US20090291001A1

US20090291001A1 - Centering coupling for electrical submersible pump splined shafts

Info

Publication number: US20090291001A1
Application number: US12/332,717
Authority: US
Inventors: David Neuroth; Terry Shafer
Original assignee: Baker Hughes Inc
Current assignee: Baker Hughes Holdings LLC
Priority date: 2008-05-22
Filing date: 2008-12-11
Publication date: 2009-11-26
Also published as: US20130101447A1; US8591205B2; US20130343933A1; US8876500B2

Abstract

An electrical submersible well pump assembly having a pump, a pump motor, and a seal section. The motor drives the pump via shafts rotatingly coupled with a coupling assembly. The coupling assembly includes an alignment device that maintains the shaft ends in coaxial alignment. The alignment device compressibly engages one or both of the shafts. The alignment device may be an elongated member having slots cut along its length on one or both ends configured to compress when inserted into a bore coaxially formed into the shaft ends within the coupling assembly.

Description

RELATED APPLICATIONS

This application is a continuation-in-part of patent application having Ser. No. 12/125,350, filed May 22, 2008.

FIELD OF THE INVENTION

This invention relates in general to electrical submersible well pumps, and in particular to couplings between splined shafts of an electrical submersible pump.

BACKGROUND OF THE INVENTION

Electrical submersible pumps (ESP) are commonly used for hydrocarbon well production, FIG. 1 provides an example of a submersible pumping system 10 disposed within a wellbore 5. The wellbore 5 is lined with casing 4 and extends into a subterranean formation 6. Perforations 9 extend from within the wellbore 5 through the casing 4 into the formation 6. Hydrocarbon fluid flow, illustrated by the arrows A, exits the perforations 9 into the wellbore 5, where it can either be pumped by the system 10 or migrate to a wellhead 12 disposed on top of the wellbore 5. The wellhead 12 regulates and distributes the hydrocarbon fluid for processing or refining through an associated production line 7.
The pumping system 10 includes an electrical submersible pump (ESP) 14 with production tubing 24 attached to its upper end. The ESP 14 comprises a motor 16, an equalizer or seal 18, a separator 20, and a pump 22. A fluid inlet 26 is formed in the housing in the region of the ESP 14 proximate to the separator section 20. The fluid inlet 26 provides a passage for the produced hydrocarbons within the wellbore 5 to enter the ESP 14 and flow to the pump 22. Fluid pressurized by the pump 22 is conveyed through the production tubing 24 connecting the ESP 14 discharge to the wellhead 12. The pump 22 and separator 20 are powered by the motor 16 via a shaft (not shown) that extends from the motor 16. The shaft is typically coupled to respective shafts in each of the pump 22, separator 20, and seal 14.
Delivering the rotational torque generated by an ESP motor 16 typically involves coupling a motor shaft (i.e., a shaft connected to a motor or power source) to one end of a driven shaft, wherein the other end of the driven shaft is connected to and drives rotating machinery. Examples of rotating machinery include a pump, a separator, and tandem pumps. One type of coupling comprises adding splines on the respective ends of the shafts being coupled and inserting an annular collar over the splined ends, where the annular collar includes corresponding splines on its inner surface. The rotational force is well distributed over the splines, thereby reducing some problems of stress concentrations that may occur with keys, pins, or set screws. Examples of a spline cross-section include an involute and a square tooth. Typically, splines having an involute cross-section are smaller than square tooth splines, thereby leaving more of the functional shaft diameter of a shaft to carry a rotational torque load. Additionally, involute spline shapes force the female spline to center its profile on the male spline, thus coaxially aligning the shafts in the coupling with limited vibration. Square tooth splines are made without specialized cutters on an ordinary mill. However square teeth spline couplings do not align like involute teeth unless the clearance is reduced or the male and female fittings are forced together. However, reducing clearance or force fitting square teeth splines prevents ready assembly or disassembly.

SUMMARY OF THE INVENTION

Disclosed herein is a submersible pumping system for pumping wellbore fluid, comprising, a pump motor, a seal section a motor shaft having an end rotatably affixed within an end of a shaft coupling, the motor shaft rotatable by the motor, a driven shaft having an end rotatably affixed within an end of the shaft coupling opposite to the motor shaft, the respective ends of the motor shaft and driven shaft being substantially coaxial within the shaft coupling, and an alignment element provided in the shaft coupling, the element coaxially engaging the respective terminal ends of the motor shaft and driven shaft within the shaft coupling. In one embodiment, the element is disposed in bores formed in the respective terminal ends of the motor shaft and driven shaft. The alignment element may comprise a member having a slot or channel axially extending along a portion of the element body axis and bisecting the element body. The bisected element body may be compressibly inserted within a respective bore. An optional second slot or channel axially extends along a portion of the element body axis to bisect the element body. The second slot extends from an end of the body oppositely disposed from the end where the first slot extends. The element body bisected by the second slot may be compressibly inserted within the other respective bore.
Optionally, the alignment element may comprise a tolerance ring coaxially disposed between a shaft and the shaft coupling. A second tolerance ring may be disposed between the other shaft and the shaft coupling. Yet further optionally, a single tolerance ring may extend between within the shaft coupling along a portion of both the motor shaft and the driven shaft.
Also disclosed herein is a method of using an electrical submersible pump (ESP) in a wellbore involving providing the ESP in the wellbore. The ESP may include a motor, a motor shaft rotatingly affixed to the motor; a rotating device, a driven shaft rotatingly affixed to the rotating device, and a coupling rotatingly affixing ends of the motor shaft and driven shaft. The method may further include energizing the motor, thereby rotating the motor shaft, the coupling, and the driven shaft. Additionally, the present method includes substantially coaxially aligning the ends of the motor shaft and driven shaft during shaft rotation. The method optionally further comprises providing a compressible alignment element in the coupling between the shaft ends, and coaxially mating the shaft ends with the alignment element. The compressible alignment element may comprise a member having a slot or channel axially extending along a portion of the element body axis and bisecting the element body. Optionally, the compressible alignment element may comprise a tolerance ring.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a side view of a prior art submersible electrical pumping system in a wellbore.

FIG. 2 a is an exploded view of a shaft coupling for use with the system of FIG. 1.

FIG. 2 b is an assembled view of the shaft coupling of FIG. 2 a.

FIG. 3 a is an exploded view of an alternative shaft coupling for use with the system of FIG. 1.

FIG. 3 b is an assembled view of the shaft coupling of FIG. 3 a.

FIG. 4 a is an exploded view of an alternative shaft coupling for use with the system of FIG. 1.

FIG. 4 b is an assembled view of the shaft coupling of FIG. 4 a.

FIG. 5 is a side partial cut-away view of an alternative shaft coupling for use with the system of FIG. 1.

FIG. 6 is a side partial cut-away view of an alternative shaft coupling for use with the system of FIG. 1.

FIG. 7 is a perspective view of an embodiment of an alignment member.

FIG. 8 is a side partial sectional view of the alignment member of FIG. 7 engaged with opposing shafts.

FIG. 9 is a perspective view of an embodiment of a tolerance ring.

FIG. 10 is a side partial sectional view of the tolerance ring of FIG. 9 disposed between a shaft and a shaft coupling.

DETAILED DESCRIPTION OF THE INVENTION

The present invention will now be described more fully hereinafter with reference to the accompanying drawings in which embodiments of the invention are shown. This invention may, however, be embodied in many different forms and should not be construed as limited to the illustrated embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like numbers refer to like elements throughout. For the convenience in referring to the accompanying figures, directional terms are used for reference and illustration only. For example, the directional terms such as “upper”, “lower”, “above”, “below”, and the like are being used to illustrate a relational location.
It is to be understood that the invention is not limited to the exact details of construction, operation, exact materials, or embodiments shown and described, as modifications and equivalents will be apparent to one skilled in the art. In the drawings and specification, there have been disclosed illustrative embodiments of the invention and, although specific terms are employed, they are used in a generic and descriptive sense only and not for the purpose of limitation. Accordingly, the invention is therefore to be limited only by the scope of the appended claims.
The present disclosure includes a square tooth spline coupling with vibration control. The coupling disclosed herein provides sufficient clearance between the respective male and female splines providing ready assembly and disassembly. With reference now to FIG. 2 a, an exploded side partial cutaway view of one embodiment of a coupling assembly and respective shafts is provided. As noted above, during operation of a pumping assembly, a motor shaft is powered by a pump motor, either directly or through a shaft coupling. The coupling assembly provides a manner of connecting the motor shaft to a driven shaft that drives rotating machinery. The coupling connection also transfers rotational energy between the motor and driven shaft, thus providing power for the rotating machinery. Thus with respect to couplings described herein, the term motor shaft includes any shaft mechanically coupled to the motor that is being coupled to a driven shaft. As such, embodiments exist where one end of a rotating shaft is a driven shaft coupled to a motor shaft and the other end of the rotating shaft is a motor shaft coupled to a driven shaft. Accordingly, ESP systems may include the couplings of the present disclosure at any shaft connection within the system and ESP systems may include multiple couplings of the present disclosure.
The coupling assembly 30 of FIG. 2 a comprises an annular collar 48 with a bore 50 formed lengthwise therein. Female splines 52 extend axially along the bore 50 inner surface. The bore 50 diameter transitions at a point to form a shoulder 56 that is substantially perpendicular to the collar 48 axis A_x. An alignment element 54 is on the shoulder 56. In the embodiment shown, the alignment element 54 has a disc-like midsection and disposed in the collar 48 with its midsection axis (not shown) largely aligned with or parallel to the collar axis A_x. The alignment element 54 outer diameter exceeds the shoulder 56 inner diameter and its lower side abuts on the shoulder 56. The outer diameter fits closely in the bore 50. An insert or sleeve 60 is coaxially received within the collar 48 in the portion of the bore 50 having an increased diameter. The insert 60 extends from the upper surface of the alignment member 54 terminating at the upper end of the collar 48. The insert 60 is optionally threaded on its outer diameter to mate with corresponding threads provided on the collar 48 inner diameter. Female splines 52 are formed along the insert 60 inner diameter. Positioning the insert 60 against the alignment element 54 toward the shoulder 56, retains the alignment element 54 within the collar 48.
Centering guides (62, 63) are shown extending from the upper and lower surface of the alignment element 54. In this embodiment, the centering guides (62, 63) comprise conically shaped protusions. Above and below the coupling assembly 30 are an upper shaft 32 and lower shaft 40. The upper shaft 32 lower end 36 is provided with male splines 34 configured for coupling engagement with the female splines 52 of the coupling assembly 30. Similarly, the lower shaft 40 upper end 44 includes male splines 42 configured for coupling engagement with the female splines 52. The shafts (32, 40) are profiled on their terminal ends for centering engagement with the centering guides (62, 63) of the alignment element 54. In the embodiment shown, the profiling on the shafts comprises recesses or bores (38, 46) extending from the terminal mating tips of the shafts and substantially aligned with the respective axes (A_SH, A_SL) of the upper or counterbore lower shafts (32, 40). Each recess (38, 46) has a conical entry way with a taper matching the centering guides (62, 63). The recess and protrusion provide examples of guide profiles formed on the shaft ends and alignment element for engaging the shaft ends to the alignment element. During pumping operations, impellers in the pump create an axial thrust force in the pump shaft forcing the shafts (32, 40) together and engaging the centering guides (62, 63) with the recesses (38, 46).
Referring now to FIG. 2 b, an example of an assembled shaft coupling is shown in side cross-sectional view. The male splines 34 on the lower end 36 of the upper shaft 32 engage the female splines 52 and the upper shaft 32 bore 38 mates with the centering guide 62 that extends from the alignment element 54. Similarly, the male splines 42 on the upper end 44 of the lower shaft 40 are engaged with the female splines 52 of the collar 48 and the bore 46 on the upper terminal end of the shaft 40 mates with the centering guide 63 that extends from the opposite side of the alignment element 54. The upper shaft 32 and lower shaft 40 are aligned along a common axis within the collar 48 thus preventing shaft vibration when one of the shafts energizes the other.
FIG. 3 a shows an alternative embodiment of a shaft coupling 30a for coupling an upper shaft 36 a to a lower shaft 44 a. In this embodiment, the alignment element 54 a has a largely disc-like cross-sectional area and is seated on the shoulder 56. The insert 60 retains the element 54 a within the collar 48. The centering guides (62 a, 63 a) comprise a conical profile bored into the body of the alignment element 54 a. Similarly, the terminal tips of the upper shaft 36 a and lower shaft 44 a include conically profiled protrusions (39, 47) formed to engaged the bores of the centering guides (62 a, 63 a). FIG. 3 b illustrates the assembled shaft coupling 30 a and engagement of the protrusions (39, 47) with the centering guides (62 a, 63 a). This configuration also control s shaft vibration during transmission of torque through the coupling 30 a. The profiles on the alignment elements and the terminal tips of the shafts are not limited to the figures described herein, but can include other shapes such as conical, concave, convex, spherical or other curved surfaces. Additionally, cylindrical profiles with may be employed and may include rounded tips on the cylinder end.
Yet another embodiment of a shaft coupling 30 b is provided in side cross-sectional view in FIG. 4 a. In this embodiment, the centering guides 62 b and centering guide 63 b comprise a raised profile on the respective upper and lower sides of the alignment element 54 b. The alignment element 54 b comprises an upper housing 64, a lower housing 66, and a resilient member housed within the upper and lower housings (64, 66). One example of a resilient member is a spring 68. In this embodiment, the upper and lower housing (64, 66) both comprise a generally cup-like structure having a closed base that is largely perpendicular to the axis of the collar 48 a. The housings have sides extending from the base towards an open end; the sides lie generally concentric with the axis A_Xof the collar 48 a. The upper housing 64 inner diameter is greater than the lower housing 66 outer diameter allowing insertion of the lower housing 66 into the upper housing 64 in telescoping relation. The spring 68 provides a resilient force for urging the upper and lower housing (64, 66) apart.
As shown in FIG. 4 b, in some embodiments, a vertical force may move the shaft (32, 40) toward one another and pushes on one of the upper or lower housing (64, 66), thereby compressing the spring 68 there between. One of the advantages of this embodiment is an axial force from one of the shafts (32, 40) is fully absorbed by the spring 68 and not transferred to the other or any other adjacent shaft within a pumping system. Moreover, the resilient nature of the spring 68 can force the housings (64, 66) apart upon absence of the vertical force while continuing axial alignment of the shafts (32, 40) during operation of the pumping system. Because rotational shafts in an ESP seal portion typically are not subjected to axial thrust, the resilient feature may be useful for these couplings. As shown, the housings (64, 66) have protrusions profiled on their respective outer surfaces formed to match recesses (38, 46) on the shafts (32, 40). However, the housings (64, 66) could be fashioned to include recesses and the shafts (32, 40) having corresponding protrusions.
Another embodiment illustrating ESP shaft coupling is provided in a side partial cut-away view in FIG. 5. Here an upper shaft 36 b and lower shaft 44 b are aligned with a retaining pin 70 that extends from a bore 38 b in the lower terminal end of the upper shaft 36 b into a corresponding bore 46 b in the upper terminal end of the lower shaft 44 b. The retaining pin 70 may include an annular shoulder 71 radially disposed around the body of the pin 70 approximately at its mid-section. To accommodate the retaining pin 70, the bores (38 b, 46 b) are formed deeper into the shafts (36 b, 44 b) than the bores (38, 46) illustrated in FIGS. 2 a and 2 b.
A coupling assembly is presented in side partial cross sectional view in FIG. 6 that combines concepts described above. An upper shaft 36 with a bore 38 is disposed within a collar 48 b into coaxial alignment with a corresponding lower shaft 44 b. A protrusion 47 a extends from the lower shaft 44 b upper terminal end into the bore 38 and is retained therein for coaxial alignment of the shafts (36, 44 b). The protrusion 47 a of FIG. 6 is similar to the protrusion 47 of FIGS. 3 a and 3 b, but has increased dimensions, including an increased length, to ensure mating cooperation with the bore 38. The collar 48 b inner diameter is smaller at its upper end to match the upper shaft 36 outer diameter. The collar 48 b can be machined or forged as a uni-body configuration, or reduced with an insert (not shown) similar to the collar 48 of FIGS. 2 a-3 b.
An example of an alternative shaft coupling is provided in FIGS. 7 and 8. FIG. 7 depicts split pin 74 in perspective view. The embodiment of the split pin 74 illustrated is an elongated member having a substantially cylindrical shaped body 75, however the split pin 74 can also have cross sectional shapes with multiple sides. In the embodiment of FIG. 7, a vertical slot 76 initiates from a first end 77 of the body 75 extending through the body 75 to a vertical terminal end 78. Projecting from the body 75 second end 79 is a horizontal slot 81 that extends past the vertical terminal end 78 to a horizontal terminal end 83. FIG. 7 illustrates the first end 77 in forward looking view depicting an optional filler material 80 inserted within the slot 76. The filler material 80 should compress to allow pin 74 insertion and may include a fiber type material, such as cotton, felt, or fiberglass. Other materials include foam, cork, polymers, elastomeric polymers, and the like.
With reference now to FIG. 8, an example of a shaft coupling is provided in a side partial sectional view. Here an embodiment of the split pin 74 is coaxially disposed between an upper end 44 b and a lower end 36 b. Similar to the embodiment of FIG. 5, the split pin 74 has an end extending into the bore 38 b of the lower end 36 b and an opposite end extending into the bore 46 b of the upper end 44 b. The pin 74 ends can have an outer dimension approximately the same or greater than the bores 38 b, 46 b. The slots 76, 81 enable the ends 77, 79 to be compressed and inserted within the bores 38 b, 46 b. Forming the split pin 74 from an elastic material, such as steel, results in the pin 74 ends outwardly pushing against the inner circumference of the bores 38 b, 46 b; this couples the pin 74 to the ends of the shafts. The bores 38 b, 46 b being substantially aligned with the respective shaft axes shaft, provides alignment of the shaft ends 38 b, 44 b during use when the split pin 74 is coupled with the bores 38 b, 46 b.
Another optional compressive alignment element is illustrated in FIGS. 9 and 10. With reference to FIG. 9, an annular sleeve 82 is shown in perspective view. The annular sleeve 82 is a tubular member having a corrugated outer peripheral surface formed by protrusions 84 extending therefrom. Optionally, the protrusions 84 may extend from the sleeve 82 inner surface, or from both the inner and outer surfaces. The protrusions 84 are preferably formed from an elastic material, such as steel, that is able to be deformed and then return to its previous shape and also exert a resistive force while in the deformed state. An example of an annular sleeve 82 suitable for use as herein disclosed is a tolerance ring, that may be purchased from Rencol, 85 Route 31 North, Pennington, N.J. 08534, Tel: 609-745-5000, Fax: 609-745-5012, www.usatolerancerings.com.
FIG. 10 illustrates a side partial sectional view of a shaft 86 having splines 87 formed on the end of the shaft 86. An optional collar 88 is depicted on the end of the shaft 86, having on its inner circumference a corresponding profile of splines 89 for mating with the splines 87 on the shaft 86. A pin 85 is pictured inserted into bores 91, 92 formed on the ends of the shafts 86, 90 to align and stabilize the shafts 86, 90 during rotation. An embodiment of the annular sleeve 82, with protrusions 84, circumscribes the pin 85 ends to enhance coupling stability between the pin 85 and bores 91, 92. The protrusions 84 on the annular sleeve 82 are in temporary deformable compression when the pin 85 is in the bores 91, 92. The elasticity of the protrusions 84 couples the pin 85 within each bore 91, 92 thereby aligning the ends of the shafts 86, 92. As shown, two annular sleeves 82 are provided on each pin 85 end, but other arrangements are possible. For example, a pin 85 may have a single sleeve 82 on one end with a pair of sleeves 82 on its opposite end. Embodiments exist with more than two sleeves 82 on an end of a pin 85.
The present invention described herein, therefore, is well adapted to carry out the objects and attain the ends and advantages mentioned, as well as others inherent therein. While a presently preferred embodiment of the invention has been given for purposes of disclosure, numerous changes exist in the details of procedures for accomplishing the desired results. These and other similar modifications will readily suggest themselves to those skilled in the art, and are intended to be encompassed within the spirit of the present invention disclosed herein and the scope of the appended claims. While the invention has been shown in only one of its forms, it should be apparent to those skilled in the art that it is not so limited but is susceptible to various changes without departing from the scope of the invention.

Claims

1. A submersible pumping system for pumping wellbore fluid, comprising:

a pump motor;

a splined shaft coupling;

a motor shaft having a splined end rotatably affixed within one end of the shaft coupling, the motor shaft being rotatable by the motor;

a driven shaft having a splined end rotatably affixed within an opposite end of the shaft coupling opposite to the motor shaft, the respective ends of the motor shaft and driven shaft being substantially coaxial within the shaft coupling;

a bore formed into the splined end of each shaft; and

a radially compressible element inserted within the motor shaft bore on one end and the driven shaft bore on its other end.

2. The pumping system of claim 1, the compressible element comprising a body, a slot formed in the body, the slot axially extending along a portion of the element body axis, wherein the slot defines body sections on its outer periphery.

3. The pumping system of claim 2, the slot bisecting the element body.

4. The pumping system of claim 2, further comprising an optional second slot axially extending along a portion of the element body axis to bisect the element body.

5. The pumping system of claim 2 further comprising an additional slot extending along a portion of the element body axis.

6. The pumping system of claim 5, the slots forming more than two body sections.

7. The pumping system of claim 2 further comprising a filler material within the slot.

8. The pumping system of claim 2, wherein the compressible element is substantially cylindrical.

9. The pumping system of claim 1, wherein the coupling has internal square tooth splines.

10. A submersible pumping system for pumping wellbore fluid, comprising:

a pump motor;

a splined shaft coupling;

an annular sleeve circumscribing a portion of one of the shafts disposed within the shaft coupling; and

flexible protrusions formed on the sleeve, the protrusions being compressible between the shaft and the shaft coupling.

11. The pumping system of claim 10, wherein the annular sleeve comprises a tolerance ring.

12. The pumping system of claim 10, further comprising a second annular sleeve circumscribing a portion of the other one of the shafts disposed within the shaft coupling.

13. The pumping system of claim 10, wherein the annular sleeve axially extends within the shaft coupling and circumscribes a portion of the other shaft disposed within the shaft coupling.

14. The pumping system of claim 10, the protrusions extending from the sleeve outer surface.

15. The pumping system of claim 10, the protrusions extending from the sleeve inner surface.

16. A submersible pumping system for pumping wellbore fluid, comprising:

a pump motor;

a splined shaft coupling;

a driven shaft having a splined end rotatably affixed within an opposite end of the shaft coupling opposite to the motor shaft, the respective ends of the motor shaft and driven shaft being substantially coaxial within the shaft coupling; and

an alignment element in compressed engagement with at least one of the motor shaft or the driven shaft, the motor shaft and the driven shaft being substantially coaxially aligned.

17. The submersible pumping system of claim 16 wherein the alignment element comprises an elongated member comprising a body, a slot formed in the body, the slot axially extending along a portion of the element body axis, wherein the slot defines body sections on its outer periphery.

18. The submersible pumping system of claim 16, wherein the alignment element comprises an annular sleeve circumscribing a portion of one of the shafts disposed within the shaft coupling; and flexible protrusions formed on the sleeve, the protrusions compressible between the shaft and the shaft coupling.

19. The submersible pumping system of claim 18, further comprising a second annular sleeve circumscribing a portion of the other one of the shafts disposed within the shaft coupling.

20. The pumping system of claim 18, wherein the annular sleeve axially extends within the shaft coupling and circumscribes a portion of the other shaft disposed within the shaft coupling.