ADJUSTABLE VANE DIFFUSER INSERT FOR ELECTRICAL SUBMERSIBLE PUMP

Abstract

A pump having an insert between an impeller and diffuser, where the insert includes an annulus that is in communication with fluid flow passages in the impeller and diffuser. The passages and annulus define a fluid flow path through the pump. Vanes are provided in the annulus that can pivot and vary the cross sectional area of the fluid flow path. Regulating the fluid flow path area alters the flow rate where the pump operates at its maximum efficiency. Thus by monitoring flow through the pump, the vanes can be adjusted so the flow rate of maximum efficiency corresponds to the actual flow rate.

Description

BACKGROUND

1. Field of Invention

The present disclosure involves a device and method for dynamically regulating operating characteristics of a pump and increasing a range of optimal operating parameters. More specifically, the present disclosure relates to adjustable vanes upstream of a pump diffuser that respond to varying flow conditions allowing the pump to optimally operate at the varying conditions.

2. Description of Prior Art

Submersible pumping systems are often used in hydrocarbon producing wells for pumping fluids from within the wellbore to the surface. These fluids are generally liquids and Include produced liquid hydrocarbon as well as water. One type of system used employs an electrical submersible pump (ESP). ESPs are typically disposed at the end of a length of production tubing and have an electrically powered motor. Often, electrical power may be supplied to the pump motor via a cable. The pumping unit is usually disposed within the well bore just above where perforations are made into a hydrocarbon producing zone.

Centrifugal submersible pumps typically employ a stack of rotatable impellers and stationary diffusers, where the impellers and diffusers alternate in the stack and are arranged coaxial with one another. Passages provided through both the impellers and diffusers define a flow path through which fluid is forced while being pressurized in the pump. Maximum pump efficiency generally occurs at a particular flow rate or along a range of flow rates, where the range is typically significantly less than the operating range of flow rates. Pumps are usually designed to operate at or close to a maximum efficiency. However, fluid flow rates through a pump may change, such as due to depletion of fluids in a reservoir, so that over time a pump may not be operating at its maximum efficiency.

SUMMARY OF INVENTION

The present disclosure describes example embodiments of a pump that is adjustable to operate at a best efficiency at varying rates of fluid flow. In an example embodiment the pump includes art impeller and a diffuser that is generally coaxial with the impeller. Passages are included in the impeller and the diffuser, where the passages define at least a portion of a flow path. Between the impeller and diffuser is an insert that has an annulus in fluid communication with the passages and is intersected by the flow path. Vanes are included that mount in the annulus, the vanes are adjustably positioned within the annulus, so that when a position of the vanes is adjusted, an area of the flow path in the annulus is varied. Optionally, the vanes are elongate members that pivot about a line substantially transverse to the annulus. In an alternate embodiment, the vanes are elongate members that pivot about a line substantially aligned with travel of the annulus. A motor may optionally be coupled with the vanes that is used for adjustably positioning the vanes. The insert can further include an annular hub, where the hub has an inner radius circumscribing an outer radius of a portion of the impeller, and an outer radius that defines an inner radial-surface of the annulus. The insert may also include a shroud having an inner radius that defines an outer radial surface of the annulus and having a lower end in contact with an upper end of a lower diffuser and an upper end in contact with a lower end of an upper diffuser. In an example, adjusting the area of the flow path in the annulus changes a flow rate at which the pump operates at a maximum efficiency. Optionally, the passages are spaced apart from one another at angular locations around an axis of the pump; the spaced apart passages can define multiple flow paths through the pump, that are also spaced apart at angular locations around the axis of the pump. In this example an adjustable vane is provided in each of the flow paths.

Also included herein is method of pumping fluid. In an example embodiment the method includes providing a pump having an impeller, a diffuser coaxial to and adjacent the impeller, and passages in the impeller and the diffuser that are in fluid communication. The method includes rotating the impeller to urge fluid through the passages and along a flow path in the pump. The pump can be operated at a maximum efficiency by adjusting an area of the flow path in a space between the impeller and the diffuser. In one example, adjusting the area of the flow path includes providing adjustable vanes in the flow path between the impeller and the diffuser, and pivoting the vanes. Alternatively, the flow rate of fluid through the pump can be monitored, and the area of the flow path can be reduced when the flow rate decreases. In an optional embodiment, the flow rate of fluid through the pump is monitored and increased when the flow rate increases. The impeller and diffuser can each have multiple passages to define multiple flow paths. In this alternate embodiment, the area of each flow path in the space between the impeller and the diffuser can be adjusted to operate the pump at its maximum efficiency.

The present disclosure also includes a pumping system. In one example embodiment the pumping system includes an electrical submersible pump (ESP) that is made up of an impeller and a diffuser that are coaxial and adjacent one another. Passages are included-that are formed axially through the impeller aid diffuser and an insert is set between the impeller and diffuses. The insert has an annular space that is in fluid communication with the passages. The annular space and passages define a flow path through the ESP. Also included with this embodiment is a vane in the annular space, where the vane is selectively pivotable into orientations to define a restriction in the flow path. The system further includes production tubing attached to the ESP. The system can optionally further include a motor operatively coupled to the vanes for orienting the vanes. In an example, adjusting the vanes regulates flow through the ESP and varies a value of a flow rate of maximum efficiency of the pump. Adjusting the vanes can regulate flow through the ESP and may vary a range of operating flow rates of the pump. In an example embodiment, the insert further includes an annular hub with an inner radius that circumscribes an outer radius of a portion of the impeller. The hub also has an outer radius that defines an inner radial surface of the annul us. A shroud is included with this embodiment that has an inner radius defining an outer radial surface of the annulus. The shroud has a lower end in contact with an upper end of a lower diffuser and an upper end in contact with a lower end of an upper diffuser. The passages of this example are spaced apart from one another at angular locations around an axis of the pump to define multiple Sow paths through the pump spaced apart at angular locations around the axis of the pump and wherein an adjustable vane is provided in each of the flow paths.

BRIEF DESCRIPTION OF DRAWINGS

Some of the features and benefits of the present invention having been stated, others will become apparent as the description proceeds when taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a side partial sectional view of a prior art submersible pumping system disposed in a wellbore.

FIG. 1 is a side sectional view of a portion of a pump in accordance with the present disclosure,

FIGS. 2A-2C are perspective side partial sectional views of a pump insert with adjustable vanes at varying pitch angles in accordance with the present disclosure,

FIG. 3 is a plot of pump head and pump efficiency curves.

FIG. 4 is a sectional plan view of a portion of an alternate embodiment of a pump insert coupled with a motor.

FIG. 5 is a partial sectional view of an example of a pumping system having the pump of FIG. 1 in accordance with the present disclosure.

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.

DETAILED DESCRIPTION OF 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,

An example embodiment of a portion of a pump 30 in accordance with the present disclosure is shown in a side sectional view in FIG. 1. The portion of the pump 30 is shown having a lower diffuser 32₁ and upper diffuser 32₂ separated by an impeller 34. A passage 36₁ is shown formed through the body of the lower impeller 32₁ that follows a path curves generally upwards through the lower diffuser 32₁ while extending radially inwards towards an axis A_x of the pump 30. The passage 361 has an upper end that is in fluid communication with a corresponding passage 38 formed within the impeller 34. Passage 38 also follows a curved path upward within the impeller 34; but instead of extending radially inward like passage 36₁, passage 38 projects radially outward with distance away from the lower diffuser 32₁. As is known, operating the pump urges fluid (not shown) upward through passage 36₁ and into passage 38. Rotating the impeller 34 discharges fluid from the passage 38 where it enters passage 36₂; shown formed through the upper diffuser 32₂ and mirroring the path of the passage 36₁ in the lower diffuser 32₁.

the example of FIG. 1 though, a disk like insert 40 is provided between the impeller 38 and upper diffuser 32₂ that selectively adjusts a cross sectional area of the flow path that courses through the pump 30. More specifically, the insert 40 is shown having an outer annular shroud 42 whose outer surface has a radius that is substantially the same as a radius of the outer surfaces of the upper and lower diffusers 32₁, 32₂. The insert 40 is shown further including an annular hub 44 with an outer radius spaced radially inward from an inner radius of the shroud 42. Further in the example of FIG. 1, the axial height of the hub 44 is less than the axial height of the shroud 42. Shroud 42 has a lower end that contacts an upper end of the lower diffuser 32₁ that is roughly the same axial distance along the pump 30 as where the passage 38 exits the impeller 34. The upper end of the shroud 42 extends into contact with a lower end of the upper diffuser 32₂. In contrast, the hub 44 has a lower end that is spaced upward from or axially past, and. radially inward from, where the passage 38 exits the impeller 34. The radial spacing between the shroud 42 and hub 44 defines an annulus 46 between these two members. A first portion of the annulus 46 is in fluid communication with passage 38; and a second portion of the annulus 46, distal from the first portion, is also in fluid communication with passage 36₂. The fluid being pressurized by the pump 30 follows a flow path defined by interconnectivity of the passages 36₁, 36₂, 38 and annulus 46. Fluid exiting the passage 38 flows through the annulus 46 and upward into the passage 36₂; A seal (not shown) may be included between the hub 44 and upper end of the impeller 34 to prevent fluid exiting the passage 38 then making its way to the inner circumference of the hub 44.

A vane 48 is shown set within the annulus 46 that in one example is a generally elongate member selectively positioned into different orientations within the annulus 46. The pump 30 is shown inserted within a tubular 49, where the tubular 49 can be a wellbore tubular and the pump 30 can be an electrical submersible pump. Optionally, the tubular 49 can be a transfer line, such as a caisson, for transmitting fluid to another location. Additional details of the vane 48 are illustrated in the side partial sectional views of FIGS. 3A through 3C.

Referring now to FIG. 2A, a series of vanes 48₁-48₄ are shown pivotingly attached to an outer radial surface of the hub 44. While a total of four vanes are shown in FIGS. 3A through 3C, for the purposes of discussion herein additional vanes may be included within the annulus 46 and spaced at various angular locations along the circumference of the annulus 46. In an example embodiment, the vanes 48₁-48₄ are pivotingly attached by pins 50 shown extending through the body of the vanes 48₁-48₄ and into the hub 44. As such, and as shown in the example sequence of FIGS. 3A through. 3C, the vanes 48₁-48₄ can be adjusted to pivot about pin 50 at an angle with respect to the axis A_x thereby affecting the sectional area of the flow path through the pump 30; and thus the flow rate of fluid across the insert 40. For the purposes of illustration in FIGS. 3A through 3C a flow path portion 52 is shown extending through the annulus 46 that schematically represents a flow channel for fluid passing from the impeller 38 (FIG. 1) below the insert 40, across the insert 40 through the annulus 46, and to the diffuser 32₂ above the insert 40. In the example of FIGS. 3A through 3C, adjacent vanes define boundaries of the flow path portion 52 at spaced apart angles with respect to the axis A_x. Alternate example embodiments exist wherein the vane flow path portion 52 may include one or more vanes in the space of the flow path portion 52.

In FIG. 2A the vanes 48₁-48₄ are pivoted at an angle θ₁. In this configuration the vane 48₂ reduces the available area through the flow path, portion 52 by restricting passage exit 54₁ at the upper end of the flow path portion 52. Pivoting vane 48₃ extends it into the flow path portion 52; where the amount of restriction is defined by an inlet restriction 56₁. In contrast, in one example when vanes 48₁-48₄ are substantially aligned with axis A_x, passage exit 54₁ has a cross sectional area substantially the same as that of the inlet to the passage 36₂, and the inlet to the flow path portion 52 has a cross sectional area substantially the same as that of the exit of the passage 36.

The depiction in FIG. 2B illustrates operation where the vanes 48₁-48₄ have been adjusted to tilt at an angle θ₂ with respect to the axis A_x, wherein angle θ₂ is greater than angle θ₁. As such, the passage exit 54₂ at the upper end of the flow path portion 52 is reduced in FIG. 2B over that of the passage exit 54₁ of FIG. 2A. Similarl, the inlet restriction 56₂ shown on the lower end of the flow path portion 51 aid defined by the intersection of the vane 48₃ into the flow path portion 52 is increased in size over that of the inlet restriction 56₁ from FIG. 2A. It necessarily follows that fluid flow across the insert 40 of FIG. 2B is less than fluid flow across the insert 40 of FIG. 3A. FIG. 2C illustrates another variation wherein the vanes 48₁-48₄ are tilted at an angle θ₃ with respect to the axis Ax wherein angle θ₃ exceeds angle θ₂. This example provides an illustration of yet further restriction of the flow of fluid through the flow path portion 52. Thus, the passage exit 54₃ in FIG. 2C is smaller than passage exit 54₂ in FIG. 2B and inlet restriction 563 of FIG. 2C is greater than inlet restriction 56₂ of FIG. 28.

Pump efficiency can he affected by the cress sectional area of the flow path, including the cross sectional area of the pardon of the flow path between the impeller and diffuser. As such, selectively regulating the area of the flow path through the pump 30, such as within the area between an impeller and diffuser, can allow for operating adjustments so the pump can operate at a maximum efficiency. Referring now to FIG. 3, a plot is provided that contains curves for pump efficiency and pump head, which in an example are representative of an ESP. A series of pump efficiency curves 58₁, 58₂, 58₃ are shown that in one example embodiment illustrate pump head performance realized by adjusting the vanes 48₁-48₄ as illustrated in FIG. 3. For example, as pump efficiency curve 58₁ is shown having a maximum efficiency at a .flow rate greater than pump efficiency curves 58₂ or 58₃, pump efficiency curve 58₁ correlates to the configuration of FIG. 3, i.e. the configuration providing the most flow. Similarly, pump efficiency curve 58₂ correlates to the configuration of FIG. 2B, and pump efficiency curve 58₃ correlates to the configuration of FIG. 2C.

The pump head curves 60₁, 60₂, 60₃, also correlate to the cross sectional area of the flow path portion 52 and how it is controlled by selective positioning of the vanes 48₁-48₄. As shown, pump head curve 60₁ generally yields an increased pump head with increased Sow rate and thus can be shown to correspond to the configuration of the pump in FIG. 2A. In descending order, the pump head curves 60₂, 60₃ also correspond to the configuration of the pumps in FIG. 2B and FIG. 2C respectively. As such, by monitoring the flow and flow rate of the fluid through the pump 30 the vanes can be adjusted to affect the flow rate of fluid through the flow path portion 52, thereby regulating flow and flow rate through the pump 30, and providing the ability to operate the pump 38 at a maximum efficiency,

Further identified in the plot of FIG. 3 are maximum efficiency points 62₁, 62₂, 62₃ that illustrate where on the pump efficiency curves 58₁, 58₂, 58₃ the maximum efficiency of the pump is realized and at which corresponding flow rate. As discussed above, regulating and/or controlling flow and flow rate of pumped fluid that flows from an impeller to an adjacent diffuser, provides an ability to operate the pomp at a maximum efficiency irrespective of the particular flow through the pump. In one example of operation, the flow and flow rate through, the pump is monitored and if the current configuration of the pump has a best operating efficiency at a flow rate different from the monitored flow rate, the vanes can be adjusted while pumping to be at maximum efficiency at or close to the actual flow rate. Fluid flow monitoring can occur at an entrance to the pump or at a terminal point where fluid exits the pump or production tubing.

A plan sectional view of an example embodiment of an insert 40 is shown in FIG. 4 and depicting an example means for pivoting the vanes 48_i. A circular drive ring 64 is shown that may engage gears (not shown) disposed on the pins 50 that mount in each of the vanes 48_i. The ring 64 may be powered by a motor 66 and coupled to the motor 66 via a drive shaft 68. Motor 66 may he disposed within the insert 40, or cavities (not shown) may be formed inside an adjacent diffuser 32 (FIG. 1) for housing the motor 66. Optionally, pin 50A may extend longitudinally through the vanes 48_i so that the vanes 48_i can he pivoted about their elongate axis.

With reference now to FIG. 5, shown in a partial sectional view is an example of an ESP system 70 disposed in a well bore 71 tor pumping fluids from the wellbore 71. The ESP system 70 is made up of a motor 72, a seal section 74, and pump 76. Where the pump 76 is substantially the same as pump 30 of FIG. 1. Production tubing 78 on the discharge end of the pump 76 provides a conduit tor delivering the fluid pressurized by the pump 30 to a wellhead assembly 79 on surface above the wellbore 71. Seal section 74 reduces a pressure differential between wellbore fluid and lubricant in motor 72. Energizing the motor 72 drives a shaft (not shown) coupled between the motor 72 and the pump 76. The source of the fluid drawn into the pump comprises perforations 80 formed through a casing 81 that lines the wellbore 70. The fluid is represented by arrows extending from the perforations 80 to an inlet 82 on the pump 76. The perforations 80 extend into a surrounding hydrocarbon producing formation 84. Thus the fluid flows from the formation 84, past the motor 72 on its way to the inlet 82.

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. For example, pump 30, 76 is not limited to a single insert 40 therein, but instead can optionally include inserts 40 strategically positioned therein, an insert 40 between each adjacent diffuser 32 and impeller 34, or an insert 40 between a discharge of an impeller 34 and inlet to a diffuser 32. 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.

Claims

1. A submersible pump comprising: an impeller;a diffuser generally coaxial with the impeller;passages in the impeller and diffuser that define a flow path; andan insert between the impeller and diffuser comprising, an annulus in fluid communication with the passages and that is intersected by the flow path, and vanes mounted in the annulus that are adjustably positioned within the annulus, so that when a position of the vanes is adjusted, an area of the flow path in the annulus is varied.

2. The pump of claim 1, wherein the vanes are elongate members that pivot about a line substantially transverse to the annulus.

3. The pump of claim 1, wherein the vanes are elongate members that pivot about a line substantially aligned with travel of the annulus.

4. The pump of claim 1, further comprising a motor coupled with the vanes and for adjustably positioning the vanes.

5. The pump of claim 1, wherein the insert further comprises an annular hub having an inner radius that circumscribes an outer radius of a portion of the impeller and an outer radius that defines an inner radial surface of the annulus.

6. The pump of claim 5, wherein the insert further comprises a shroud having an inner radius that defines an outer radial surface of the annulus and having a lower end in contact with an upper end of a lower diffuser and an upper end in contact with a lower end of an upper diffuser.

7. The pump of claim 1, wherein adjusting the area of the flow path in the annulus changes a flow rate at which the pump operates at a maximum efficiency.

8. The pump of claim 1, wherein the passages are spaced apart from one another at angular locations around an axis of the pump to define multiple flow paths through the pump spaced apart at angular locations around the axis of the pump and wherein an adjustable vane is provided in each of the flow paths.

9. A method of pumping fluid comprising: providing a pump having an impeller, a diffuser coaxial to and adjacent the impeller, passages in the impeller and the diffuser that are in fluid communication;rotating the impeller to urge fluid through the passages and along a flow path in the pump; andadjusting an area of the flow path in a space between the impeller and the diffuser so that the pump operates at a maximum efficiency.

10. The method of claim 8, wherein the step of adjusting an area of the flow path comprises providing adjustable vanes in the flow path between the impeller and the diffuser and pivoting the vanes.

11. The method of claim 8, further comprising monitoring the flow rate of fluid through the pump and reducing the area of the flow path when the flow rate decreases.

12. The method of claim 8, further comprising monitoring the flow rate of fluid through the pump and increasing the area of the flow path when the flow rate increases.

13. The method of claim 8, wherein the impeller and diffuser each have multiple passages thereby defining multiple flow paths, the method further comprising adjusting an area of each flow path in the space between the impeller and the diffuser so that the pump operates at a maximum efficiency.

14. A pumping system comprising: an electrical submersible pump (ESP) comprising: an impeller,a diffuser mounted coaxial to and adjacent the impeller,passages formed axially through the impeller and diffuser,an insert between the impeller and diffuser comprising an annular space in fluid communication with the passages that define a flow path through the ESP, anda vane in the annular space and selectively pivotable into orientations to define a restriction in the flow path;production tubing having an end attached to the ESP.

15. The system of claim 14, further comprising a motor operatively coupled to the vanes for orienting the vanes.

16. The system of claim 14, wherein adjusting the vanes regulates flow through the ESP and varies a value of a flow rate of maximum efficiency of the pump.

17. The system of claim 14, wherein adjusting the vanes regulates flow through the ESP and varies a range of operating flow rates of the pump.

18. The system of claim 14, wherein the insert further comprises an annular hub having an inner radius that circumscribes an outer radius of a portion of the impeller and an outer radius that defines an inner radial surface of the annulus, wherein the insert further comprises a shroud having an inner radius that defines an outer radial surface of the annulus and having a lower end in contact with an upper end of a lower diffuser and an upper end in contact with a lower end of an upper diffuser, and wherein the passages are spaced apart from one another at angular locations around an axis of the pump to define multiple flow paths through the pump spaced apart at angular locations around the axis of the pump and wherein an adjustable vane is provided in each of the flow paths.