WO2014107813A1 - Système, procédé et appareil pour un assemblage flexible pour un moteur de forage de fond de trou - Google Patents

Système, procédé et appareil pour un assemblage flexible pour un moteur de forage de fond de trou Download PDF

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Publication number
WO2014107813A1
WO2014107813A1 PCT/CA2014/050020 CA2014050020W WO2014107813A1 WO 2014107813 A1 WO2014107813 A1 WO 2014107813A1 CA 2014050020 W CA2014050020 W CA 2014050020W WO 2014107813 A1 WO2014107813 A1 WO 2014107813A1
Authority
WO
WIPO (PCT)
Prior art keywords
joint
ball
key
socket
axis
Prior art date
Application number
PCT/CA2014/050020
Other languages
English (en)
Inventor
David S. Cramer
Karlo SLISKO
Original Assignee
General Downhole Technologies Ltd.
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 General Downhole Technologies Ltd. filed Critical General Downhole Technologies Ltd.
Publication of WO2014107813A1 publication Critical patent/WO2014107813A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • F16D3/2057—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having four or more pins, e.g. with compensation for relative pin movement
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
    • F16C11/0623—Construction or details of the socket member

Definitions

  • the present invention relates in general to downhole drilling motors and, in particular, to a system, method and apparatus for a flexible joint for a downhole drilling motor.
  • PDM positive displacement mud motor
  • a mud motor comprises four primary components: a power section, a bent housing (or offset housing), a bearing section, and a driveshaft.
  • the power section converts energy from the flow of mud into rotational energy.
  • a central rotor in the power section spins as mud flows between it and a stator. The rotation of the central rotor is not constrained to a central axis of the motor and is thus slightly eccentric.
  • the bent housing is located directly below the power section. The bent housing facilitates the bend in the outer body of the motor. The bend is useful at directing the drill bit to steer in a selected direction.
  • the bearing section is below the bent housing. The bearing section secures the drill bit and stabilizes the rotation of the bit within the housing.
  • the drive shaft is located inside the bent housing.
  • the drive shaft connects the bearing section and the power section, and transmits power and torque from the power section to the bit.
  • the axis of the power section is displaced at an angle from the axis of the bearing section, some means of transmitting torque to this bend is required.
  • the eccentric motion of the rotor means that an extra degree of freedom should be accounted for.
  • CV joints compensation for the extra degree of freedom is provided by one or more universal or constant velocity (CV) joints.
  • CV joints for transmitting torque to the bottom of the mud motor, although each of them has negative attributes.
  • a traditional Cardan type or double Cardan type universal joint lacks the strength required to handle the heavy torsional loads required by drilling applications.
  • Cardan or double Cardan type CV joints are prone to catastrophic failure since their lugs can shear off under high impact loading.
  • Cardan type joints do not transmit rotational velocity with constant input speed and constant output speed.
  • the bend angle of the joint increases, the oscillation and velocity of the output shaft increases. Even though the angles that are used for directional drilling are small, any rotational irregularities can cause drilling problems.
  • a more traditional type of CV joint is a Rezzpa joint, which is typically used for the front wheels of most front wheel drive cars. These joints employ balls that slide along tracks in both mating parts of the joint. Rezzpa joints are typically very smooth and exhibit a constant output velocity over a wide range of joint angles. However, they do not allow a high amount of torque to be transmitted per unit of diameter. Because of this limitation, Rezzpa joints are not good candidates for mud motor drive shaft applications.
  • a common industry practice has been to use a modified version of the Rezzpa joint for mud motor drive shafts. Because the range of angles that mud motor joints are subjected to is relatively low (e.g., less than about 10 degrees), the modified Rezzpa joint has pits in the ball section of its joint rather than tracks. Thus, the ball bearings seat in the pits in fixed locations in the ball section of the joint.
  • This design reduces flexibility by one degree of freedom that is necessary for the ball bearings to contact all of the housing groove surfaces simultaneously. However, it does add the advantage of eliminating the need for a bearing cage and increases the amount of torque that can be transmitted in a joint of a given cross-sectional size.
  • modified Rezzpa joints are subject to wear and breakage since their contact surface area used to transmit torque is very low. Also, the use of spherical ball bearings to transmit the torque generates a high amount of hoop stress in the housing section, which necessitates a thicker section to carry torque.
  • An alternative design to the modified Rezzpa joint uses spline features on the ball section of the joint, rather than pits. This design somewhat improves the torque load by distributing it over a larger surface area, theoretically decreasing the amount of galling wear.
  • the static splines in the ball section have at least two disadvantages. First, in order to allow for misalignment of the shafts, the splines must be cut relatively loosely with respect to one another. This requirement permits significant backlash that increases impact loading in variable drilling conditions.
  • the second and most important disadvantage is that the splines are subject to a high degree of wear on the splines that are disposed laterally with respect to the bend angle. That is, the high-side and low-side splines fit into their respective grooves with a good mating fit.
  • a spline parallel to the shaft of the ball section will no longer be parallel to the mating spline on the socket section that is parallel to its connected shaft. This misalignment necessarily causes wear and prematurely fatigues the component.
  • USP 6203435 and USP 8033917 disclose swivel spline flex joint designs that overcome these low surface area and misalignment wear problems.
  • Each of those patents describe mud motor CV, universal joint, or drive shaft devices that employ rotating keys in a ball section that mate with grooves cut in a socket section.
  • the keys are always arranged in pairs so that the torque load is always distributed across the faces of the keys, so that there is never any side force exerted on the ball/socket assembly.
  • a joint for a downhole mud motor may include a ball having a ball shaft extending therefrom along a ball axis.
  • the ball has a recess formed therein.
  • a key may be configured to be mounted to the ball.
  • embodiments may include a socket having a socket shaft extending therefrom along a socket axis.
  • the socket axis may be anti-aligned with the ball axis.
  • a slot may be formed inside the socket and configured to receive the key.
  • the recess, key and slot may include a plurality of each of them.
  • FIG. 1 is a sectional side view of an embodiment of a joint.
  • FIG. 2 is an exploded isometric view of an embodiment of a ball for a joint.
  • FIG. 3 is an isometric view of an embodiment of a socket for a joint.
  • FIG. 4 is a sectional side view of an embodiment of a socket for a joint.
  • FIG. 5 is a sectional side isometric view of another embodiment of a joint.
  • FIG. 6 is an isometric view of an embodiment of a disassembled joint.
  • FIGS. 1 and 2 depict an embodiment of a joint 11 that may include a ball 13 attached to a shaft 15.
  • a housing or mating socket 17 may be attached to another shaft 19.
  • the ball 13 may sit inside the socket 17, such that torque may be transmitted through the joint 11 with one or more spline protrusions or keys 21 that can swivel.
  • the keys 21 on the ball 13 can mate with one or more grooves 23 (FIGS. 3 and 4) formed inside the socket 17.
  • Embodiments of the keys 21 may have a generally cylindrical outer surface 30 (FIG. 2).
  • Each key 21 may include an underside 31 (FIGS. 1 and 5).
  • the underside 31 may comprise different shapes.
  • the underside 31 can be flat, or a generally concave spherical profile that is complementary in shape to the outer profile of the ball 13.
  • Each key 21 also may include flat sides 33 that mate with the grooves 23 formed in the socket 17.
  • Embodiments of the ball 13 may include one or more holes 35 (FIG. 2) formed around its major outer diameter (i.e., equator). Holes 35 can be equally spaced apart and odd numbered and allow the keys 21 to be located therein.
  • the grooves 23 in the socket 17 may be angled at a slight inclination (e.g., about 1 to 5 degrees), such that (under load) the driving torque will force the ball 13 and socket 17 towards each other. This slight angle may be equivalent to about half of the angle that the joint 11 would be expected to work under.
  • the keys 21 may be held in place in the ball 13 with spring pins or dowel pins 37. Pins 37 may be secured in holes 35 adjacent to each main recess or locating hole 39 for respective ones of the keys 21. Each key 21 may be provided with complementary circumferential grooves 41 that can correspond to the location of a respective pin 37 so that the key 21 may rotate but will not be allowed to move axially out of the hole 39.
  • the ball 13 may retain its spherical profile from the distal tip 43 (FIGS. 1 and 5) of the ball 13 to a line or area 45 that is past the equator of the ball 13.
  • the angle a of the spherical profile beyond the equator may correspond to a "latitude" in degrees relative to the equator of the highest amount of axial eccentricity ⁇ that the joint 11 would be expected to accommodate. For example, that angle a may be up to about 10 degrees.
  • the spherical profile on the ball 13 up to and past the equator may be load bearing as the joint 11 experiences torque.
  • the surface of the ball 13 may be treated to be wear resistant.
  • an apparatus and method for sealing the joint 11 from mud invasion are disclosed.
  • one embodiment uses a metal boot shield 51.
  • the exterior 53 (FIG. 4) of the socket 17 may be provided with a spherical profile having a center point that corresponds to the center point of the ball section.
  • the metal boot shield 51 may include a seal 55 (FIG. 1) that slides slightly around the spherical profile exterior 53 of the socket 17.
  • a lubricating fluid may be used to seal inside the joint and reduce or eliminate the ingress of contaminating materials.
  • the apparatus and method of sealing the joint may comprise a conventional elastomeric boot.
  • the elastomeric boot may comprise a bellows-style configuration, as is known in the art.
  • a joint 11 for a downhole mud motor may include a ball 13 having a ball shaft 15 extending therefrom along a ball axis 14.
  • the ball 13 may include a plurality of recesses or blind holes 39 formed therein.
  • a plurality of keys 21 may be configured to be mounted to the ball 13.
  • Embodiments of a socket 17 may include a socket shaft 19 extending therefrom along a socket axis 20.
  • the socket axis 20 may be anti-aligned with the ball axis 14.
  • the term "anti-aligned" as used herein means that the ball shaft axis and the socket shaft axis can be axially aligned or misaligned (e.g., skewed), but are not required to be aligned or coaxial.
  • a plurality of slots 23 may be formed inside the socket 17 and may be configured to receive respective ones of the keys 21.
  • Each key 21 may be provided with a top surface 22 (FIG.
  • a front surface 30 and a rear surface 32 are arcuate.
  • the top, front and rear surfaces 22, 30, 32 of the keys 21 may be cylindrical or spherical.
  • Each key 21 also has side surfaces 33.
  • the side surfaces 33 are flat.
  • Embodiments of each key 21 may be provided with a base 26 (FIG. 2) and a head 28 protruding from the base 26.
  • the head 28 may be larger than the base 26.
  • the head 28 can be longer but narrower than the base 26.
  • the underside 31 (FIGS. 1 and 5) of the head 28 may circumscribe the base 26. In two examples, the underside 31 of the head 28 may be flat or spherically concave.
  • the key 21 may further comprise chamfered surfaces 25 (FIG. 6) between the top surface 22 and the side surfaces 33.
  • the chamfered surfaces 25 can be non-contact surfaces relative to the socket 17.
  • the recesses 39 and keys 21 may be generally cylindrical and complementary to each other in shape.
  • the recesses 39 may be stepped 61 (FIG. 5), such as coaxial cylinders having different diameters.
  • the keys 21 may include stepped profiles that are complementary in shape to the steps 61 in the recesses 39.
  • each slot 23 may be provided with a helical twist relative to the socket axis 20 (FIG. 1), rather than simple rectangular grooves. In essence, the slots may be slightly rotated about the socket axis 20.
  • the helical twist can be less than or equal to about 2 degrees relative to the socket axis 20.
  • each key 21 may be provided with a dimension 27 (FIG. 6) between the flat side surfaces 33.
  • the dimension 27 of key 21 can be between about 0.005 inches and about 0.020 inches less than a complementary width 29 between the flat side surfaces of one of the slots 23 in the socket 17.
  • Some embodiments of the joint 11 have a quantity of the keys 21 that consists of an odd number of the keys 21 (e.g., 1, 3, 5, 7, etc.).
  • Each key 21 may include a hole 28 (FIG. 5) extending therethrough.
  • the hole 28 may be is configured to facilitate a venting of lubricant when the key 21 is installed in the ball 13.
  • the keys 21 are not balls and the keys 21 are elongated.
  • Each key 21 may include a key axis (e.g., along hole 28), about which the keys 21 are configured to swivel in the ball 13 when installed in the ball 13.
  • an exterior of the ball 13 and an interior of the socket 17 may be substantially spherical and complementary in shape.
  • the ball 13 may be provided with a spherical profile from a distal end 43 (FIG. 1) thereof past an equator 44 thereof.
  • the spherical profile may extend to an angle a beyond the equator 44 that corresponds to a latitude relative to the equator 44 of up to about 10 degrees.
  • the recesses 39 can be approximately centered on the equator 44 of the ball 13.
  • Embodiments of the socket 17 may include a distal end 18 (FIG. 4) and an interior surface extending axially inward from the distal end 18.
  • the interior surface may be spherical up to about an equator of the socket 17.
  • the joint 11 may further include a compensating piston 81 configured to be located in an axial recess 83 in the socket 17.
  • the joint 11 may further include an axial bearing 71 configured to be located between the compensating piston 81 and a distal end 43 of the ball 13.
  • the axes 14, 20 of the shafts 15, 19 are configured to intersect in approximately a same location throughout a rotation of the shafts 15, 19.
  • embodiments of a device for use in transmitting torque between two shafts may comprise one ball body shaped roughly spherically and connected to the end of one of the shafts.
  • a socket body profile with a roughly spherical inner surface may accept the spherically shaped end.
  • the socket body can contain slots located in the socket face oriented substantially in line with the shaft connected to the socket.
  • the ball section may contain a plurality of holes drilled around the diameter of the ball on a plane that is perpendicular to the orientation of the shaft connected to the ball section.
  • the device may further comprise a plurality of torque transmission elements.
  • the torque transmission elements may be rotatably fastened to the ball section by a plurality of pin elements.
  • the number of torque transmission elements may consist of an odd number of elements, rather than an even number of elements as is known in the art.
  • the ball section can have a spherical profile past the equator location.
  • the grooves in the socket section may be angled such that the transmission of torque in the drive direction forces the ball and socket section towards or into one another.
  • the torque transmission elements may include a roughly cylindrical shape with one face spherically profiled to rest closely to the ball section.
  • the torque transmission elements may include a flat face to mate with grooves cut in the socket section.
  • the torque elements can be rotatably fastened to the ball section with pins shaped roughly cylindrically.
  • the flat sides of the torque transmission elements can be sized slightly less than the thickness of the angled mating grooves in the socket section.
  • the device for use in transmitting torque between two parts of a downhole mud motor may include a joint where the axis of the shaft that is supplying the torque intersects the axis of the shaft that is receiving the torque in roughly the same location throughout the rotation of the shaft.
  • the joint can include a socket section that is roughly spherical in outer profile over a length that envelopes the intersection of the axis of both shafts.
  • the joint can further include a shield component shaped roughly conically and attached in a sealed manner to the shaft of the joint bearing the ball section of the joint and internally profiled to accept elastomer seals to exclude debris from entering the joint area.
  • some embodiments provide an odd number of keys, and eliminate the need for the keys to be provided as matched pairs. Eliminating one or more keys from matched pairs of keys allows for the use of relatively larger keys for improved torque transfer. Selecting a reasonable number of keys (e.g., five radially symmetric arranged keys) may ensure smooth rotational velocity.
  • the key may include a plurality of keys, the recess may include a plurality of recesses, and the slot may include a plurality of slots.
  • a quantity of the keys, recesses and slots can be an odd number of keys, an odd number of recesses and an odd number of slots.
  • the terms “comprises,” “comprising,” “includes,” “including,” “has,” “having” or any other variation thereof, are intended to cover a non-exclusive inclusion.
  • a process, method, article, or apparatus that comprises a list of features is not necessarily limited only to those features but may include other features not expressly listed or inherent to such process, method, article, or apparatus.
  • “or” refers to an inclusive-or and not to an exclusive-or. For example, a condition A or B is satisfied by any one of the following: A is true (or present) and B is false (or not present), A is false (or not present) and B is true (or present), and both A and B are true (or present).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (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)
  • Pivots And Pivotal Connections (AREA)

Abstract

L'invention concerne un assemblage pour un moteur à boue de fond de trou, lequel peut comprendre un boisseau sphérique ayant une tige de boisseau sphérique s'étendant à partir de celui-ci le long d'un axe de boisseau sphérique. Le boisseau sphérique peut comprendre une cavité formée dans celui-ci. Une languette peut être configurée pour être montée sur le boisseau sphérique. De plus, l'assemblage peut comprendre une douille ayant un logement à douille s'étendant à partir de celle-ci le long d'un axe de douille. L'axe de douille peut ne pas être aligné avec l'axe de boisseau sphérique. Une rainure peut être formée à l'intérieur de la douille et configurée pour recevoir la languette. La cavité, la languette et la rainure peuvent comprendre une pluralité de chacune de celles-ci.
PCT/CA2014/050020 2013-01-14 2014-01-14 Système, procédé et appareil pour un assemblage flexible pour un moteur de forage de fond de trou WO2014107813A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201361848858P 2013-01-14 2013-01-14
US61/848,858 2013-01-14

Publications (1)

Publication Number Publication Date
WO2014107813A1 true WO2014107813A1 (fr) 2014-07-17

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2553306A (en) * 2016-08-31 2018-03-07 Deepwater Oil Tools Ltd Apparatus for transmitting torque through a work string
JPWO2017094217A1 (ja) * 2015-12-02 2018-09-20 パナソニックＩｐマネジメント株式会社 球面軸受装置、および、スイッチ

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3733853A (en) * 1971-07-19 1973-05-22 W Sutliff Flexible drill string joint
US4982801A (en) * 1989-01-04 1991-01-08 Teleco Oilfield Services Inc. Flexible coupling for downhole motor
US8033917B2 (en) * 2008-04-30 2011-10-11 National Oilwell Varco, L.P. Drive shaft assembly for a downhole motor
WO2012039700A1 (fr) * 2010-09-21 2012-03-29 Todd Benson Ensemble joint homocinétique à rotule double, à couple élevé, flexible, pour moteur à boue utilisé dans le forage de puits directionnel

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3733853A (en) * 1971-07-19 1973-05-22 W Sutliff Flexible drill string joint
US4982801A (en) * 1989-01-04 1991-01-08 Teleco Oilfield Services Inc. Flexible coupling for downhole motor
US8033917B2 (en) * 2008-04-30 2011-10-11 National Oilwell Varco, L.P. Drive shaft assembly for a downhole motor
WO2012039700A1 (fr) * 2010-09-21 2012-03-29 Todd Benson Ensemble joint homocinétique à rotule double, à couple élevé, flexible, pour moteur à boue utilisé dans le forage de puits directionnel

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2017094217A1 (ja) * 2015-12-02 2018-09-20 パナソニックＩｐマネジメント株式会社 球面軸受装置、および、スイッチ
GB2553306A (en) * 2016-08-31 2018-03-07 Deepwater Oil Tools Ltd Apparatus for transmitting torque through a work string
WO2018042148A1 (fr) * 2016-08-31 2018-03-08 Deepwater Oil Tools Ltd. Appareil de transmission de couple à travers un train de tiges de travail
GB2553306B (en) * 2016-08-31 2019-02-27 Deltatek Oil Tools Ltd Apparatus for transmitting torque through a work string
US11015400B2 (en) 2016-08-31 2021-05-25 Deltatek Oil Tools, Ltd. Apparatus for transmitting torque through a work string
AU2017318540B2 (en) * 2016-08-31 2023-04-13 Deltatek Oil Tools Limited Apparatus for transmitting torque through a work string

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