WO2012162408A1 - Système de moteur à boue - Google Patents

Système de moteur à boue Download PDF

Info

Publication number
WO2012162408A1
WO2012162408A1 PCT/US2012/039172 US2012039172W WO2012162408A1 WO 2012162408 A1 WO2012162408 A1 WO 2012162408A1 US 2012039172 W US2012039172 W US 2012039172W WO 2012162408 A1 WO2012162408 A1 WO 2012162408A1
Authority
WO
WIPO (PCT)
Prior art keywords
entitled
mud motor
drilling
motor assembly
mud
Prior art date
Application number
PCT/US2012/039172
Other languages
English (en)
Inventor
William Banning Vail, Iii
Original Assignee
Smart Drilling And Completion
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
Priority claimed from US13/506,887 external-priority patent/US9051781B2/en
Application filed by Smart Drilling And Completion filed Critical Smart Drilling And Completion
Priority to CA2837082A priority Critical patent/CA2837082C/fr
Priority to EP12789232.1A priority patent/EP2715031B1/fr
Publication of WO2012162408A1 publication Critical patent/WO2012162408A1/fr

Links

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
    • E21B4/02—Fluid rotary type drives
    • 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
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/20—Driving or forcing casings or pipes into boreholes, e.g. sinking; Simultaneously drilling and casing boreholes
    • E21B7/201—Driving or forcing casings or pipes into boreholes, e.g. sinking; Simultaneously drilling and casing boreholes with helical conveying means
    • E21B7/203—Driving or forcing casings or pipes into boreholes, e.g. sinking; Simultaneously drilling and casing boreholes with helical conveying means using down-hole drives

Definitions

  • Provisional Patent Application Serial. No. 61/189,253 was erroneously referenced as Serial. No. 60/ . . . within Provisional Patent Application Serial. No. 61/270,709 and within Provisional Patent Application No. 61/274,215 mailed to the USPTO on Aug. 13, 2009, and these changes are noted here, and are incorporated by herein by reference. Entire copies of the cited Provisional Patent Applications are incorporated herein by reference unless they present information which directly conflicts with any explicit statements in the application herein.
  • the term “smart shuttle” will be capitalized as “Smart Shuttle”; the term “well locomotive” will be capitalized as “Well Locomotive”; the term “downhole rig” will be capitalized as “Downhole Rig”; the term “universal completion device” will be capitalized as “Universal Completion Device”; and the term “downhole bop” will be capitalized as “Downhole BOP”.
  • the Universal Drilling and Completion SystemTM is comprised of the Universal Drilling MachineTM and the Universal Completion MachineTM.
  • UDCSTM is the trademarked abbreviation for the Universal Drilling and Completion System.
  • UDMTM is the trademarked abbreviation for the Universal Drilling MachineTM.
  • UCMTM is the trademarked abbreviation for the Universal Completion MachineTM.
  • the Leaky SealTM, The Force SubTM and The Torque SubTM are used in various embodiments of these systems and machines.
  • the Mud Motor Apparatus described herein is now called the Mark IV Mud MotorTM for commercial purposes.
  • the general field of the invention relates to the drilling and completion of wellbores in geological formations, primarily in the oil and gas industries.
  • Typical rotary drilling systems may be used to drill oil and gas wells.
  • a surface rig rotates the drill pipe attached to the rotary drill bit at depth. Mud pressure down the drill pipe circulates through the bit and carries chips to the surface via annular mud flow.
  • a mud motor may be placed at the end of a drill pipe, which uses the power from the mud flowing downhole to rotate a drill bit. Mud pressure still carries chips to the surface, often via annular mud flow.
  • Typical mud motors as presently used by the oil and gas industry are based upon the a progressing cavity design, typically having a rubber type stator and a steel rotor. These are positive displacement devices that are hydraulically efficient at converting the power available from the mud flow into rotational energy of the drill bit. These devices convert that energy by having an intrinsically asymmetric rotor within the stator cavity - so that following pressurization with mud, a torque develops making the rotor spin. These devices also generally have tight tolerance requirements.
  • An object of the invention is to provide a long-lasting mud motor assembly that may be used in applications where progressing cavity mud motors are presently used.
  • Another object of the invention is to provide a long-lasting mud motor assembly that continues to function even when its internal parts undergo significant wear. Another object of the invention is to provide a long-lasting mud motor assembly that is primarily made from all-metal parts.
  • Another object of the invention is to provide a long-lasting mud motor assembly having internal parts that have relatively loose tolerances that are therefore relatively inexpensive to manufacture.
  • Another object of the invention is to provide a long-lasting mud motor assembly that is primarily made from all-metal, relatively loosely fitting parts that operates at temperatures much higher than the operational temperatures of typical progressing cavity type mud motors.
  • Another object of the invention is to provide a long-lasting mud motor assembly having loosely fitting internal parts that allows relatively small amounts of pressurized mud to leak through these loosely fitting internal parts.
  • Another object of the invention is to provide a long-lasting mud motor assembly having at least one loosely fitting internal piston within a cylindrical housing that forms a leaky seal that allows a predetermined mud flow through the leaky seal during operation.
  • Another object of the invention is to provide a long-lasting mud motor assembly that produces more power per unit length than standard progressing cavity mud motors.
  • Yet another object of the invention is to provide a mud motor assembly having a drive shaft that rotates concentrically about an axis of rotation.
  • Another object of the invention is to provide a mud motor assembly that does not require a wiggle rod to compensate for eccentric motion of internal parts.
  • a mud motor apparatus (12) possessing one single drive shaft (20) that turns a rotary drill bit (70), which apparatus is attached to a drill pipe (486) that is a source of high pressure mud (14) to said apparatus, wherein said drive shaft (20) receives at least a first portion (494) of its rotational torque from any high pressure mud (492) flowing through a first hydraulic chamber (84) within said apparatus, and said drive shaft (20) receives at least a second portion (498) of its rotational torque from any high pressure mud (496) flowing through a second hydraulic chamber (98) within said apparatus.
  • a method is provided to provide torque and power to a rotary drill bit (70) rotating clockwise attached to a drive shaft (20) of a mud motor assembly (12) comprising at least the following steps: a. providing relatively high pressure mud (14) from a drill pipe (486) attached to an uphole end of said mud motor assembly (484);
  • said first ratchet means (30) is comprised of a first pawl (40) that is flexibly attached by a first torsion rod spring (350) and second torsion rod spring (352) to said first crankshaft (22), and first pawl latch (44) that is an integral portion of the drive shaft (20).
  • said second ratchet means (48) is comprised of a second pawl (58) that is flexibly attached by third torsion rod spring (504) and fourth torsion rod spring (506) to said second crankshaft (26), and second pawl latch (62) that is an integral portion of the drive shaft (20).
  • said first control means is comprised of a first pawl lifter means (46) that is an integral portion of the drive shaft (20) that lifts said first pawl (40) in a first fixed relation to said drive shaft (20).
  • said second control means is comprised of a second pawl lifter (64) means that is an integral portion of the drive shaft (20) that lifts said second pawl (58) in a second fixed relation to said drive shaft.
  • said first pawl lifter means (46) disengages said first pawl (40) from said first pawl latch (44), so that first torsion spring (78) returns first crankshaft (22) in a counter-clockwise rotation to its initial starting position completing a first power stroke and first return cycle for said first crankshaft (22) while said drive shaft (20) continues to rotate clockwise unimpeded by the return motion of said first crankshaft (Figure 9 J and Figure 16B).
  • said second pawl lifter means (64) disengages said second pawl (58) from said second pawl latch (62), so that second torsion spring (92) returns second crankshaft (26) in a counter-clockwise rotation to its initial starting position completing a second power stroke and second return cycle for the second crankshaft (26) while said drive shaft (20) continues to rotate clockwise unimpeded by the return motion of said second crankshaft (508 and 510).
  • the first torsional energy stored in said first torsion return spring (78) at the end of said first power stroke is obtained by said first crankshaft (22) twisting said first torsion return spring (78) during said first power stroke ( Figures 9, 9A, 9B,9C, 9D, 9E, 9F,and 9G).
  • the second torsional energy stored in said second torsion return spring (92) at the end of said second power stroke is obtained by said second crankshaft 26 twisting said second torsion return spring (92) during said second power stroke (502).
  • said first power stroke and said second power stroke are repetitiously repeated so that torque and power is provided to said clockwise rotating drive shaft (20) attached to said drill bit (70), whereby said clockwise rotation is that rotation observed looking downhole toward the top of the rotary drill bit.
  • Figure 1 shows a side view of the Mud Motor Assembly 12.
  • Figure 2 shows regions within the Mud Motor Assembly having Relatively High Pressure Mud Flow (RHPMF) 14. Special shadings are used in Figures 2 and 2 A as discussed in the specification.
  • RHPMF Relatively High Pressure Mud Flow
  • FIG. 2A shows regions within the Mud Motor Assembly having Relatively Low Pressure Mud Flow (RLPMF) 16
  • Figure 3 shows the Housing 18 of the Mud Motor Assembly. Special shadings are used for the series of Figure 3, 4 and 5 drawings as discussed in the specification.
  • Figure 3 A shows the Drive Shaft 20 of the Mud Motor Assembly.
  • FIG. 3B shows Crankshaft A 22 of the Mud Motor Assembly.
  • FIG. 3C shows Piston A 24 of the Mud Motor Assembly.
  • FIG. 3D shows Crankshaft B 26 of the Mud Motor Assembly.
  • FIG. 3E shows Piston B 28 of the Mud Motor Assembly
  • FIG. 3F shows Ratchet Assembly A 30 of the Mud Motor Assembly.
  • FIG. 3G shows Return Assembly A 32 of the Mud Motor Assembly.
  • FIG. 3H shows Flywheel A 34 of the Mud Motor Assembly.
  • FIG. 3J shows the Raised Guide for Pawl A Capture Pin 36 of the Mud Motor Assembly.
  • Figure 3K shows the Pawl A Capture Pin 38 of the Mud Motor Assembly.
  • FIG. 3L shows Pawl A 40 of the Mud Motor Assembly.
  • Figure 3M shows Drive Pin A 42 of the Mud Motor Assembly.
  • FIG. 3N schematically shows the Pawl A Latch Lobe 44 of the Mud Motor Assembly.
  • FIG. 3P schematically shows the Pawl A Lifter Lobe 46 of the Mud Motor Assembly.
  • FIG 4 shows Ratchet Assembly B 48 of the Mud Motor Assembly.
  • Figure 4 A shows Return Assembly B 50 of the Mud Motor Assembly.
  • Figure 4B shows Flyweel B 52 of the Mud Motor Assembly.
  • FIG. 4C shows the Raised Guide for Pawl B Capture Pin 54 of the Mud Motor Assembly.
  • Figure 4D shows the Pawl B Capture Pin 56 of the Mud Motor Assembly.
  • Figure 4E shows Pawl B 58 of the Mud Motor Assembly.
  • Figure 4F shows Drive Pin B 60 of the Mud Motor Assembly.
  • Figure 4G schematically shows the Pawl B Latch Lobe 62 of the Mud Motor
  • FIG 4H schematically shows the Pawl B Lifter Lobe 64 of the Mud Motor Assembly.
  • Figure 4J shows the Drill Bit Coupler 66 of the Mud Motor Assembly.
  • Figure 4K shows the Drill Pipe 68 of the Mud Motor Assembly.
  • Figure 4L shows the Rotary Drill Bit 70 of the Mud Motor Assembly.
  • Figure 4M shows the Upper, Middle and Lower Main Bearings (respectively numerals 72, 74, and 76 from left-to-right) of the Mud Motor Assembly.
  • Figure 4N shows Return Spring A 78 of the Mud Motor Assembly.
  • Figure 4P shows Intake Valve A 80 of the Mud Motor Assembly.
  • Figure 5 shows the First External Crankshaft A Bearing 82 of the Mud Motor Assembly.
  • Figure 5A schematically shows Chamber A 84 of the Mud Motor Assembly.
  • Figure 5B shows the Internal Crankshaft A Bearing 86 of the Mud Motor Assembly.
  • Figure 5C shows Second External Crankshaft A Bearing 88 of the Mud Motor Assembly.
  • FIG. 5D shows Exhaust Valve A 90 of the Mud Motor Assembly.
  • Figure 5E shows Return Spring B 92 of the Mud Motor Assembly.
  • Figure 5F shows Intake Valve B 94 of the Mud Motor Assembly.
  • Figure 5G shows the First External Crankshaft B Bearing 96 of the Mud Motor Assembly.
  • Figure 5H schematically shows Chamber B 98 of the Mud Motor Assembly.
  • Figure 5 J shows the Internal Crankshaft B Bearing 100 of the Mud Motor Assembly.
  • Figure 5K shows the Second External Crankshaft B Bearing 102 of the Mud Motor Assembly.
  • Figure 5L shows the Exhaust Valve B 104 of the Mud Motor Assembly.
  • Figure 5M shows the Coupler Bearing 106 of the Mud Motor Assembly.
  • FIG. 6 side view of the Mud Motor Assembly 108 which is longitudinally divided into portions shown in Figures 6A, 6B, 6C, 6D, 6E, 6F and 6G.
  • Figure 6A shows an enlarged first longitudinal portion 110 of the Mud Motor Assembly as noted on Figure 6.
  • Figure 6B shows an enlarged second longitudinal portion 112 of the Mud Motor Assembly.
  • Figure 6C shows an enlarged third longitudinal portion 114 of the Mud Motor Assembly.
  • Figure 6D shows an enlarged fourth longitudinal portion 116 of the Mud Motor
  • Figure 6E shows an enlarged fifth longitudinal portion 118 of the Mud Motor Assembly.
  • Figure 6F shows an enlarged sixth longitudinal portion 120 of the Mud Motor Assembly.
  • Figure 6G shows an enlarged seventh longitudinal portion 122 of the Mud Motor Assembly.
  • Figure 7 shows an Isometric View of Hydraulic Chamber S 124 that is a schematic portion of one embodiment of one embodiment of a Mud Motor Assembly.
  • Figure 7A shows an Isometric View of Hydraulic Chamber T 182 that is a schematic portion of one embodiment of one embodiment of a Mud Motor Assembly.
  • Figures 7B shows a end view 238 of Chamber S looking uphole which is Shown Isometically in Figure 7.
  • Figure 7C shows an End View 240 of Chamber T looking uphole which is shown isometrically in Figure 7A.
  • Figure 8 shows the Right-Hand Rule 268 appropriate for the Mud Motor Assembly.
  • Figure 9 shows a cross-section view FF of the Mud Motor Assembly in Figure 6C with Piston A at angle theta of 0 Degrees in the Mud Motor Assembly.
  • Figure 9 A shows Piston A in Position at 30 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9B shows Piston A in Position at 60 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9C shows Piston A in Position at 90 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9D shows Piston A in Position at 120 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9E shows Piston A in Position at 150 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9F shows Piston A in Position at 180 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9G shows Piston A in Position at 210 Degrees in the Mud Motor Assembly at the end of its 100% full strength Power Stroke.
  • Figure 9H shows the various compnents within cross section FF in Figure 6C.
  • Figure 9J shows Piston A during a portion of its Reset Stroke, or its Return Stroke.
  • Figure 9K shows Piston A during a portion of its Power Stroke.
  • Figure 9L shows new positions for previous elements 278 and 280.
  • Figure 10 shows a Cross-Section View of the Housing 18 in the Mud Motor
  • Figure 10A shows a Cross-Section View of Crankshaft A 22 in the Mud Motor Assembly.
  • Figure 10B shows a Cross-Section View of the Internal Crankshaft A Bearing 86 in the Mud Motor Assembly.
  • Figure IOC shows a Cross-Section View of the Drive Shaft 20 in the Mud Motor Assembly.
  • Figure 10D shows a Cross-Section of Piston A 24 in the Mud Motor Assembly.
  • Figure 10E shows a Cross-Section of Backstop A 272 in the Mud Motor
  • Figure 10F shows a Cross-Section of Bypass Tube A-1 274 in the Mud Motor Assembly.
  • Figure 10G shows a Cross-Section of Bypass Tube A-2 276 in the Mud Motor Assembly.
  • Figure 10H shows a Cross-Section of the Drive Port of Chamber A ("DPCHA") 278 in the Mud Motor Assembly.
  • Figure 10J shows a Cross-Section of the Exhaust Port of Chamber A ("EPCHA") 280 in the Mud Motor Assembly.
  • Figure 10K shows a Cross-Section of the Backstop Port of Chamber A ("BPCHA") 282 in the Mud Motor Assembly.
  • BPCHA Backstop Port of Chamber A
  • Figure 10L shows a Cross-Section of the Backstop to Housing Weld 284 in the Mud Motor Assembly.
  • Figure 10M shows a Cross-Section of Piston A to Crankshaft A Weld 286 in the Mud Motor Assembly.
  • Figure 11 shows the Basic Component Dimensions for a preferred embodiment of the Mud Motor Assembly having an OD of 6 1/4 Inches.
  • Figure 12 shows an Uphole View of the Upper Main Bearing 72 in the Mud Motor
  • Figure 12A shows a Section View of the Upper Main Bearing 72 in the Mud Motor Assembly.
  • Figure 12B shows an Uphole View of the Middle Main Bearing 74 in the Mud Motor Assembly having passageways .
  • Figure 12C shows a Section View of the Middle Main Bearing 74 in the Mud Motor Assembly.
  • Figure 13 shows a Section View of Installed Return Spring A 78 which is a Portion of Ratchet Assembly A 30 in the Mud Motor Assembly.
  • Figure 13A shows a Perspective View of Return Spring A 78 in the Mud Motor
  • Figure 14 shows a Cross Section View CC of Ratchet Assembly A in the Mud Motor Assembly.
  • Figure 14A shows a cross section portion 354 of Drive Pin A for a Preferred Embodiment of the Mud Motor Assembly Having an OD of 6 1/4 Inches.
  • Figure 14B shows a Cross Section View DD of one embodiment of Ratchet Assembly A in the Mud Motor Assembly.
  • Figure 14C shows a Cross Section View EE of one embodiment of Ratchet Assembly A in the Mud Motor Assembly.
  • Figure 14D shows How to Utilize a Larger Drive Pin 364 than that shown in Figure
  • Figure 14E shows an Optional Larger and Different Shaped Drive Pin 370 than in Figure 14C.
  • Figure 14F shows a Cross Section View AA of Ratchet Assembly A in the Mud Motor Assembly.
  • Figure 14G shows an Uphole View of Flywheel A and Raised Guide for Pawl A Capture Pin in Section BB of Ratchet Assembly A Showing Sequential Movement of Pawl A Capture Pin in the Mud Motor Assembly.
  • Figure 15 shows one embodiment of the Pawl A Latch Lobe 44 Fully Engaged With Pawl A 40 at mating position 376 in the Mud Motor Assembly.
  • Figure 15A shows one embodiment of the Pawl A Latch Lobe 44 Completely Disengaged From Pawl A 40 in the Mud Motor Assembly.
  • Figure 15B shows an Optional Slot 378 Cut in Pawl A 40 to Make Torsion Cushion at mating position 376 During Impact of Pawl A Latch Lobe in the Mud Motor Assembly.
  • Figure 16 shows the Pawl A Lifter Lobe at theta of 0 Degrees in the Mud Motor Assembly.
  • Figure 16A shows the Pawl A Lifter Lobe at 210 Degrees in the Mud Motor Assembly.
  • Figure 16B shows the Pawl A Lifter Lobe 46 at -90 Degrees and the Partial Return of Pawl A 40 in the Mud Motor Assembly.
  • Figure 17 shows Intake Port A 402 in Intake Valve A 80 Passing theta of 0
  • Figure 17A shows the Intake Port A 402 in Intake Valve A 80 Passing theta of 90 degrees during the Power Stroke of Piston A in the Mud Motor Assembly.
  • Figure 17B shows the Intake Port A 402 in Intake Valve A 80 Passing theta of 180 degrees during the Power Stroke of Piston A in the Mud Motor Assembly.
  • Figure 17C shows the Intake Port A 402 in Intake Valve A 80 Passing theta of 210 degrees during the very end of the Power Stroke of Piston A in the Mud Motor Assembly.
  • Figure 17D shows Intake Port A 402 in Intake Valve A 80 Passing theta of 240 degrees after the Power Stroke of Piston A has ended.
  • Figure 17E shows Intake Port A 402 in Intake Valve A 80 at theta of - 30 Degrees in the Mud Motor Assembly During the Return Stroke of Piston A.
  • Figure 17F shows Intake Port A 402 in Intake Valve A again passing theta of 0 degrees that begins the Power Stroke of Piston A in the Mud Motor Assembly.
  • Figure 18 shows the upper portion of the Bottom Hole Assembly 408 that includes the Mud Motor Assembly 12.
  • Figure 19 shows the downhole portion of the Bottom Hole Assembly 422.
  • FIG 20 shows the Relatively High Pressure Mud Flow (“RHPMF”) through various ports, valves, and channels within the Mud Motor Apparatus.
  • RHPMF Relatively High Pressure Mud Flow
  • FIG 20A shows the Relatively Low Pressure Mud Flow (“RLPMF”) through various ports, valves, and channels within the Mud Motor Apparatus.
  • RPMF Relatively Low Pressure Mud Flow
  • FIG 21 compares the pressure applied to the Drive Port of Chamber B ("DPCHB") to the pressure applied to Drive Port of Chamber A (“DPCHA").
  • Figure 21 A shows that a low pressure PL is applied to the Exhaust Port of Chamber A (“EPCHA”) and to the Exhaust Port of Chamber B (“EPCHB”) during the appropriate Return Strokes.
  • Figure 2 IB shows the relationship between the maximum lift of the tip of the Pawl A Lifter Lobe 394 and the pressure applied to the Drive Port of Chamber A ("DPCHA").
  • Figure 1 shows a side view of the Mud Motor Assembly 12.
  • FIG. 2 shows regions within the Mud Motor Assembly having Relatively High Pressure Mud Flow (RHPMF) 14 designated by the unique shading used only for this purpose defined on the face of Figure 2.
  • RHPMF Relatively High Pressure Mud Flow
  • Figure 2A shows regions within the Mud Motor Assembly having Relatively Low Pressure Mud Flow (RLPMF) 16 designated by the unique shading used only for this purpose defined on the face of Figure 2A.
  • RPMF Relatively Low Pressure Mud Flow
  • Figure 3 shows the Housing 18 of the Mud Motor Assembly.
  • Figure 3 A shows the Drive Shaft 20 of the Mud Motor Assembly.
  • FIG. 3B shows Crankshaft A 22 of the Mud Motor Assembly.
  • FIG. 3C shows Piston A 24 of the Mud Motor Assembly.
  • FIG. 3D shows Crankshaft B 26 of the Mud Motor Assembly.
  • FIG. 3E shows Piston B 28 of the Mud Motor Assembly
  • FIG. 3F shows Ratchet Assembly A 30 of the Mud Motor Assembly.
  • FIG. 3G shows Return Assembly A 32 of the Mud Motor Assembly.
  • FIG. 3H shows Flywheel A 34 of the Mud Motor Assembly.
  • FIG. 3J shows the Raised Guide for Pawl A Capture Pin 36 of the Mud Motor Assembly.
  • Figure 3K shows the Pawl A Capture Pin 38 of the Mud Motor Assembly.
  • FIG. 3L shows Pawl A 40 of the Mud Motor Assembly.
  • Figure 3M shows Drive Pin A 42 of the Mud Motor Assembly.
  • FIG. 3N schematically shows the Pawl A Latch Lobe 44 of the Mud Motor Assembly.
  • FIG. 3P schematically shows the Pawl A Lifter Lobe 46 of the Mud Motor
  • FIG 4 shows Ratchet Assembly B 48 of the Mud Motor Assembly.
  • Figure 4 A shows Return Assembly B 50 of the Mud Motor Assembly.
  • Figure 4B shows Flyweel B 52 of the Mud Motor Assembly.
  • FIG. 4C shows the Raised Guide for Pawl B Capture Pin 54 of the Mud Motor
  • Figure 4D shows the Pawl B Capture Pin 56 of the Mud Motor Assembly.
  • Figure 4E shows Pawl B 58 of the Mud Motor Assembly.
  • Figure 4F shows Drive Pin B 60 of the Mud Motor Assembly.
  • Figure 4G schematically shows the Pawl B Latch Lobe 62 of the Mud Motor Assembly.
  • FIG 4H schematically shows the Pawl B Lifter Lobe 64 of the Mud Motor Assembly.
  • Figure 4J shows the Drill Bit Coupler 66 of the Mud Motor Assembly.
  • Figure 4K shows the Drill Pipe 68 of the Mud Motor Assembly.
  • Figure 4L shows the Rotary Drill Bit 70 of the Mud Motor Assembly.
  • Figure 4M shows the Upper, Middle and Lower Main Bearings (respectively numerals 72, 74, and 76 from left-to-right) of the Mud Motor Assembly.
  • Figure 4N shows Return Spring A 78 of the Mud Motor Assembly.
  • Figure 4P shows Intake Valve A 80 of the Mud Motor Assembly.
  • Figure 5 shows the First External Crankshaft A Bearing 82 of the Mud Motor Assembly.
  • Figure 5 A schematically shows Chamber A 84 of the Mud Motor Assembly.
  • Figure 5B shows the Internal Crankshaft A Bearing 86 of the Mud Motor Assembly.
  • Figure 5C shows Second External Crankshaft A Bearing 88 of the Mud Motor Assembly.
  • FIG. 5D shows Exhaust Valve A 90 of the Mud Motor Assembly.
  • Figure 5E shows Return Spring B 92 of the Mud Motor Assembly.
  • Figure 5F shows Intake Valve B 94 of the Mud Motor Assembly.
  • Figure 5G shows the First External Crankshaft B Bearing 96 of the Mud Motor Assembly.
  • Figure 5H schematically shows Chamber B 98 of the Mud Motor Assembly.
  • Figure 5 J shows the Internal Crankshaft B Bearing 100 of the Mud Motor Assembly.
  • Figure 5K shows the Second External Crankshaft B Bearing 102 of the Mud Motor Assembly.
  • Figure 5L shows the Exhaust Valve B 104 of the Mud Motor Assembly.
  • Figure 5M shows the Coupler Bearing 106 of the Mud Motor Assembly.
  • Figure 6 shows a particular side view of the Mud Motor Assembly 108 which is longitudinally divided into seven portions respectively identified by double-ended arrows meant to designate the particular longitudinal portions appearing in Figures 6A, 6B, 6C, 6D, 6E, 6F and 6G.
  • Figure 6A shows an enlarged first longitudinal portion 110 of the Mud Motor
  • Figure 6B shows an enlarged second longitudinal portion 112 of the Mud Motor Assembly as noted on Figure 6.
  • Cross-sections AA, BB, CC, DD and EE are defined in Figure 6B.
  • Figure 6C shows an enlarged third longitudinal portion 114 of the Mud Motor Assembly as noted on Figure 6.
  • Cross-section CC is defined in Figure 6C.
  • Figure 6D shows an enlarged fourth longitudinal portion 116 of the Mud Motor Assembly as noted on Figure 6.
  • Figure 6E shows an enlarged fifth longitudinal portion 118 of the Mud Motor
  • Figure 6F shows an enlarged sixth longitudinal portion 120 of the Mud Motor Assembly as noted on Figure 6.
  • Figure 6G shows an enlarged seventh longitudinal portion 122 of the Mud Motor Assembly as noted on Figure 6.
  • Figure 7 shows an Isometric View of Hydraulic Chamber S 124 that is a schematic portion of one embodiment of one embodiment of a Mud Motor Assembly. This view is looking uphole. It posses cylindrical housing 126 and integral interior backstop 128 that may be welded to the interior of the housing 126. Piston S 130 is welded to rotating shaft 132 that rotates in the clockwise direction (see the legend CW) looking downhole.
  • Lower plate 134 and upper plate 135 form a hydraulic cavity. Relatively high pressure mud 136 is forced into input port 138, and relatively low pressure mud 140 flows out of the hydraulic chamber through exhaust port 142.
  • the distance of separation 146 between the downhole edge 148 of the cylindrical housing and the uphole face 150 of lower plate 134 results in a gap between these components that generally results in mud flowing in direction 152 during the Power Stroke of Piston S 130.
  • the distance of separation and other relevant geometric details defines of the leaky seal 154. Different distances of separation may be chosen. For example, various embodiments of the invention may choose this distance to be .010, .020, .030 or .040 inches.
  • Rotating shaft 132 is constrained to rotate concentrically within the interior of cylindrical housing 126 by typical bearing assemblies 156 (not shown for brevity) that are suitably affixed to a sp lined shaft (158 not shown), a portion of which slips into sp lined shaft interior 160 through hole 161 in lower plate 134.
  • pressure P136 is applied to input port 138 that causes mud to flow into that input port 138 at the rate of F 136.
  • Typical units of pressure PI 36 are in psi (pounds per square inch) and typical units of mud flow rates F136 into that input port 138 are in gpm (gallons per minute).
  • mud 140 flows out of the exhaust port 142 at the rate of F 140 and at pressure PI 40.
  • leaky seal 154 might be a tight seal and impervious to leakage
  • the flow rate F136 into the Hydraulic Chamber S would then equal the flow rate F140 out of the Hydraulic Chamber S.
  • the horsepower HP 136 delivered to the mud 136 flowing into the input port 138 is given by the following:
  • the horsepower HP 140 delivered to the mud 140 flowing out the exhaust port 142 is given by the following:
  • HP132 HP136 - HP140 - HPFS (Equation 3)
  • HPFS HPMS + HPFS, where HPMS provide the combined mechanical frictional losses and HPF are combined fluid frictional losses in Hydraulic Chamber S, and each of these components, can be further subdivided into individual subcomponents.
  • This rotational power can be used to do work - including providing the rotational power to rotate a drill bit during a portion of the "Power Stroke" of Piston S 130.
  • the rotational speed of the Piston S 130 is given by the volume swept out by the piston as it rotates about the axis of rotating shaft 132. That rotational speed is in RPM, and is defined by RPM 132. If the volume swept out by Piston S due to a hypothetical 360 degree rotation is VPS360, then one estimate of the RPM is given by the following:
  • HP132 HP136 - HP140 - HPFS - HP154 (Equation 5)
  • Hydraulic Chamber S In general, hydraulic cavities are relatively expensive to manufacture. And, close tolerances typically lead to relatively earlier failures - especially in the case of using Hydraulic Chamber S to provide rotational energy from mud flowing down a drill string. The looser the tolerances on the leaky seal, the less expensive, and more prone to long service lives. So, there is a trade-off between loss of horsepower delivered to mud flowing through leaky seal 154 in this one example, and expense and longevity of the related Hydraulic Chamber S.
  • the Hydraulic Chamber S shown in Figure 7 may have many leaky seals.
  • Leaky seal 154 has been described. However, there may be another leaky seal 158 between the analogous seal between the upper edge 162 of housing 126 and the downhole face 164 (not shown) of upper plate 135 (not shown). Yet another leaky seal 168 exists between the outer radial portion of the rotating shaft 170 (not shown) and the inner edge of the backstop 172 (not shown). Yet another leaky seal 174 exists between
  • the mud flow rates associated with these leaky seals 154, 158, 168 and 174 are respectively F154, F158, F168, and F174.
  • the horsepower's consumed by these leaking seals are respectively HP154, HP158, HP168 and HP174.
  • the power delivered to the rotating shaft during the Powered Stroke of Piston is then given by:
  • HP132 HP136 - HP140 - HPFS - HP154 - HP158 - HP168 - HP174
  • the Power Stroke of Piston S 130 is defined as when Piston S is rotating CW as shown in Figure 7. Of course, as shown there, Piston S 130 will eventually rotate through an angle approaching 360 degrees, and will hit the backstop 128. Therefore, to extract further power, Piston S 130 must be "reset” by rotation CCW back to its original starting position. This is called the Reset Stroke of Piston S 130. To provide continuous rotation to a rotating drill bit then requires other features to be described in the following.
  • FIG. 7A shows an Isometric View of Hydraulic Chamber T 182 that is a schematic portion of one embodiment of one embodiment of a Mud Motor Assembly. This view is looking uphole. It posses cylindrical housing 184 and integral interior backstop 186 that may be welded to the interior of the housing 184. Piston T 188 is welded to rotating shaft 190 that rotates in the clockwise direction (see the legend CW) looking downhole. Lower plate 192 and upper plate 193 (not shown) form a hydraulic cavity. Relatively high pressure mud 194 is forced into input port 196, and relatively low pressure mud 198 flows out of the hydraulic chamber through exhaust port 200.
  • the distance of separation 204 between the downhole edge 206 of the cylindrical housing and the uphole face 208 of lower plate 192 results in a gap between these components that generally results in mud flowing in direction 210 during the Power Stroke of Piston T 188.
  • the distance of separation and other relevant geometric details defines of the leaky seal 212.
  • Different distances of separation may be chosen. For example, various embodiments of the invention may choose this distance to be .010, .020, .030 or .040 inches.
  • a close tolerance in one embodiment might be chosen to be .001 inches.
  • a loose tolerance in another embodiment might be chosen to be .100 inches.
  • a loose tolerance in another embodiment might be chosen to be .100 inches.
  • How much mud per unit time F212 flows out of this leaky seal 212 at a given pressure PI 94 of mud flowing into input port 196 is one parameter of significant interest.
  • Rotating shaft 190 is constrained to rotate concentrically within the interior of cylindrical housing 184 by typical bearing assemblies 214 (not shown for brevity) that are suitably affixed to a sp lined shaft (216 not shown), a portion of which slips into sp lined shaft interior 218 through hole 219 in lower plate 192.
  • pressure PI 94 is applied to input port 196 that causes mud to flow into that input port 196 at the rate of F 194.
  • Typical units of pressure PI 94 are in psi (pounds per square inch) and typical units of mud flow rates F194 into that input port 196 are in gpm (gallons per minute).
  • mud 198 flows out of the exhaust port 200 at the rate of F 198 and at pressure PI 98.
  • leaky seal 212 might be a tight seal and impervious to leakage
  • the flow rate F194 into the Hydraulic Chamber T would then equal the flow rate F198 out of the Hydraulic Chamber T.
  • the horsepower HP 194 delivered to the mud 194 flowing into the input port 196 is given by the following:
  • the horsepower HP 198 delivered to the mud 198 flowing out the exhaust port 200 is given by the following:
  • the difference in the two horsepower's is used to provide rotational power to the rotating shaft 190 (HP 190) and to overcome mechanical and fluid
  • HP212 HP 194 - HP 198 - HPFT (Equation 9)
  • HPFT HPMT + HPFT, where HPMT provide the combined mechanical frictional losses HPMT and HPFT are combined fluid frictional losses in Chamber T, and each of these components, can be further subdivided into individual subcomponents.
  • This rotational power can be used to do work - including providing the rotational power to rotate a drill bit during a portion of the "Power Stroke" of Piston T 188.
  • the rotational speed of the Piston T 188 is given by the volume swept out by the piston as it rotates about the axis of rotating shaft 190. That rotational speed is in RPM, and is defined by RPM 190. If the volume swept out by Piston T due to a hypothetical 360 degree rotation is VPT360, then one estimate of the RPM is given by the following:
  • HP190 HP194 - HP198 - HPFT - HP212 (Equation 11)
  • hydraulic cavities are relatively expensive to manufacture. And, close tolerances typically lead to relatively earlier failures - especially in the case of using Hydraulic Chamber T to provide rotational energy from mud flowing down a drill string. The looser the tolerances on the leaky seal, the less expensive, and more prone to long service lives. So, there is a trade-off between loss of horsepower delivered to mud flowing through leaky seal 212 in this one example, and expense and longevity of the related Hydraulic Chamber T.
  • the Hydraulic Chamber T shown in Figure 7A may have many leaky seals.
  • Leaky seal 212 has been described. However, there may be another leaky seal 216 between the analogous seal between the upper edge 220 of housing 184 and the downhole face 222 (not shown) of upper plate 193 (not shown). Yet another leaky seal 226 exists between the outer radial portion of the rotating shaft 228 (not shown) and the inner edge of the backstop 230 (not shown). Yet another leaky seal 232 exists between the outer radial edge of Piston T 234 (not shown) and the inside surface of the housing 236 (not shown).
  • the mud flow rates associated with these leaky seals 212, 216, 226 and 232 are respectively F212, F216, F226, and 232.
  • the horsepower's consumed by these leaking seals are respectively HP212, HP216, HP226 and HP232.
  • the power delivered to the rotating shaft during the Powered Stroke of Piston T is then given by:
  • HP190 HP194 - HP198 - HPFT - HP212 - HP216 - HP226 - HP232
  • the Power Stroke of Piston T 188 is defined as when Piston T is rotating CW as shown in Figure 7A.
  • Piston T 188 will eventually rotate through an angle approaching 360 degrees, and will hit the backstop 186. Therefore, to extract further power, Piston T 188 must be "reset” by rotation CCW back to its original starting position. This is called the Reset Stroke of Piston T 188.
  • To provide continuous rotation to a rotating drill bit then requires other features to be described in the following.
  • Figures 7B shows a end view 238 of Chamber S looking uphole which is Shown Isometically in Figure 7.
  • the other numerals have been previously defined above.
  • Figure 7C shows an End View 240 of Chamber T looking uphole which is shown isometrically in Figure 7A.
  • the other numerals have been previously defined above.
  • a special splined shaft 242 (not shown) with a first splined head 244 (not shown) and a second splined head 246 (not shown) is used to accomplish this goal.
  • This invention is disclosed in detail in Serial No. 61/573,631 This embodiment of the device generally works as follows:
  • first splined head 244 is engaged splined shaft interior 160.
  • first splined head 244 is disengaged from splined shaft interior 160.
  • second splined head 246 is engaged within splined shaft interior 218.
  • second splined head 246 is disengaged within splined shaft interior 218.
  • the single splined shaft having two splined heads shuttles back and forth during the appropriate power strokes to provide continuous rotation of the drive shaft that is suitably coupled to the rotating drill bit.
  • Different methods and apparatus are used to suitably control the motion of the two splined heads.
  • Many methods and apparatus here use hydraulic power for the Return Strokes of the Pistons within the Hydraulic Chambers. This approach, while very workable, requires additional hydraulic passageways within the Hydraulic Chambers to make the hydraulic Return Stokes work.
  • the Mark IV is drives from the 4th fundamental approach to provide continuous rotation of the rotary drill bit by two separate Hydraulic Chambers each having its own Power Stroke and Return Stroke - and which "Free Runs".
  • Typical rotary drilling systems may be used to drill oil and gas wells.
  • a surface rig rotates the drill pipe attached to the rotary drill bit at depth.
  • Mud pressure carries chips to the surface via annular mud flow.
  • a mud motor may be placed at the end of a drill pipe 482 (not shown), which uses the power from the mud flowoing downhole to rotate a drill bit. Mud pressure still carries chips to the surface, often via annular mud flow.
  • Typical mud motors as used by the oil and gas industry are based upon the a progressing cavity design, typically having a rubber stator and a steel rotor. These are positive displacement devices that are hydraulically efficient at turning the power available from the mud flow into rotational energy of the drill bit. These devices convert that energy by having intrinsically asymmetric rotors within the stator cavity - so that following pressurization with mud, a torque develops making the rotor spin. These devices also generally have tight tolerance requirements.
  • mud motors tend to wear out relatively rapidly, requiring replacement that involves tripping the drill string to replace the mud motor. Tripping to replace a mud motor is a very expensive process. In addition, there are problems using these mud motors at higher temperatures.
  • the applicant began investigating motor designs having parts that run concentrically about an axis. If all the parts are truly concentric about a rotational axis, then in principle, there is no difference between right and left, and no torque can develop. However, the applicant decided to investigate if it was possible to make motors that are "almost" positive displacement motors that can be described as "quasi-positive displacement motors" which do develop such torque.
  • the Mark IV Mud Motor is one such design. It runs about a concentric axis. However, the existence of leaky seals within its interior means that it is not a true positive displacement mud motor.
  • leaky seals leak about 10% of the fluid from within a hydraulic chamber to the mud flow continuing downhole without imparting the energy from the leaked fluids to the piston, nevertheless, the piston would still obtain 90% of its power from the mud flow. In this case, a relatively minor fraction of the horsepower, such as 15% would be “lost”.
  • These leaky seal devices can then be classified as "quasi-positive displacement motors".
  • such motors may have relatively loose fitting components that reduce manufacturing costs. But more importantly, as the interior parts of these motors wear, the motor keeps operating. Therefore, these "quasi-postive displacement motors" have the intrinsic internal design to guarantee long lasting operation under adverse environmental conditions.
  • the "quasi-positive displacement motors" are made of relatively loose fitting metal components, so that high temperature operation is possible. The materials are selected so that there is no galling during operation, or jamming due to thermal expansion.
  • the Drive Shaft in Figure 8 can be chosen to be Drive Shaft 20 in Figure 3A.
  • the flywheel can be chosen to be Flywheel A 34 in Figure 3H. It is conceivable to make another assembly drawing appropriate for only this situation that could be labeled with numeral 270 (not shown), but in the interests of brevity, this approach will not be used any further.
  • Figure 9 shows a cross-section view FF of the Mud Motor Assembly in Figure 6C with Piston A at angle theta of 0 Degrees in the Mud Motor Assembly. This view is looking uphole. The position of theta equal 0 degrees is defined as that position of Piston A when mud pressure inside Chamber A reaches a sufficient pressure where Piston A just begins initial movement during the Power Stroke of Piston A.
  • Figure 9 A shows Piston A in Position at 30 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9B shows Piston A in Position at 60 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9C shows Piston A in Position at 90 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9D shows Piston A in Position at 120 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9E shows Piston A in Position at 150 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9F shows Piston A in Position at 180 Degrees in the Mud Motor Assembly during its Power Stroke.
  • Figure 9G shows Piston A in Position at 210 Degrees in the Mud Motor Assembly at the end of its 100% full strength Power Stroke.
  • Figure 9H shows the various compnents within cross section FF in Figure 6C.
  • Numerals 18, 20, 22, 24 and 86 had been previously defined.
  • Numerals 272, 274, 276, 278, 280, 282, 284, and 286 are defined in Figures 10, 10A,...., 10L, 10M which follow.
  • Element 288 in this direction looking uphole shows the direction of the Power Stroke for Piston A.
  • Figure 9J shows Piston A during a portion of its Reset Stroke, or its Return Stroke, where Piston A rotates clockwise looking uphole (counter-clockwise looking downhole), until it reaches at "Stop” at theta equals 0 degrees.
  • the "Stop” it may be mechanical in nature, or may be hydraulic in nature.
  • Element 290 is this direction looking uphole shows the direction of the Reset Stroke, or Return Stroke, of Piston A.
  • Figure 9K shows Piston A during a portion of its Power Stroke.
  • leaky seal 292 may produce mud flowing in a direction past the seal shown as element 294 in Figure 9K.
  • F292 is the flow rate in gpm through leaky seal 292.
  • HP292 is the horsepower dissipated by the mud flow F292 through leaky seal 292.
  • F292 and HP 292 are expected, of course, to be dependent upon the average pressure acting on Piston A during its Power Stroke.
  • the term “average pressure” includes a spatial or volumetric average, but that average may be at just one instant in time. The "average pressure" may be time dependent. Similar comments apply below to the usage "average pressure”.
  • leaky seal 296 may produce mud flowing in a direction past the seal shown as element 298 in Figure 9K.
  • F296 is the flow rate in gpm through leaky seal 296.
  • HP296 is the horsepower dissipated by the mud flow F296 through leaky seal 296. F296 and HP296 are expected, of course, to be dependent upon the average pressure acting on Piston A during its Power Stroke.
  • Element 300 in Figure 9K defines the region called the Power Chamber. Pressurized mud in the Power Chamber 300 acts upon Piston A to cause it to move during its Power Stroke.
  • the average pressure acting upon Piston A during its Power Stroke is defined to be P300.
  • the pressure within the Power Chamber 300 may vary with position, and that knowledge is a minor variation of this invention.
  • Element 302 in Figure 9K defines the region called the Backstop Chamber.
  • the mud within the Backstop Chamber 302 may will have an average pressure acting upon the "back side" Piston A.
  • the average pressure acting upon the back side of Piston A during its Power Stroke is defined to be P302.
  • the pressure within the Backstop Chamber may vary with position, and that knowledge is a minor variation of this invention.
  • the portion of Piston A facing the Power Chamber 300 is designated by numeral 304, and has average pressure P304 acting on that portion 304.
  • the portion of Piston A facing the Backstop Chamber 302 is designated by numeral 306, and has average pressure P306 acting on that portion 306.
  • the portion of the Backstop facing the Power Chamber 300 is designated by numeral 308, and has average pressure P308 acting on that portion 308.
  • the portion of the Backstop facing the Backstop Chamber 302 is designated by numeral 310, and has average pressure P310 on that portion of 310.
  • Figure 9L shows new positions for previous elements 278 and 280.
  • Element 312 corresponds to original 278 ("DPCHA”).
  • Element 314 corresponds to original element 280 ("EPCHA").
  • centers of elements 312 and 314 are now at different radii in this embodiment which may assist in the design of the proper operation of intake and exhaust valuing. Either of these new elements can be put at different radial positions than the radial position of the center of 282 (“EPCHA”). See Figures 10H, 10J, and 10K. Cross Section Views of the Mud Motor Assembly
  • Figure 10 shows a Cross-Section View of the Housing 18 in the Mud Motor
  • Figure 10A shows a Cross-Section View of Crankshaft A 22 in the Mud Motor Assembly.
  • Figure 10B shows a Cross-Section View of the Internal Crankshaft A Bearing 86 in the Mud Motor Assembly.
  • Figure IOC shows a Cross-Section View of the Drive Shaft 20 in the Mud Motor Assembly.
  • Figure 10D shows a Cross-Section of Piston A 24 in the Mud Motor Assembly.
  • Figure 10E shows a Cross-Section of Backstop A 272 in the Mud Motor Assembly.
  • Figure 10F shows a Cross-Section of Bypass Tube A-l 274 in the Mud Motor Assembly.
  • Figure 10G shows a Cross-Section of Bypass Tube A-2 276 in the Mud Motor Assembly.
  • FIG 10H shows a Cross-Section of the Drive Port of Chamber A (“DPCHA”)
  • Figure 10J shows a Cross-Section of the Exhaust Port of Chamber A ("EPCHA") 280 in the Mud Motor Assembly.
  • Figure 10K shows a Cross-Section of the Backstop Port of Chamber A (“BPCHA”) 282 in the Mud Motor Assembly.
  • Figure 10L shows a Cross-Section of the Backstop to Housing Weld 284 in the Mud Motor Assembly.
  • Figure 10M shows a Cross-Section of Piston A to Crankshaft A Weld 286 in the
  • Figure 11 shows the Basic Component Dimensions for a preferred embodiment of the Mud Motor Assembly having an OD of 6 1/4 Inches.
  • the original source drawing used to generate Figure 1 herein was a scale drawing that showed on a 1 :1 scale the parts that would be used to make a 6 1/4 inch OD Mud Motor Assembly. Many of those details appear in Serial No. 61/687,394 which contains many drawings (which is 601 pages long).
  • Figure 12 shows an Uphole View of the Upper Main Bearing 72 in the Mud Motor Assembly. It is a "split bearing" having an upper bearing part 316 and a lower bearing part 318. The bearing joining line is shown as element 320. It has a hole 322 that is designed to have the proper clearance around the drive shaft during operation.
  • the split bearing is assembled over the proper portion of the drive shaft, and then Allen head cap screws 324 and 326 are tightened in place. When first placed on the drive shaft, and after the caps screws are tightened, bearing 72 will rotate about the center line of the drive shaft. The entire interior portion of the mud motor assembly is designed to slip into the housing.
  • external Allen head cap screws such as those designed by numeral 328 in Figure 20 are used to hold the bearing in place within the housing by screwing into threaded hole 330.
  • a narrow tool can be inserted into the hole in the housing used to accept the cap screw, and that tool can be used to rotate the bearing into proper orientation.
  • Small holes on the radial exterior of the bearing called “indexing holes” 332 (not shown) can be used to conveniently line up the bearing before the cap screw is put into place through the housing to engage threaded hole 330.
  • Typical assembly methods and apparatus known to those having ordinary skill in the art are employed to design and install such split bearings. Bearing materials are chosen so as not to gall against the drive shaft.
  • Figure 12A shows a Section View of the Upper Main Bearing 72 in the Mud Motor Assembly.
  • Figure 12B shows an Uphole View of the Middle Main Bearing 74 in the Mud
  • Hole passageways 334 and 336 are shown in Figure 12B. These are typical of the various types of passageways through a bearing for the pass-through of tubing above and below a bearing as may be typically required.
  • Figure 12C shows a Section View of the Middle Main Bearing 74 in the Mud Motor Assembly.
  • Tubing 335 is shown passing through the hole 334 shown in Figure 12B.
  • Tubing 337 is shown passing through the hole 336 shown in Figure 12B.
  • Figure 13 shows a Section View of Installed Return Spring A 78 which is a
  • Ratchet Assembly A 30 in the Mud Motor Assembly one end 338 of the Return Spring A is positively anchored into a portion of Crankshaft A 22.
  • the other end 340 of the Return Spring A is positively anchored into a split-bearing-like structure 344 held in place to the housing 18 by Allen cap screw 346 as is typical with such parts in the Mud Motor Assembly.
  • Return Spring A 78 is a type of torsion spring. Typical design and testing procedures are used that are well known to individuals having ordinary skill in the art. Adequate space is to be made available to allow the Return Spring A to suitably change its radial dimensions during operation.
  • Figure 13A shows a Perspective View of Return Spring A 78 in the Mud Motor Assembly.
  • Figure 14 shows a Cross Section View CC of Ratchet Assembly A in the Mud
  • FIG. 6B This figure derives from a 1 : 1 scale drawing for a 6 1/4 inch OD Mud Motor Assembly. The detailed dimensions can be found in Serial No. 61/687,394.
  • the rounded base portion 348 of the Drive Pin A 42 may be chosen to be a robust 3/4 inches OD.
  • First torsion rod return spring 350 and second torsion rod return spring 352 are shown. The first and second torsion rod return springs provide the spring forces to drive the Pawl A 40 onto the Pawl A Latch Lobe 44 during the final portion of the Return Stroke of Piston A.
  • the symbol EQ stands for equal angles, and convenient choices may be made.
  • Figure 14 A shows a cross section portion 354 of Drive Pin A 42 for a Preferred Embodiment of the Mud Motor Assembly Having an OD
  • Figure 14B shows a Cross Section View DD of one embodiment of Ratchet Assembly A in the Mud Motor Assembly.
  • This Cross Section DD is marked on Figure 6B.
  • Portion 356 of Drive Pin A 42 is shown.
  • First and second torsion rods 350 and 352 are also shown.
  • Various dimensions are shown that are appropriate for a 6 1/4 inch OD Mud Motor Assembly. There are many different choices for other dimensions including the radius R4 and a distance of separation XI 5.
  • One particular choice of these dimensions for one embodiment invention may be found in Serial No. 61/687,394 that are appropriate for a 6 1/4 inch OD Mud Motor Assembly.
  • Figure 14C shows a Cross Section View EE of one embodiment of Ratchet
  • Figure 14D shows How to Utilize a Larger Drive Pin 364 than that shown in Figure 14C.
  • Arrows 366 and 368 show the directions of the enlargement of the Drive Pin A Slot 362. The dimensions shown are appropriate for a 6 1/4 inch OD Mud Motor Assembly. The remainder of the legends have been previously defined.
  • Figure 14E shows an Optional Larger and Different Shaped Drive Pin 370 than in Figure 14C.
  • the dimensions shown are appropriate for a 6 1/4 inch OD Mud Motor Assembly. The remainder of the legends have been previously defined.
  • Figure 14F shows a Cross Section View AA of Ratchet Assembly A in the Mud Motor Assembly.
  • This Cross Section AA is marked on Figure 6B.
  • Pawl A Capture Pin 38 is shown in its "down position" 372 seated against the OD of Drive Shaft 20.
  • This drawing was derived from a 1 : 1 scale drawing for a Mud Motor Assembly having an OD of 6 1/4 inches.
  • There are many different choices for other dimensions including the radii identified by the legends Rl, R2, and R3, and the distances identified by the legends X7, X8, and X9.
  • One particular choice of these dimensions for one embodiment invention may be found in Serial No. 61/687,394 that are appropriate for a 6 1/4 inch OD Mud Motor Assembly.
  • Figure 14G shows an Uphole View of Flywheel A and Raised Guide for Pawl A Capture Pin in Section BB of Ratchet Assembly A Showing Sequential Movement of Pawl A Capture Pin in the Mud Motor Assembly.
  • a portion 374 of Flywheel 40 is shown.
  • Raised Guide for Pawl A Capture Pin 36 is also shown.
  • Sequential positions a, b, and c of the Pawl A Capture Pin 38 shows how that pin is captured so that the Pawl A 40 is returned to its proper seated position at the end of the Reset Stroke of Piston A.
  • position "a" the Pawl A Capture Pin is shown in its maximum radial distance R2 away from the center of rotation of the Drive Shaft 20, which is it's maximum “up position” and which can be identified herein as R2(a).
  • R2(a) - R2(c) 3/8 inch plus 1/32 inch.
  • the Pawl A Seat Width (“PASW") is chosen to be 3/8" (see element 377 in Figure 15 A), so that the clearance distance 379 is 1/32" between the Tip of Pawl A lifter Lobe 381 and the ID 383 of the Pawl A 40 in Figure 15 A.
  • flywheel A there are many choices for Flywheel A.
  • the energy stored in Flywheel A and in Flywheel B is sufficient to keep the rotary drill bit turning through 360 degrees even if the mud pressure through the drill string drops significantly.
  • FIG. 15 shows one embodiment of the Pawl A Latch Lobe 44 Fully Engaged With Pawl A 40 at mating position 376 in the Mud Motor Assembly. As shown, the Pawl A Capture Pin 38 is opposite theta of 0 degrees ready for the beginning of the Power Stroke of Piston A.
  • FIG 15A shows one embodiment of the Pawl A Latch Lobe 44 Completely
  • Pawl A Capture Pin is opposite an angle theta slightly in excess of 230 degrees. Pawl A 40 has been lifted into this position by the Pawl A Lifter Lobe 46 of the Mud Motor Assembly, and is ready to begin its return with the Return Stoke of Piston A.
  • Numeral 377 is to designate the Pawl A Seat Width ("PASW"). In several preferred embodiments of the 6 1/4 inch OD Mud Motor Assembly, PASW is chosen to be 3/8".
  • Figure 15A shows the clearance distance 379 between the Tip of Pawl A Lifter Lobe 381 and the ID 383 of the Pawl A 40. As explained in relation to Figure 14G, the clearance distance 379 is chosen to be 1/32 inch in one preferred embodiment.
  • Figure 15B shows a Optional Slot 378 Cut in Pawl A 40 to Make Torsion Cushion at mating position 376 During Impact of Pawl A Latch Lobe in the Mud Motor Assembly.
  • FIG 16 shows the Pawl A Lifter Lobe at theta of 0 Degrees in the Mud Motor Assembly.
  • Pawl A 40 is also shown.
  • the Pawl A Lifter Lobe 46 has Lifter Lobe Profile 380 that rides within Pawl A Lifter Recession 382. At theta equals 0 degrees, the Pawl A Lobe Lifter 46 does NOT contact any portion of the Pawl A Lifter Recession 382.
  • Pawl A Stop 386 is shown that is welded in place with weld 388 to the Housing 18 at location 390.
  • Figure 16A shows the Pawl A Lifter Lobe at 210 Degrees in the Mud Motor Assembly.
  • the leading edge 392 of Pawl A has made contact with the Pawl A Stop 386, and when that happens, the Pawl A Lifter Lobe makes contact with the Pawl A Lift Recession 382, and drives the Pawl A radially away from the center line of the Mud Motor Assembly.
  • the tip of the Pawl A Lifter Lobe 394 rides on the interior portion of the maximum excursion 396 of the Pawl A Lifter Recession 382.
  • the Pawl A Lifter Lobe that is a part of the Drive Shaft 20 continues its clockwise rotation looking downhole. Meanwhile, Pawl A will begin its return ruing the Return Stroke of Piston A.
  • FIG 16B shows the Pawl A Lifter Lobe 46 at -90 Degrees and the Partial Return of Pawl A 40 in the Mud Motor Assembly.
  • the Pawl A Lifter Lobe 46 is rotating clockwise 398 looking downhole.
  • the Pawl A in Figure 16 is rotating counter-clockwise 400 looking downhole.
  • FIG 17 shows Intake Port A 402 in Intake Valve A 80 Passing theta of 0 Degrees allowing relatively high pressure mud to flow through the Intake Port A 402 and then through the Drive Port of Chamber A ("DPCHA") 278 and thereafter into Chamber A, thus beginning the Power Stroke of Piston A in the Mud Motor Assembly.
  • This portion of mud flowing through this route is designated as numeral 492 (not shown).
  • the Intake Port A 402 in Intake Valve A 80 is shown as a dotted line; the Drive Port of Chamber A (“DPCHA”) 278 is shown as a solid circle; and these conventions will be the same in the following through Figure 17F. These views are looking uphole.
  • the distance of separation between Intake Port A 402 in Valve 80 and the Drive Port of Chamber A (“DPCHA”) 278 is discussed in relation to Figures 20A and 20B.
  • FIG 17A shows the Intake Port A 402 in Intake Valve A 80 Passing theta of 90 degrees during the Power Stroke of Piston A in the Mud Motor Assembly.
  • the Drive Port of Chamber A (“DPCHA) 278 synchronously tracks Intake Port A 402 in Intake Valve A 80.
  • DPCHA Drive Port of Chamber A
  • FIG 17B shows the Intake Port A 402 in Intake Valve A 80 Passing theta of 180 degrees during the Power Stroke of Piston A in the Mud Motor Assembly.
  • the Drive Port of Chamber A (“DPCHA) 278 is shown still synchronously tracking the Intake Port 402 while rotating in the clockwise direction 404.
  • FIG 17C shows the Intake Port A 402 in Intake Valve A 80 Passing theta of 210 degrees during the very end of the Power Stroke of Piston A in the Mud Motor Assembly.
  • the Drive Port of Chamber A (“DPCHA) 278 is shown still synchronously tracking the Intake Port A 402.
  • FIG 17D shows Intake Port A 402 in Intake Valve A 80 Passing theta of 240 degrees after the Power Stroke of Piston A has ended.
  • the Port A 402 in Intake Valve A 80 is an integral part of the Drive Shaft 20, and continues to rotate in the clockwise direction 404 looking downhole.
  • the Drive Port of Chamber A (“DPCHA) 278 is shown during its counter-clockwise motion during the Return Stroke of Piston A that is rotating in the counter-clockwise direction 406 looking downhole.
  • FIG 17E shows Intake Port A 402 in Intake Valve A 80 at theta of - 30 Degrees in the Mud Motor Assembly During the Return Stroke of Piston A.
  • the Drive Port of Chamber A (“DPCHA) 278 is shown at the end of the Return Stroke of Piston A.
  • Figure 17F shows Intake Port A 402 in Intake Valve A again passing theta of 0 degrees that begins the Power Stroke of Piston A in the Mud Motor Assembly. That Power Stroke of Piston A begins when relatively high pressure mud flows through Intake Port A 402 in Intake Valve A and then through the Drive Port of Chamber A ("DPCHA") 278 and then into Chamber A that in turns puts a torque on Piston A.
  • DPCHA Drive Port of Chamber A
  • Figure 18 shows the upper portion of the Bottom Hole Assembly 408 that includes the Mud Motor Assembly 12.
  • the upper threaded portion 410 of the housing 18 accepts the lower threaded portion 412 of the Instrumentation and Control System 414.
  • the upper threaded portion 484 of the Instrumentation and Control System 414 is attached to the drill pipe 486 (not shown) that receives mud from the mud pumps 488 (not shown) located on the surface near the hoist 490 (not shown).
  • the Instrumentation and Control System may include directional drilling systems, rotary steerable systems, Measurement- While-Drilling ("MWD”) Systems, Logging- While-Drilling Systems (“LWD”), data links, communications links, systems to generate and determine bid weight, and all the other typical components used in the oil and gas industries to drill wellbores, particularly those that are used in conjunction with currently used progressing cavity mud motors.
  • the uphole portion of the Bottom Hole Assembly 408 is connected to the drill string 416 (not shown) that is in turn connected to suitable surface hoist equipment typically used by the oil and gas industries 418 (not shown).
  • housing 18 may be optionally separated into shorter threaded sections by the use of suitable threaded joints such the one that is identified as element 420.
  • the threads 420 may also be conveniently used when assembling Piston A and related parts into Chamber A. Similar threads are used in the Housing near Chamber B that is element 512 (not shown). Other threads 514 (not shown) are also in the Housing. Element 328 is representative of the Allen head caps screws used to hold bearings and other components in place that is further referenced in relation to Figure 12.
  • the downhole portion of the Bottom Hole Assembly 422 is shown in Figure 19.
  • the entire Bottom Hole Assembly 424 (not shown) is comprised of elements 408 and 422 and is being used to drill borehole 426.
  • Downward flowing mud 428 is used to cool the bit and to carry rock chips with the mud flowing uphole 430 in annulus 432 that is located in geological formation 434.
  • the legend RLPMF stands for Relatively Low Pressure Mud Flow (RLPMF) 16 designated by the unique shading used only for this purpose in this application (see Figure 2A).
  • FIG 20 shows the Relatively High Pressure Mud Flow (“RHPMF”) through the
  • Mud Motor Apparatus See Figure 2. The paths for mud flow through the apparatus is described. Whether or not fluid actually flows is, of course, dependent upon whether or not certain valves are open, and in turn, that depends upon the "Timing State" of the apparatus.
  • the Mud Motor Apparatus 12 receives its input of mud flow 436 from the drill pipe 484 (not shown) and through the Instrument and Control System 414.
  • the RHPMF then flows through upper apparatus A flow channels 438 and proceeds to two different places (dictated by the timing of the apparatus):
  • FIG 20A shows the Relatively Low Pressure Mud Flow ("RLPMF") through the Mud Motor Apparatus. See Figure 2A. The paths for mud flow through the apparatus is described. Whether or not fluid actually flows is, of course, dependent upon whether or not certain valves are open, and in turn, that depends upon the "Timing State" of the apparatus. Mud flows to the drill bit as follows:
  • the Intake Valve A 80 can be a split member itself, and welded or bolted in place before the entire assembly is slipped into the Housing 10. Similar comments apply to the other intake and exhaust valves.
  • the customer chooses the desired mud flow rate, the RPM, and the required HP (horsepower). If a pressure drop across the Mud Motor Assembly is then chosen to be a specific number, such as 750 psi for example, then the internal geometry of the Chambers and Pistons can thereafter be determined using techniques known to anyone having ordinary skill in the art.
  • Figure 21 compares the pressure applied to the Drive Port of Chamber B
  • DPCHB Pressure applied to Drive Port of Chamber A
  • DPCHA Pressure applied to Drive Port of Chamber A
  • PH higher pressure
  • PL lower pressure
  • Figure 21 A shows that a low pressure PL is applied to the Exhaust Port of Chamber A (“EPCHA”) and to the Exhaust Port of Chamber B (“EPCHB”) during the appropriate Return Strokes.
  • Figure 2 IB shows the relationship between the maximum lift of the tip of the Paw A Lifter Lobe 394 and the pressure applied to the Drive Port of Chamber A ("DPCHA").
  • Figures 9, 9A, 9B,9C, 9D, 9E, 9F, and 9G show a Power Stroke for Chamber A.
  • the third torsion rod return spring for Crankshaft B is 504 (also b350).
  • the fourth torsion rod return spring for Crankshaft B is 506 (also b352)
  • Figure 9 J pertains to Chamber A.
  • the analogous figure pertaining to Chamber B is numeral 508 (not shown).
  • Figure 16B pertains to Chamber A.
  • the analogous figure pertaining to Chamber B is 510 (not shown).
  • the Mud Motor Assembly 12 is also called equivalently the Mud Motor Apparatus
  • FIG. 3F shows Ratchet Assembly A 30 of the Mud Motor Assembly.
  • Ratchet Assembly A 30 is an example of a ratchet means.
  • embodiments of the invention may use selected features of the below defined methods and apparatus.
  • the present invention provides a closed-loop drilling system for drilling oilfield boreholes.
  • the system includes a drilling assembly with a drill bit, a plurality of sensors for providing signals relating to parameters relating to the drilling assembly, borehole, and formations around the drilling assembly.
  • Processors in the drilling system process sensors signal and compute drilling parameters based on models and programmed instructions provided to the drilling system that will yield further drilling at enhanced drilling rates and with extended drilling assembly life.
  • the drilling system then automatically adjusts the drilling parameters for continued drilling.
  • the system continually or periodically repeats this process during the drilling operations.
  • the drilling system also provides severity of certain dysfunctions to the operator and a means for simulating the drilling assembly behavior prior to effecting changes in the drilling parameters.”
  • An automated drilling system for drilling oilfield wellbores at enhanced rates of penetration and with extended life of drilling assembly comprising: (a) a tubing adapted to extend from the surface into the wellbore; (b) a drilling assembly comprising a drill bit at an end thereof and a plurality of sensors for detecting selected drilling parameters and generating data representative of said drilling parameters; (c) a computer comprising at least one processor for receiving signals representative of said data; (d) a force application device for applying a predetermined force on the drill bit within a range of forces; (e) a force controller for controlling the operation of the force application device to apply the predetermined force; (f) a source of drilling fluid under pressure at the surface for supplying a drilling fluid (g) a fluid controller for controlling the operation of the fluid source to supply a desired predetermined pressure and flow rate of the drilling fluid; (h) a rotator for rotating the bit at a predetermined speed of rotation within a range
  • transmitters associated with the computer for sending control signals directing the force controller, fluid controller and rotator controller to operate the force application device, source of drilling fluid under pressure and rotator to achieve enhanced rates of penetration and extended drilling assembly life.
  • US6662110 include the following, entire copies of which are incorporated herein by reference: US4019148 entitled “Lock-in noise rejection circuit”; US4254481 entitled “Borehole telemetry system automatic gain control”; US4507735 entitled “Method and apparatus for monitoring and controlling well drilling parameters”;US4954998 entitled “Method for reducing noise in drill string signals”; US5160925 entitled “Short hop communication link for downhole MWD system”; US5220963 entitled “System for controlled drilling of boreholes along planned profile”; US5259468 entitled “Method of dynamically monitoring the orientation of a curved drilling assembly and apparatus”; US5269383 entitled “Navigable downhole drilling system”; US5314030 entitled “System for continuously guided drilling”; US5332048 entitled “Method and apparatus for automatic closed loop drilling system”; US5646611 entitled “System and method for indirectly determining inclination at the bit”; US5812068 entitled “Drilling system with downhole apparatus for determining parameters
  • US7650950 include the following, entire copies of which are incorporated herein by reference: US3429385 entitled “Apparatus for controlling the pressure in a well”;
  • US3443643 entitled “Apparatus for controlling the pressure in a well”; US3470971 entitled “Apparatus and method for automatically controlling fluid pressure in a well bore”; US3470972 entitled “Bottom-hole pressure regulation apparatus”; US3550696 entitled “Control of a well”; US3552502 entitled “Apparatus for automatically controlling the killing of oil and gas wells”; US3677353 entitled “Apparatus for controlling oil well pressure”; US3827511 entitled “Apparatus for controlling well pressure”; US4440239 entitled “Method and apparatus for controlling the flow of drilling fluid in a wellbore”; US4527425 entitled “System for detecting blow out and lost circulation in a borehole”; US4570480 entitled “Method and apparatus for determining formation pressure”;
  • US7178592 include the following, entire copies of which are incorporated herein by reference: US4020642 entitled “Compression systems and compressors”; US4099583 entitled “Gas lift system for marine drilling riser”; US4319635 entitled “Method for enhanced oil recovery by geopressured waterflood”; US4477237 entitled “Fabricated reciprocating piston pump”; US4553903 entitled “Two-stage rotary compressor”;

Landscapes

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

Abstract

L'invention concerne un moteur à boue entièrement métallique, plus puissant, de moindre coût et durant plus longtemps que les moteurs à boue à cavité progressive actuellement disponible pour forer des puits de forage dans le sol. L'invention concerne un appareil à moteur à boue comprenant un arbre d'entraînement unique qui fait tourner un trépan rotatif, lequel appareil est fixé à une tige de forage qui envoie de la boue sous haute pression vers le moteur à boue ; l'arbre d'entraînement reçoit une première partie au moins de son couple de rotation d'une quelconque boue sous haute pression circulant dans une première chambre hydraulique de l'appareil, et reçoit au moins une seconde partie de son couple de rotation d'une quelconque boue sous haute pression circulant dans une seconde chambre hydraulique dans l'appareil. L'appareil à moteur à boue comprend deux chambres hydrauliques possédant chacune sa propre course de puissance et course de retour, et agissant ensemble de manière contrôlée afin de fournir une puissance continue au trépan rotatif.
PCT/US2012/039172 2011-05-23 2012-05-23 Système de moteur à boue WO2012162408A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CA2837082A CA2837082C (fr) 2011-05-23 2012-05-23 Systeme de moteur a boue
EP12789232.1A EP2715031B1 (fr) 2011-05-23 2012-05-23 Système de moteur à boue

Applications Claiming Priority (14)

Application Number Priority Date Filing Date Title
US201161519487P 2011-05-23 2011-05-23
US61/519,487 2011-05-23
US201161573631P 2011-09-08 2011-09-08
US61/573,631 2011-09-08
US201161629000P 2011-11-12 2011-11-12
US61/629,000 2011-11-12
US201261633776P 2012-02-18 2012-02-18
US61/633,776 2012-02-18
US201261687394P 2012-04-24 2012-04-24
US61/687,394 2012-04-24
US201261688726P 2012-05-18 2012-05-18
US61/688,726 2012-05-18
US13/506,887 2012-05-22
US13/506,887 US9051781B2 (en) 2009-08-13 2012-05-22 Mud motor assembly

Publications (1)

Publication Number Publication Date
WO2012162408A1 true WO2012162408A1 (fr) 2012-11-29

Family

ID=47217713

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2012/039172 WO2012162408A1 (fr) 2011-05-23 2012-05-23 Système de moteur à boue

Country Status (3)

Country Link
EP (1) EP2715031B1 (fr)
CA (1) CA2837082C (fr)
WO (1) WO2012162408A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9051781B2 (en) 2009-08-13 2015-06-09 Smart Drilling And Completion, Inc. Mud motor assembly
US9745799B2 (en) 2001-08-19 2017-08-29 Smart Drilling And Completion, Inc. Mud motor assembly

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10563459B2 (en) 2001-08-19 2020-02-18 Smart Drilling And Completion, Inc. Mud motor assembly
US9803424B2 (en) 2001-08-19 2017-10-31 Smart Drilling And Completion, Inc. Mud motor assembly

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3485221A (en) * 1967-12-11 1969-12-23 Ralph S Feeback Omnitorque opposed piston engine
US3985110A (en) * 1975-01-20 1976-10-12 William J. Casey Two-rotor engine
US4283779A (en) * 1979-03-19 1981-08-11 American Petroscience Corporation Torsional wave generator
US5613568A (en) * 1993-05-06 1997-03-25 Lennart Nilsson Rock drilling machine
US5957220A (en) * 1995-10-17 1999-09-28 Dresser-Rand Company Percussion drill assembly
US5988994A (en) * 1997-10-21 1999-11-23 Global Cooling Manufacturing Company Angularly oscillating, variable displacement compressor
US6267185B1 (en) * 1999-08-03 2001-07-31 Schlumberger Technology Corporation Apparatus and method for communication with downhole equipment using drill string rotation and gyroscopic sensors
US20080017419A1 (en) * 2005-10-11 2008-01-24 Cooley Craig H Cutting element apparatuses, drill bits including same, methods of cutting, and methods of rotating a cutting element
US20090139769A1 (en) 2007-11-29 2009-06-04 Smith International, Inc. Apparatus and method for a hydraulic diaphragm downhole mud motor
US20110073372A1 (en) * 2008-05-29 2011-03-31 Dreco Energy Services Ltd. Mechanism for providing controllable angular orientation while transmitting torsional load

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6289998B1 (en) * 1998-01-08 2001-09-18 Baker Hughes Incorporated Downhole tool including pressure intensifier for drilling wellbores

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3485221A (en) * 1967-12-11 1969-12-23 Ralph S Feeback Omnitorque opposed piston engine
US3985110A (en) * 1975-01-20 1976-10-12 William J. Casey Two-rotor engine
US4283779A (en) * 1979-03-19 1981-08-11 American Petroscience Corporation Torsional wave generator
US5613568A (en) * 1993-05-06 1997-03-25 Lennart Nilsson Rock drilling machine
US5957220A (en) * 1995-10-17 1999-09-28 Dresser-Rand Company Percussion drill assembly
US5988994A (en) * 1997-10-21 1999-11-23 Global Cooling Manufacturing Company Angularly oscillating, variable displacement compressor
US6267185B1 (en) * 1999-08-03 2001-07-31 Schlumberger Technology Corporation Apparatus and method for communication with downhole equipment using drill string rotation and gyroscopic sensors
US20080017419A1 (en) * 2005-10-11 2008-01-24 Cooley Craig H Cutting element apparatuses, drill bits including same, methods of cutting, and methods of rotating a cutting element
US20090139769A1 (en) 2007-11-29 2009-06-04 Smith International, Inc. Apparatus and method for a hydraulic diaphragm downhole mud motor
US20110073372A1 (en) * 2008-05-29 2011-03-31 Dreco Energy Services Ltd. Mechanism for providing controllable angular orientation while transmitting torsional load

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2715031A4 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9745799B2 (en) 2001-08-19 2017-08-29 Smart Drilling And Completion, Inc. Mud motor assembly
US9051781B2 (en) 2009-08-13 2015-06-09 Smart Drilling And Completion, Inc. Mud motor assembly

Also Published As

Publication number Publication date
CA2837082C (fr) 2020-02-25
EP2715031A1 (fr) 2014-04-09
CA2837082A1 (fr) 2012-11-29
EP2715031B1 (fr) 2016-12-28
EP2715031A4 (fr) 2015-11-25

Similar Documents

Publication Publication Date Title
US9051781B2 (en) Mud motor assembly
US9027673B2 (en) Universal drilling and completion system
US10294723B2 (en) Mud motor assembly
US9611693B2 (en) Mud motor assembly
US10689927B2 (en) Universal drilling and completion system
US9243492B2 (en) Downhole apparatus, device, assembly and method
US7881155B2 (en) Pressure release encoding system for communicating downhole information through a wellbore to a surface location
US9771793B2 (en) Downhole apparatus, device, assembly and method
WO2011140426A1 (fr) Système de forage et de complétion universel
US10563459B2 (en) Mud motor assembly
CA2837082C (fr) Systeme de moteur a boue
US9803424B2 (en) Mud motor assembly
US9587435B2 (en) Universal drilling and completion system
US20090242276A1 (en) Pump Mechanism for Cooling of Rotary Bearings in Drilling Tools
CN113586040A (zh) 泥浆脉冲发生器及其操作方法
AU2013291759B2 (en) Downhole apparatus and method
US10180058B2 (en) Telemetry module with push only gate valve action

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12789232

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2837082

Country of ref document: CA

REEP Request for entry into the european phase

Ref document number: 2012789232

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2012789232

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE