• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Downhole Motor for Directional Drilling A downhole motor for directional drilling includes a drive shaft assembly that includes a drive shaft housing and a drive shaft rotatably disposed within the drive shaft housing. further, the downhole motor includes a bearing assembly including a bearing housing and a bearing mandrel rotatably disposed within the bearing housing. the bearing chuck has a first end directly connected to the drive shaft with a universal joint and a second end coupled to a drill bit. in addition, the downhole motor includes an adjustment chuck configured to adjust the acute angle of deflection (theta) between the central axis of the bearing housing and the central axis of the drive shaft housing. the adjustment mandrel has a central axis aligned coaxially with the bearing housing, a first end coupled with the drive shaft housing and a second end coupled with the bearing housing.
    公开号:BR112015021667B1
    申请号:R112015021667-6
    申请日:2014-02-10
    公开日:2022-01-11
    发明作者:Nicholas Ryan Marchand；Jonathan Ryan Prill
    申请人:National Oilwell Varco, L.P.；
    IPC主号:
    专利说明:

    REFERENCE TO RELATED ORDERS
    [001] This application claims priority to US Application No. 13/786,076, filed March 5, 2013 and entitled “Adjustable Bend Assembly for a Downhole Motor”, which is hereby incorporated herein by reference in its entirety for all the purposes. DECLARATION REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT
    [002] Not applicable FUNDAMENTALS OF THE INVENTION Description Field
    [003] The description refers generically to downhole engines, used to drill boreholes in terrestrial formations, for the final recovery of oil, gas or minerals. More particularly, the description pertains to downhole motors, including adjustable curve assemblies for directional drilling. Technology Fundamentals
    [004] In drilling a borehole in a terrestrial formation, such as for the recovery of hydrocarbons or minerals from a subsurface formation, it is conventional practice to attach a bit to the lower end of a drill string formed from a plurality of gaskets. pipe connected end-to-end and then rotate the drill string so that the bit advances down into the earth to create a borehole along a predetermined trajectory. In addition to pipe joints, the drill string typically includes heavier tubular members, known as drill collars, positioned between the pipe joints and the drill bit. Drill collars increase the vertical load applied to the drill to increase its operating efficiency. Other accessories commonly incorporated into drillstrings include stabilizers, to assist in maintaining the desired direction of the drilled hole, and reamers to ensure that the drilled hole is maintained at a desired gauge (ie, diameter). In vertical drilling operations, the drill string and bit are typically rotated across the surface with a top diver or rotary table.
    [005] During drilling operations, the drilling fluid or mud is pumped under pressure down the drill string, out of the drill face, into the drill hole, and then circular crown above, between the drill string and the sidewall of the borehole to the surface. Drilling fluid, which can be water-based or oil-based, is typically viscous, to increase its ability to transport drillhole cuttings to the surface. Drilling fluid can perform a number of other valuable functions, including increasing the bit's performance (e.g., by injecting fluid under pressure through the bit holes, creating jets of mud that are blasted inside and weaken the underlying formation in anticipation of the bit), cooling the bit and forming a protective cake over the borehole wall (to stabilize and seal the borehole wall).
    [006] Recently, it has become increasingly common and desirable in the oil and gas industry to drill horizontal and other non-vertical or offset boreholes (i.e. “directional drilling”), to facilitate greater description of and greater production from larger regions. formations containing subsurface hydrocarbons than would be possible using only vertical boreholes. In directional drilling, specialized drill string components and “downhole assemblies” (BHAs) are often used to induce, monitor and control deviations in the bit path in order to produce a drillhole of the desired offset configuration.
    [007] Directional drilling is typically performed using a downhole or mud motor provided in the downhole assembly (BHA) at the lower end of the drill string immediately above the bit. Downhole motors typically include several components, such as, for example, (in order starting from the top of the motor): (1) a power section including a stator and rotor rotatably disposed within the stator; (2) a drive shaft assembly including a drive shaft disposed within a housing, with the upper end of the drive shaft being coupled to the lower end of the rotor; and (3) a bearing assembly positioned between the driveshaft assembly and the bit to support radial and thrust loads. For directional drilling, the motor often includes a curved housing to provide a deflection angle between the bit and the BHA. The deflection angle is usually between 0° and 5°. The axial distance between the bottom end of the bit and the curve inside the motor is commonly referred to as the “bit-to-curve” distance.
    [008] To drill straight sections of the drillhole with a curved motor, the entire drillstring and BHA are rotated from the surface with the drillstring, thereby rotating the bit around the longitudinal axis of the drillstring; and to change the borehole trajectory, the bit is rotated exclusively with the downhole motor, thereby enabling the bit to rotate around its own central geometric axis, which is oriented at the deflection angle relative to the drill string. , due to the curved housing. Since the bit is inclined (i.e., oriented at the angle of deflection) when the entire drill string is rotated while drilling through straight sections, the downhole motor is subjected to bending moments, which can result in potentially harmful in critical locations inside the engine. BRIEF SUMMARY OF DESCRIPTION
    [009] These and other needs of the technique are addressed in one embodiment by a downhole motor for directional drilling. In one embodiment, the downhole motor comprises a drive shaft assembly, including a drive shaft housing and a drive shaft rotatably disposed within the drive shaft housing. The drive shaft housing has a central axis, a first end, and a second end opposite the first end. The drive shaft has a central axis, a first end and a second end opposite the first end. Furthermore, the downhole motor comprises a bearing assembly, including a bearing housing and a bearing mandrel rotatably disposed within the bearing housing. The bearing housing has a central axis, a first end comprising a connector and a second end opposite the first end. The bearing chuck has a central axis, coaxially aligned with the central axis of the bearing housing, a first end directly connected to the second end of the drive shaft with a universal joint, and a second end coupled to a drill bit. Furthermore, the downhole motor comprises an adjustment mandrel configured to adjust an acute deflection angle θ between the central axis of the bearing housing and the central axis of the drive shaft housing. The adjustment mandrel has a central axis coaxially aligned with the central axis of the bearing housing, a first end and a second end opposite the first end. The first end of the adjustment mandrel is coupled to the second end of the drive shaft housing and the second end of the adjustment mandrel is coupled to the first end of the bearing housing.
    [0010] These and other needs of the technique are addressed in another embodiment by a downhole motor for directional drilling. In one embodiment, the downhole motor comprises a drive shaft assembly including a drive shaft housing and a drive shaft rotatably disposed within the drive shaft housing. The drive shaft housing has a central axis, a first end, and a second end opposite the first end. The drive shaft has a central axis, a first end and a second end opposite the first end. Furthermore, the downhole motor comprises a bearing assembly including a bearing housing and a bearing mandrel coaxially disposed within the bearing housing. The bearing housing has a central axis, a first end and a second end opposite the first end. The bearing chuck has a first end pivotally coupled to the second end of the drive shaft and a second end coupled to the bit. The first end of the bearing chuck extends from the bearing housing into the drive shaft housing. Furthermore, the downhole motor comprises an adjustment mandrel, having a first end coupled to the second end of the drive shaft housing and a second end coupled to the first end of the bearing housing. The rotation of the adjustment chuck relative to the drive shaft housing is configured to adjust an acute deflection angle θ between the central axis of the drive shaft housing and the central axis of the bearing housing.
    [0011] These and other needs of the technique are addressed in another embodiment by a downhole motor for directional drilling. In one embodiment, the downhole motor comprises a drive shaft assembly including a drive shaft housing and a drive shaft rotatably disposed within the drive shaft housing. The drive shaft housing has a central axis, a first end, and a second end opposite the first end. The drive shaft has a central axis, a first end, a second end opposite the first end, and a receptacle extending axially from the second end of the drive shaft. Furthermore, the downhole motor comprises a bearing assembly including a bearing housing and a bearing mandrel rotatably disposed within the bearing housing. The bearing housing has a central axis, a first end and a second end opposite the first end. The bearing chuck has a first end pivotally coupled to the drive shaft and a second end coupled to the bit. The first end of the bearing chuck is disposed within the drive shaft receptacle. The central axis of the drive shaft housing is oriented at an acute deflection angle θ relative to the central axis of the bearing housing.
    [0012] The modalities described here comprise a combination of details and advantages intended to address various defects associated with certain devices, systems and prior methods. The foregoing has rather broadly summarized the technical details and advantages of the invention, in order that the detailed description of the invention which follows may be better understood. The various features described above, as well as other details, will be readily apparent to those skilled in the art, upon reading the following detailed description and by referring to the accompanying drawings. It should be appreciated by those skilled in the art that the design and specific embodiments described can be readily used as a basis for modifying or designing other structures to accomplish the same purposes of the invention. It should also be understood by those skilled in the art that such equivalent constructions do not deviate from the spirit and scope of the invention, as described in the appended claims. BRIEF DESCRIPTION OF THE DRAWINGS
    [0013] For a detailed description of preferred embodiments of the description, reference will now be made to the accompanying drawings, in which: Figure 1 is a schematic partial cross-sectional view of a drilling system including an embodiment of a borehole mud motor below, in accordance with the principles described herein; Figure 2 is a partial-sectional perspective view of the force section of Figure 1; Figure 3 is an extreme cross-sectional view of the force section of Figure 1; Figure 4 is an enlarged cross-sectional view of the slurry engine of Figure 1 illustrating the drive shaft assembly, bearing assembly and curve fit assembly; Figure 5 is an enlarged cross-sectional view of the lower housing section of the drive shaft housing of Figure 4; Figure 6 is an enlarged cross-sectional view of the bearing assembly and curve fit assembly of Figure 4; Figure 7 is an enlarged cross-sectional view of the chuck Figure 4 adjustment 1; Figure 8 is an enlarged cross-sectional view of the adjustment chuck and lower housing section of the drive shaft housing of Figure 4; Figure 9 is an enlarged cross-sectional view of the lower housing of the drive shaft assembly and adjustment ring of Figure 4, rotationally locked together. Figure 10 is an enlarged cross-sectional view of the lower housing of the drive shaft assembly and adjustment ring of Figure 4, rotationally unlocked; and Figure 11 is a cross-sectional view of another embodiment of a bearing chuck in accordance with the principles described herein. DETAILED DESCRIPTION OF THE PREFERRED MODALITIES
    [0014] The following discussion is addressed to several exemplary embodiments. However, one skilled in the art will understand that the examples described herein have wide application and that the discussion of any embodiment is intended only to be exemplary of that embodiment and not intended to suggest that the scope of the description, including the claims, is limited. to that modality.
    [0015] Certain terms are used throughout the following description and claims to refer to particular details or components. As one skilled in the art will appreciate, different people may refer to the same detail or component by different names. This document is not intended to distinguish between components or details that differ in name but not in function. Drawing figures are not necessarily to scale. Certain details and components here may be shown exaggerated to scale or in somewhat schematic form and some details of conventional elements may not be shown in the interests of clarity and brevity.
    [0016] In the following discussion and claims, the terms "including" and "comprising" are used in an unlimited manner and thus shall be interpreted to mean "including" but not limited to "".It is also intended that the term " couple” or “couple” means an indirect or direct connection. Thus, if a first device couples with a second device, that connection can be through a direct connection or through an indirect connection via other devices, components and connections. Furthermore, as used herein, the terms "axial" and "axially" generally mean along or parallel to a central axis (e.g., central axis of a body or an orifice), while the terms "radial" and “radially” generally mean perpendicular to the central axis. For example, an axial distance refers to a distance measured along or parallel to the central axis, and a radial distance means a distance measured perpendicular to the central axis. Any reference to up or down in the description and claims is made for purposes of clarity, with “up”, “top”, “up”, “top of well” or “upstream” meaning towards the surface of the borehole. borehole and with “down”, “bottom”, “down”, “downhole” or “downstream” meaning towards the terminal end of the borehole, irrespective of the borehole orientation.
    [0017] Referring now to Figure 1, a system 10 for drilling a borehole 16 in a land formation is shown. In this embodiment, the system 10 includes a surface-disposed probe 20, a drillstring 21 extending downhole from the drillstring 20, a downhole assembly (BHA) 30 coupled to the lower end of the drillstring 21 and a drill bit 90 attached to the lower end of the BHA 30. A downhole mud motor 35 is provided in the BHA 30 to facilitate drilling of bypassed parts of the borehole 16. Moving down along the BHA 30, the motor 35 includes a hydraulic transmission or power section 40, a drive shaft assembly 100, and a bearing assembly 200. The portion of the BHA 30 disposed between the drill string 21 and the motor 35 may include other components, such as collars. drill bits, drill-while-measure (MWD) tools, reamers, stabilizers and the like.
    [0018] The force section 40 converts the pressure of the drilling fluid pumped down through the drill string 21 into rotational torque to drive the rotation of the bit 90. The drive shaft assembly 100 and bearing assembly 200 transfer torque generated in the force section 40 for the bit 90. With force or weight applied to the bit 90, also referred to as weight-on-the-bit (“WOB”), the rotary bit 90 engages the land formation and proceeds to form the borehole 16 along a predetermined path towards a target zone. The drilling fluid or mud pumped down the drill string 21 down and through the motor 30 passes out of the face of the drill bit 90 and back to the annulus 18 above, formed between the drill string 21 and the wall 19 of the borehole 16 Drilling fluid cools the bit 90 and jets the chips away from the face of the bit 90 and carries the chips to the surface.
    [0019] Referring now to Figures 2 and 3, the hydraulic transmission section 40 comprises a helical-shaped rotor 50, preferably made of steel, which may be chrome-galvanized or coated for wear and corrosion resistance, disposed within a stator 60, comprising a cylindrical stator housing 65, coated with a helical shaped elastomeric insert 61. The helical shaped rotor 50 defines a set of rotor lobes 57, which intermesh with a set of stator lobes 67, defined by the helical shaped insert 61. As best shown in Figure 7, rotor 50 has one less lobe 57 than stator 60. When rotor 50 and stator 60 are assembled, a series of cavities 70 are formed between the outer surface 53 of rotor 50 and the inner surface 63 of stator 60. Each cavity 70 is sealed from adjacent cavities 70 by seals formed along lines of contact between rotor 50 and stator 60. 58 of rotor 50 is radially offset from central axis 68 of stator 60 by a fixed amount known as the "eccentricity" of the rotor-stator assembly. Accordingly, rotor 50 can be described as eccentrically rotating within stator 60.
    [0020] During operation of hydraulic transmission section 40, fluid is pumped under pressure into one end of hydraulic transmission section 40, where it fills a first set of open cavities 70. A pressure differential across adjacent cavities 70 forces rotor 50 to rotate relative to stator 60. As rotor 50 rotates within stator 60, adjacent cavities 70 are opened and filled with fluid. When this rotation and filling process is repeated in a continuous manner, the fluid progressively flows down the hydraulic transmission section 40 and continues to drive rotation of the rotor 50. The drive shaft assembly 100, shown in Figure 1, includes a drive shaft discussed in more detail below, which has an upper end coupled to the lower end of rotor 50. Rotational motion and torque from rotor 50 are transferred to bit 90 via drive shaft assembly 100 and assembly bearing 200.
    [0021] In this embodiment, the drive shaft assembly 100 is coupled to an outer housing 210 of the bearing assembly 200, with a curve adjustment assembly 300, which provides an adjustable curve along the motor 35. Due to curve 301 , a deflection angle θ is formed between the central axis 95 of the drill bit 90 and the longitudinal axis of the drill string 21. To drill a straight section of borehole 16, the drill string 21 is rotated by the probe 20 with a rotary table or top drive for turning the BHA 30 and drill bit 90 attached thereto. The drill string 21 and BHA 30 rotate about the longitudinal axis of the drill string 21 and thus the drill bit 90 is also forced to rotate about the longitudinal axis of the drill string 21.
    [0022] Referring again to Figure 1, with the bit 90 arranged at the deflection angle θ, the lower end of the BHA 30 distal of the bit 90 seeks to move in an arc around the longitudinal axis 25 of the drill string 21 when it rotates, but is constrained by the sidewall 19 of the borehole 16, thereby imposing bending moments and associated stresses on the BHA 30 and the mud motor 35. In general, the magnitudes of such bending moments and associated stresses are directly related to the drill-to-curve D distance - the greater the drill-to-curve D distance, the greater the bending moments and stresses experienced by the BHA 30 and the mud motor 35.
    [0023] In general, the drive shaft assembly 100 functions to transfer torque from the eccentrically rotating rotor 50 of the force section 40 to a concentrically rotating bearing chuck 220 of the bearing assembly 200 and drill bit 90. As best seen in Figure 3, rotor 50 rotates about rotor axis 50 in the direction of arrow 54 and radial axis 58 rotates about stator axis 68 in the direction of arrow 55. However, drill 90 and bearing chuck 220 are coaxially aligned and rotate about a common axis, which is offset and/or oriented at an acute angle relative to rotor axis 58. Thus, drive shaft assembly 100 converts the eccentric rotation of rotor 50 into concentric rotation of the bearing chuck 220 and drill bit 90, which are radially offset and/or angularly inclined with respect to the rotor axis 58.
    [0024] Referring now to Figure 4, the drive shaft assembly 100 includes an outer housing 110 and a one-piece (i.e. unitary) drive shaft 120 rotatably disposed within the housing 110. The housing 110 has a linear or longitudinal central axis 115. An upper end 110a coupled end-to-end with the lower end of the stator housing 65 and a lower end 110b coupled to the housing 210 of the bearing assembly 200, via the curve fit assembly 300. As best shown in Figure 1, in this embodiment, the drive shaft housing 110 is coaxially aligned with the stator housing 65, however, due to the curve 301 between the drive shaft assembly 100 and the bearing assembly 200, drive shaft housing 100 is oriented at deflection angle θ relative to bearing assembly 200 and drill bit 90.
    [0025] In this embodiment, the drive shaft housing 110 is formed from a pair of coaxially aligned, generally tubular housings connected together end-to-end. That is, the drive shaft housing 110 includes a first or upper housing section 111 extending axially from the upper end 110a and a second or lower housing section 116 extending axially from the lower end 110b to the upper housing section 111 The upper housing section 111 has a first or upper end 111a coincident with the end 110a and a second or lower end 111b coupled with the lower housing section 116. The upper end 110a, 111a comprises a threaded connector 112 and the lower end 111b comprises a threaded connector 113. The threaded connectors 112, 113 are coaxially aligned, each being concentrically disposed about axis 115. In this embodiment, the connector 112 is an externally threaded connector or pin end, and the connector 113 is an internally threaded connector or box end.
    [0026] Referring now to Figures 4 and 5, the lower housing section 116 has a first or upper end 116a coupled to the upper housing section 111 and a second or lower end 116b coincident with the end 110b. The upper end 116a comprises a threaded connector 117 and the lower end 110b, 116b comprises a threaded connector 118. The threaded connector 117 is coaxially aligned with the connectors 112, 113 and concentrically disposed about the axis 115, however, the threaded connector 118 is concentrically disposed about an axis 118a, oriented at a non-zero acute angle α, relative to axis 115. In this embodiment, connector 117 is an externally threaded connector or pin end, and connector 118 is a connector. or internally connected box end. Thus, axis 18a is the central axis of the inner threaded cylindrical surface of lower housing section 116 at end 116b. Therefore, the connector 18 can be described as being "displaced". Angle α is preferably greater than 0° and less than or equal to 2°.
    [0027] The externally threaded connector 112 of the upper housing section 111 threadably engages an internally threaded union or box end connector disposed at the lower end of the stator housing 65, and internally threaded connector 113 of the upper housing section 111 threadably engages externally joining the threaded connector 117 of the lower housing section 116. As will be described in more detail below, the lower end 110b, 116b of the lower housing section 116, and in particular the threaded internally offset connector 118, of threaded manner engages an externally threaded union component of the 300 curve fit assembly.
    [0028] The drive shaft housing 110 has a through hole or passage 114 axially extending between the ends 110a, 110b. Hole 114 defines a radially inner surface 119 within housing 110 that includes a first or upper annular recess 119a and a second or lower annular recess 119b axially spaced below recess 119a. In this embodiment, the upper recess 119a is disposed along the upper housing section 111 and the lower recess 119b is disposed along the lower housing section 116. The recesses 119a, 119b are arranged in a radius that is greater than the rest. of the inner surface 119 and provides sufficient space for movement (rotation and pivoting) of the drive shaft 120.
    [0029] Referring again to Figure 4, the drive shaft 120 has a linear central or longitudinal axis 125, a first or upper end 120a and a second or lower end 120b and opposite end 120a. Upper end 120a is pivotally coupled to lower end of rotor 50 with drive shaft adapter 130 and universal joint 140, and lower end 120b is pivotally coupled to upper end 220a of bearing chuck 220 with universal joint 140 In this embodiment, the upper end 120a and a universal joint 140 are disposed within the drive shaft adapter 130, while the lower end 120b comprises an axially extending countersunk or receptacle 121, which receives the upper end 220a of the chuck. bearing 220 and a universal joint 140. Thus, the upper end 120a may also be referred to as a male end 120a and the lower end 120b may also be referred to as a female end 120b.
    [0030] The drive shaft adapter 130 extends along a central or longitudinal axis 135, between a first upper end 130a, coupled to the rotor 50, and a second or lower end 130b, coupled to the upper end 120a of the drive shaft 120. Upper end 130a comprises a male pin or externally threaded pin end 131 131, which threadably engages a female housing or junction box end at the lower end of rotor 50. A receptacle or countersink 132 extends - axially (with respect to the axis 135) of the end 130b. The upper male end 120a of the drive shaft 120 is disposed within the counterbore 132 and pivotally coupled with the adapter 130 with a universal joint 140 disposed within the counterbore 132.
    [0031] Universal joints 140 allow ends 120a, 120b to pivot with respect to adapter 130 and bearing mandrel 220, respectively, while transmitting rotational torque between rotor 50 and bearing mandrel 220. Specifically, upper universal joint 140 allows upper end 20a to pivot relative to upper adapter 130 about an upper pivot point 121a and lower universal joint 140 allows lower end 120b to pivot relative to bearing mandrel 220 about a lower pivot point 121b. Upper adapter 130 is coaxially aligned with rotor 50 (i.e., upper adapter axis 135 and rotor axis 58 are coaxially aligned). Since the rotor shaft 58 is radially offset and/or oriented at an acute angle relative to the central axis of the bearing chuck 220, the axis 225 of the drive shaft 120 is inclined or oriented at an acute angle relative to the axis geometry 115 of housing 110, axis 58 of rotor 50, and center axis 225 of bearing mandrel 220. However, universal joints 140 accommodate angularly inclined drive shaft 120, while simultaneously allowing rotation of drive shaft 120 within of housing 110. Ends 20a, 120b and corresponding universal joints 140 are axially positioned within recesses 119a, 119b, respectively, of housing 110, which provide clearance for end 120b, 130b when drive shaft 120 simultaneously rotates and pivots in from housing 110.
    [0032] In general, each universal joint 140 may comprise any joint or coupling that permits two parts, which are coupled together and not coaxially aligned with each other (e.g., drive shaft 120 and adapter 30 oriented at an acute angle relative to each other), limited freedom of movement in any direction while transmitting rotary motion and torque including, without limitation, universal joints (Cardan joints, Hardy-Spicer joints, Hooke joints etc.), constant velocity joints or any other designed joint custom made.
    [0033] As previously described, adapter 130 couples drive shaft 120 to the lower end of rotor 50. During drilling operations, high pressure drilling fluid or mud is pumped under pressure down the drill string 21 and through cavities. 70 between rotor 50 and stator 60, causing rotor 50 to rotate in relation to stator 60. Rotation of rotor 50 drives rotation of adapter 130, drive shaft 120, bearing assembly chuck and drill bit 90. drilling fluid flowing to the drill string below 21, through force section 40, also flows through the drive shaft assembly 100 and bearing assembly 200 to the bit 90, where the drilling fluid flows through the nozzles on the bit face. 90, into the o-ring 18. Within the drive shaft assembly 100 and the upper part of the bearing assembly 200, drilling fluid flows through the o-ring 150 formed between the drive shaft housing 200 and the top of the bearing assembly 200. 110 and drive shaft 120, and between drive shaft housing 110 and bearing chuck 220 of bearing assembly 200.
    [0034] Referring now to Figures 4 and 6, bearing assembly 200 includes bearing housing 210 and one-piece (i.e., unitary) bearing mandrel 220, rotatably disposed within housing 210. Bearing housing 210 has a linear central or longitudinal axis 215, a first or upper end 210a coupled to the lower end 110b of the drive shaft housing 110 with curve fit assembly 300, a second or lower end 210b, and a central through hole or passage 214 extending axially between ends 210a, 210b. The bearing housing 10 is coaxially aligned with the bit 90, however, due to the curve 301 between the drive shaft assembly 100 and the bearing assembly 200, the bearing housing 210 is oriented at the deflection angle θ relative to the bearing housing 200. drive shaft 110.
    [0035] In this embodiment, the bearing housing 210 is formed from a pair of generally tubular housings connected together end-to-end. That is, the housing 210 includes a first or upper housing section 211 extending axially from the upper end 210a and a second or lower housing section 216 extending axially from the lower end 210b to the housing section 211. upper housing 211 has a first or upper end 211a coincident with end 210a and a second or lower end 211b mated with lower housing section 216. Upper end 210a, 211a comprises a threaded connector 212 and lower end comprises a connector threaded connectors 213. Threaded connectors 212, 213 are coaxially aligned, each being concentrically disposed about axis 215. In this embodiment, connector 212 is an externally threaded connector or pin end and connector 213 is a connector or threaded end. internally threaded housing.
    [0036] Referring further to Figures 4 and 6, the lower housing section 216 has a first or upper end 216a coupled to the upper housing section 211 and a second or lower end 216b coincident with the end 210b. Upper end 216a comprises a threaded connector 217, coaxially aligned with axis 215. In this embodiment, connector 217 is an externally threaded connector or pin end. The internally threaded connector 213 of the upper housing section 211 threadably engages the externally threaded union connector 217 of the lower housing section 211. As will be described in more detail below, the upper end 210b, 211a of the upper housing section 211 and, in particular, the externally threaded connector 212 threadably engages an internally threaded connector joining the curve fit assembly 300.
    [0037] Referring further to Figures 4 and 6, the bearing mandrel 220 has a central axis 225 coaxially aligned with the central axis 215 of the housing 210, a first upper end 220a, a second lower end 220b and a through passage hub 221 extending axially from lower end 220b and terminating axially below upper end 220a. Upper end 220a of mandrel 20 extends axially from upper end 210a of bearing housing 210 into passage 114 of drive shaft housing 110. Further upper end 220a is directly coupled to lower end 120b of drive shaft 110. drive via a universal joint 140. In particular, the upper end 220a is disposed within the receptacle 121 at the lower end 120b of the drive shaft 120 and pivotally coupled thereto with a universal joint 140. The lower end 20b of the mandrel 220 is coupled to the drill 90.
    [0038] The mandrel 220 also includes a plurality of circumferentially spaced and axially spaced drilling fluid holes 222, extending radially from the passage 221 to the outer surface of the mandrel 220. The holes 222 provide fluid communication between the o-ring 150 and passage 221. During drilling operations, mandrel 220 is rotated about axis 215 with respect to housing 210. In particular, high pressure drilling mud is pumped through force section 40 to drive the rotation of rotor 50 which in turn drives rotation of drive shaft 120, chuck 220 and bit 90. Drilling mud flowing through force section 40 flows through o-ring 150, holes 222 and passage 221 from chuck 220 en route to drill 90.
    [0039] When abrasive drilling fluid flows from o-ring 150 into holes 222, uneven distribution of drilling fluid between holes 222 can result in excessive erosion - in general, holes (e.g., holes 222 ) that drain a larger volume of drilling fluid experience greater erosion than holes that drain a smaller volume of drilling fluid. However, in this embodiment, the o-ring 150 and holes 222 are sized, shaped and oriented to facilitate a more uniform distribution of drilling fluid between the different holes 222, thereby offering the potential to reduce excessive erosion of certain holes 222. More specifically , each hole 222 is oriented at an angle of 45° with respect to the axis 225 of the mandrel 220. In addition, the radial width of the annulus 150 decreases movement axially towards the holes 222. That is, the annulus portion 150 disposed around the bearing mandrel 220 has three axially adjacent segments or sections that decrease in radial width moving axially toward the holes 222. Moving toward the holes 222, the o-ring 150 includes a first axial segment 150a, having a radial width W150a measured radially from the bearing mandrel 220 to the housing 110, a second axial segment 150b adjacent the second socket 150a having a radial width W150b measured radially from the bearing mandrel 220 to an adjustment mandrel 310 disposed within the recess 110, and a third axial segment 150c adjacent the segment 150b, having a radial width W150c measured radially from the bearing mandrel 220 to the adjustment mandrel 310. Radial widths W150a, W150b and W150c progressively decrease, moving axially toward holes 222. Computational fluid dynamics (CFD) modeling indicates the angular orientation of holes 222, and stepwise decrease in width of the o-ring 150, moving axially towards the holes 222, more evenly distributes the drilling fluid between the different holes 222.
    [0040] Referring again to Figure 4, as previously described in this embodiment, the drive shaft 120 is a one-piece, unitary and the bearing mandrel 220 is a unitary, one-piece. In particular, the end 120a of the drive shaft 120 is coupled to the rotor 50 with a drive shaft adapter 130 and universal joint 140, and the end 120b of the drive shaft 120 is coupled to the bearing mandrel 220 with receptacle 121 and gasket. universal 140. However, between ends 120a, 120b, coupled to rotor 50 and bearing mandrel 220, drive shaft adapter 120 is a single unitary, monolithic structure devoid of gaskets (eg, universal joints). Similarly, end 220a of bearing mandrel 220 is coupled to drive shaft 120 via receptacle 121 and universal joint 140 and end 220b of bearing mandrel 220 is coupled to a drill bit. However, between the ends 220a, 220b coupled to the drive shaft 120 and the bit, the bearing mandrel 220 is a single unitary, monolithic structure devoid of gaskets (e.g., universal joints). Consequently, between the rotor 50 and the bit only two universal joints 140 are provided along the drive train comprising the drive shaft 120 and the bearing mandrel 220. Furthermore, only one universal joint is provided between the drive shaft 120. and the bearing mandrel 220. Providing only a single universal joint 140 between the drive shaft 120 and the mandrel 220 eliminates any intermediate universal joints, which can increase the strength of the coupling between the drive shaft 120 and the bearing chuck 220. chuck 220, as well as facilitating further reduction of the drill-to-curve D distance. In other embodiments, the drive shaft (e.g. drive shaft 120) and/or the bearing chuck (e.g. housing 220) can contain a variable number of universal joints (eg universal joints 140).
    [0041] Referring further to Figures 4 and 6, housing 210 has a radially inner surface 128 defining through passage 214. Inner surface 218 includes a plurality of axially spaced apart annular shoulders. Specifically, inner surface 218 includes a first annular shoulder 218a. The shoulders 218a, 218b face each other. The first annular shoulder 218a is formed along the inner surface 218 of the upper housing section 211 and the second annular shoulder 218b is defined by the end 216a of the lower housing section 216. The mandrel 220 has a radially outer surface 223 including an annular shoulder. 223a axially aligned with shoulder 218b.
    [0042] As best shown in Figure 6, a plurality of annular crowns are positioned between the chuck 220 and the housing 210. In particular, a first or upper annular crown 250 is axially positioned between the housing shoulders 218a and 210a, a second or intermediate ring 251 is axially positioned between lug 218a and lugs 223, 218b, and a third or lower ring 252 is axially positioned between lug 223a, 218b and end 210b. An upper radial bearing 260 is arranged in the upper O-ring 250, a thrust bearing assembly 261 is arranged in the intermediate O-ring 251, and a lower radial bearing 262 is arranged in the lower O-ring 252.
    [0043] Upper radial bearing 260 is arranged around mandrel 220 and axially positioned above thrust bearing assembly 261 and lower radial bearing 262 is arranged around mandrel 220 and axially positioned below thrust bearing assembly 261 In general, radial bearings 260, 262 allow rotation of mandrel 220 with respect to housing 210, while simultaneously supporting radial forces therebetween. In this embodiment, the upper radial bearing 260 and the lower radial bearing 262 are both sleeve-type bearings, which slidably engage the cylindrical surfaces of the outer surface 223 of the mandrel 220. However, in general, any suitable type of bearing(s) can be employed. , including, without limitation, needle roller bearings, radial ball bearings, or combinations thereof. The annular thrust bearing assembly 261 is arranged around the chuck 220 and allows rotation of the chuck 220 with respect to the housing 210 while simultaneously supporting axial loads in both directions (e.g., off-bottom axial loads). and over-the-bottom). In this ®, the thrust bearing assembly 261 generally comprises a pair of caged roller bearings and corresponding beds, with the center bed threadnably engaged with the bearing mandrel 220. Although this embodiment includes a single thrust bearing assembly 261 arranged in an O-ring 251, and other embodiments more than one thrust bearing assembly (e.g., thrust bearing assembly 261) may be included, and in addition, the thrust bearing assemblies may be arranged in the same or different thrust bearing chambers (eg two-prong or four-prong thrust bearing chambers).
    [0044] In this embodiment, radial bearings 260, 262 and thrust bearing assembly 261 are oil sealed bearings. In particular, an upper seal assembly 270 is radially positioned between the upper end 210a of the housing 210 and the mandrel 220, and a lower seal assembly 271 is radially positioned between the lower end 210b of the housing 210 and the mandrel 220. seals 270, 271 provide annular seals between housing 210 and mandrel 220 at ends 210a, 210b, respectively. Thus, the seal assemblies 270, 271 isolate the radial bearings 260, 262 and bearing assembly 261 from ring gear drilling fluid 150 and borehole drilling fluid 16, respectively. A pressure compensation system is preferably used in connection with oil-sealed bearings 260, 262, 261. Examples of compression systems that can be used in connection with bearings 260, 262, 261 are described in US Patent Application No. 61/765,164, which is incorporated herein by reference in its entirety. As previously described, in this embodiment the bearings 260, 261, 262 are oil sealed. However, in other embodiments, the bearings in the bearing assembly (eg, bearing assembly 200) are slurry lubricated. For example, with reference to Figure 11, an embodiment of a mud motor 35' is shown. The mud motor 35' is the same as the mud motor 35 described above, except that the bearing assembly 200' includes slurry lubricated radial bearings 260', 262' and thrust bearing 261', the seal assemblies 270, 271 are omitted to allow a portion of the drilling mud flowing through the annulus 150 to access bearings 260', 261', 262', and the bearing mandrel 220' includes a plurality of circumferentially spaced apart mud return holes. 222', lower proximal end 220b to return drilling mud flowing through bearings 260', 261', 262' to center passage 221. Each hole 222' extends radially from central passage 221 to the outer surface of mandrel 220'. Thus, in this embodiment, a portion of the drilling fluid flowing through o-ring 150 bypasses holes 222 and lubricates bearings 260', 261' and 262' before returning to central passage 221 via holes 222'.
    [0045] With reference to Figures 1, 4 and 6, as previously described, the curve fitting assembly 300 couples the drive shaft housing 110 to the bearing housing 210 and introduces the curve 301 and the deflection angle θ along of motor 35. The axis 115 of the drive shaft housing 110 is coaxially aligned with the axis 25 and the axis 215 of the bearing housing 210 is coaxially aligned with the axis 95, thus the deflection angle θ also represents the angle between the geometry axes 115, 215 when the mud motor 35 is in an undeflected state (eg, outside the borehole 16). Due to the deflection of the motor 35 in the borehole 16, the angle between the axes 115, 215 will typically be less than the deflection angle θ. As will be described in more detail below, the deflection angle θ can be adjusted as desired with the 300 curve adjustment kit.
    [0046] As best shown in Figure 6, in this embodiment, the bearing adjustment assembly 300 includes an adjustment mandrel 310 and an adjustment locking ring 320. The adjustment mandrel 310 is disposed around the mandrel 220 and the ring 320 is arranged around adjustment mandrel 310. As will be described in more detail below, ring 320 enables rotation of adjustment mandrel 310 with respect to drive shaft housing 110 to adjust the deflection angle θ between a maximum and a minimum.
    [0047] Referring now to Figures 6 - 8, the mandrel 310 has a central or longitudinal axis 315, a first or upper end 310a, a second or lower end 310b opposite the end 310a and a central through hole or passage 311, extending axially between ends 310a, 310b. Axis 315 is coaxially aligned with axis 215 of bearing housing 210.
    [0048] The upper end 310a comprises a threaded connector 312 and a lower end 310b comprises a threaded connector 313. Threaded connector 313 is coaxially aligned with axis 315 and concentrically disposed about axis 315, however, threaded connector 312 is concentrically disposed about axis 312a, oriented at a non-zero acute angle β relative to geometry axis 315. In this embodiment, connector 312 is an externally threaded connector or pin end, and connector 313 is an internally threaded connector or box end. Thus, axis 312a is the central axis of the threaded outer cylindrical surface of adjustment mandrel 310 at end 310a. Therefore, connector 312 can be described as being "offset". Angle β is preferably greater than 0° and less than or equal to 2° and preferably the same as angle α.
    [0049] As best shown in Figures 6 and 8, the threaded externally offset connector 312 of the chuck 310 threadably engages the mating internally threaded offset connector 118 of the lower housing section 116 and the internally threaded connector 313 of the chuck 310 in a manner threaded connector engages the mating externally threaded connector 12 of the bearing housing 210. When the connectors 118, 312 are threaded together and the connectors 212, 313 are threaded together, the axes 118a, 312a are coaxially aligned, the axes 215, 315 are coaxially aligned and the geometry axes 215, 315 are oriented at the deflection angle θ relative to the geometry axis 115, thereby inducing the curve 301 along the motor 35. Depending on the rotational position of the chuck 310 relative to the lower housing section 116, the deflection angle θ can be adjusted to an intermediate angle between a minimum deflection angle θmin equal to the angle difference α, β (ie 0o if α = β) and a maximum deflection angle θmax equal to the sum of the angles α, β.
    [0050] Referring now to Figures 6 and 7, the cylindrical outer surface of the mandrel 310 includes a plurality of circumferentially spaced elongated semi-cylindrical recesses 319, positioned proximal to the lower end 310b. The recesses 319 are oriented parallel to the axis 315. As will be described in more detail below, each recess 319 receives an elongated cylindrical joint key 330. Although the keys 330 slidably engage the recesses 319 in this embodiment, and other embodiments, a plurality of circumferentially spaced apart keys may extend radially and be integrally formed with the adjustment mandrel (e.g., mandrel 310).
    [0051] Referring now to Figs. 6, 9 and 10, the annular fit locking ring 320 is axially positioned between the lower end 116b of the lower housing section 116 and an annular shoulder 211c on the outer surface of the upper housing section 211, and is disposed around the upper end 211a of upper housing section 211 and lower end 110b of adjustment mandrel 310. Locking ring 320 has a central or longitudinal axis 325, a first or upper end 320a, a second or lower end 320b opposite end 320a , and a through hole or passage 321 extending axially between ends 320a, 320b. Passage 321 defines a cylindrical inner surface 322 extending between ends 320a, 320b. Inner surface 322 includes a plurality of circumferentially spaced semi-cylindrical recesses 323, each recess 323 is oriented parallel to axis 325 and extends from upper end 320a to upper end 320b. As best shown in Figure 7, when locking ring 320 is secured to mandrel 310, each recess 323 is circumferentially aligned with a corresponding recess 319 and a key 330 is disposed within each set of aligned recesses 319, 323. Keys 330 allow locking ring 320 to move axially with respect to mandrel 310, but prevent locking ring 320 from rotationally moving with respect to mandrel 310. Thus, rotating locking ring 320 about the geometric axis 315, mandrel 310 is rotated about axis 315.
    [0052] Referring now to Figures 9 and 10, the adjustment ring 320 further includes a plurality of circumferentially spaced teeth 326 at the upper end 320a. Teeth 326 are sized and shaped to releasably engage a mating set of circumferentially spaced apart teeth 327 at lower end 116b of lower housing section 116. As shown in Figure 9, engagement and interlocking of mating teeth 326, 327 prevents the locking ring 320 rotates with respect to the lower housing section 116, however, as shown in Figure 10, when the locking ring 320 is axially spaced from the lower housing section 116 and the teeth 326, 327 are disengaged, the locking ring 320 is axially spaced from the lower housing section 116. Lock 320 can be rotated with respect to lower housing section 116. It should also be noted that teeth 326, 327 can releasably engage and interlock while accommodating bend 301 at the junction of lock ring 320 and housing 110.
    [0053] Referring now to Figures 1 and 4, before lowering the BHA 30 to the bottom of the well, the deflection angle θ is adjusted and established based on the projected or objectified profile of the drillhole 16 to be drilled with the system 10. In general, the deflection angle θ can be adjusted and set to any angle between 0° and the sum of angles α, β by turning the annular adjustment ring 320 with respect to the housing 110. The deflection angle θ is controlled and varied via curve fitting assembly 300. In particular, mandrel 310 is rotated relative to housing 110, via locking ring 320 and keys 330, to adjust and set the deflection angle θ. As previously described, the engagement of the teeth 326, 327 prevents the locking ring 320 from being rotated with respect to the housing 110 and thus to enable the rotation of the locking ring 320 (and, consequently, rotation of the mandrel 310) in With respect to housing 110, teeth 326, 327 are disengaged. Thus, bearing housing 210 is disengaged from mandrel 310 to create axial clearance between lock ring 320 and shoulder 211c. With sufficient axial clearance between lock ring 320 and shoulder 211c, lock ring 320 is slid axially downwardly away from housing 110 via sliding engagement of keys 330 and recesses 323, until teeth 326, 327 are fully disengaged. . With teeth 326, 327 fully disengaged, torque is applied to adjustment ring 320 to rotate ring 320 and mandrel 310 (keyways 330) relative to housing 110. Rotation of mandrel 310 relative to housing 110 causes the connector to offset 312 of mandrel 310 rotates in relation to offset connector 118 of housing 110.
    [0054] The full range of variation of the deflection angle θ can be achieved by rotating the chuck 310 between 0° and 180° with respect to the housing 110, with the angular position of 0° of the chuck 310 relative to the housing 110 providing the angle of minimum deflection θmin equal to the difference between angles α, β (ie ... 0o if α = β) and the 180o angular position of chuck 310 relative to housing 110 providing the maximum deflection angle θmx equal to the sum of the angles α, β. In general, the deflection angle θ varies non-linearly, moving between the 0° and 180° angular positions of the chuck 310 with respect to the housing 110. Thus, an incremental deflection angle θ between the minimum deflection angle θmin and the maximum deflection angle θimix can be set. The specific incremental values of the deflection angle θ that can be selected depend on the number and spacing of teeth 326, 327 and the values of angles α, β. In this embodiment, the radially outer surfaces of the lock ring 320 and housing 110 at the ends 320a, 110b, respectively, are marked/indexed to provide an indication of the deflection angle θ for various angular positions of the lock ring 320 and, accordingly, chuck 310 with respect to housing 110 between 0° and 180°.
    [0055] Once mandrel 310 has been rotated sufficiently to provide the desired deflection angle 6, ring 320 is axially moved into housing 110 to engage teeth 326, 327, which prevents relative rotation of locking ring 320 and chuck 310 with respect to housing 110, thereby locking at the desired deflection angle θ. Then, bearing housing 210 is threaded into mandrel 310 until shoulder 211c axially contacts lock ring 320, thereby preventing lock ring 320 from moving axially away from housing 110 and disengaging teeth 326, 327.
    [0056] In the manner described here, an adjustable curve motor assembly is provided for use in drillhole boreholes having non-vertical or offset sections. When compared to conventional curved motor assemblies, the embodiments described here provide a substantially reduced drill-to-bend distance, via a curve positioned immediately above the bearing housing and axial overlap of the curve-fitting assembly with the chuck assembly. bearing. The reduced drill-to-bend distance offers the potential for increased durability and construction speeds. In particular, for a given deflection angle, the magnitude of bending moments and stresses experienced by downhole mud motors are directly related to the drill-to-bend distance (i.e., the greater the drill-to-bend distance). , the greater the bending moments). Consequently, the maximum deflection angle of a downhole mud motor is typically limited by the magnitude of stresses resulting from the deflection moments. Therefore, by decreasing the bit-to-bend distance for a given deflection angle, the modalities described here offer the potential to reduce the deflection moments and associated stresses experienced by the downhole mud motor. In addition, a shorter drill-to-bend distance decreases the minimum bend radius (i.e., a sharper turn) of the borehole path that can be excavated by the drill at a given deflection angle provided by the curved pocket. . For a drillhole having a deflected section that includes a desired radius of curvature, by decreasing the drill-to-bend distance, a smaller angle of deflection of the curved housing can be used in order to produce a drillhole section at that desired radius. Thus, a downhole motor, having a relatively short drill-to-bend distance, can both reduce the stresses imparted to the motor at a given deflection angle and allow the use of a smaller deflection angle to drill a hole of borehole having a desired radius of curvature.
    [0057] Also, in conventional slurry motors, the threaded connection between the upper end of the bearing chuck and an adapter threaded into it and coupled to the lower end of the drive shaft with a universal joint, is particularly susceptible to failure or fracture when excessive bending moments and stresses are applied to the motor. However, in embodiments described here, this screwed connection is eliminated. In particular, as previously described, the upper end 220a of the bearing mandrel 220 is disposed within the receptacle 121 provided at the lower end 120b of the drive shaft 120 and coupled to the drive shaft 120 with universal joint 140. In other words, no adapter is threaded into the upper end 220a of the bearing mandrel 220 in this embodiment.
    [0058] Although the mud motor 35 embodiments described here include an adjustable curve 301, potential advantageous details of the mud motor 35 can also be used in connection with fixed curve mud motors. For example, a mud flow ring, having a decreasing radial width moving towards the mud inlet holes of the chuck, can be employed in fixed curve mud motors to more evenly distribute the drilling fluid between the entry holes. As another example, a bearing chuck having an upper end coupled to the lower end of a drive shaft without a threaded connection may be employed in fixed curve mud motors to increase durability.
    [0059] Although preferred embodiments have been shown and described, their modifications may be made by a person skilled in the art, without deviation from the scope or teachings here. The embodiments described herein are exemplary only and are not limiting. Many variations and modifications of the systems, apparatus and processes described herein are possible and are within the scope of the invention. For example, the relative dimensions of various parts, the materials the various parts are made of, and other parameters can be varied. Therefore, the scope of protection is not limited to the modalities described here, but is only limited by the claims that follow, the scope of which will include all equivalents of the subject matter of the claims. Unless expressly stated otherwise, the steps of a method claim may be performed in any order. Recitation of identifiers such as (a), (b), (c) or (1), (2), (3) before steps in a method claim is not intended to and does not specify an order. particular to steps, but is undoubtedly used to simplify subsequent reference to such steps.
    权利要求:
    Claims (19)
    [0001]
    1. Downhole motor (35) for directional drilling, the motor comprising: a drive shaft assembly (100) including a drive shaft housing (110) and a drive shaft (120) rotatably disposed therein drive shaft housing (110); wherein the drive shaft housing (110) has a central axis (115), a first end (110a), and a second end (110b) that is opposite the first end (110a). 110a); characterized in that: the drive shaft (120) has a central axis (125), a first end (120a), a second end (120b) which is opposite the first end (120a), and a receptacle (121) extending axially from the second end (120b) of that drive shaft (120); a bearing assembly (200) including a bearing housing (210) and a rotatably disposed bearing mandrel (220) inside that bearing housing (210); wherein the housing the bearing housing (210) has a central axis (215), a first end (210a) comprising a connector (213), and a second end (210b) which is opposite the first end (210a); wherein the bearing mandrel bearing (220) has a central axis (225) coaxially aligned with the central axis (215) of the bearing housing (210), a first end (220a) directly connected to the second end (120b) of the drive shaft (120) ) with a universal joint (140), and a second end (220b) which is coupled to a drill bit (90), wherein the first end (220a) of that bearing chuck (220) is disposed within said receptacle (121) of that drive shaft (120); an adjustment mandrel (310) configured to adjust an acute angle of deflection θ between the central axis (215) of that bearing housing (210) and the central axis (115) of that drive shaft housing (110); wherein the adjusting chuck (3 10) has a central axis (315) coaxially aligned with the central axis (215) of that bearing housing (210), a first end (310a), and a second end (310b) that is opposite the first end (310a). ); wherein the first end (310a) of the adjustment mandrel (310) is coupled to the second end (110b) of that drive shaft housing (110) and the second end (310b) of the adjustment mandrel (310) is coupled to the first end (210a) of that bearing housing (210).
    [0002]
    2. Downhole motor (35), according to claim 1, characterized in that the connector (213) of the first end (210a) of the bearing housing (210) comprises a threaded connector (213), and wherein the first end (310a) of the adjustment mandrel (310) is threadedly coupled to the second end (110b) of the drive shaft housing (110) and the second end (310b) of the adjustment mandrel (310) is threadedly coupled to the first end (210a) of the bearing housing (210).
    [0003]
    3. Downhole motor (35) according to claim 2, characterized in that it additionally comprises: a locking ring (320) arranged around the adjustment mandrel (310) and the first end (210a) of the bearing housing (210), wherein the locking ring (320) is configured to rotatably lock the adjusting mandrel (310) in that drive shaft housing (110); wherein that locking ring (320) is configured to move axially with respect to said adjusting mandrel (310) and is prevented from moving rotationally with respect to said adjusting mandrel (310).
    [0004]
    4. Downhole motor (35) according to claim 3, characterized in that: the locking ring (320) has an inner surface comprising a plurality of circumferentially spaced recesses (323); wherein the fitting (310) has an outer surface comprising a plurality of circumferentially spaced recesses (319), wherein a recess (319) of the adjusting mandrel (310) is circumferentially aligned with a recess (323) of the locking ring (320) , and wherein a groove (330) is disposed in each set of aligned recesses (319, 323); and, wherein the locking ring (320) has a first end (320a) comprising a plurality of circumferentially spaced teeth (326) which releasably engage and interlock with a plurality of circumferentially spaced mating teeth (327) on that second end (110b) of that drive shaft housing (110).
    [0005]
    5. Downhole motor (35) according to claim 2, characterized in that the bearing mandrel (220) extends axially into the drive shaft housing (110).
    [0006]
    6. Downhole motor (35) according to claim 2, characterized in that the bearing mandrel (220) extends completely through the adjustment mandrel (310).
    [0007]
    7. Downhole motor (35) according to claim 2, characterized in that: the bearing mandrel (220) is a single unitary piece and the drive shaft (120) is a single unitary piece; a universal joint (140) is provided between the bearing mandrel (220) and the drive shaft (120); and the central axis (125) of that drive shaft (120) is linear and the bearing mandrel (220) has a linear central axis (225).
    [0008]
    8. Downhole motor (35) according to claim 2, characterized in that the bearing mandrel (220) comprises a plurality of axially spaced holes (222), and wherein each hole (222) is arranged at an acute angle to a central axis (225) of the bearing mandrel (220).
    [0009]
    9. Downhole motor (35) according to claim 1, characterized in that an angular displacement between the central axis (315) of the adjustment chuck (310) and the central axis (115) of the housing of the drive shaft (110) is concentrically arranged around the bearing mandrel (220).
    [0010]
    10. Downhole motor (35) according to claim 8, characterized in that each orifice (222) has a central geometric axis oriented at 45° in relation to the central geometric axis of the bearing mandrel (220).
    [0011]
    11. Downhole motor (35) according to claim 8, characterized in that: a circular crown (150) is formed around an external surface of the bearing mandrel (220) which has a decreasing radial width axially moving towards the plurality of holes (222); wherein the annulus (150) has a first portion (150a) having a first radial width (W150a), a second portion (150b) having a second radial width (W150b), and a third portion (150c) having a third width. (W150c), wherein the first portion (150a) extends axially from the first end (220a) of the bearing mandrel (220) to the second portion (150b), wherein the third portion (150c) extends axially. from the second portion (150b) to the plurality of holes (222), wherein the first radial width (W150a) is greater than the second radial width (W150b) and the third radial width (W150c), and wherein the third radial width (W150c) is smaller than the second radial width (W150b).
    [0012]
    12. Downhole motor (35) according to claim 3, characterized in that a threaded coupling of the first end (210a) of the bearing housing (210) and of the second end (310b) of the adjustment mandrel ( 310) is restricted to axial movement of the lock ring (320).
    [0013]
    A downhole motor (35) according to claim 1, characterized in that: and rotation of the adjustment mandrel (310) with respect to the drive shaft housing (110) is configured to be adjusted to the acute angle of deflection θ.
    [0014]
    14. Downhole motor (35) according to claim 13, characterized in that the second end (110b) of the drive shaft housing (110) comprises a threaded connector (118) arranged concentrically around a first displacement axis (118a) oriented at an acute angle α with respect to the central axis (115) of said drive shaft housing (110); wherein the first end (310a) of the adjustment mandrel (310) comprises a threaded connector (312) arranged concentrically about a second displacement axis (312a) oriented at an acute angle β with respect to the central axis (315) of said adjustment mandrel (310).
    [0015]
    15. Downhole motor (35) according to claim 14, characterized in that the first end (220a) of the bearing mandrel (220) and the universal joint (140) are arranged in the receptacle (121).
    [0016]
    16. Downhole motor (35) according to claim 14, characterized in that at least one radial bearing (260) and a thrust bearing (261) are positioned radially between the first end (210a) of said housing (210) and said bearing mandrel (220), wherein the at least one radial bearing (260) is configured to support radial loads and the thrust bearing (261) is configured to support axial loads.
    [0017]
    17. Downhole motor (35) according to claim 14, characterized in that the second end (110b) of said drive shaft housing (110) comprises an internally threaded connector (118), the first end (118). 310a) of said adjustment mandrel (310) comprises an externally threaded connector (312), the second end (310b) of said adjustment mandrel (310) comprises an internally threaded connector (313), and the first end (210a) of the said bearing housing (210) comprises an externally threaded connector (212).
    [0018]
    18. Downhole motor (35), according to claim 1, characterized in that: the central geometric axis (115) of said drive shaft housing (110) is oriented at the acute angle of deflection θ in relation to to the central axis (215) of said bearing housing (210).
    [0019]
    19. Downhole motor (35) according to claim 18, characterized in that: the bearing mandrel (220) comprises a plurality of axially spaced holes (222), and wherein each hole (222) is arranged at an acute angle to the central axis (225) of the bearing mandrel (220); an annular ring (150) is formed around an outer surface of the bearing mandrel (220) which has a decreasing radial width that moves axially to the plurality of holes (222); and, the annulus (150) has a first portion (150a) of a first radial width (W150a), a second portion (150b) of a second radial width (W150b), and a third portion (150c) of a third width. (W150c), wherein the first portion (150a) extends axially from the first end (220a) of the bearing mandrel (220) to the second portion (150b), wherein the third portion (150c) extends axially. from the second portion (150b) to the plurality of holes (222), wherein the first radial width (W150a) is greater than the second radial width (W150b) and the third radial width (W150c), and wherein the third radial width (W150c) is smaller than the second radial width (W150b).
    类似技术:
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    同族专利:
    公开号 | 公开日
    US9347269B2|2016-05-24|
    US10184298B2|2019-01-22|
    MX365502B|2019-06-05|
    MX2015011449A|2016-06-10|
    CN105143589A|2015-12-09|
    WO2014137543A4|2015-03-26|
    CA2903743A1|2014-09-12|
    US20160237749A1|2016-08-18|
    US20140251695A1|2014-09-11|
    RU2648412C2|2018-03-26|
    BR112015021667A2|2017-07-18|
    CA2903743C|2020-04-14|
    EP3369888A1|2018-09-05|
    EP2964866A2|2016-01-13|
    AU2014226500A1|2015-09-24|
    WO2014137543A3|2015-01-08|
    WO2014137543A2|2014-09-12|
    RU2765901C1|2022-02-04|
    CN105143589B|2017-07-28|
    NO3052742T3|2018-05-26|
    RU2015137979A|2017-04-07|
    AU2014226500B2|2018-03-15|
    EP2964866B1|2018-04-04|
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    法律状态:
    2018-11-13| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2020-04-07| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-11-03| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2022-01-11| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 10/02/2014, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US13/786,076|2013-03-05|
    US13/786,076|US9347269B2|2013-03-05|2013-03-05|Adjustable bend assembly for a downhole motor|
    PCT/US2014/015499|WO2014137543A2|2013-03-05|2014-02-10|Adjustable bend assembly for a downhole motor|
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