis;
`a reversible first fluid motor (50, 60) having a first
`output shaft (49, 62);
`a percussion piston (10) for striking said bar (3), said
`piston being reciprocatingly received in a cylinder
`(14) of said housing;
`a fluid valve (15) connected to said cylinder (14) for
`controlling periodic pressure changes within said
`cylinder to reciprocate said piston;
`a fixed-ratio transmission (38, 43; 38, 37) connecting
`said first output shaft (49, 62) to said striking bar to
`rotate said striking bar and connecting said first
`output shaft (49, 62) to said fluid valve (15) for
`controlling a reciprocation frequency of said per-
`cussion piston, said transmission being selectively
`engageable; and
`means for selectively engaging said transmission.
`5. The drilling device according to claim 4, wherein
`said transmission includes rotary gears selectively en-
`gaged by relative axial sliding of said gears to selec-
`tively mesh and disconnect teeth of said gears.
`6. The drilling device according to claim 4, wherein
`said transmission further comprises:
`a fixed-ratio first transmission (38, 43) connecting said
`first output shaft (49, 62) to said fluid valve (15) for
`controlling a reciprocation frequency of said per-
`cussion piston, said first transmission being selec-
`tively engageable; and
`a fixed—ratio second transmission (38, 37) connecting
`said first output shaft (49, 62) to said striking bar to
`rotate said striking bar, said second transmission
`being selectively engageable.
`7. The drilling device according to claim 6, wherein
`said first transmission and said second transmission in-
`clude rotary gears and are selectively engaged by rela-
`tive axial sliding of said gears to selectively mesh and
`disconnect teeth of said gears.
`
`NOV
`
`Exhibit 2009
`
` NOV
`Exhibit 2009
`
`

`
`5,415,240
`
`15
`
`20
`
`25
`
`5
`8. The drilling device according to claim 6, wherein
`said means for selectively engaging includes means for
`selectively engaging said first
`transmission and said
`second transmission.
`9. The drilling device according to claim 8, wherein
`said means for selectively engaging said first transmis-
`sion and said second transmission allows for engaging
`the first transmission but not the second transmission;
`allows for engaging the second transmission but not
`the first transmission;
`and allows for engaging simultaneously the first
`'
`transmission and the second transmission.
`10. The drilling device according to claim 9, wherein
`said first transmission and said second transmission in-
`clude rotary gears and are selectively engaged by rela-
`tive axial sliding of said gears to mesh and disconnect
`teeth of said gears.
`11. The drilling device according to claim 4, further
`comprising:
`a second motor (50);
`and a second output shaft (62) coupled to said second
`motor (50);
`said second output shaft (49) directly coupled to said
`fluid valve for controlling a reciprocation fre-
`quency of said percussion piston;
`said first output shaft (62) is directly coupled to said
`striking bar to rotate said striking bar;
`said transmission connects said first output shaft (62)
`‘
`to said fluid valve (15) for controlling a reciproca-
`tion frequency of said percussion piston and con-
`
`6
`nects said second output shaft (49) to said striking
`bar to rotate said striking bar; and
`said means for selectively engaging includes means
`for disengaging said second output shaft (49) from
`said striking bar, whereby said second output shaft
`will not rotate said striking bar through said trans-
`mission.
`12. The drilling device according to claim 11,
`wherein said transmission includes rotary gears selec-
`0 tively engaged by relative axial sliding of said gears to
`selectively mesh and disconnect teeth of said gears.
`13. A drilling device for a drill steel, comprising:
`7 a housing (2);
`a striking bar (3) for holding a rear end of said drill
`steel, said striking bar being supported in said hous-
`ing (2) for rotation around its axis and for recipro-
`cal movement along its axis;
`a reversible first fluid motor (60) with an output shaft
`(62) coupled to said striking bar (3) for rotating said
`striking bar;
`a percussion piston (10) for striking said striking bar
`(3) and reciprocatingly received in a cylinder (14);
`a fluid valve (15) connected to said cylinder (14) for
`reciprocating said piston (10); and
`a disconnectable first coupling (37,38) between said
`output shaft (62) and said fluid valve (15);
`further comprising a second fluid motor (50) coupled
`to said fluid valve (15).
`*
`*
`*
`*
`it
`
`30
`
`35
`
`45
`
`50
`
`55
`
`65
`
`NOV
`
`Exhibit 2009
`
` NOV
`Exhibit 2009