Motor

1. Cross Reference to Related Application:

[0001] This application claims priority to provisional application S.N. 62/307,633, filed March 14, 2016.

2. Field of the Disclosure:

[0002] This disclosure relates in general to electrical submersible well pumps and in particular to a motor with rotor sections with disks mounted on a center tube through which the motor shaft extends.

3. Background:

[0003] Electrical submersible pump assemblies ("ESP") are commonly used to pump well fluid from hydrocarbon producing wells. A typical ESP has a rotary pump driven by an electrical motor. The motor is filled with a dielectric motor oil. A pressure equalizer couples to the motor to reduce a pressure differential between the motor oil and the hydrostatic pressure of the well fluid. [0004] The motor has a stator with windings that are normally configured in a three- phase arrangement. The stator has a central bore in which a rotor is located. The rotor is made up of a number of rotor sections mounted on a shaft for rotation in unison. Radial bearings separate the rotor sections from each other and frictionally engage the bore of the stator to prevent rotation of the radial bearing and radially stabilize the shaft.

[0005] Each rotor section has a large number of thin disks or laminations. Each disk has a central opening and a number of slots spaced circumferentially around the central opening. Copper rods extend through the slots and attach to end rings at opposite end of the rotor section. The central openings of the disks slide over the shaft. A slot and groove arrangement secures the disks to the shaft for rotation in unison.

[0006] While these motors work well, slight radial movement can occur between the rotor disks and the shaft. The slight radial movement can create rotor imbalance, causing vibration. Aligning the rotor sections 35 during assembly can be difficult.

4. Summary:

[0007] A submersible well pump assembly has a pump and a motor. The motor has a rotatable motor shaft with rotor sections axially spaced apart from each other by radial bearings. A pressure equalizer is coupled to the motor to reduce a pressure differential between lubricant in the motor and a hydrostatic pressure of well fluid on the exterior of the motor. Each of the rotor sections has a large number of disks stacked together. Each of the disks has a central opening and slots circumferentially spaced around the central opening. Metal rods extend through the slots. A center tube extends through the central openings of the disks for rotation therewith. The center tube has an inner diameter that receives the motor shaft. A slot and key arrangement between the inner diameter of the center tube and the motor shaft causes the motor shaft to rotate in unison.

[0008] The center tube and the disks may be axially fixed to each other as well as rotationally. In one example, an interference fit exists between the central opening of each of the disks and an outer diameter of the center tube.

[0009] In one embodiment, the center tube protrudes past opposite ends of the rotor section into abutment with the center tubes of adjacent ones of the rotor sections. Each of the radial bearings has a hub into which the center tubes of adjacent ones of the rotor sections extend. Each of the center tubes is rotatable relative to hub.

[0010] In another embodiment, a bearing sleeve is located between and in abutment with opposing ends of the center tubes of adjacent ones of the rotor sections. The bearing sleeve is coupled to the shaft for rotation therewith. Each of the radial bearings has a hub surrounding one of the bearing sleeves in rotating sliding engagement. The bearing sleeve has an axial length less than axial lengths of the center tubes of adjacent ones of the rotor sections.

[0011] An end ring is located at each end of each rotor section. In one embodiment, the center tube has ends protruding past each of the end rings. A length of the center tube is less than an axial distance from an upper side of one of the end rings to a lower side of the other of the end rings. In another embodiment, the center tube is shorter and has ends recessed within the end rings.

[0012] In the embodiment wherein the center tube extends past the end rings, the ends of the center tube are in abutment with ends of the center tubes of adjacent ones of the rotor sections. In this embodiment, the center tube has an outer diameter smaller than the inner diameters of the end rings, defining annular gaps between the center tube and each of the end rings. Each of the radial bearings has a hub with one end that extends into the annular gap of one of the rotor sections and an opposite end that extends into the annular gap of an adjacent one of the rotor sections.

5. Brief Description of the Drawings:

[0013] Fig. 1 is a side view of an electrical submersible well pump assembly having a motor with a rotor constructed in accordance with this disclosure.

[0014] Fig. 2 is a sectional view of part of the motor of Fig. 1, illustrating rotor sections of the rotor mounted on center tubes.

[0015] Fig. 3 is perspective view, partly sectioned, of a portion of one of the rotor sections of Fig. 2, shown removed from the motor shaft and housing.

[0016] Fig. 4 is an enlarged sectional view of a portion of the rotor section shown in

Fig. 3.

[0017] Fig. 5 is an axial sectional view of a portion of the rotor section of Fig. 3.

[0018] Fig. 6 is an enlarged axial sectional view of part of the rotor shown in Fig. 2, with more details of a radial bearing, and showing the rotor section center tubes extending past the ends of the rotor sections into an inner diameter of the radial bearing. [0019] Fig. 7 is a view similar to Fig. 6, but showing an alternate embodiment with the rotor section center tubes terminating at the ends of the rotor sections and engaging a sleeve of the radial bearing.

[0020] While the invention will be described in connection with the preferred embodiments, it will be understood that it is not intended to limit the invention to that embodiment. On the contrary, it is intended to cover all alternatives, modifications, and equivalents, as may be included within the spirit and scope of the invention as defined by the appended claims.

6. Detailed Description of the Disclosure:

[0021] The method and system of the present disclosure will now be described more fully hereinafter with reference to the accompanying drawings in which embodiments are shown. The method and system of the present disclosure may be 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 its scope to those skilled in the art. Like numbers refer to like elements throughout. In an embodiment, usage of the term "about" includes +/- 5% of the cited magnitude. In an embodiment, usage of the term "substantially" includes +/- 5% of the cited magnitude.

[0022] It is to be further understood that the scope of the present disclosure 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 and, although specific terms are employed, they are used in a generic and descriptive sense only and not for the purpose of limitation.

[0023] Referring to Fig. 1, a well has a string of casing 11 cemented within. An electrical submersible pump (ESP) 13 pumps well fluid flowing into casing 11. ESP 13 includes a motor 15, which is typically a three-phase electrical motor. An end of motor 15 connects to a seal section 17 that seals dielectric lubricant in motor 15. Also, seal section 17 may have a pressure equalizing element to equalize the pressure of the lubricant in motor 15 with the hydrostatic pressure of the well fluid on the exterior of motor 15.

[0024] A pump 19 connects to seal section 17. Pump 19 has an intake for receiving well fluid from casing 11 and a discharge connected to a string of production tubing 21. Pump 19 is normally a rotary type, such as a centrifugal pump having a large number of stages, each stage having a rotating impeller and a nonrotating diffuser. Alternately, pump 19 could be another type, such as a progressing cavity pump.

[0025] A power cable 23 with a motor lead on a lower end extends alongside tubing

21 to motor 15 for supplying power. Although ESP 13 is shown vertically in the drawings, it could be located in inclined or horizontal sections of casing 11.

[0026] Referring to Fig. 2, motor 15 has a tubular housing 25 with a longitudinal axis 27. A stator 29 fits nonrotatably in housing 25. Stator 29 is made up of a large number of steel stator disks or laminations 30 stacked on top of each other. Motor windings (not shown) extend through slots in stator disks 30, the windings being connected to power cable 23 (Fig. 1). Stator 29 has a stator bore or passage 31 through which a drive shaft 33 extends. [0027] Shaft 33 supports a rotor made up of a number of rotor sections 35 that cause shaft 33 to rotate when electrical power is supplied to stator 29. Each rotor section 35 has end rings 37, normally copper, on opposite ends. Rotor sections 35 may be about 1 to 2 feet in length and are axially spaced apart from each other a shorter distance. Radial bearings 39 fit between adjacent rotor sections 35. Each radial bearing 39 is in gripping engagement with stator bore 31 to prevent rotation of radial bearing 39.

[0028] Each rotor section 35 has a center tube 41 that is mounted to shaft 33 for rotating shaft 33 in unison. Center tube 41 is a rigid member that may be formed of steel. The wall thickness of each center tube 41 may vary, such as from about 3/16 to ¼ inch.

[0029] Fig. 3 illustrates a portion of one of the rotor sections 35, the others having the same configuration. In this embodiment, a groove 43 extends axially along an inner diameter of center tube 41. A key 44 (Fig. 4) fits within groove 43 and a mating groove in shaft 33 to cause center tube 41 to rotate shaft 33 in unison. During assembly, rotor sections 35 slide over shaft 33 in engagement with key 44. Each rotor section 35 is made up of a stack of thin, steel laminations or disks 45.

[0030] As shown also in Fig. 4, each disk 45 has slots 47 spaced circumferentially apart from each other. Slots 47 are located between an outer diameter 49 of disk 45 and a central opening 51. Slots 47 may be closed such that they do not intersect either outer diameter 49 or central opening 51. Slots 47 of each disk 45 align with each other, and copper rods 52 extend through the aligned slots 47. The shape of slots 47 and rods 52 is shown as trapezoidal but may vary. The ends of rods 52 extend into and are secured to each end ring 37 (Fig. 2), such as by a welding or brazing process. [0031] Each disk central opening 51 is attached to center tube 41 to retain center tube 41 to rotate in unison with disks 45. The attachment between center tube 41 and disks 45 may be rigid, preventing rotational and axial relative movement between disks 45 and center tube 41. For example, in Figs. 3 and 4, each disk inner diameter 51 is initially slightly smaller than the outer diameter of center tube 41, creating an interference fit.

Alternately, disks 45 could be secured to center tube 41 with epoxy or solder. In another alternate, a key and slot arrangement may be used to lock disks 45 to center tube 41 for rotation in unison. For example, each disk 45 would have a tab or key (not shown) protruding radially inward from inner diameter 51 that engages an axially extending groove on the exterior of center tube 41.

[0032] Referring to Figs. 5 and 6, in one embodiment, center tube 41 is longer than the axial dimension of rotor section 35 from the upper side of the upper end ring 37 to the lower side of the lower end ring 37. The ends 53 of each center tube 41 protrude past both end rings 37. As shown in Figs. 2 and 6, the center tube end 53 of one rotor section 35 abuts the center tube end 53 of an adjacent rotor section 35 in this embodiment. Thus, shaft 33 will be completely enclosed by center tubes 41 throughout the entire length of the rotor made up of rotor sections 35. In this embodiment, the inner diameter of end rings 37 is larger than the outer diameter of center tubes 41, creating annular gaps between them.

[0033] Fig. 6 also illustrates an example of radial bearing 39. Many types of radial bearings 39 may be employed. In Fig. 6, radial bearing 39 has a hub 55 that slides over center tubes 41. The upper and lower ends of hub 55 extend the gaps between the inner diameter of end rings 37 and the outer diameter of center tubes 41. Center tube ends 53 may abut approximately midway along the length of hub 55. [0034] At least one anti-rotation ring 57 is located on the outer diameter of hub 55 for frictionally engaging stator bore 31 to prevent rotation of hub 55. Anti-rotation rings 57 may be of various types, such as a ring formed of an elastomer that swells when immersed in the lubricant of motor 15.

[0035] Thrust washers 59 may be positioned between the upper and lower ends of hub 55 and adjacent rotor sections 35. The thrust washer 59 on the upper end of hub 55 engages the lowermost disk 45 of the rotor section 35 next above. The thrust washer 59 on the lower end of hub 55 engages the uppermost rotor disk 45 of the rotor section 35 next below. The axial dimension of hub 55 plus thrust washers 59 determines the axial distance that adjacent rotor sections 35 are apart from each other.

[0036] Fig. 7 illustrates an alternate embodiment, and components that are the same as the first embodiment have the same reference numerals. Each center tube 60 is shorter than the overall length of its rotor section 35, rather than longer as in the first embodiment. Each end 61 of center tube 60 terminates approximately at one end of the stack of rotor disks 45. Each end 61 is thus recessed within the inner diameter of one of the end rings 37.

[0037] A bearing sleeve 63 is located between and in abutment with adjacent center tube ends 61. Bearing sleeve 63 has a length equal to hub 55 plus thrust washers 59. The length of bearing sleeve 63 is much less than the length of center tubes 60. Bearing sleeve 63 has a key and slot arrangement with shat 33 to rotate in unison with shaft 33. The inner diameter of bearing sleeve 63 is in sliding rotational engagement with radial bearing hub 55. The wall thickness of bearing sleeve 63 may be the same as the wall thickness of each center tube 60. [0038] Center tubes 53 or 60 provide more rigidity to rotor sections 35. The additional stiffness allows a smaller annular gap between the outer diameters 49 of rotor sections 35 and the inner wall of stator bore 31 than rotor sections lacking center tubes. Center tubes 53 or 60 control slight radial movement of rotor disks 45 and stabilize rotor imbalance. Center tubes 53 or 60 assist in aligning adjacent rotor sections 35 during assembly.

[0039] In addition to the variations mentioned, adjacent center tubes 41 could be formed with a male/female feature on the ends 53 to facilitate alignment of adjacent rotor sections 35. Further, end portions of center tubes 41 could be threaded to allow end rings 37 to be screwed onto rotor sections 35.

[0040] 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 only a few embodiments of the invention have 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.