WO2015057336A1 - Tunable progressive cavity pump - Google Patents
Tunable progressive cavity pump Download PDFInfo
- Publication number
- WO2015057336A1 WO2015057336A1 PCT/US2014/055812 US2014055812W WO2015057336A1 WO 2015057336 A1 WO2015057336 A1 WO 2015057336A1 US 2014055812 W US2014055812 W US 2014055812W WO 2015057336 A1 WO2015057336 A1 WO 2015057336A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- reservoir
- fluid
- stator
- pump
- pressure
- Prior art date
Links
- 230000000750 progressive effect Effects 0.000 title claims abstract description 34
- 239000012530 fluid Substances 0.000 claims abstract description 142
- 239000012636 effector Substances 0.000 claims abstract description 33
- 230000007423 decrease Effects 0.000 claims abstract description 16
- 230000004044 response Effects 0.000 claims abstract description 14
- 230000005672 electromagnetic field Effects 0.000 claims abstract description 9
- 238000004891 communication Methods 0.000 claims description 8
- 230000003247 decreasing effect Effects 0.000 claims description 8
- 238000005086 pumping Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 claims 5
- 238000004519 manufacturing process Methods 0.000 description 11
- 230000008859 change Effects 0.000 description 10
- 238000005516 engineering process Methods 0.000 description 6
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000007613 environmental effect Effects 0.000 description 4
- 230000008961 swelling Effects 0.000 description 4
- 239000003638 chemical reducing agent Substances 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 239000004215 Carbon black (E152) Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 239000013536 elastomeric material Substances 0.000 description 2
- 230000003628 erosive effect Effects 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 229930195733 hydrocarbon Natural products 0.000 description 2
- 150000002430 hydrocarbons Chemical class 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 239000013078 crystal Substances 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 239000003129 oil well Substances 0.000 description 1
- 230000002040 relaxant effect Effects 0.000 description 1
- 229910001285 shape-memory alloy Inorganic materials 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
- E21B43/121—Lifting well fluids
- E21B43/128—Adaptation of pump systems with down-hole electric drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/008—Pumps for submersible use, i.e. down-hole pumping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
- F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
- F04C2/1075—Construction of the stationary member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/03—Torque
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/20—Flow
Definitions
- This disclosure relates in general to progressive cavity pumps for wells and in particular to a system that changes the inner diameter of the stator in response to changes in operating conditions.
- the pump has a stator with an elastomeric inner portion.
- An axial cavity having an internal helical profile extends through the stator.
- a rotor with an external helical profile fits within the axial cavity.
- a motor causes the rotor to rotate, with the interaction of the helical profile on the rotor and the helical profile in the stator causing fluid to be pumped upward through the cavity.
- the rotation of the rotor also causes the rotor to orbit within the stator.
- the interface between the rotor and axial cavity is sensitive and may change due to various conditions in the well.
- the stator may swell, causing the interference between the rotor and the helical profile of the axial cavity to create excessive friction, increasing the torque and creating a potential to lock or break of the rotor.
- the stator shrinks, the cross-sectional area of the axial cavity increases, reducing the interference between the rotor and the axial cavity. Erosive wear may also increase the cross-sectional area of the axial cavity. If too large, the interface between the rotor and the stator may allow leakage of well fluid, reducing the efficiency of the pump.
- the radial shrinkage or swelling of the stator depends on well fluids and environmental conditions.
- the hydrocarbon content of the well fluid may cause the stator to swell, decreasing the cross-sectional area of the axial cavity while the pump is being lowered into the well. Consequently, manufacturers custom size the interference between the rotor and the axial cavity for a particular well.
- the axial cavity geometry may cause the pump to either become less efficient or cease to function.
- a well pump assembly includes a progressive cavity pump having a stator with an elastomeric inner portion.
- the stator has an axial cavity with an internal helical profile.
- a rotor with an external helical profile is positioned within the axial cavity.
- a motor operatively coupled to the progressive cavity pump rotates the rotor when supplied with power.
- At least one effector is cooperatively associated with the stator to selectively increase and decrease a stiffness of the stator.
- a controller senses operating conditions of the progressive cavity pump assembly and controls the effector in response. The change in stiffness may be caused by the effector increasing and decreasing a cross sectional area of the axial cavity in the stator.
- the effector may comprises a reservoir within the stator separate from the axial cavity and containing a pressure fluid.
- a reservoir pump for selectively increases and decreases a pressure of the pressure fluid in the reservoir.
- the reservoir may be elongated and extend along a length of the stator, separated from the axial cavity.
- the stator may contain a reservoir filled with a magneto-rheological fluid (MR fluid).
- MR fluid magneto-rheological fluid
- a coil generates an electromagnetic field within the MR fluid to selectively increase and decrease a viscosity of the MR fluid.
- the MR fluid reservoir may have two portions axially spaced apart and connected by an orifice. A coil generates an electromagnetic field within the MR fluid at the orifice to selectively increase and decrease a viscosity of the MR fluid.
- the pump assembly may have a plurality of separate effectors spaced along a length of the progressive cavity pump. Each of the effectors is separately controllable for varying a stiffness of the stator along the length of the progressive cavity pump.
- Figures 1 A and IB are a sectioned side view, partially schematic, of a progressive cavity well pump assembly having a stator with tunable features in accordance with this disclosure.
- Figure 2 is an enlarged transverse cross-sectional view of an alternate embodiment of the pump of Figure 1A.
- Figure 3 is an enlarged axial cross-sectional view of the pump of Figure 1 A with the rotor not shown.
- Figure 4 is an axial cross- sectional view of an alternate embodiment of the pump of Figure 3.
- Figure 5 is an enlarged axial cross-sectional view of another alternate embodiment of the pump of Figure 1A.
- Figure 6 is a schematic, perspective exploded view of the pump of Figure 5.
- Figure 7 is a schematic, perspective exploded view of a portion of the effector of the pump of Figure 5.
- a cased well 1 1 has a wellhead assembly or production tree 13 mounted at its upper end.
- Production tree 13 is shown schematically and has a flow line 15 for discharging production fluid from well 1 1.
- a valve 17 opens and closes flow line 15.
- the surface equipment includes a flow meter 19 connected into flow line 15 for measuring the flow rate of the well fluid.
- flow meter 19 could be located in the well.
- An electrical line 21 connects flow meter 19 to a controller 23 located on the surface adjacent production tree 13.
- Production tubing 25 has an upper end supported by a hanger (not shown) in production tree 13 and extends into cased well 1 1.
- Tubing 25 may comprises joints of pipe secured by threads to each other. Alternately, tubing 25 could be continuous coiled tubing deployed from a reel.
- a progressive cavity pump 27 secures to a lower end of tubing 25 to pump well fluid up to production tree 13. Alternately, progressive cavity pump 27 could be deployed through tubing 25.
- Pump 27 has a stator 31 within a cylindrical housing 29, which may be considered to be part of stator 31. Stator 31 is fixed against rotation in housing 29, and at least an inner portion is formed of an incompressible but resilient elastomeric material. Stator 31 has an axial cavity 33 extending its length that is formed with a helical configuration. In Figures 1 A and 3, axial cavity 33 has two helical lobes, creating a sinusoidal appearance, narrowing and widening with inward projecting lobes separated by outward extending valleys. Axial cavity 33 could have more than two helical lobes, such as stator 31 ' in Figure 2, which has an axial cavity 33' with three helical lobes.
- a rotor 35 rotatably extends through stator axial cavity 33.
- Rotor 35 is normally of metal and has an exterior profile 37 that slidingly engages the profile of axial cavity 33.
- Exterior profile 37 has a single helical configuration that is also sinusoidal in appearance. However, when viewed in cross-section, the lobes appear on one side of rotor 35 to be offset from the lobes on the opposite side, presenting a sinuous appearance.
- the transverse cross-sectional appearance of rotor 35 is illustrated by rotor 35' in Figure 2.
- Exterior profile 37 and the profile of axial cavity 33 are well known and conventional. Because of exterior profile 37 and the profile of axial cavity 33, when rotor 35 rotates, it orbits around axis 39 of pump housing 29. As rotor 35 rotates, an interference fit with axial cavity 33 causes rotor 35 to deflect or deform elastomeric stator 31 inward and outward as well fluid is pushed upward into tubing 25.
- a gripping section 40 may be mounted to the upper end of rotor 35 to be engaged by a tool for retrieving rotor 35 from stator 31. Normally, the upper end of rotor 35 extends above stator 31 , and the lower end of rotor 35 extends below stator 3 1.
- the interface between rotor 35 and axial cavity 33 is sensitive and may change due to various conditions in the well.
- Stator 31 may swell, causing the interference between rotor 35 and the profile of axial cavity 33 to create excessive friction, increasing the torque and creating a potential to lock or break of rotor 35.
- stator 31 shrinl-cs
- the cross-sectional area of axial cavity 33 increases, reducing the interference between rotor 35 and axial cavity 33.
- Erosive wear may also increase the cross-sectional area of axial cavity 33. If too large, the interface between rotor 35 and axial cavity 33 may allow leakage of well fluid, reducing the efficiency of pump 27.
- stator 31 The radial shrinkage or swelling of stator 31 depends on well fluids and environmental conditions. For example, the hydrocarbon content of the well fluid may cause stator 31 to swell, decreasing the cross-sectional area of axial cavity 33 while pump 27 is being lowered into the well. Consequently, manufacturers custom size the interference between rotor 35 and axial cavity 33 for a particular well. However, if the environmental conditions change, the axial cavity geometry may cause the pump to either become less efficient or cease to function.
- an effector that selectively increases and decreases the stiffness of elastomeric stator 31 in response to changes in operating conditions.
- a change in stiffness also changes the interference between rotor 35 and axial cavity 33.
- the effector may also reduce the cross-sectional area of the axial cavity, which in effect, changes the stiffness of stator 31.
- an effector chamber or reservoir 41 within pump housing 29 is formed within or outside of stator 31.
- reservoir 41 comprise several separate axially extending cavities, each formed within stator 31 and evenly spaced around axis 39.
- Each reservoir 41 could have an axis parallel with axis 39, or each reservoir could be helical and extend helically around axis 39.
- reservoir 41 could be annular, extending completely around an outer diameter of stator 31.
- Effector reservoir 41 may be elongated, as shown, and could extend all or just part of the length of stator 31.
- a pressure fluid 43 pumped by a reservoir pump or compressor 45 selectively increases and reduces fluid pressure within reservoirs 41.
- Pressure fluid 43 may be incompressible, such as a hydraulic fluid.
- Pressure fluid 43 may alternately be a compressible fluid, such as air.
- Pressure fluid 43 within each reservoir 41 is isolated or blocked from fluid communication with well fluid in axial cavity 33.
- Reservoir pump 45 may be located adjacent to production tree 13 and controller 23 (Fig. 1 A). Controller 23 (Fig. 1A) controls reservoir pump 45 based on torque sensed and the flow rate of well fluid being monitored by flow meter 19. As an alternate to being mounted adjacent to production tree 13, the portion of controller 23 that controls reservoir pump 45 could be mounted to progressive cavity pump 23 within the well. Reservoir pump 45 draws fluid 43 from a tank 47. A valve 48 allows reservoir pump 45 to pump fluid 43 to reservoirs 41 and will hold the pressure when reservoir pump 45 is turned off. When actuated by controller 23, valve 48 allows flow back of fluid 43 to tank 47.
- reservoirs 41 expand and stiffen stator 31. If rotor 35 is not present, as shown in Figure 3, the increase in fluid pressure in reservoirs 41 causes the dimensions of axial cavity 33 to shrinlc, as indicated by the dotted lines 49. The flow area of axial cavity 33 thus shrinks. The difference between the unaltered size of axial cavity 33 and the reduced size shown by the dotted lines may only be 0.20 inches or less, as an example.
- rotor 35 (Fig. 1) will be present, and being metal, it does not change dimensions in response to increasing pressure in reservoirs 41. Thus the interference between rotor 35 and axial cavity 33 increases in response to increasing fluid pressure within reservoirs 41.
- rotor 35 may be driven in various conventional manners.
- a flex shaft 51 couples to a lower end of rotor 35 via a coupling 53 that allows rotor 35 to stab into engagement with flex shaft 51.
- Flex shaft 51 rotates within a connector shaft housing 55 that has a well fluid intake 57 for admitting well fluid to axial cavity 33.
- a concentric coupling 59 connects to and causes the lower end of flex shaft 51 to remain concentric on axis 39.
- the upper end of flex shaft 51 and coupling 53 orbit.
- Flex shaft 51 is typically formed of a steel material.
- a drive shaft 61 has an upper end that connects to concentric coupling 59.
- Drive shaft 61 extends through a seal section 63.
- a gear reducer 65 secures to the lower end of seal section 63 to reduce the rotational speed of drive shaft 61.
- An electrical motor 67 couples to the lower end of gear reducer 65.
- Motor 67 may be a three-phase type that rotates typically around 3600 rpm.
- Motor 67 has a drive shaft (not shown) that couples to gear reducer 65 for rotating drive shaft 61 at a lower rate of speed.
- a dielectric lubricant fills motor 67 and also part of seal section 63. Seal section 63 reduces a pressure differential between well fluid on the exterior and the lubricant within motor 67.
- Seal section 63 may be a conventional type having a communication port that admits well fluid to one side of a bag or bellows, the other side being in contact with the lubricant.
- a power cable 69 connects to motor 67 and extends alongside tubing 25 to the surface where it connects to controller 23.
- a sensing unit 71 may connect to motor 67. Sensing unit 71 senses various parameters such as temperature and well fluid pressure.
- Pump 27 may alternately be driven by a motor located adjacent production tree 13. In that case, a drive rod (not shown) extends from the surface motor to pump 27.
- controller 23 supplies electrical power to motor 67, which causes rotor 35 to rotate, pumping well fluid up tubing 25 to production tree 13. Controller 23 monitors the flow rate with flow meter 19. Controller 23 also monitors the torque required to rotate rotor 35. Torque monitoring can be accomplished various ways. In one example, controller 23 monitors the electrical current supplied via power cable 69 to motor 67. Controller 23 will actuate reservoir pump 45 to increase the pressure of fluid 43 in reservoirs 41 if the flow rate drops below an acceptable level. Controller 23 will stop reservoir pump 45 from increasing the fluid pressure in reservoirs 41, and with valve 48, hold the desired pressure once a desired flow rate is reached. Controller 23 will also control valve 48 to bleed off pressure in reservoirs 41 if the torque monitored is too high.
- stator 35 and stator axial cavity 33 could be sized loosely enough so that once pump 27 has been located in the well, the start up torque will not be excessive. That is, possible swelling of stator 31 could be accounted for in advance by making the dimensions of stator axial cavity 33 sufficiently large so that expected swelling would not cause too much interference between stator 31 and rotor 35.
- reservoir pump 45 would not be operating, and the pressure of fluid 43 in reservoirs 41 would be equal to the hydrostatic pressure of the well fluid in the well.
- controller 23 may increase the stiffness of stator 31 by causing reservoir pump 45 to increase the pressure of fluid 43 in reservoirs 41 , thereby increasing the flow rate of well fluid.
- controller 23 actuates valve 48 to bleed off some of the pressure in reservoirs 41. Controller 23 thus continually tunes pump 27 to operate with a desired stiffness of stator 31. As an alternate to automatic control by controller 23 based on torque and flow rate, the operator could manually adjust the stiffness of stator 31 with manual controls on controller 23 to change the pressure within reservoirs 41.
- progressive cavity pump 27' has more than one stator portion, and three portions are shown by the numerals 31 a, 31b, and 31 c.
- Stator portions 31 a, 31b, 31c are shown stacked coaxially on each other within a single housing 29', however they could have separate housings secured to each other.
- Each stator portion 31 a, 31b, and 31c has one or more reservoirs 41a, 41b and 41c, respectively.
- a separate flow line 74a, 74b and 74c leads from the reservoirs 41 a, 41b and 41c.
- a separate valve 48a, 48b and 48c is located in each flow line 74a, 74b and 74c, respectively.
- a single reservoir pump 45 Fig.
- Controller 23 can control pump 45 and valves 48a, 48b and 48c to provide a different reservoir fluid pressure in each reservoir 41 a, 41b and 41c. Alternately, an operator could manually control valves 48a, 48b and 48c to maintain different pressures in reservoirs 41a, 41b and 41c.
- stator portions 31a, 31b and 31c pump 27' could have more or fewer. Also, rather than separate stator portions, a single stator could have several zones along its length, each zone having a separate reservoir.
- stator sections 73a, 73b are illustrated, but more could be employed.
- Stator sections 73a, 73b are axially aligned along a longitudinal axis 75 and spaced axially apart from each other a short distance.
- each stator section 73a, 73b is of incompressible elastomeric material fixed for non rotation within a steel housing 77. The ends of housings 77 may protrude past the ends of stator sections 73a, 73b and abut each other.
- Each stator section 73a, 73b has an axial cavity 79 for receiving a conventional rotor 80, which is a single-piece member extending through both stator sections 73a, 73b.
- a stator stiffness effector 81 is mounted between opposing ends of stator sections 73a, 73b.
- Effector 81 has a rigid tubular body 83 with one end abutting stator section 73a and the other end abutting stator section 73b.
- Body 83 has an axial bore 85 that is cylindrical and has a diameter large enough so that rotor 80 does not contact it as rotor 80 rotates and orbits.
- Effector body 83 has at least one, and preferably several magneto rheological (MR) passages 87.
- MR magneto rheological
- three MR passages 87 are shown in Figure 7, spaced equally around axis 75.
- Each MR passage 87 has a first or upper section 87a and a second or lower section 87b.
- Each section 87a, 87b joins a central pocket 88 formed in effector body 83.
- effector body 83 has three pockets 88.
- Mating MR fluid reservoirs 89 are formed within stator sections 73a, 73b to register with MR passages 87. Each MR fluid reservoir 89 may have the same diameter as each MR passage 87. Seals (not shown) seal the interface between MR passages 87 and MR fluid reservoirs 89. Each MR fluid reservoir 89 extends parallel to axis 75 a selected distance and has a closed end opposite the end joining MR passages 87. The axial length of each MR fluid reservoir 89 need not be as long as each stator section 73a, 73b, but could be. MR fluid reservoirs 89a are located in stator section 73a and mate with MR passage sections 87a.
- MR fluid reservoirs 89b are located in stator section 73b and mate with MR passage sections 87b.
- An orifice or tube 91 extends through each pocket 88 and connects each MR fluid passage 87a with the corresponding MR fluid passage 87b.
- Orifice tube 91 seals to MR fluid passages 87a, 87b and has a flow area smaller than the flow areas of MR fluid passages 87a, 87b, creating an orifice.
- a magneto rheological (MR) fluid 93 is located in MR reservoirs 89, MR fluid passages 87 and orifice tubes 91.
- MR fluid 93 is a known liquid that will undergo a significant change in viscosity when an electromagnetic field passes through MR fluid 93.
- One or more coils or electromagnets 95 are located within each pocket 88 adjacent to each orifice tube 91 to impose an electromagnetic field on MR fluid 93 contained in orifice tube 91.
- two substantially flat electromagnets 95 are located in each pocket 88, one or each side of orifice tube 91.
- Electromagnets 95 are connected by wires (not shown) to a controller, such as controller 23 (Fig. 1) to selectively supply electrical current.
- Stator sections 73a, 73b may be secured together with effector 81 sandwiched between in various manners. If desired, effectors 81 could also be located at the upper end of stator section 73a and lower end of stator section 73b.
- a collar or clamp 99 is schematically illustrated as enclosing effector 81 and joining stator housings 77. Effector body 83 may have an outer diameter smaller than the inner diameter of housings 77, as illustrated, and fits within the portions of housings 77 that extend beyond stators 73a, 73b. Rather than a collar 99, the abutting ends of housings 77 could be welded to each other or secured in other manners.
- rotation of rotor 80 exerts radial outward forces on each stator section 73a, 73b, causing lobes within axial cavity 79 to deflect radially back and forth.
- the deflection force transmits through stator sections 73a, 73b and acts radially on MR fluid reservoirs 89a, 89b, alternately squeezing and relaxing reservoirs 89a, 89b.
- This alternating force on MR fluid reservoirs 89a, 89b causes a pumping action of MR fluid 93, causing it to flow in an oscillating manner through orifice tubes 91.
- the rotation of rotor 80 pumps well fluid through axial cavity 79 up from stator section 73a.
- controller 23 (Fig. 1A) senses from flow meter 19 that the flow rate of well fluid is too low, it will send a signal to electromagnets 95, which impose an electromagnetic field on MR fluid 93 flowing through orifice tube 91.
- the viscosity of MR fluid 93 within each orifice tube 91 increases as a result, which slows the flow rate between MR fluid reservoirs 89a, 89b.
- the fluid pressure within reservoirs 89a, 89b increases as the helical lobes of rotor 80 exert radial outward forces on stator sections 73a, 73b.
- stator sections 73a, 73b The increased pressure resists the outward deflection of stator sections 73a, 73b, thereby increasing the stiffness of stator sections 73a, 73b.
- the increased stiffness effectively increases the interference between rotor 80 and stator sections 73a, 73b, thereby increasing the flow rate.
- controller 23 If controller 23 senses that the torque to rotate rotor 80 is too high, it will cut off the voltage supplied to electromagnets 95. The viscosity of MR fluid 93 within orifice tubes 91 rapidly drops, lowering the pumping pressure within MR fluid reservoirs 89. The stiffness of stator sections 73, 73b thus decreases to reduce the torque. Rather than automatically controlling the stiffness with controller 23 based on torque and well fluid flow, an operator could manually vary the stiffness with manual controls on controller 23 to supply voltage to electro magnets 95.
- Shape memory gel and shape memory alloys change shapes in response to voltage changes.
- Piezoelectric crystals, voice coils or any other media or elements that alter geometry in response to changing conditions sensed could also be used.
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- Physics & Mathematics (AREA)
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Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2014334885A AU2014334885A1 (en) | 2013-09-16 | 2014-09-16 | Tunable progressive cavity pump |
CA2923430A CA2923430A1 (en) | 2013-09-16 | 2014-09-16 | Tunable progressive cavity pump |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201361878367P | 2013-09-16 | 2013-09-16 | |
US61/878,367 | 2013-09-16 | ||
US14/486,316 | 2014-09-15 | ||
US14/486,316 US20150078943A1 (en) | 2013-09-16 | 2014-09-15 | Tunable Progressive Cavity Pump |
Publications (1)
Publication Number | Publication Date |
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WO2015057336A1 true WO2015057336A1 (en) | 2015-04-23 |
Family
ID=52668133
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/US2014/055812 WO2015057336A1 (en) | 2013-09-16 | 2014-09-16 | Tunable progressive cavity pump |
Country Status (4)
Country | Link |
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US (1) | US20150078943A1 (en) |
AU (1) | AU2014334885A1 (en) |
CA (1) | CA2923430A1 (en) |
WO (1) | WO2015057336A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10450800B2 (en) * | 2011-03-08 | 2019-10-22 | Schlumberger Technology Corporation | Bearing/gearing section for a PDM rotor/stator |
WO2017095466A1 (en) * | 2015-11-30 | 2017-06-08 | Halliburton Energy Services, Inc. | Stiffness tuning and dynamic force balancing rotors of downhole drilling motors |
WO2017131647A1 (en) * | 2016-01-27 | 2017-08-03 | Halliburton Energy Services, Inc. | Rheological fluid lock of shaft to housing |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5145343A (en) * | 1990-05-31 | 1992-09-08 | Mono Pumps Limited | Helical gear pump and stator with constant rubber wall thickness |
US5171138A (en) * | 1990-12-20 | 1992-12-15 | Drilex Systems, Inc. | Composite stator construction for downhole drilling motors |
US5474432A (en) * | 1993-02-22 | 1995-12-12 | Mono Pumps Limited | Progressive cavity pump or motors |
US7878774B2 (en) * | 2007-06-05 | 2011-02-01 | Smith International, Inc. | Moineau stator including a skeletal reinforcement |
US20120156078A1 (en) * | 2010-12-20 | 2012-06-21 | Guidry Jr Michael J | Progressing Cavity Pump/Motor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3119568A1 (en) * | 1981-05-16 | 1982-12-02 | Big Dutchman (International) AG, 8090 Wezep | Eccentric worm screw pump |
FR2794498B1 (en) * | 1999-06-07 | 2001-06-29 | Inst Francais Du Petrole | PROGRESSIVE CAVITY PUMP WITH COMPOSITE STATOR AND MANUFACTURING METHOD THEREOF |
-
2014
- 2014-09-15 US US14/486,316 patent/US20150078943A1/en not_active Abandoned
- 2014-09-16 WO PCT/US2014/055812 patent/WO2015057336A1/en active Application Filing
- 2014-09-16 AU AU2014334885A patent/AU2014334885A1/en not_active Abandoned
- 2014-09-16 CA CA2923430A patent/CA2923430A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5145343A (en) * | 1990-05-31 | 1992-09-08 | Mono Pumps Limited | Helical gear pump and stator with constant rubber wall thickness |
US5171138A (en) * | 1990-12-20 | 1992-12-15 | Drilex Systems, Inc. | Composite stator construction for downhole drilling motors |
US5474432A (en) * | 1993-02-22 | 1995-12-12 | Mono Pumps Limited | Progressive cavity pump or motors |
US7878774B2 (en) * | 2007-06-05 | 2011-02-01 | Smith International, Inc. | Moineau stator including a skeletal reinforcement |
US20120156078A1 (en) * | 2010-12-20 | 2012-06-21 | Guidry Jr Michael J | Progressing Cavity Pump/Motor |
Also Published As
Publication number | Publication date |
---|---|
US20150078943A1 (en) | 2015-03-19 |
CA2923430A1 (en) | 2015-04-23 |
AU2014334885A1 (en) | 2016-03-24 |
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