Source: https://patents.justia.com/patent/7481281
Timestamp: 2019-06-17 09:21:30
Document Index: 99194368

Matched Legal Cases: ['Application No. 0', 'Application No. 0', 'arts 714', 'arts 714', 'arts 714', 'arts 726', 'arts 726', 'arts 726']

US Patent for Systems and methods for the drilling and completion of boreholes using a continuously variable transmission to control one or more system components Patent (Patent # 7,481,281 issued January 27, 2009) - Justia Patents Search
Justia Patents Boring Curved Or Redirected BoresUS Patent for Systems and methods for the drilling and completion of boreholes using a continuously variable transmission to control one or more system components Patent (Patent # 7,481,281)
Apr 26, 2004 - Intersyn IP Holdings, LLC
Latest Intersyn IP Holdings, LLC Patents:
The control mechanisms described by Ikeda et al. and Comeau et al. include shaft deflection assemblies that include eccentric rings, as shown in FIGS. 7a and 7b. This type of assembly is known in the art. The assembly includes two eccentric rings, inner ring 174 and outer ring 176, which are capable of relative rotation. Relative rotation between the two eccentric rings results in a relative displacement between the center of the outer ring and the center of the inner ring. The system can be designed such that at 0 degrees of rotation, the centers of the two eccentric rings coincide, as shown in FIG. 7a. The rings have a maximum displacement between their centers at 180 degrees of relative rotation, as shown in FIG. 7b. Such a system provides the ability to impart a controlled deflection on the drilling shaft at the location of the assembly.
A second group of push-the-bit systems exist that include non-rotating stabilizers. A side force is applied to the formation through a non-rotating assembly. Examples of such systems are illustrated in U.S. Pat. No. 5,979,570 to McLoughlin et al. and European Patent Application No. 0 744 526 by Oppelt et al., which are incorporated by reference as if fully set forth herein. FIGS. 9a and 9b are schematic diagrams illustrating a push-the-bit system utilizing a non-rotating sleeve and eccentric rings. FIGS. 10a and 10b are schematic diagrams illustrating a push-the-bit system utilizing a non-rotating sleeve and hydraulic action.
As shown in FIG. 9a, this push-the-bit system is attached to adapter sub 188, which would in turn be attached to the drill string (not shown). The adapter sub is attached to inner rotatable mandrel 190 and may not be necessary if the drill string pipe threads match the device threads. This mandrel is free to rotate within inner eccentric sleeve 192. Inner eccentric sleeve 192 may be turned freely within an arc by a drive means (not shown) inside the outer eccentric housing or mandrel 194, as shown in FIGS. 9a and 9b.
As further shown in FIG. 9a, inner rotating mandrel 190 is shown as being attached directly to drill bit 196. Outer housing 194 consists of a bore passing longitudinally through the outer sleeve which accepts the inner sleeve. The outer housing is eccentric on its outside clearly shown as “pregnant” portion 198. The pregnant portion or weighted side 198 of the outer housing forms the heavy side of the outer housing and is manufactured as a part of the outer sleeve. The pregnant housing contains the drive means for controllably turning the inner eccentric sleeve within the outer housing. Additionally, the pregnant housing may contain logic circuits, power supplies, hydraulic devices, and the like which are (or may be) associated with the “on demand” turning of the inner sleeve. Additional details of the system shown in FIGS. 9a and 9b can be found in U.S. Pat. No. 5,979,570.
As shown in FIGS. 10a and 10b, this push-the-bit system includes bit 198 coupled to hydraulic actuator assembly 200. The hydraulic actuator assembly is coupled to non-rotating sleeve assembly 202. The hydraulic actuator assembly may be configured such that a side force can be selectively applied to a formation (not shown) through non-rotating sleeve assembly 202. The amount and direction of the side force will vary depending on the direction in which drilling is desired. The amount and direction of the side force that is applied to the formation may be controlled by hydraulic control assembly 204, which is coupled to hydraulic actuator assembly 200. Additional details of the system shown in FIGS. 10a and 10b can be found in European Patent Application No. 0 744 526 A1.
FIGS. 3-7b are schematic diagrams illustrating cross-sectional views of point-the-bit rotary steerable systems that utilize shaft deflection;
FIG. 9a is a schematic diagram illustrating a cross-sectional view of a push-the-bit rotary steerable system that includes non-rotating stabilizers;
FIG. 9b is a schematic diagram illustrating a cross-sectional view of the system of FIG. 9a when viewed along plane A;
FIG. 10a is a schematic diagram illustrating a cross-sectional view of a push-the-bit rotary steerable system that includes non-rotating stabilizers;
FIG. 10b is a schematic diagram illustrating a cross-sectional view of the system of FIG. 10a when viewed along plane B;
FIGS. 14a and 14b are schematic diagrams illustrating cross-sectional side views of a CVT that includes planetary members;
FIGS. 14c-14e are schematic diagrams illustrating cross-sectional side views of a system that includes a CVT coupled to planetary gears;
FIG. 14f is a schematic diagram illustrating a cross-sectional view of the system of FIG. 14e when viewed along plane C;
FIGS. 14a and 14b illustrate one embodiment of a CVT that includes planetary members. This CVT may be included in any of the systems described herein. Referring to FIGS. 14a and 14b, this CVT mechanism is formed as a variable radius epicyclic mechanism having rolling traction torque transfer with the advantage that the shaft bearings and housing are not subject to large forces and the moving parts can be based on traditional roller and ball bearing technology. It also has the advantages that it includes a purely mechanical preload and torque sensing system and that it can be splash or grease lubricated by a known traction fluid lubricant without requiring special lubricating techniques. As will be appreciated from the description which follows, the control of the transmission ratio can be effected by a simple mechanical device.
The variable radius epicyclical transmission device shown in FIGS. 14a and 14b sometimes referred to as a variator, includes housing 700 within which is mounted input shaft 702 bearing rolling element bearings 704, 706 within planet cage 708 carrying three planet follower members 710. Planet follower members 710 are rotatably borne on planet cage 708 by planet follower shafts 712. In this example, planet cage 708 constitutes the output shaft of the transmission mechanism.
On input shaft 702 is carried radially inner race 714 which is engaged to shaft 702 by means of a coupling that includes a helical interengagement in the form of screw threaded engagement 716. Radially inner race 714 and screw threaded engagement 716 are configured such that a relative rotation of input shaft 702 and inner race parts 714, 718 in a one directional sense will cause the two parts to be displaced towards one another whereas axial separation of two race parts 714, 718 of the inner raceway occurs where there is relative rotation between them and input shaft 702 in the opposite directional sense. Such displacement of the inner race parts is further illustrated in FIG. 14b in high ratio displacement 720 and low ratio displacement 722. Axial displacement of the inner race parts 714, 718 is limited by priming spring 723, which urges the two inner race parts apart.
Outer raceway members 726, 728 are engaged by an axial adjustment mechanism generally indicated 730 and schematically shown in FIG. 14a as lever 732 pivotally mounted on reaction member 736 such that turning the lever in one direction or the other about pivot 734 by which it is connected to reaction member 736 causes raceway parts 726, 728 to be urged axially towards one another or allowed to separate axially from one another by means of outer race ball screw 729. The outer raceway is provided with means for preventing its rotation about the common axis of rotation of input shaft 702, inner and outer raceways, output shaft 708 and spherical planetary members 724.
In the configuration illustrated in FIG. 14b it will be seen that the radius of rolling contact between balls 724 and the inner raceway is relatively large and the radius of contact between balls 724 and the outer raceway is relatively small. In this configuration the transmission ratio between input shaft 702 and output shaft 708 is at its lowest. By allowing lever 732 to move in the opposite direction, however, the outer raceway parts are allowed to move apart so that balls 724 can move radially outwardly compensated by axial approach of the inner raceway parts.
Although as illustrated in FIG. 14a, the separation of two race parts 726, 728 is controlled by simple lever 732 with suitable counteracting member 736 applying symmetrical forces to two race parts 726, 728 to cause them to move together or apart as determined by the movement of lever 732, it will be appreciated that in a practical embodiment it is necessary to apply the axial forces to the raceway parts over the entirety of the circumference or at least at several symmetrically located positions.
FIGS. 14c-14f illustrate various ways in which a CVT similar to those described by Milner and shown in FIGS. 14a and 14b may be incorporated in a system configured to drill a borehole or any of the other systems described herein (e.g., a system configured to complete a well, etc.). The CVTs included in these systems may be configured as IVTs. As shown in FIG. 14c, this embodiment of the system is designed as having an internal mandrel type architecture. The system includes power supply unit 510 coupled to input shaft 512 of the CVT. The power supply unit may include any of the power supplies described herein. The CVT includes CVT roller ball 516 and CVT toroids 518. The CVT may be further configured as described above in FIGS. 14a and 14b in the patents and patent applications of Milner that are incorporated by reference above.
As shown in FIG. 14c, the CVT is coupled to input planetary gears 514 and output planetary gears 520. Input planetary gears 514 and output planetary gears 520 may function as fixed gear ratio devices as described further herein. In addition, the input and output planetary gears may be configured such that the CVT functions as an IVT. The input and output planetary gears may be further configured as described by Milner.
The system may also include CVT control arm 522, which may be configured as described herein. Output shaft 524 of the CVT is coupled to adjustment device 526. The adjustment device may include any suitable adjustment device known in the art. The adjustment device is coupled to bit shaft 528. Bit shaft 528 may include any suitable bit shaft known in the art. Pivot knuckle 530 may also be coupled to bit shaft 528. The system shown in FIG. 14c may be further configured as described herein.
As shown in FIG. 14d, this embodiment of the system is designed as having an annular type architecture. In other words, this system includes central cylinder 532 through which drilling fluid can flow. This system also includes power supply unit 534 coupled to input shaft 536 of CVT 538. Power supply unit 534 may include any of the power supplies described herein or known in the art. CVT 538 may be further configured as described by Milner in any of the patents or patent applications incorporated herein by reference.
The system also includes control arm 544 coupled to the CVT, which may be configured as described herein. Electronics 546 may also be coupled to the CVT. The control arm and the electronics may be further configured as described herein and may form at least a portion of a control subsystem. Output shaft 548 of the CVT may be coupled to bit shaft 550 by pivot knuckle 552. The system shown in FIG. 14d may be further configured as described herein.
The system shown in FIGS. 14e and 14f is also designed as having an annular type architecture. For example, like the system shown in FIG. 14d, the system shown in FIGS. 14e and 14f includes central cylinder 554 through which drilling fluid can flow. The system shown in FIGS. 14e and 14f includes a power supply unit (not shown) coupled to input shaft 556 of the CVT. The power supply unit may include any power supply described herein or known in the art. The CVT includes CVT toroids 558, CVT roller ball 560, and CVT follower assembly 562. The CVT may be further configured as described by Milner in any of the patents or patent applications incorporated herein by reference.
Input planetary gears 564 and output planetary gears 566 are coupled to the CVT. Input planetary gears 564 and output planetary gears 566 may function as fixed gear ratio devices as described further herein. In addition, the input and output planetary gears may be configured such that the CVT functions as an IVT. The input and output planetary gears may be further configured as described by Milner. CVT control arm 568 may be coupled to the CVT. The CVT control arm may be configured as described herein. Output shaft 570 of the CVT may be coupled to a bit shaft or other system elements (not shown) as described herein. The system shown in FIGS. 14e and 14f may be further configured as described herein.
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International Search Report, PCT/US2004/012753, mailed Dec. 15, 2004.
Patent number: 7481281
Patent Publication Number: 20040262043
Assignee: Intersyn IP Holdings, LLC (Houston, TX)
Inventor: Stuart Schuaf (Houston, TX)
Application Number: 10/831,975
Current U.S. Class: Boring Curved Or Redirected Bores (175/61); Using A Resistance Strain Gage (73/862.045); With Above Ground (1) Motor Carried By Casing Or Casing Support Or (2) Well Fluid Pump (166/68.5); Automatically Controlled (74/113); Plural Fluid Power Paths To Planetary Gearing (475/73); Pump And Motor In Series With Planetary Gearing (475/83); Toroidal (476/40); And Load Responsive (474/12); Adjustable To Impacting Device (173/48)