US20170184089A1 - Rotary Hydraulic Pump with ESP Motor - Google Patents
Rotary Hydraulic Pump with ESP Motor Download PDFInfo
- Publication number
- US20170184089A1 US20170184089A1 US14/983,022 US201514983022A US2017184089A1 US 20170184089 A1 US20170184089 A1 US 20170184089A1 US 201514983022 A US201514983022 A US 201514983022A US 2017184089 A1 US2017184089 A1 US 2017184089A1
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- United States
- Prior art keywords
- pump
- pumping system
- cylinders
- submersible pumping
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000005086 pumping Methods 0.000 claims abstract description 42
- 230000000712 assembly Effects 0.000 claims abstract description 25
- 238000000429 assembly Methods 0.000 claims abstract description 25
- 239000012530 fluid Substances 0.000 claims description 29
- 230000000750 progressive effect Effects 0.000 claims description 3
- 238000011144 upstream manufacturing Methods 0.000 description 18
- 238000004519 manufacturing process Methods 0.000 description 7
- 239000003208 petroleum Substances 0.000 description 4
- 238000007906 compression Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 230000008602 contraction Effects 0.000 description 1
- 239000010779 crude oil Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 229910052500 inorganic mineral Inorganic materials 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000011707 mineral Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 239000003209 petroleum derivative Substances 0.000 description 1
- 230000003134 recirculating effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 210000000707 wrist Anatomy 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
- F04B47/06—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/128—Driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/141—Details or component parts
- F04B1/143—Cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/141—Details or component parts
- F04B1/146—Swash plates; Actuating elements
- F04B1/148—Bearings therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/16—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
- F04B53/144—Adaptation of piston-rods
-
- 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
Definitions
- This invention relates generally to the field of submersible pumping systems, and more particularly, but not by way of limitation, to a rotary hydraulic pump driven by a submersible electric motor.
- Submersible pumping systems are often deployed into wells to recover petroleum fluids from subterranean reservoirs.
- a submersible pumping system includes a number of components, including an electric motor coupled to one or more centrifugal pump assemblies.
- Production tubing is connected to the pump assemblies to deliver the petroleum fluids from the subterranean reservoir to a storage facility on the surface.
- the pump assemblies often employ axially and centrifugally oriented multistage turbomachines.
- the present invention includes a submersible pumping system that has an electric motor and a pump driven by the electric motor.
- the pump includes a rotatable shaft driven by the motor, one or more piston assemblies configured for linear reciprocating motion and means for converting the rotational movement of the shaft to linear reciprocating movement in the piston assemblies.
- inventions of the invention include a pump useable within submersible pumping system.
- the pump includes a cylinder block that includes a plurality of cylinders, a rotatable shaft, a tilt disc assembly and a plurality of piston assemblies.
- the tilt disc assembly includes a drive plate connected to the rotatable shaft and configured for rotation with the shaft and a rocker plate that is not configured for rotation with the shaft.
- Each of the plurality of piston assemblies includes a plunger that is configured for reciprocating linear motion in a corresponding one of the plurality of cylinders and a piston rod connected to the plunger and to the rocker plate.
- embodiments of the invention include a pump useable within a submersible pumping system.
- the pump includes a plurality of manifolds and one or more banks of cylinders. Each of the banks of cylinders corresponds to a separate one of the plurality of manifolds.
- the pump further includes a plurality of cylinders within each of the banks of cylinders and each cylinder is in fluid communication with the corresponding manifold.
- the pump also includes a rotatable camshaft and a plurality of pistons assemblies. Each piston assembly includes a piston and a connecting rod that connects the piston to the camshaft.
- FIG. 1 depicts a submersible pumping system constructed in accordance with an embodiment of the present invention.
- FIG. 2 provides a cross-sectional view of a rotary hydraulic pump of the pumping system of FIG. 1 constructed in accordance with an embodiment.
- FIG. 3 is a view of the downstream side of the cylinder block of the rotary hydraulic pump of FIG. 2 .
- FIG. 4 is a view of the upstream side of the cylinder block of the rotary hydraulic pump of FIG. 2 .
- FIG. 5 is a view of the downstream side of the tilt plate of the rotary hydraulic pump of FIG. 2 .
- FIG. 6 is a view of the downstream side of the drive of the rotary hydraulic pump of FIG. 2 .
- FIG. 7 provides a cross-sectional view of a rotary hydraulic pump constructed in accordance with an alternate embodiment.
- FIG. 8 provides a side cross-sectional view of a rotary hydraulic pump of the pumping system of FIG. 1 constructed in accordance with an alternate embodiment.
- FIG. 9 provides a top cross-sectional depiction of the rotary hydraulic pump of FIG. 8 .
- FIG. 1 shows an elevational view of a pumping system 100 attached to production tubing 102 .
- the pumping system 100 and production tubing 102 are disposed in a wellbore 104 , which is drilled for the production of a fluid such as water or petroleum.
- a fluid such as water or petroleum.
- the term “petroleum” refers broadly to all mineral hydrocarbons, such as crude oil, gas and combinations of oil and gas.
- the production tubing 102 connects the pumping system 100 to a wellhead 106 located on the surface.
- the pumping system 100 includes a pump 108 , a motor 110 , and a seal section 112 .
- the pumping system 100 is primarily designed to pump petroleum products, it will be understood that the present invention can also be used to move other fluids. It will also be understood that, although each of the components of the pumping system are primarily disclosed in a submersible application, some or all of these components can also be used in surface pumping operations.
- upstream and downstream will be understood to refer to the relative positions within the pumping system 100 as defined by the movement of fluid through the pumping system 100 from the wellbore 104 to the wellhead 106 .
- the term “longitudinal” will be understood to mean along the central axis running through the pumping system 100 ; the term “radial” will be understood to mean in directions perpendicular to the longitudinal axis; and the term “rotational” will refer to the position or movement of components rotating about the longitudinal axis.
- the motor 110 is an electric submersible motor that receives power from a surface-based facility through power cable 114 . When electric power is supplied to the motor 110 , the motor converts the electric power into rotational motion that is transferred along a shaft (not shown in FIG. 1 ) to the pump 108 .
- the motor 110 is a three-phase motor that is controlled by a variable speed drive 116 located on the surface. The variable speed drive 116 can selectively control the speed, torque and other operating characteristics of the motor 110 .
- the seal section 112 is positioned above the motor 110 and below the pump 108 .
- the seal section 112 shields the motor 110 from mechanical thrust produced by the pump 108 and isolates the motor 110 from the wellbore fluids in the pump 108 .
- the seal section 112 may also be used to accommodate the expansion and contraction of lubricants within the motor 110 during installation and operation of the pumping system 100 .
- the seal section 112 is incorporated within the motor 110 or within the pump 108 .
- the pump 108 is a rotary hydraulic pump that is driven by the motor 110 .
- the pump 108 translates rotational motion produced by the motor 110 into linearly motion that drives reciprocating pistons within the pump 108 .
- a single pump 108 is depicted in FIG. 1 , it will be appreciated that the pump 108 can be used in combination with additional pumps and motors.
- the pump 108 can be used with other hydraulic rotary pumps, to feed a surface-based sucker rod pump or to feed a centrifugal pump.
- the pump 108 utilizes a tilt-plate to translate the rotational movement of motor 110 into reciprocating linear motion.
- the pump 108 includes an upstream chamber 118 , a downstream chamber 120 and a pump shaft 122 . It will be appreciated, however, that the scope of exemplary embodiments is not limited to two-chamber designs.
- the pump 108 could alternatively include a single chamber or more than two chambers.
- the pump 108 further includes an intake 124 , a discharge 126 and a housing 128 . Each of the internal components within the pump 108 is contained within the housing 128 . Fluid from the wellbore 104 enters the pump 108 through the intake 124 and is carried by the upstream and downstream chambers 118 , 120 to the production tubing 102 through the discharge 126 .
- the pump shaft 122 is connected to the output shaft from the motor 110 (not shown) either directly or through a series of interconnected shafts.
- the pump 108 may include one or more shaft seals that seal the shaft 122 as it passes through the upstream and downstream chambers 118 , 120 .
- Each of the upstream and downstream chambers 118 , 120 includes a cylinder block 130 , one or more piston assemblies 132 and a tilt disc assembly 134 .
- the tilt disc assembly 134 includes a drive plate 136 and a rocker plate 138 .
- FIGS. 5 and 6 illustrate the upstream face of the rocker plate 138 and the upstream face of the drive plate 136 .
- the rocker plate 138 and the drive plate 136 may both be formed as substantially cylindrical members.
- the drive plate 136 is connected to the pump shaft 122 in a non-perpendicular orientation. In this way, rotation of the pump shaft 122 causes an upstream and a downstream edge of the drive plate 136 to rotate around the shaft 122 within the upstream and downstream chambers 118 , 120 at opposite times.
- the drive plate 136 is connected to the pump shaft 122 at a fixed angle. In other embodiments, the angular disposition of the connection between the drive plate 136 and the pump shaft 122 can be adjusted during use.
- the rocker plate 138 is not configured for rotation with the pump shaft 122 and remains rotationally fixed with respect to the cylinder block 130 and housing 128 .
- the upstream face of the rocker plate 138 is in sliding contact with the downstream face of the drive plate 136 .
- the pump 108 includes a bearing between the rocker plate 138 and the drive plate 136 to reduce friction between the two components.
- the rocker plate 138 includes a central bearing 140 and piston rod recesses 142 .
- the central bearing 140 permits the rocker plate 138 to tilt in response to the rotation of the adjacent drive plate 136 .
- the central bearing 140 may include ball bearings, lip seals or other bearings that allow the rocker plate 138 to tilt in a longitudinal manner while remaining rotationally fixed.
- the cylinder block 130 is fixed within the housing 128 .
- the cylinder block 130 includes a plurality of cylinders 144 , intake ports 146 and one-way valves 148 .
- the cylinder block 130 includes six cylinders 144 , six intake ports 146 , six intake way valves 148 and six discharge valves 150 . It will be understood, however, that the cylinder block 130 may include different numbers of cylinders 144 , intake ports 146 and one-way valves 148 .
- the piston assemblies 132 include a piston rod 152 and a plunger 154 .
- the pump 108 includes six piston assemblies 132 . It will be understood, however, that fewer or greater numbers of piston assemblies 132 may also be used.
- a proximal end of each the piston rods 152 is secured within a corresponding one of the piston rod recesses 142 in the rocker plate 138 .
- a distal end of each of the piston rods 152 is attached to the plunger 154 .
- Each plunger 154 resides within a corresponding one of the cylinders 144 .
- the intake ports 146 extend to the upstream side of the cylinder blocks 130 .
- An intake valve 148 within the intake ports 146 allows fluid to enter the intake port 146 from the upstream side of the cylinder block 130 , but prohibits fluid from passing back out of the upstream side of the cylinder block 130 .
- a corresponding discharge valve 150 allows fluid to exit the cylinder 144 , but prohibits fluid from entering the cylinder 144 .
- the intake ports 146 extend through the downstream side of a single cylinder block 130 .
- An intake valve 148 within the intake ports 146 allows fluid to enter the intake port 146 from the downstream side of the cylinder block 130 , but prohibits fluid from passing back out of the intake port 146 .
- a corresponding discharge valve 150 allows fluid to exit the cylinder 144 , but prohibits fluid from entering the cylinder 144 .
- the motor 110 turns the pump shaft 122 , which in turn rotates the drive plate 136 .
- the drive plate 136 rotates, it imparts reciprocating longitudinal motion to the rocker plate 136 .
- the rocker plate 138 undergoes a full cycle of reciprocating, linear motion.
- the linear, reciprocating motion of the rocker plate 138 is transferred to the plungers 154 through the piston rods 152 .
- the piston rods 152 force the plungers 154 to move back and forth within the cylinders 144 .
- FIG. 8 shown therein is a cross-sectional depiction of the pump 108 constructed in accordance with another embodiment.
- the pump 108 uses a central camshaft 158 to drive one or more series of pistons 160 within banks of cylinders 162 .
- the cylinders 162 are connected to manifolds 164 that extend the length of the pump 108 .
- the pump 108 includes 2, 4, 6 or 8 banks of cylinders 162 , manifolds 164 and series of pistons 160 that are equally distributed around the pump 108 , as depicted in the top cross-sectional view of FIG. 9 .
- the camshaft 158 includes a number of radially offset lobes 166 to which connecting rods 168 are secured for rotation.
- the camshaft 158 is connected directly or indirectly to the output shaft from the motor 110 such that operation of the motor 110 causes the camshaft 158 to rotate at the desired speed.
- the pistons 160 , camshaft 158 and connecting rods 168 may include additional features not shown or described that are known in the art, including for example, wrist pins, piston seal rings and piston skirts.
- Each set of pistons 160 and connecting rods 168 can be collectively referred to as a “piston assembly” within the description of this embodiment.
- Each of the manifolds 164 includes an inlet 170 and outlet 172 and one or more check valves 174 .
- the inlets 170 are connected to the pump intake 124 and the outlets 172 are connected to the discharge 126 .
- each manifold 164 includes a separate check valve between adjacent pistons 160 .
- the check valves 174 prevent fluid from moving upstream in a direction from the outlet 172 to the inlet 170 . In this way, the check valves 174 separate the manifolds 164 into separate stages 176 that correlate to each of the pistons 160 and cylinders 162 .
- the camshaft 158 rotates and causes the pistons 160 to move in reciprocating linear motion in accordance with well-known mechanics.
- a temporary reduction in pressure occurs within the portion of the manifold 164 adjacent to the cylinder 162 of the retracting piston 160 .
- the reduction in pressure creates a suction that draws fluid into the stage 176 from the adjacent upstream stage 176 through the intervening check valve 174 .
- the piston 160 moves through the cylinder 162 toward the manifold 164 , thereby reducing the volume of the open portion of the cylinder 162 and stage 176 .
- fluid is discharged to the adjacent downstream stage through the check valve 174 .
- the configuration and timing of the camshaft 158 can be optimized to produce suction-compression cycles within each stage 176 that are partially or totally offset between adjacent stages 176 that provide for the sequential stepped movement of fluid through the manifolds 164 .
- the pistons 160 are configured to extend into the manifold 164 .
- the check valves 174 are omitted and the progression of fluid through the manifold 164 is made possible by holding the pistons 160 in a closed position within the manifold 164 to act as a stop against the reverse movement of fluid toward the inlet 170 .
- the timing of the pistons 160 can be controlled using lobed cams and rocker arms as an alternative to the camshaft 158 and connecting rods 168 . In this way, the pistons 160 produce rolling progressive cavities within the manifolds 164 that push fluid downstream through the pump 108 .
- the pump 108 provides a positive displacement, linearly reciprocating pump that is powered by the rotating shaft of a conventional electric submersible motor 110 .
- the pump 108 will find particular utility in lower volume pumping operations and in wellbores 104 that present fluids with a large gas fraction. Because the pump 108 can be configured to be shorter than conventional multistage centrifugal pumps, the pump 108 is also well-suited for deployment in deviated (non-vertical) wellbores 104 .
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Abstract
Description
- This invention relates generally to the field of submersible pumping systems, and more particularly, but not by way of limitation, to a rotary hydraulic pump driven by a submersible electric motor.
- Submersible pumping systems are often deployed into wells to recover petroleum fluids from subterranean reservoirs. Typically, a submersible pumping system includes a number of components, including an electric motor coupled to one or more centrifugal pump assemblies. Production tubing is connected to the pump assemblies to deliver the petroleum fluids from the subterranean reservoir to a storage facility on the surface. The pump assemblies often employ axially and centrifugally oriented multistage turbomachines.
- In certain applications, however, the volume of fluid available to be produced from the well is insufficient to support the costs associated with conventional electric submersible pumping systems. In the past, alternative lift systems have been used to encourage production from “marginal” wells. Surface-based sucker rod pumps and gas-driven plunger lift systems have been used in low volume wells. Although widely adopted, these solutions may be unacceptable or undesirable for a number of reasons. There is, therefore, a need for an improved submersible pumping system that is well-suited for use in marginal wells.
- In some embodiments, the present invention includes a submersible pumping system that has an electric motor and a pump driven by the electric motor. The pump includes a rotatable shaft driven by the motor, one or more piston assemblies configured for linear reciprocating motion and means for converting the rotational movement of the shaft to linear reciprocating movement in the piston assemblies.
- In another aspect, embodiments of the invention include a pump useable within submersible pumping system. The pump includes a cylinder block that includes a plurality of cylinders, a rotatable shaft, a tilt disc assembly and a plurality of piston assemblies. The tilt disc assembly includes a drive plate connected to the rotatable shaft and configured for rotation with the shaft and a rocker plate that is not configured for rotation with the shaft. Each of the plurality of piston assemblies includes a plunger that is configured for reciprocating linear motion in a corresponding one of the plurality of cylinders and a piston rod connected to the plunger and to the rocker plate.
- In yet another aspect, embodiments of the invention include a pump useable within a submersible pumping system. The pump includes a plurality of manifolds and one or more banks of cylinders. Each of the banks of cylinders corresponds to a separate one of the plurality of manifolds. The pump further includes a plurality of cylinders within each of the banks of cylinders and each cylinder is in fluid communication with the corresponding manifold. The pump also includes a rotatable camshaft and a plurality of pistons assemblies. Each piston assembly includes a piston and a connecting rod that connects the piston to the camshaft.
-
FIG. 1 depicts a submersible pumping system constructed in accordance with an embodiment of the present invention. -
FIG. 2 provides a cross-sectional view of a rotary hydraulic pump of the pumping system ofFIG. 1 constructed in accordance with an embodiment. -
FIG. 3 is a view of the downstream side of the cylinder block of the rotary hydraulic pump ofFIG. 2 . -
FIG. 4 is a view of the upstream side of the cylinder block of the rotary hydraulic pump ofFIG. 2 . -
FIG. 5 is a view of the downstream side of the tilt plate of the rotary hydraulic pump ofFIG. 2 . -
FIG. 6 is a view of the downstream side of the drive of the rotary hydraulic pump ofFIG. 2 . -
FIG. 7 provides a cross-sectional view of a rotary hydraulic pump constructed in accordance with an alternate embodiment. -
FIG. 8 provides a side cross-sectional view of a rotary hydraulic pump of the pumping system ofFIG. 1 constructed in accordance with an alternate embodiment. -
FIG. 9 provides a top cross-sectional depiction of the rotary hydraulic pump ofFIG. 8 . - In accordance with exemplary embodiments of the present invention,
FIG. 1 shows an elevational view of apumping system 100 attached toproduction tubing 102. Thepumping system 100 andproduction tubing 102 are disposed in awellbore 104, which is drilled for the production of a fluid such as water or petroleum. As used herein, the term “petroleum” refers broadly to all mineral hydrocarbons, such as crude oil, gas and combinations of oil and gas. Theproduction tubing 102 connects thepumping system 100 to awellhead 106 located on the surface. - The
pumping system 100 includes apump 108, amotor 110, and aseal section 112. Although thepumping system 100 is primarily designed to pump petroleum products, it will be understood that the present invention can also be used to move other fluids. It will also be understood that, although each of the components of the pumping system are primarily disclosed in a submersible application, some or all of these components can also be used in surface pumping operations. - As used in this disclosure, the terms “upstream” and “downstream” will be understood to refer to the relative positions within the
pumping system 100 as defined by the movement of fluid through thepumping system 100 from thewellbore 104 to thewellhead 106. The term “longitudinal” will be understood to mean along the central axis running through thepumping system 100; the term “radial” will be understood to mean in directions perpendicular to the longitudinal axis; and the term “rotational” will refer to the position or movement of components rotating about the longitudinal axis. - The
motor 110 is an electric submersible motor that receives power from a surface-based facility throughpower cable 114. When electric power is supplied to themotor 110, the motor converts the electric power into rotational motion that is transferred along a shaft (not shown inFIG. 1 ) to thepump 108. In some embodiments, themotor 110 is a three-phase motor that is controlled by avariable speed drive 116 located on the surface. Thevariable speed drive 116 can selectively control the speed, torque and other operating characteristics of themotor 110. - The
seal section 112 is positioned above themotor 110 and below thepump 108. Theseal section 112 shields themotor 110 from mechanical thrust produced by thepump 108 and isolates themotor 110 from the wellbore fluids in thepump 108. Theseal section 112 may also be used to accommodate the expansion and contraction of lubricants within themotor 110 during installation and operation of thepumping system 100. In some embodiments, theseal section 112 is incorporated within themotor 110 or within thepump 108. - Unlike prior art electric submersible pumping systems, the
pump 108 is a rotary hydraulic pump that is driven by themotor 110. Thepump 108 translates rotational motion produced by themotor 110 into linearly motion that drives reciprocating pistons within thepump 108. Although asingle pump 108 is depicted inFIG. 1 , it will be appreciated that thepump 108 can be used in combination with additional pumps and motors. For example, thepump 108 can be used with other hydraulic rotary pumps, to feed a surface-based sucker rod pump or to feed a centrifugal pump. - In the embodiment depicted in
FIG. 2 , thepump 108 utilizes a tilt-plate to translate the rotational movement ofmotor 110 into reciprocating linear motion. In the cross-sectional depiction of thepump 108 inFIG. 2 , thepump 108 includes anupstream chamber 118, adownstream chamber 120 and apump shaft 122. It will be appreciated, however, that the scope of exemplary embodiments is not limited to two-chamber designs. Thepump 108 could alternatively include a single chamber or more than two chambers. - The
pump 108 further includes anintake 124, adischarge 126 and ahousing 128. Each of the internal components within thepump 108 is contained within thehousing 128. Fluid from thewellbore 104 enters thepump 108 through theintake 124 and is carried by the upstream anddownstream chambers production tubing 102 through thedischarge 126. Thepump shaft 122 is connected to the output shaft from the motor 110 (not shown) either directly or through a series of interconnected shafts. Thepump 108 may include one or more shaft seals that seal theshaft 122 as it passes through the upstream anddownstream chambers - Each of the upstream and
downstream chambers cylinder block 130, one ormore piston assemblies 132 and atilt disc assembly 134. Thetilt disc assembly 134 includes adrive plate 136 and arocker plate 138.FIGS. 5 and 6 illustrate the upstream face of therocker plate 138 and the upstream face of thedrive plate 136. Therocker plate 138 and thedrive plate 136 may both be formed as substantially cylindrical members. - Referring back to
FIG. 2 , thedrive plate 136 is connected to thepump shaft 122 in a non-perpendicular orientation. In this way, rotation of thepump shaft 122 causes an upstream and a downstream edge of thedrive plate 136 to rotate around theshaft 122 within the upstream anddownstream chambers drive plate 136 is connected to thepump shaft 122 at a fixed angle. In other embodiments, the angular disposition of the connection between thedrive plate 136 and thepump shaft 122 can be adjusted during use. - The
rocker plate 138 is not configured for rotation with thepump shaft 122 and remains rotationally fixed with respect to thecylinder block 130 andhousing 128. In some embodiments, the upstream face of therocker plate 138 is in sliding contact with the downstream face of thedrive plate 136. In other embodiments, thepump 108 includes a bearing between therocker plate 138 and thedrive plate 136 to reduce friction between the two components. - The
rocker plate 138 includes acentral bearing 140 and piston rod recesses 142. Thecentral bearing 140 permits therocker plate 138 to tilt in response to the rotation of theadjacent drive plate 136. Thus, as thedrive plate 136 rotates with thepump shaft 122, the varying rotational position of the downstream edge of thedrive plate 136 cause therocker plate 138 to tilt in a rolling fashion while remaining radially aligned with thecylinder block 130 andhousing 128. Thecentral bearing 140 may include ball bearings, lip seals or other bearings that allow therocker plate 138 to tilt in a longitudinal manner while remaining rotationally fixed. - Referring now to
FIGS. 2, 3 and 4 , thecylinder block 130 is fixed within thehousing 128. Thecylinder block 130 includes a plurality ofcylinders 144,intake ports 146 and one-way valves 148. In the exemplary embodiment depicted inFIGS. 3 and 4 , thecylinder block 130 includes sixcylinders 144, sixintake ports 146, sixintake way valves 148 and sixdischarge valves 150. It will be understood, however, that thecylinder block 130 may include different numbers ofcylinders 144,intake ports 146 and one-way valves 148. - The
piston assemblies 132 include apiston rod 152 and aplunger 154. In the embodiment depicted inFIG. 3 , thepump 108 includes sixpiston assemblies 132. It will be understood, however, that fewer or greater numbers ofpiston assemblies 132 may also be used. A proximal end of each thepiston rods 152 is secured within a corresponding one of the piston rod recesses 142 in therocker plate 138. A distal end of each of thepiston rods 152 is attached to theplunger 154. Eachplunger 154 resides within a corresponding one of thecylinders 144. - In the embodiment depicted in
FIG. 3 , theintake ports 146 extend to the upstream side of the cylinder blocks 130. Anintake valve 148 within theintake ports 146 allows fluid to enter theintake port 146 from the upstream side of thecylinder block 130, but prohibits fluid from passing back out of the upstream side of thecylinder block 130. Acorresponding discharge valve 150 allows fluid to exit thecylinder 144, but prohibits fluid from entering thecylinder 144. - In an alternate embodiment depicted in
FIG. 7 , theintake ports 146 extend through the downstream side of asingle cylinder block 130. Anintake valve 148 within theintake ports 146 allows fluid to enter theintake port 146 from the downstream side of thecylinder block 130, but prohibits fluid from passing back out of theintake port 146. Acorresponding discharge valve 150 allows fluid to exit thecylinder 144, but prohibits fluid from entering thecylinder 144. In the embodiment depicted inFIG. 7 , it may be desirable to attachdischarge tubes 156 to each of thecylinders 144 to prevent fluid from recirculating through thecylinder block 130. - During operation, the
motor 110 turns thepump shaft 122, which in turn rotates thedrive plate 136. As thedrive plate 136 rotates, it imparts reciprocating longitudinal motion to therocker plate 136. With each complete rotation of thedrive plate 136, therocker plate 138 undergoes a full cycle of reciprocating, linear motion. The linear, reciprocating motion of therocker plate 138 is transferred to theplungers 154 through thepiston rods 152. Thepiston rods 152 force theplungers 154 to move back and forth within thecylinders 144. - As the
plungers 154 move in the upstream direction, fluid is drawn into the cylinders through theintake ports 146 andintake valves 148. As theplungers 154 continue to reciprocate and move in the downstream direction, theintake valves 148 close and fluid is forced out of thecylinders 144 through thedischarge valves 150. In this way, the stroke of thepiston assemblies 132 is controlled by the longitudinal distance between the upstream and downstream edges of therocker plate 138. The rate at which thepiston assemblies 132 reciprocate within thecylinder block 130 is controlled by the rotational speed of themotor 110 andpump shaft 122. - Turning to
FIG. 8 , shown therein is a cross-sectional depiction of thepump 108 constructed in accordance with another embodiment. In the embodiment depicted inFIG. 8 , thepump 108 uses acentral camshaft 158 to drive one or more series ofpistons 160 within banks ofcylinders 162. Thecylinders 162 are connected to manifolds 164 that extend the length of thepump 108. In exemplary embodiments, thepump 108 includes 2, 4, 6 or 8 banks ofcylinders 162,manifolds 164 and series ofpistons 160 that are equally distributed around thepump 108, as depicted in the top cross-sectional view ofFIG. 9 . - The
camshaft 158 includes a number of radially offsetlobes 166 to which connectingrods 168 are secured for rotation. Thecamshaft 158 is connected directly or indirectly to the output shaft from themotor 110 such that operation of themotor 110 causes thecamshaft 158 to rotate at the desired speed. It will be appreciated that thepistons 160,camshaft 158 and connectingrods 168 may include additional features not shown or described that are known in the art, including for example, wrist pins, piston seal rings and piston skirts. Each set ofpistons 160 and connectingrods 168 can be collectively referred to as a “piston assembly” within the description of this embodiment. - Each of the
manifolds 164 includes aninlet 170 andoutlet 172 and one ormore check valves 174. Theinlets 170 are connected to thepump intake 124 and theoutlets 172 are connected to thedischarge 126. In the embodiment depicted inFIG. 8 , each manifold 164 includes a separate check valve betweenadjacent pistons 160. Thecheck valves 174 prevent fluid from moving upstream in a direction from theoutlet 172 to theinlet 170. In this way, thecheck valves 174 separate themanifolds 164 intoseparate stages 176 that correlate to each of thepistons 160 andcylinders 162. - During operation, the
camshaft 158 rotates and causes thepistons 160 to move in reciprocating linear motion in accordance with well-known mechanics. As apiston 160 retracts from the manifold 164, a temporary reduction in pressure occurs within the portion of the manifold 164 adjacent to thecylinder 162 of theretracting piston 160. The reduction in pressure creates a suction that draws fluid into thestage 176 from the adjacentupstream stage 176 through the interveningcheck valve 174. - During a compression stroke, the
piston 160 moves through thecylinder 162 toward the manifold 164, thereby reducing the volume of the open portion of thecylinder 162 andstage 176. As the pressure increases within thestage 176 adjacent thepiston 160 in a compression stroke, fluid is discharged to the adjacent downstream stage through thecheck valve 174. The configuration and timing of thecamshaft 158 can be optimized to produce suction-compression cycles within eachstage 176 that are partially or totally offset betweenadjacent stages 176 that provide for the sequential stepped movement of fluid through themanifolds 164. - In an alternate embodiment, the
pistons 160 are configured to extend into themanifold 164. In another embodiment, thecheck valves 174 are omitted and the progression of fluid through the manifold 164 is made possible by holding thepistons 160 in a closed position within the manifold 164 to act as a stop against the reverse movement of fluid toward theinlet 170. The timing of thepistons 160 can be controlled using lobed cams and rocker arms as an alternative to thecamshaft 158 and connectingrods 168. In this way, thepistons 160 produce rolling progressive cavities within themanifolds 164 that push fluid downstream through thepump 108. - Thus, in each of the embodiments disclosed herein, the
pump 108 provides a positive displacement, linearly reciprocating pump that is powered by the rotating shaft of a conventional electricsubmersible motor 110. Thepump 108 will find particular utility in lower volume pumping operations and inwellbores 104 that present fluids with a large gas fraction. Because thepump 108 can be configured to be shorter than conventional multistage centrifugal pumps, thepump 108 is also well-suited for deployment in deviated (non-vertical)wellbores 104. - It is to be understood that even though numerous characteristics and advantages of various embodiments of the present invention have been set forth in the foregoing description, together with details of the structure and functions of various embodiments of the invention, this disclosure is illustrative only, and changes may be made in detail, especially in matters of structure and arrangement of parts within the principles of the present invention to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed. It will be appreciated by those skilled in the art that the teachings of the present invention can be applied to other systems without departing from the scope and spirit of the present invention.
Claims (20)
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/983,022 US20170184089A1 (en) | 2015-12-29 | 2015-12-29 | Rotary Hydraulic Pump with ESP Motor |
CA3009540A CA3009540A1 (en) | 2015-12-29 | 2016-12-27 | Rotary hydraulic pump with esp motor |
BR112018012780A BR112018012780A2 (en) | 2015-12-29 | 2016-12-27 | submersible pumping system and pumps |
PCT/US2016/068729 WO2017117141A1 (en) | 2015-12-29 | 2016-12-27 | Rotary hydraulic pump with esp motor |
EP16826621.1A EP3397864A1 (en) | 2015-12-29 | 2016-12-27 | Rotary hydraulic pump with esp motor |
CN201680077306.4A CN108700059A (en) | 2015-12-29 | 2016-12-27 | Rotary type hydraulic pump with ESP motors |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/983,022 US20170184089A1 (en) | 2015-12-29 | 2015-12-29 | Rotary Hydraulic Pump with ESP Motor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20170184089A1 true US20170184089A1 (en) | 2017-06-29 |
Family
ID=57799896
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/983,022 Abandoned US20170184089A1 (en) | 2015-12-29 | 2015-12-29 | Rotary Hydraulic Pump with ESP Motor |
Country Status (6)
Country | Link |
---|---|
US (1) | US20170184089A1 (en) |
EP (1) | EP3397864A1 (en) |
CN (1) | CN108700059A (en) |
BR (1) | BR112018012780A2 (en) |
CA (1) | CA3009540A1 (en) |
WO (1) | WO2017117141A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170370357A1 (en) * | 2016-06-22 | 2017-12-28 | Faurecia Automotive Seating, Llc | Pneumatic pump |
US11118582B2 (en) | 2015-12-29 | 2021-09-14 | Baker Hughes Esp, Inc. | Linear hydraulic pump for submersible applications |
WO2023007193A1 (en) * | 2021-07-30 | 2023-02-02 | Kingdom Innovative Technologies Ltd | Borehole water pump |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11466548B2 (en) | 2020-06-05 | 2022-10-11 | Saudi Arabian Oil Company | Downhole linear pump system |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11118582B2 (en) | 2015-12-29 | 2021-09-14 | Baker Hughes Esp, Inc. | Linear hydraulic pump for submersible applications |
US20170370357A1 (en) * | 2016-06-22 | 2017-12-28 | Faurecia Automotive Seating, Llc | Pneumatic pump |
US10648464B2 (en) * | 2016-06-22 | 2020-05-12 | Faurecia Automotive Seating, Llc | Pneumatic pump |
WO2023007193A1 (en) * | 2021-07-30 | 2023-02-02 | Kingdom Innovative Technologies Ltd | Borehole water pump |
Also Published As
Publication number | Publication date |
---|---|
BR112018012780A2 (en) | 2018-12-04 |
EP3397864A1 (en) | 2018-11-07 |
CA3009540A1 (en) | 2017-07-06 |
CN108700059A (en) | 2018-10-23 |
WO2017117141A1 (en) | 2017-07-06 |
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