WO2013106207A1 - Tête de forage à arbre double progressive et ses systèmes et ses procédés - Google Patents

Tête de forage à arbre double progressive et ses systèmes et ses procédés Download PDF

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Publication number
WO2013106207A1
WO2013106207A1 PCT/US2012/072106 US2012072106W WO2013106207A1 WO 2013106207 A1 WO2013106207 A1 WO 2013106207A1 US 2012072106 W US2012072106 W US 2012072106W WO 2013106207 A1 WO2013106207 A1 WO 2013106207A1
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WO
WIPO (PCT)
Prior art keywords
hollow shaft
drill head
drive
gear
gearbox
Prior art date
Application number
PCT/US2012/072106
Other languages
English (en)
Inventor
Jason Dominic ARGENT
David R. RITTER
Original Assignee
Longyear Tm, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Longyear Tm, Inc. filed Critical Longyear Tm, Inc.
Publication of WO2013106207A1 publication Critical patent/WO2013106207A1/fr

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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
    • E21B4/006—Mechanical motion converting means, e.g. reduction gearings
    • 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
    • E21B3/00—Rotary drilling
    • E21B3/02—Surface drives for rotary drilling
    • E21B3/022—Top drives

Definitions

  • Drill rigs generally include an upstanding mast with a mounted drill head.
  • the drill head can be capable of moving along the mast Additionally, the drill head can receive and engage the upper end of a drill string.
  • the drill head can rotate the drill string and a drill bit mounted to the drill string to drill a formation.
  • the drill string can include a plurality of drill rods that are connected end to end.
  • an operator of the drill rig can choose a particular speed of rotation for the drill head and, consequently, for the drill string.
  • Changing the speed of rotation can typically be accomplished by shifting gears or splines in a gearbox, and/or modulating flow of hydraulic fluid to the motor, which transmits the rotational motion from a drive source to the drill string. For instance, by engaging a small gear, a highest number of revolutions per minute can be achieved (i*., a higher speed). By contrast, by engaging a larger gear, a lower speed can be achieved and transferred to the drill string.
  • the present disclosure comprises apparatus, systems and methods for shifting gears of a drill head.
  • the present disclosure comprises an apparatus and system that can allow engagement and disengagement of low and high gears with a single shift movement, which can improve mechanical robustness for deep-hole drilling applications.
  • a single shift movement can eliminate or reduce the possibility of improper disengagement and/or engagement of the gears.
  • at least one of a drill head and a gearbox can be further configured to provide for an automated shifting process. As such, gears can be shifted remotely, thereby further reducing the possibility of operator error and potential damage to equipment.
  • the system can be configured for higher torque output, can have various mounting arrangements, and can be configured for drilling in upward orientation.
  • FIG. 1 illustrates a perspective view of a drill head in accordance with one aspect of the present invention.
  • FIG. 2A illustrates a cross-sectional view of the drill head of FIG. 1 in high gear in accordance with one aspect of the present disclosure.
  • FIG. 2B illustrates a transparent perspective view of a drill head of FIG. 2A.
  • FIG. 3A illustrates a cross-sectional view of a drill head of FIG. 1 in neutral gear.
  • FIG. 3B illustrates a transparent perspective view of a gearbox of FIG. 3 A.
  • FIG. 4A illustrates across-sectional view of the drill head of FIG.1 in low gear.
  • FIG. 4B illustrates a transparent perspective view of a gearbox of FIG. 4A.
  • FIG. 5 illustrates a perspective view of a shifter fork in accordance with one aspect of the present disclosure.
  • aspects of the present disclosure provide systems, methods, and apparatus for shifting gears of a drill head.
  • the present disclosure relates to a system that can allow engagement and disengagement of low and high gears with a single shift movement, which can improve mechanical robustness for deep-hole drilling applications.
  • a single shift movement can eliminate or reduce the possibility of improper disengagement and/or engagement of the gears.
  • at least one of a drill head and a gearbox can be configured to provide for automation of the shifting process.
  • a drill head and/or gearbox configured for automated shifting can enable an operator to shift gears remotely, thereby further reducing the possibility of operator error and potential damage to equipment.
  • the system can be configured for a range of different torque output, can have various mounting arrangements, and can be configured for drilling in an upward orientation.
  • At least one aspect of the present disclosure can comprise a power transmission system configured to shift gears via a single linear or axial motion of an actuator.
  • a power transmission system configured to shift gears via a single linear or axial motion of an actuator.
  • Such a system can simplif shifting between gears and, consequently, can reduce likelihood of human error or machine failure associated with shifting between gears.
  • a system also has a reduced size as compared with conventional gearboxes used on drill heads. Size reduction can increase versatility and operability of the drill head that employs such a system.
  • the power transmission system can also comprise a manual or automated shifting mechanism.
  • the single shift or single motion gear change can comprise an improved mechanism for incorporating an automated shifting mechanism.
  • the automated shifting mechanism can result in improved reliability thereof.
  • the single motion gear change within the power transmission system can lead to improved reliability of the system.
  • FIG. 1 illustrates a first aspect of a drill head 100 comprising a power transmission system 110, a drive shaft 120, and a drive source 130.
  • the power transmission system 1 10 can operatively connect to the drive shaft 120 such that the power transmission system 110 can transmit rotation from the drive source 130 to the drive shaft 120.
  • the power transmission system 110 can be configured operate at various speeds, and can allow an operator to adjust the rotation transferred to the drive shaft 120.
  • the power transmission system 110 can have a high gear and a low gear, where the high gear can transfer higher rate of rotational speed to the drive shaft 120 than the low gear.
  • the power transmission system 110 can comprise a gearbox 140 and a gear shifting system (not shown).
  • the gear shifting system can cause a change in gear selection within the gearbox 140— i.e., the gear shifting system can cause the gearbox 140 to shift into a low gear thereby converting the input RPM to a lower output RPM (and higher torque).
  • the gear shifting system can actuate the change from the low gear to the high gear, and vice versa, in a single motion.
  • the power transmission system 110 can comprise at least one input end and at least one output end.
  • At least one drive source 130 e.g., hydraulic or electric motors
  • the power transmission system 110 can convert the input RPM into an output RPM that the power transmission system 110 can output at the one or more output ends.
  • the gearbox 140 can be operatively coupled to the drive shaft 120.
  • the drive source 130 can couple to a top portion of the gearbox 140 through a drive source adapter 132.
  • the gearbox 140 can have an output gear 150 that can be operatively coupled to and drive an input gear 160 of the drive shaft 120.
  • the output gear 150 can be operatively coupled to a freely spinning gear 170 that, in turn, can mesh the input gear 160.
  • the gearbox 140 and/or the drive shaft 120 can further comprise an enclosure or housing.
  • the gearbox 140 can have a housing 180 configured to house various components of the gearbox 140.
  • the housing 180 can protect the moving elements of the gearbox 140 from the surrounding environment and can also protect the operator from injury by the moving elements of the gearbox 140.
  • the drive shaft 120 can have a housing 190 operable to house the internal elements of the drive shaft 120 and protect such elements from the surrounding environment as well as the operator from injury by the moving elements within the drive shaft 120.
  • the gearbox 140 comprises a first hollow shaft 200 and a second hollow shaft 210.
  • the first and second hollow shafts 200, 210 can be configured to rotate independently and freely if not engaged.
  • the first and second hollow shafts 200, 210 can also be configured to rotate in unison, if coupled by an upper coupler or collar 220, as further described below.
  • bearings 230a and 230b can be rotatably secured the first hollow shaft 200 to the housing 180 to accommodate rotation.
  • bearings 230c and 230d can be rotatably secured the second hollow shaft 210 within the housing 180.
  • the housing 180 can secure the bearings 230a, 230b, 230c, 230d with, for example and without limitation, clamps, channels, gibs, and the like.
  • the housing 180 can further comprise integrated bearings 230a, 230b, 230c, 23 Od, such as, for example and without limitation, integrated journal bearings, outer rings of a ball bearing and the like.
  • a single bearing can be used to restrain the first hollow shaft 200 and a single bearing to restrain second hollow shaft 210.
  • the first and second hollow shafts 200, 210 can be restrained from axial (or lateral) movement with respect to the housing and permitted to rotate within the housing 180.
  • the first hollow shaft 200 can have the output gear 150 secured thereto.
  • the output gear 150 can be secured to the first hollow shaft 200 such that the output gear 150 can be fixed and can rotate only together with the first hollow shaft 200.
  • the output gear 150 can connect to the first hollow shaft 200 in a manner that can allow the output gear 150 and the first hollow shaft 200 to rotate independently of one another in the event a predetermined amount of torque is applied to the connection therebetween.
  • a torque limiter can be installed between the output gear 150 and first hollow shaft 200, which can prevent damage to the output gear 150 and/or to the first hollow shaft 200 from excessive torque.
  • a drive rod 240 can be configured to engage the first hollow shaft 200 and transfer rotation from the drive source 130 to the first hollow shaft 200.
  • the first hollow shaft 200 can also have an internal spline section 202 that can be configured to engage a corresponding section of the external spline on the drive rod 240.
  • the drive rod 240 can have an external spline section that can engage an internal spline of the drive source 130.
  • the drive rod 240 can have an internal spline section that can engage an external spline of the drive source 130.
  • other connections can be used that can allow the drive rod 240 to move axial ly with respect to the drive source 130 such as, for example and without limitation, mating square sections, mating teethed sections and the like.
  • the drive rod 240 can be configured to move axially with respect to the drive source 130.
  • a lower-shift connector 250 can be configured to couple to the first hollow shaft 200such that movement of the lower-shift connector 250 can result in corresponding axial movement of the drive rod 240 as further described below.
  • placing the lower-shift connector 250 into a first position can correspondingly place the drive rod 240 into a first position, as illustrated in Figures 2 A and 2B.
  • the drive rod 240 can comprise multiple spline sections, which can be configured to engage mating splines of various elements within the gearbox 140.
  • the drive rod 240 can have at least one recessed regions separating the spline sections from adjacent spline sections.
  • the drive rod 240 can comprise a lower drive spline section 242a that can be configured to engage a mating internal spline section 202 of the first hollow shaft 200.
  • the lower drive spline section 242a can engage the internal spline section 202 of the first hollow shaft 200.
  • the drive rod 240 when the drive rod 240 is in the first position, the drive rod 240 can be configured to transmit power (i.e., rotation) from the drive source 130 to the first hollow shaft 200, which can, in turn, transmit power to the drive shaft 120.
  • the gearbox 140 can comprise at least a high gear and a low gear.
  • the gearbox 140 can be in high gear when the output end of the gearbox MOispower powered directly by the drive source 130.
  • the gearbox 140 can be in high gear and can transfer power directly from the drive source 130 to the output end (e.g., the output gear 150) of the gearbox 140.
  • the drive rod 240 can further comprise one or more recesses that can abut or surround the spline sections.
  • the drive rod 240 can have recesses 244a, 244b on both sides of the lower drive spline section 242a.
  • the drive rod 240 can move in an axial direction to disengage the lower drive spline section 242a from the internal spline section 202 of the first hollow shaft 200.
  • the lower-shift connector 250 can move the drive rod 240 in an axial direction such that the drive rod 240 is no longer coupled to the first hollow shaft 200.
  • the lower-shift connector 250 can be configured to move the drive rod 240 to a second position, as illustrated in Figures 3A and 3B.
  • the second position at least a portion of the recess 244b of the drive rod 240 can approximately align with the internal spline section 202 of the first hollow shaft 200.
  • the drive rod 240 can be disengaged from the first hollow shaft 200, and no power (or rotation) can be transferred to the drive shaft 120 from the drive source 130.
  • the gearbox 140 in the second position, can be in a neutral gear. When the gearbox 140 is in a neutral gear, the gearbox 140 can be configured to transfer no power or rotation from the drive source 130 to the output end of the gearbox 140.
  • the drive rod 240 can also be configured to engage a planetary gear system 260, which, in turn, can be configured to transmit power and rotation to the second hollow shaft 210.
  • the planetary gear system 260 can comprise a sun gear 262, one or more planet gears 264, and an outer ring 266.
  • the planetary gear system 260 can further comprise a planet carrier 268, which can be configured to connect one or more planet gears 264 within the planetary gear system 260.
  • the sun gear 262 can be configured to transmit motion to the planet gears 264.
  • the planet gears 264 can transmit motion to the outer ring 266 and/or to the planet carrier 268.
  • the planetary gear system 260 can be configured to act as a reducer and reduce the number of RPM from the drive source 130.
  • the drive source 130 can transmit power to the sun gear 262 that can further transmit the power to the outer ring 266 or planet carrier 268, thereby reducing the RPM from the drive source 130.
  • the drive source 130 can couple to the outer ring 266 or planet carrier 268, thereby transmitting power through the outer ring 266 or planet carrier 268 to the sun gear 262, which can increase the output RPM.
  • the outer ring 266 can be configured to couple to or be incorporated into the housing 180 such that the outer ring 266 is stationary with respect to the drive source 130 and the drive rod 240.
  • the drive rod 240 can couple to or engage the sun gear 262 and transmit power and rotation from the drive source 130 to the sun gear 262.
  • the sun gear 262 can also transmit power to the planet carrier 268 through the one or more planet gears 264. In operation, when the drive rod 240 couples to or engages the sun gear 262, the drive rod 240 and the sun gear 262 can transmit power and rotation from the drive source 130 to the planet carrier 268.
  • the planet carrier 268 can be coupled to the second hollow shaft 210.
  • planet carrier 268 (and the planetary gear system 260) can be configured to transmit motion from the sun gear 262 onto the second hollow shaft 210.
  • the planetary gear system 260 can transmit power and rotational motion from the drive source 130 to the second hollow shaft 210.
  • the drive rod 240 can comprise an upper drive spline section 242b that can mate with and engage an internal spline in the sun gear 262.
  • the drive rod 240 can be configured to transmit power and rotation from the drive source 130 to the sun gear 262.
  • the lower-shift connector 250 can be configured to move the drive rod 240 axially. Accordingly, as illustrated in Figures 4 A and 4B, the lower-shift connector 250 can move the drive rod 240 into a third position such that the upper drive spline section 242b of the drive rod 240engages the internal spline of the sun gear 262. In operation, in the third position, the drive rod 240 can transmit power and rotational motion from the drive source 130 through the planetary gear system 260 onto the second hollow shaft 210.
  • the internal spline sections ofthe first hollow shaft 200 and the sun gear 262 can comprise symmetrical or asymmetrical teeth that can be configured to correspond with external spline section of the drive rod 240.
  • the spline sections can have teeth that have one angle on a first side of each tooth and a second, different angle on an opposite side.
  • the internal spline section 202 can have the same or substantially the same first and second angles on both sides of the teeth.
  • the first hollow shaft 200 and the second hollow shaft 210 can be configured to rotate independently when not engaged with each other. It is contemplated that, when the drive rod 240 engages the sun gear 262 of the planetary gear system 260 and, thereby, transmits power from the drive source 130 to the second hollow shaft 210, the first hollow shaft 200 can remain stationary unless engaged with the second hollow shaft 210. It is further contemplated that, when the first hollow shaft 200 remains stationary, the first hollow shaft 200 cannot transmit power or rotation to the drive shaft 120.
  • the gearbox 140 can further comprise a separator bushing 270.
  • the separator bushing 270 can be operable to separate the first hollow shaft 200 and second hollow shaft 210.
  • the separator bushing 270 can include a cylindrical portion that can fit into a hollow portion of the first or second hollow shaft 200, 210, and a flange that can separate ends of the first hollow shaft 200 and the second hollow shaft 210.
  • the separator bushing 270 ca act as a thrust bearing and/or can prevent the ends of the first hollow shaft 200 and second hollow shaft 210 from rubbing against each other, binding, and/or galling, when the first hollow shaft 200 or the second hollow shaft 210 rotate independently of one another.
  • the upper coupler 220 can be configured to engage the first hollow shaft 200 and the second hollow shaft 210 such that the second hollow shaft 210 can transmit rotation to the first hollow shaft 200 which can, in turn, transmit rotation to the drive shaft 120.
  • respective ends of the first hollow shaft 200 and second hollow shaft 210 can have external gears secured thereto or incorporated therewith.
  • the upper coupler 220 can have at least one internal gear that can mate with the external gears of the first hollow shaft 200 and second hollow shaft 210. In operation, when the upper coupler 220 engages the respective gears on the ends of the first hollow shaft 200 and second hollow shaft 210, the first hollow shaft 200 and second hollow shaft 210 can rotate in unison.
  • first hollow shaft 200 and second hollow shaft 210 can have a locking taper (e.g., a Morse taper) that can mate with a matching taper of the upper coupler 220 or the like.
  • the upper coupler 220 can also have internal and external portions that can move with respect to each other.
  • the internal portion can comprise of multiple floating leafs, made from a material with relatively high coefficient of friction on a surface that can come into contact with the ends of the first and second hollow shafts 200, 210.
  • the internal portion can have a taper on a surface that can come into contact with the external portion of the upper coupler 220.
  • the external portion can be configured to have a matching taper, which can force the leafs of the internal portion against the ends of the first hollow shaft 200 and second hollow shaft 210, thereby coupling the first and second hollow shafts 200, 210.
  • drive dogs can be used to mate the first hollow shaft 200 and second hollow shaft 210.
  • the gearbox 140 can further comprise an upper-shift connector 280.
  • the upper-shift connector 280 can be configured to engage the upper coupler 220 and move the upper coupler 220 such that the upper coupler 220 can couple and decouple the first hollow shaft 200 and the second hollow shaft 210.
  • the upper-shift connector 280 can move the upper coupler 220 toward the drive source 130, thereby disengaging the internal gear of the upper coupler 220 from the external gear on the end of the first hollow shaft 200 and/or external gear on the end of the second hollow shaft 210.
  • the upper-shift connector 280 can move the upper coupler 220 away from the drive source 130, such that upper coupler 220 can couple the first hollow shaft 200 and the second hollow shaft 210.
  • the gearbox 140 can further comprise a link 151 ( Figures 2B, 3B, 4B) configured to couple the lower-shift connector 250 and upper-shift connector 280, such that the lower and the upper-shift connectors 250, 280 can move in unison.
  • a link 151 Figures 2B, 3B, 4B
  • the lower-shift connector 250 can urge the drive rod 240 to the first position
  • the upper-shift connector 280 can urge the upper coupler 220 to the first position.
  • the lower-shift connector 250 and upper-shift connector 280 can urge the drive rod 240 to the second or third position and the upper-shift connector 280 can urge the upper coupler 220 to the second or third position, respectively.
  • the lower-shift connector 250 and upper-shift connector 280 can shift the gearbox 140 into the high gear, as described above.
  • the lower-shift connector 250 and upper-shift connector 280 can shift the gearbox 140 into the neutral gear.
  • the lower-shift connector 250 and upper-shift connector 280 can shift the gearbox 140 into the low gear.
  • the lower-shift connector 250 and upper- shift connector 280 can be coupled to a gear shifting system.
  • shifting between the first, second, and third positions can occur while the drive rod 240, the first hollow shaft 200, and/or second hollow shaft 210 rotate within the gearbox 140.
  • the upper coupler 220 can begin to engage and couple the first hollow shaft 200 and second hollow shaft 210 while the former and/or the latter rotate independently of one another.
  • the drive rod 240 can begin to engage the internal spline section 202 of the first hollow shaft 200 as well as the sun gear 262 of the planetary gear system 260 as the drive rod 240, first hollow shaft 200, and/or sun gear 262 rotate independently of one another.
  • the upper coupler 220 can be configured to engage and/or disengage the first and second hollow shafts 200, 210 independently of the drive rod 240 engaging and/or disengaging the sun gear 262 or the first hollow shaft 200. In operation, shifting between gears can occur irrespective of alignment between various moving components within the gearbox 140.
  • the lower-shift connector 250 (and similarly the upper-shift connector 280) further comprises spring-loaded elements 290.
  • the spring-loaded elements 290 can allow the lower-shift connector 250 and upper-shift connector 280 to move independently of each other while applying pressure in a direction of movement.
  • the spring-loaded elements 290 can operate to permit shifting between gears while various elements of the gearbox 140 rotate independently of one another.
  • the gear shifting system can move the lower-shift connector 250 and/or upper-shift connector 280 into the first, second, and/or third position while the first hollow shaft 200, second hollow shaft 210, upper coupler 220, drive rod 240, and/or sun gear 262 (as applicable) are disengaged.
  • the spring-loaded elements 290 of the lower and upper-shift connectors 250, 280 can operate to limit the amount of force applied at engagement interfaces of the drive rod 240 and internal spline section 202 and the spline section of the sun gear 262 as well as at the engagement interface of the upper coupler 220 and the end of the first hollow shaft 200, which can improve reliability of the gearbox 140 and reduce wear and tear of the elements thereof.
  • the lower-shift connector 250 when the lower and upper-shift connectors 250, 280 move from the second position to the third position, the lower-shift connector 250 can urge the drive rod 240 from the second position to the third position.
  • the sun gear 262 can have rotational movement at an instance when the lower-shift connector 250 urges the upper drive spline section 242b of the drive rod 240 into the internal spline of the sun gear 262.
  • the upper drive spline section 242b can not immediately engage the spline of the sun gear 262.
  • the spring-loaded elements 290 can allow the lower-shift connector 250 to deflect (as the gear shifting system shifts the lower-shift connector 250 into the third position) and apply force onto the drive rod 240 until the upper drive spline section 242b of drive rod 240 aligns with and engages the spline of the sun gear 262.
  • the spring-loaded elements 290 of the lower- shift connector 250 can be configured apply continuous force onto the drive rod 240 until the lower drive spline section 242a engages the internal spline section 202 of the first hollow shaft 200 when the gear shifting system moves the lower-shift connector 250 into the first position.
  • the spring-loaded elements of the upper shift connector 280 can apply continuous force onto the upper coupler 220 when the upper-shift connector 280 shifts to the third position, until the upper coupler 220 moves to the third position.
  • the spring-loaded elements of the upper-shift connector 280 can press the upper coupler 220 against the gear on the end of the first hollow shaft 200 (while the first hollow shaft 200 rotates) until the gear of the upper coupler 220 aligns with and engages the gear on the end of the first hollow shaft 200.
  • the upper coupler 220 in the third position the upper coupler 220 can engage and/or couple the ends of the first hollow shaft 200 and second hollow shaft 210 such that the second hollow shaft 210 can transfer rotation to the first hollow shaft 200.
  • the first hollow shaft 200, the second hollow shaft 210, and the sun gear 262 can be configured to rotate independently.
  • the spring loaded elements can allow engagement of the first hollow shaft 200 (and coupling to the second hollow shaft 210) by the upper coupler 220 independent of the engagement of the drive rod 240 and the sun gear 262.
  • the gearbox 140 can shift into the low gear by first engaging the drive rod 240 and the 262 of the planetary gear system 260, and subsequently, couple to the first and second hollow shafts 200, 210 by the upper coupler 220, or vice versa.
  • the gearbox 140 can also shift into the low gear by, first, coupling the first and second hollow shafts 200, 210 with the aid of the upper coupler 220, and then engaging the drive rod 240 and the 262 of the planetary gear system 260.
  • the upper coupler 220 can be configured to disengage the end of the first hollow shaft 200 independently of the drive rod 240 disengaging the sun gear 262.
  • the spring-loaded elements can help engage the gears, in at least one aspect, the spring-loaded elements can be configured to not provide positioning during disengagement.
  • the drill head can include positive disengagement and spring-loaded engagement.
  • the above-described components of the gearbox 140 can be configured to align in a substantially linear manner.
  • the drive source 130 such as a hydraulic motor
  • the drive source 130 can be configured to couple to a top portion of the gearbox 140.
  • a hydraulic motor can be coupled to a bottom portion of the gearbox 140 (e.g., by coupling the hydraulic motor to a bottom portion of the drive rod 240).
  • two drive sources 130 can be coupled to the gearbox 140 (e.g., one to the top portion and another to the bottom portion of the gearbox) which can, individually or in parallel, power and rotate the drive rod 240.
  • the gearbox 140 can be configured to shift from the first to the third position (and vice-versa) in a single or one-directional motion.
  • gearbox 140 can be configured to shift from the first to the third position (and vice-versa) in a single or one-directional motion.
  • automated gears shifting systems can be more reliable and durable than commercially-available alternatives.
  • a manual gear shifting system embodying one-directional shifting can also improve reliability and durability of the gearbox 140 by reducing possibility of operator error.
  • the progressive dual shift design of the drill head 100 can allow the upper coupler or collar 220 and drive rod 240 to move at the same time.
  • the shift connectors 250, 280 can be interconnected by a common shift linkage 151.
  • the top shift connector 280 can be configured to move the upper coupler or collar 220 and the lower shift connector 250 configured to move the drive rod 240.
  • the shift connectors 250, 280 can be independently sprung to allow the shift to be completed regardless of spline engagement.
  • the two shifts can be timed to allow the upper coupler or collar 220 to start to engage after the drive rod 240 shift is partially engaged.
  • the lower shift shaft can comprise a lower fork split into two pieces configured to allow the two shift mechanisms to move independently against the springs.
  • a special chisel tooth asymmetrical spline pointing can be provided to increase the aggressiveness of spline engagement during the shift.
  • speed of rotation during spring loaded engagement can allow the engagement to occur without damage.
  • the drill head 100 can operate as a top drive or a spindle drive; can be shifted from high to low range manually or remotely from the driller's control station; can keep the drill operator away from the drill string; can be configured for a top or bottom mount motor; can be configured for higher or lower torque output; can be scaled up or down, can be configured for multiple mounting arrangements; can be configured to drill up holes; and can improve overall mechanical robustness for deeper hole applications.
  • Figures 1-5 provide a number of different components and mechanisms for apparatus and systems for changing the gear ratio of a drill head.
  • implementations described herein can also be described in terms acts and steps in a method for accomplishing a particular result. For example, a method comprising engaging or disengaging gears associated with a drill head with a single shift movement is described concurrently above with reference to the components and diagrams of Figures 1 through 6.
  • a one shift input shaft can allow the gearbox to be shifted with a single shift device (rather than two independent devices) such as, for example and without limitation, a hydraulic actuator, pneumatic actuator, manual actuated lever or the like.
  • one shift input can reduce or eliminate the possibility of operator error and resultant damage to the gearbox by having either shift mechanism in the wrong position when power is applied.
  • one shift input can enable automation of the shifting process.
  • the shift interconnecting linkage can be located inside the drill head to reduce damage during the drilling process and facilitate ease of installation on multiple drill rigs.
  • Both upper and lower shift forks can be spring loaded to allow one or the other shift to occur independently if spline alignment of the other is not possible; allow the external shift actuator to achieve full stroke and lock with either spline disengaged; allow the shift to be automatically completed as the drive rod rotates with a spline disengaged and loaded against a spring; to limit the max force on the engaging splines reducing spline damage and limiting the load seen by the roll pins securing the shift forks to the shift shafts; and to reduce engagement time by snapping the splined component into place quickly as the splines rotate into position.

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Abstract

Des réalisations de la présente invention portent sur un système et sur un appareil pour augmenter et diminuer la vitesse et le couple transférés à un arbre d'entraînement à partir d'une source d'entraînement. En particulier, la présente invention porte sur un système qui permet la prise et le désengagement de vitesses basse et élevée avec un dispositif de changement de vitesse unique qui peut se déplacer dans une direction unique pour effectuer un changement entre les vitesses.
PCT/US2012/072106 2012-01-11 2012-12-28 Tête de forage à arbre double progressive et ses systèmes et ses procédés WO2013106207A1 (fr)

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US201261585576P 2012-01-11 2012-01-11
US61/585,576 2012-01-11

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Cited By (1)

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